JP2008126710A - Transmission mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a transmission mechanism capable of suppressing an increase of a size in a direction along the rotation axis of an electric motor. <P>SOLUTION: In this transmission mechanism, the electric motor MG2 for outputting power from an output shaft 17 by being energized to a coil 19 and a planetary roller mechanism 25 connected to the output shaft 17 so that power may be transmitted are provided, the planetary roller mechanism 25 has three differentially rotatable rotation elements, and the output shaft 17 and the three rotation elements are rotatably arranged with the same rotation axis A1 as a center. The planetary roller mechanism 25 is arranged inside the coil 19 in the radial direction with the rotation axis A1 as the center. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a speed change mechanism in which power of an electric motor is transmitted to a planetary roller mechanism.

  Conventionally, a transmission mechanism that uses an electric motor as a power source in a vehicle, an industrial machine, a machine tool, etc., and transmits the torque of the electric motor to a planetary roller mechanism to perform a shift is known, and an example of the transmission mechanism Is described in Patent Document 1.

  The motor speed reducer described in Patent Document 1 includes an electric motor, a first stage speed reducer connected in series to the electric motor, and a second stage speed reducer connected in series to the first stage speed reducer. Equipped with a reducer. The first stage speed reducer is a friction roller type speed reducer utilizing a wedge action, and the friction roller type speed reducer has a low speed side shaft, a high speed side shaft, a guide roller, and a movable roller. The low-speed shaft is rotatably supported by a housing that houses the electric motor, and an outer ring is provided at one end of the low-speed shaft. Further, the high speed side shaft is provided eccentrically with respect to the outer ring and the low speed side shaft. This high speed side shaft is connected to the rotor of the electric motor. Further, the guide roller is in contact with the high speed side shaft and the outer ring. Further, the movable roller is configured to be able to move between the high speed side shaft and the outer ring in a direction to bite into the wedge. On the other hand, the second stage speed reducer is a planetary gear speed reducer. This planetary gear reducer has a sun gear and a ring gear, and a pinion roller shaft for holding a pinion gear meshing with the sun gear and the ring gear, and the pinion roller shaft is fixed to the housing by a carrier. Further, the sun gear is splined to the low speed side shaft. Note that a speed change mechanism in which a transmission is connected to an output shaft of an electric motor is also described in Patent Documents 2 to 6.

JP 2005-30490 A JP-A-11-82265 JP 2002-106661 A JP 2002-31203 A JP-A-6-92154 JP-A-9-226392

  However, in the speed change mechanism described in Patent Document 1, the high speed side shaft and the low speed side shaft are arranged side by side in the axial direction, and a wedge roller transmission is provided on the outer peripheral side of the high speed side shaft. Since the planetary gear speed reducer is provided on the outer peripheral side of the low speed side shaft, the structure may be increased in the axial direction of the high speed side shaft.

  The present invention has been made against the background of the above circumstances, and an object thereof is to provide a speed change mechanism capable of suppressing an increase in size in a direction along a rotation axis of an electric motor.

  In order to achieve the above object, an invention according to claim 1 is provided with an electric motor that is energized in a coil and outputs power from an output shaft, and a planetary roller mechanism that is connected to the output shaft so as to be able to transmit power. The planetary roller mechanism has three rotation elements capable of differential rotation, and the speed change mechanism in which the output shaft and the three rotation elements are arranged to be rotatable about the same rotation axis. The planetary roller mechanism is arranged inside the coil in a radial direction centered on the rotation axis.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect, a transmission connected to the planetary roller mechanism so as to be capable of transmitting power is provided, and the planetary roller mechanism, the transmission, and the electric motor are configured. The parts to be integrated are integrated with each other.

  The invention of claim 3 is characterized in that, in addition to the configuration of claim 1 or 2, a load transmission mechanism for transmitting a load applied to the output shaft to any of the three rotating elements is provided. It is.

  According to a fourth aspect of the present invention, in addition to the configuration of the third aspect, the three rotating elements include a sun roller and a ring roller arranged coaxially, and a carrier that holds a pinion roller that contacts the sun roller and the ring roller. The load transmission mechanism is a thrust bearing that transmits a thrust load applied to the output shaft to the sun roller.

  According to a fifth aspect of the present invention, in addition to the configuration of the first or second aspect, the three rotating elements hold a sun roller and a ring roller arranged coaxially and a pinion roller that contacts the sun roller and the ring roller. And a radial bearing for receiving a radial load applied to the carrier.

  According to a sixth aspect of the invention, in addition to the configuration of the fifth aspect, the output shaft has a cylindrical portion disposed on a circumference centered on the rotation axis, and the rotation axis is the center. The radial bearing is arranged inside the cylindrical portion in the radial direction.

  According to a seventh aspect of the present invention, there is provided an electric motor that energizes the coil and outputs power from an output shaft, and a first transmission that is coupled to the output shaft so as to be capable of transmitting power, the output shaft and the In the transmission mechanism in which the rotational elements of the first transmission are arranged on the same rotational axis, a second transmission is provided in addition to the first transmission, and the locations differ in the direction along the rotational axis. One end and the other end of the coil are arranged, the first transmission is arranged inside the one end of the coil in a radial direction centered on the rotation axis, and the rotation axis The second transmission is arranged inside the other end portion of the coil in a radial direction centered at the center.

  According to an eighth aspect of the invention, in addition to the configuration of the seventh aspect, the output element of the first transmission and the input element of the second transmission are connected so as to be able to transmit power. Is.

  According to a ninth aspect of the present invention, in addition to the configuration of any of the second to sixth aspects, a power distribution device having an input element, a reaction force element, and an output element capable of differential rotation is provided. A power source is connected to the input element, a motor / generator is connected to the reaction force element of the power distribution device, and the output element of the transmission and the output element of the power distribution device are driven members. The power source, the electric motor, the motor / generator, the planetary roller mechanism, and the rotating elements constituting the transmission rotate about the rotation axis. The arrangement is possible.

  The invention of claim 10 is provided with a power distribution device having an input element, a reaction force element, and an output element capable of differential rotation, in addition to the configuration of claim 7 or 8, and the input element of the power distribution device And a motor / generator is connected to a reaction force element of the power distribution device, and an output element of the second transmission and an output element of the power distribution device are connected to the driven member. The power source, the electric motor, the motor / generator, and the rotating elements constituting the first transmission and the second transmission are connected to the rotational axis. It is characterized by being arranged so as to be rotatable about the center.

  According to the first aspect of the present invention, power is transmitted by traction transmission between the three rotating elements constituting the planetary roller mechanism. In addition, a planetary roller mechanism is disposed inside the coil in the radial direction centered on the rotation axis. That is, in the direction along the rotation axis, the space (region / space) in which the coil is disposed overlaps the space (region / space) in which the planetary roller mechanism is disposed. Therefore, an occupied space for arranging the planetary roller mechanism can be reduced, and the transmission mechanism can be downsized.

  According to the invention of claim 2, in addition to obtaining the same effect as that of the invention of claim 1, the power output from the planetary roller mechanism can be transmitted to the transmission. The planetary roller mechanism, the transmission, and the components constituting the electric motor are integrated. Therefore, it becomes easier to further reduce the size in the rotation axis direction.

  According to the invention of claim 3, in addition to obtaining the same effect as that of the invention of claim 1 or 2, the load applied to the output shaft is received by any one of the three rotating elements, so that the electric motor is supported. It is not necessary to provide a bearing alone, and further downsizing can be promoted.

  According to the invention of claim 4, in addition to the same effects as those of the invention of claim 3, a thrust load applied to the output shaft is transmitted to the sun roller via a thrust bearing. Since the sun roller is disposed on the innermost circumferential side in the rotation axis direction, the radius of the thrust bearing can be reduced in the radial direction around the rotation axis.

  According to the invention of claim 5, in addition to obtaining the same effect as that of the invention of claim 1 or 2, a radial load applied to the carrier is received by the radial bearing. Therefore, when the carrier rotates at high speed, it is possible to suppress a decrease in contact pressure between the sun roller and the pinion roller.

  According to the sixth aspect of the invention, in addition to obtaining the same effect as that of the fifth aspect of the invention, the radial bearing is disposed inside the cylindrical portion in the radial direction centering on the rotation axis. Therefore, the distance between the cylindrical portion and the carrier can be shortened in the radial direction of the rotation axis, and the vibration amount (blur amount) of the carrier in the radial direction of the rotation axis can be reduced.

  According to the invention of claim 7, in the direction along the rotation axis, a space (region / space) in which the coil is disposed, and a space (region / space) in which the first transmission and the second transmission are disposed. Overlap. Therefore, the occupied space in which the first transmission and the second transmission are arranged can be narrowed, and the transmission mechanism can be downsized.

  According to the eighth aspect of the invention, in addition to the same effects as the seventh aspect of the invention, the power of the electric motor is transmitted to the second transmission via the first transmission.

  According to the ninth aspect of the present invention, in addition to obtaining the same effect as any of the second to sixth aspects, the torque of the power source is transmitted to the input element of the power distribution device, and the reaction force is generated by the motor / generator. In addition, the speed ratio between the input element and the output element of the power distribution device can be continuously controlled by controlling the rotational speed of the motor / generator. The power of the power source and the power of the electric motor can be transmitted to the wheels via the power distribution device.

  According to the invention of claim 10, in addition to the same effect as that of the invention of claim 7 or 8, the torque of the power source is transmitted to the input element of the power distribution device, and the reaction force is received by the motor / generator. By controlling the rotational speed of the motor / generator, the gear ratio between the input element and the output element of the power distribution device can be controlled steplessly. The power of the power source and the power of the electric motor can be transmitted to the wheels via the power distribution device.

  The speed change mechanism in the present invention can be used for vehicles, industrial machines, transport machines, and the like. Vehicles include passenger cars, transport vehicles, trucks, buses, and the like. In addition to a vehicle equipped with a single power source, the vehicle includes a hybrid vehicle having a plurality of types of power sources having different power generation principles. In the present invention, the electric motor, the power source, and the motor / generator are devices that output the power transmitted to the driven member. When the speed change mechanism is used in a vehicle, the power of the electric motor and the power source is configured to be transmitted to the wheels, and the speed change mechanism is disposed in a path from the electric motor to the wheels. When the speed change mechanism of the present invention is used in a vehicle or a transport machine, the driven member includes wheels. In addition, a power transmission device disposed in a power transmission path from the speed change mechanism to the wheels, for example, a transmission, a differential, a gear, a chain, a pulley, a belt, a sprocket, and the like are also included in the driven member. When the speed change mechanism of the present invention is used in an industrial machine, for example, a machine tool, a tool, a cutter, or a chuck that holds a workpiece is a driven member. The electric motor is a device that converts electric energy into kinetic energy. As the electric motor, a motor / generator having both a power running function for converting electrical energy into kinetic energy and a regeneration function for converting kinetic energy into electrical energy can be used.

  Further, in the present invention, the electric motor has a configuration in which the output shaft performs a rotational motion. Further, the electric motor may be either a direct current motor or an alternating current motor. Examples of the alternating current motor include an induction motor, a synchronous motor, and a commutator motor. The electric motor of the present invention is configured such that the output shaft rotates by energization of the coil. On the other hand, examples of the power source include an engine, a flywheel system, and a hydraulic motor. The engine is a power device that converts thermal energy into kinetic energy, and examples thereof include an internal combustion engine. An internal combustion engine is a device that generates heat energy by burning fuel, and examples thereof include a gasoline engine, a diesel engine, and an LPG engine. The hydraulic motor is a power device that converts energy (pressure / flow rate) of fluid (pressure oil) into mechanical energy (torque / rotation speed). A flywheel system is a power unit that stores and releases kinetic energy. In the present invention, the first output member, the second input member, and the rotating element are all members that are involved in torque transmission, and examples thereof include parts such as a gear, a roller, a connecting drum, a carrier, a pulley, and a rotating shaft. .

  In the present invention, the rotational elements of the power source, the electric motor, and the motor / generator can be disposed so as to be rotatable about the same rotational axis. Further, in the present invention, “on the same axis” means to be arranged so as to be rotatable about the same rotation axis. Furthermore, in the present invention, the direction along the rotation axis is a direction including the rotation axis or a direction parallel to the rotation axis. Furthermore, in this invention, when the arrangement | positioning area | region of the components in a rotating shaft direction overlaps, at least one part should just overlap. That is, it may be all or a part. The planetary roller mechanism according to the present invention has three elements that can be differentially rotated, and any one of the elements functions as an input element, and any of the elements functions as a reaction force element. The element functions as an output element. By such differential action of the three rotating elements, the rotational speed of the input element and the rotational speed of the output element can be made different, and the planetary roller mechanism has a function as a transmission.

  Furthermore, the present invention can be provided with another transmission in addition to the planetary roller mechanism. This “another transmission” includes a planetary roller mechanism, a gear transmission mechanism, and the like. That is, either a transmission that transmits power by traction transmission or a transmission that transmits power by the meshing force of a gear. In the present invention, the planetary roller mechanism and “another transmission” are transmissions that can vary the rotational speed of the input element and the rotational speed of the output element. The ratio of the number of rotations, that is, a transmission capable of changing the transmission ratio, or a transmission having a fixed transmission ratio may be used. When the planetary roller mechanism is a transmission with a fixed gear ratio, the gear ratio may be a value larger than “1” or a value smaller than “1”. A transmission having a gear ratio larger than “1” is a reduction gear, and a transmission having a gear ratio smaller than “1” is a speed increaser.

  Next, a specific example of the speed change mechanism will be specifically described with reference to the drawings. FIG. 2 is a skeleton diagram showing a configuration example of the power train of the vehicle 1. The vehicle 1 shown in FIG. 2 is a hybrid vehicle of the F / F (front engine / front drive; front wheel drive in front of the engine) type. In the vehicle 1 shown in FIG. 2, an engine 2, a motor / generator MG1, and a motor / generator MG2 which are a kind of internal combustion engine are mounted as power sources. This power source is a power device that outputs power transmitted to the wheels. The engine 2 is a power unit that burns fuel and converts its thermal energy into kinetic energy. The engine 2 is a known one having an intake / exhaust device, a fuel injection device, and the like. For example, an engine output, that is, an engine rotation is controlled by controlling an opening of an electronic throttle valve, a fuel injection amount, a fuel injection timing, and the like. The number and engine torque can be controlled. Motor generators MG1 and MG2 are rotating devices having both a power running function for converting electrical energy into kinetic energy and a regeneration function for converting kinetic energy into electrical energy.

  A power distribution device 3 is provided in which the engine 2 and the motor / generators MG1, MG2 are coupled so as to be able to transmit power. The motor / generators MG1 and MG2 and the power distribution device 3 are disposed inside the casing K1. The casing K1 is made of a metal material such as aluminum or an aluminum alloy. The power distribution device 3 is a device that distributes the power of the engine 2 to the motor / generator MG1 and wheels, and the power distribution device 3 includes a single-pinion planetary gear mechanism. More specifically, the power distribution device 3 includes a sun gear 4, a ring gear 5 that is arranged coaxially with the sun gear 4 and that surrounds the sun gear 4, and the sun gear 4 and the ring gear. 5 and a carrier 7 that supports the pinion gear 6 so as to be capable of rotating and revolving. Thus, the three rotating elements, that is, the sun gear 4, the ring gear 5, and the carrier 7 are configured so as to be differentially rotatable with respect to each other. The sun gear 4, the ring gear 5 and the carrier 6 are all constituted by helical gears.

  Further, a connection structure of the engine 2 and the motor / generator MG1 to the rotating element of the power distribution device 3 will be described. First, the carrier 7 and a crankshaft (not shown) of the engine 2 are connected so as to be able to transmit power. Specifically, the engine 2 and the carrier 7 are connected by an input shaft 8. A clutch mechanism may be provided in the power transmission path from the engine 2 to the input shaft 8. The clutch mechanism includes a friction clutch, an electromagnetic clutch, a fluid clutch, and the like. When a friction clutch or an electromagnetic clutch is used as the clutch mechanism, a damper mechanism can be used in combination. On the other hand, the motor generator MG1 has a stator 9 and a rotor 10, and the stator 9 is fixed to the casing K1. The rotor 10 and the sun gear 4 are connected so that power can be transmitted. 1 and 2, the rotor 10 and the sun gear 4 are coupled so as to rotate integrally.

  The main part of FIG. 2 is shown in FIG. FIG. 1 is a half sectional view in a direction along the rotation axis A1 of the input shaft 8, in other words, in a direction parallel to the rotation axis A1. The rotor 10 has a cylindrical portion 11 disposed on a circumference centered on the rotation axis A <b> 1, and the cylindrical portion 11 is disposed on the outer peripheral side of the input shaft 8. On the other hand, a partition wall 12 extending in the radial direction around the rotation axis is provided on the inner periphery of the casing K1, and the cylindrical portion is supported by a radial bearing 13 attached to the inner periphery of the partition wall 12. 11 is rotatably supported.

  Next, the configuration of the motor / generator MG2 will be described. An end cover 14 is attached to the casing K1 at a position farthest from the engine 2, and the motor / generator MG2 is disposed between a partition wall 15 provided in the casing K1 and the end cover 14. ing. The motor / generator MG2 includes a stator 16 and a rotor 17. First, the stator 16 will be described. The stator 16 includes a plurality of laminated electromagnetic steel plates 18 and a coil 19 wound around the laminated electromagnetic steel plates 18. The electromagnetic steel plate 18 is fastened and fixed to the casing K1 using bolts 20. The electromagnetic steel plates 18 are laminated in a direction along the rotation axis A1.

  On the other hand, the rotor 17 is attached to the hollow shaft 21 disposed around the rotation axis A1, the cylindrical portion 22 formed continuously on the outer peripheral side of the hollow shaft 21, and the outer periphery of the cylindrical portion 22. It has an electromagnetic steel plate 23. The rotor 17 is disposed on the inner peripheral side of the stator 16 in the radial direction centered on the rotation axis A1. Further, in the direction along the rotation axis A1 or in the direction parallel to the rotation axis A1 (rotation axis direction), the arrangement (occupation) length (arrangement area, arrangement range) of the electromagnetic steel plate 23 and the cylindrical portion 22 is The length of the inner ends 19A of the coils 19 in the direction of the rotation axis is equal to or less than the length. Further, the rotor 17 of the motor / generator MG 2 is rotatably supported by a radial bearing 24, and the outer ring of the radial bearing 24 is held by the end cover 14.

  Two sets of transmissions are arranged in series on the power transmission path from the rotor 17 of the motor / generator MG2 to the power distribution device 3. First, the transmission disposed upstream in the direction of power transmission from the motor / generator MG2 to the power distribution device 3 will be described. As this transmission, a planetary roller mechanism 25 is provided. The planetary roller mechanism 25 includes a sun roller 26 and a ring roller 27 that are arranged on the same axis, and a carrier 29 that supports a pinion roller 28 that contacts the sun roller 26 and the ring roller 27 so as to be able to rotate and revolve. The ring roller 27 is disposed outside the sun roller 26. The sun roller 26, the ring roller 27, and the pinion roller 28 are all made of a metal material. The sun roller 26 has a cylindrical shape integrated with the hollow shaft 21. Further, the ring roller 27 is disposed outside the sun roller 26, and the pinion roller 28 is disposed between the sun roller 26 and the ring roller 27. In this planetary roller mechanism 25, the ring roller 27 functions as a reaction force element, and the rotation speed of the carrier 29 as an output element is lower than the rotation speed of the sun roller 26 as an input element. The radius ratio of the roller is configured. That is, the planetary roller mechanism 25 functions as a speed reducer that is fixed so that the gear ratio is greater than “1”. One end of the carrier 29 in the direction of the rotation axis is supported by a radial bearing 30. The radial bearing 30 is attached to the inner periphery of the cylindrical portion 22.

  Further, the other end of the carrier 29 in the axial direction is supported by another radial bearing 31. The radial bearing 31 is attached to the partition wall 15. Thus, the radial bearings 30 and 31 are arranged on both sides of the pinion roller 28 in the rotational axis direction. Further, the ring roller 27 is fastened and fixed to the partition wall 15 with bolts 32. The planetary roller mechanism 25 configured as described above is arranged inside the coil 19 in the radial direction centering on the rotation axis A1. Specifically, most of the planetary roller mechanism 25 is disposed inside one end portion (coil end portion) 19B of the coil 19 in the direction along the line axis A1. When the planetary roller mechanism 25 is attached, the ring roller 27 is elastically deformed outward and then disposed around the pinion roller 28. Therefore, the diameter is reduced by the elastic restoring force of the ring roller 27, and the outer peripheral surface of the pinion roller 28 is pressed against the inner peripheral surface of the ring roller 27 and the outer peripheral surface of the sun roller 26. Then, traction oil is interposed in a portion where the pinion roller 28 contacts the ring roller 27 and the sun roller 26.

  Further, a single pinion type planetary gear mechanism 33 is provided between the motor / generator MG1 and the planetary roller mechanism 25 in a direction along the rotation axis A1. That is, a planetary gear mechanism 33, which is another transmission, is provided downstream of the planetary roller mechanism 25 in the power transmission path from the motor / generator MG2 to the power distribution device 3. The planetary gear mechanism 33 is meshed with the sun gear 34, the ring gear 35 disposed coaxially with the sun gear 34, and disposed so as to surround the sun gear 34, and the sun gear 34 and the ring gear 35. It has a pinion gear 36 and a carrier 37 that supports the pinion gear 36 so that it can rotate and revolve. Thus, the three rotating elements, that is, the sun gear 34, the ring gear 35, and the carrier 37 are configured to be differentially rotatable with respect to each other. The carrier 37 is fixed to the partition wall 15. In the planetary gear mechanism 33, the gear ratio of each gear is configured so that the rotational speed of the ring gear 35 as the output element is lower than the rotational speed of the sun gear 34 as the input element. That is, the planetary gear mechanism 33 functions as a speed reducer. Further, the sun gear 34 is integrally formed with a single component (metal material) so as to rotate integrally with the carrier 29. A connecting drum 38 is provided in which the ring gears 5 and 35 are formed on the inner peripheral side. The connecting drum 38 has a cylindrical shape centered on the rotation axis A1. An inner ring of the radial bearing 40 is attached to the outer peripheral side of the connecting drum 38. Two radial bearings 40 are provided at different positions in the direction along the rotation axis A1, and the outer ring of the radial bearing 40 is attached to the casing K1. One radial bearing 40 is disposed outside the power distribution device 3, and the other radial bearing 40 is disposed outside the planetary gear mechanism 33.

  On the other hand, an oil pump drive shaft 41 is provided coaxially with the input shaft 8, and the input shaft 8 and the oil pump drive shaft 41 are connected so as to rotate integrally. An oil pump cover 42 is attached to the side surface of the end cover 14, and an oil pump 43 is provided between the end cover 14 and the oil pump cover 42. The rotor of the oil pump 43 is driven to rotate by an oil pump drive shaft 41. The sun gear 34 and the rotor 17 are attached to the outer periphery of the oil pump drive shaft 41. Further, the hollow shaft 21 of the rotor 17 and the sun gear 34 are arranged at different positions in the direction along the rotational axis A1. The sun gear 34 is provided on the outer periphery of the cylindrical member 50, and a thrust bearing 44 is disposed between portions of the cylindrical member 50 and the hollow shaft 21 that are disposed on substantially the same circumference. Yes. That is, a thrust bearing 44 is disposed between the hollow shaft 21 and the cylindrical member 50 in a direction along the rotational axis A1.

  As described above, in the vehicle 1 shown in FIG. 2, the power distribution device 3 is arranged between the engine 2 and the motor / generator MG2 in the direction along the rotation axis A1. The motor / generator MG 1 is disposed between the power distribution device 3 and the engine 2. Further, a planetary gear mechanism 33 is disposed between the power distribution device 3 and the motor / generator MG2. The engine 2, the motor / generators MG1, MG2, the power distribution device 3, the planetary gear mechanism 33, and the planetary roller mechanism 25 are all arranged coaxially. Further, a gear transmission is provided in the power transmission path from the connecting drum 38 to the wheel (front wheel) 45. More specifically, a counter drive gear 46 is formed on the outer periphery of the connecting drum 38, and a counter shaft 47 parallel to the input shaft 8 is provided. A counter driven gear 48 is formed on the counter shaft 47, and the counter drive gear 46 and the counter driven gear 48 are engaged with each other. Further, a final reduction gear 49 is provided between the counter shaft 47 and the wheel 45.

  On the other hand, a power supply device (not shown) for supplying power to the motor generators MG1 and MG2 is provided. As this power supply device, a secondary battery, that is, a battery or a capacitor can be used, and the secondary battery can be charged with electric power generated by the motor generators MG1 and MG2. Furthermore, a fuel cell can be used as the power supply device. Next, a vehicle control system will be described. An electronic control device (not shown) as a controller is provided. This electronic control device includes detection signals from various sensors and switches, for example, acceleration requests, braking, etc. While the request, the engine speed, the motor generators MG1, MG2, and the like are input, the electronic control device outputs a signal for controlling the engine 2, a signal for controlling the motor generators MG1, MG2, and the like. The

  In the vehicle 1 shown in FIG. 2, the engine 2 is operated, the engine torque is input to the carrier 7 of the power distribution device 3, and the motor / generator MG1 performs control that takes charge of the reaction force of the engine torque. The motor / generator MG1 is regeneratively controlled by forward rotation or powering controlled by reverse rotation to take charge of engine torque. In the power distribution device 3, when the rotational speed of the motor / generator MG 1 responsible for the reaction force of the engine torque is controlled, the engine rotational speed and the output element are controlled by the differential action of the sun gear 4, the ring gear 5 and the carrier 7. It is possible to control the ratio with respect to the rotational speed of the ring gear 5, that is, the gear ratio in a stepless (continuous) manner. Thus, the power distribution device 3 functions as an electric continuously variable transmission capable of changing the gear ratio by electrical control. Then, the torque transmitted to the connecting drum 38 is transmitted to the wheel 45 via the counter shaft 47 and the final reduction gear 49 to generate a driving force.

  On the other hand, it is also possible to drive the motor / generator MG2 as an electric motor and transmit the torque to the wheels 45 when the engine 2 is operating or when the engine 2 is stopped. When the torque of the motor / generator MG2 is transmitted to the planetary roller mechanism 25, the traction oil pressurized by each roller is converted into glass, and power is transmitted according to the principle of traction transmission. Specifically, when the torque of the motor / generator MG2 is transmitted to the sun roller 26, the ring roller 27 becomes a reaction force element, and the carrier 29 becomes an output element. At this time, the rotation speed of the carrier 29 is lower than the rotation speed of the sun roller 26. That is, the planetary roller mechanism 25 functions as a speed reducer, and the transmission torque is amplified. The reduction ratio in the planetary roller mechanism 25 is constant (fixed).

  The torque transmitted to the carrier 29 is transmitted to a sun gear 34 that is an input element of the planetary gear mechanism 33. Then, the carrier 37 of the planetary gear mechanism 33 becomes a reaction force element, and torque is output from the ring gear 35. The planetary gear mechanism 33 is configured such that the rotational speed of the ring gear 35 is lower than the rotational speed of the sun gear 34. That is, the planetary gear mechanism 33 functions as a speed reducer, and its reduction ratio is constant. The motor / generator MG1 is rotated in the reverse direction when generating the torque for moving the vehicle 1 forward, and the motor / generator MG2 is rotated in the forward direction when generating the torque for moving the vehicle 1 backward. Is done. The forward rotation is the same rotational direction as the rotational direction of the engine 2, and the reverse rotation is a rotational direction opposite to the rotational direction of the engine 2. Further, when the vehicle 1 is moved backward, the engine 2 is stopped, and the motor / generator MG1 rotates forward (idle) with no load. As described above, the vehicle 1 is a hybrid vehicle capable of transmitting the power of the engine 2 or the motor / generator MG2 to the wheels 45.

  1 and FIG. 2, the planetary roller mechanism 25 is disposed in a dead space inside the end portion of the coil 19 in the radial direction centered on the rotational axis A1. Yes. That is, in the direction along the rotation axis A1, the space in which the coil 19 is arranged and the space in which the planetary roller mechanism 25 is arranged overlap. For this reason, the occupied space in which the planetary roller mechanism 25 is arranged can be narrowed in the direction along the rotation axis A1, and the transmission mechanism can be downsized. Further, the sun roller 26 of the planetary roller mechanism 25 and the rotor 17 of the motor / generator MG2 are integrated, and the sun gear 34 of the planetary gear mechanism 33 and the carrier 29 are integrated. Here, the term “integrated” means that it is integrally formed by a single component. Therefore, the reduction ratio of the motor / generator MG2 can be increased without increasing the length of the speed change mechanism in the direction along the rotation axis A1.

  Further, when a load that presses the rotor 17 rightward in FIG. 1 is generated, the load is transmitted to the carrier 29 via the thrust bearing 44, and the load is received by the casing K1. That is, the thrust bearing 44 has a function of positioning the rotor 17 and the sun roller 26 in a direction along the rotation axis A1 and a function of receiving a thrust load. Further, since the thrust bearing 44 is provided at a position close to the rotational axis A1 in the radial direction, the outer diameter of the thrust bearing 44 can be made as small as possible. For this reason, it is not necessary to provide a bearing for supporting the rotor 17 of the motor / generator MG2, and the size reduction of the speed change mechanism can be further promoted. The thrust bearing 44 is used for reducing the frictional force when the rotor 17 and the sun gear 34 are in contact with each other because a thrust load is not substantially applied to the rotor 17.

  Further, a radial load applied to the carrier 29 is received by the radial bearings 30 and 31. Accordingly, when the carrier 29 rotates at a high speed, a decrease in contact pressure between the sun roller 26 and the pinion roller 28 can be suppressed. Further, even when a centrifugal force acts on the carrier 29, the load is received by the rotor 17 having a highly rigid shape. Furthermore, the rotor 17 has a cylindrical portion 22 disposed on a circumference centered on the rotational axis A1, and is located inside the cylindrical portion 22 in a radial direction centered on the rotational axis A1. The radial bearing 30 is disposed. Therefore, the axial distance between the sun roller 26 and the pinion roller 28 can be shortened in the radial direction of the rotation axis A1, and the vibration amount (blur amount) in the radial direction of the sun roller 26 can be reduced. .

  Further, in the configuration examples of FIGS. 1 and 2, the planetary roller mechanism 25 is used as a speed reducer that amplifies the torque of the motor / generator MG2, and power transmission is not performed by meshing force but by traction transmission. Therefore, drive loss can be reduced, axial thrust force is not generated, and meshing vibration and noise are not generated. In particular, when a high rotation motor is used as the motor generator MG2, power loss in the high rotation region can be suppressed, and there is no concern about gear noise. Further, since the radial bearing 30 is attached to the inner periphery of the cylindrical portion 22 of the rotor 17, it is not necessary to change the inner diameter of the cylindrical portion 22. Further, the radial bearings 24 and 30 that support the rotor 17 can be reduced in the number of parts because the radial bearing 24 on one side is attached to the casing K1 and the radial bearing 30 on one side is attached to the planetary roller mechanism 25. Moreover, since the number of bearings can be reduced, an increase in power loss in the rolling part and sliding part of the bearing can be suppressed. Further, in the configuration example of FIGS. 1 and 2, the planetary roller mechanism 25 can perform the first-stage deceleration, and the planetary gear mechanism 33 can perform the second-stage deceleration. That is, when transmitting the torque of the motor / generator MG2 to the sun gear 34, two-stage deceleration can be performed, and the torque amplification function is further improved.

  Further, the rotor 17 and the sun roller 34 are integrally formed, and the carrier 29 of the planetary roller mechanism 25 is attached to the rotor 17 via a radial bearing 30. For this reason, in the assembly process of the speed change mechanism, the motor / generator MG2 and the planetary roller mechanism 25 may be unitized (assembled) before the motor / generator MG2 and the planetary roller mechanism 25 are arranged in the casing K1. Is possible. Therefore, the assembling property with respect to the casing K1 is improved. The radial bearings 30 and 31 may be either ball bearings or needle bearings. 1 and 2 show a two-wheel drive vehicle having a power train configured to transmit the torque of the engine 2 and the motor / generator MG2 to the front wheels. The present invention is also applicable to a two-wheel drive vehicle having a power train configured to transmit the torque of the generator MG2 to the rear wheels. Furthermore, the present invention is also applicable to a four-wheel drive vehicle having a power train configured to transmit the torque of the engine 2 and the motor / generator MG2 to both the front wheels and the rear wheels. Furthermore, a double pinion planetary gear mechanism can be used as the power distribution device 3. Further, instead of the planetary gear mechanism 33, it is also possible to use a transmission capable of changing the gear ratio. Further, as the planetary roller mechanism 25, a transmission capable of changing the gear ratio may be used. In this case, the speed ratio can be changed by making the number of revolutions of the reaction force element of the planetary roller mechanism variable, and this technique is known. Furthermore, the transmission mechanism shown in FIGS. 1 and 2 can be used regardless of whether the rotation axis is arranged in the vehicle width direction or the front-rear direction.

  Next, another configuration example of the speed change mechanism will be described with reference to FIG. The configuration example of FIG. 3 is an example of a configuration in which an electric motor is arranged inside each wheel 72 of the vehicle, that is, a so-called in-wheel type electric motor mechanism. That is, each wheel 72 is configured by attaching a tire 73 around the wheel 51, and a motor / generator MG <b> 2 is provided for each wheel 51. In the configuration example of FIG. 3, the same components as those of the configuration example of FIGS. 1 and 2 are denoted by the same reference numerals as those of FIGS. The motor / generator MG2 is disposed inside the casing 52, and the rotor 17 of the motor / generator MG2 is configured to be rotatable about the rotation axis A2. Further, the stator 16 is fixed to the casing 52. The casing 52 is fixed to a vehicle body, a bracket attached to the vehicle body, a frame, or the like. Therefore, the casing 52 does not rotate. Further, both end portions (coil end portions) 19B and 19C of the coil 19 are arranged at different positions in the direction along the rotation axis A2. A first transmission is provided inside the coil end portion 19B and a second transmission is provided inside the coil end portion 19C in the radial direction centered on the rotation axis A2.

  The first transmission is constituted by a planetary roller mechanism 53. The planetary roller mechanism 53 is disposed inside the casing 52. The planetary roller mechanism 53 includes a sun roller 54, a ring roller 55 disposed on the outer peripheral side of the sun roller 54, the sun roller 54, and the ring roller 55. And a carrier 57 for holding a pinion roller 56 in contact with the pinion roller 56. The carrier 57 is fixed to the casing 52, and therefore the carrier 57 cannot rotate. In this planetary roller mechanism 53, the carrier 57 functions as a reaction force element, and the rotational speed of the ring roller 55 as an output element is lower than the rotational speed of the sun roller 54 as an input element. The radius ratio of the roller is configured. In other words, the planetary roller mechanism 53 functions as a speed reducer in which the speed ratio is fixed to a value larger than “1”. Further, the ring roller 55 and the hollow shaft 63 are connected by a connecting drum 58 so that power can be transmitted. That is, the hollow shaft 63 and the ring roller 55 are configured to rotate integrally. The hollow shaft 63 is disposed inside the stator 17, and the hollow shaft 63 and the stator 17 are relatively rotatable. A needle bearing 64 is provided between the hollow shaft 63 and the stator 17. A thrust bearing 59 is provided between the shaft end of the rotor 17 and the connecting drum 58. Further, an end cover 60 is attached to the end of the casing 52 in the axial direction, and a thrust bearing 61 is provided between the end cover 60 and the connecting drum 58.

  Next, the second transmission will be described. A planetary roller mechanism 62 as the second transmission is provided between the electromagnetic steel plate 23 and the wheel 51 in a direction along the rotational axis A2. That is, the electromagnetic steel plates 23 are laminated and disposed between the planetary roller mechanism 53 and the planetary roller mechanism 62 in a direction along the rotation axis A2. The planetary roller mechanism 62 is disposed inside the casing 52. The planetary roller mechanism 62 includes a sun roller 65, a ring roller 66 disposed on the outer peripheral side of the sun roller 65, the sun roller 65, and the ring roller 66. And a carrier 68 for holding a pinion roller 67 in contact with the carrier. The sun roller 65 is formed on the outer periphery of the hollow shaft 63. The ring roller 66 is fixed to the casing 52, and therefore the ring roller 66 cannot rotate. In this planetary roller mechanism 62, the ring roller 66 functions as a reaction force element, and the rotational speed of the carrier 68 as the output element is lower than the rotational speed of the sun roller 65 as the input element. The radius ratio of the roller is configured. That is, the planetary roller mechanism 62 functions as a speed reducer in which the speed ratio is fixed to a value larger than “1”.

  Further, the carrier 68 and the wheel 51 are connected so as to be able to transmit power. Thus, the motor / generator MG2 and the planetary roller mechanisms 25 and 26 are arranged coaxially with the rotation axis A1 as the center. A thrust bearing 69 is provided between the shaft end of the rotor 17 and the carrier 68. Further, an end cover 70 is attached to a portion near the wheel 51 at an end of the casing 52 in the axial direction, and a thrust bearing 71 is provided between the end cover 70 and the carrier 68. Yes. Also in the configuration example shown in FIG. 3, the above-described power supply device is connected to motor generator MG2.

  The operation of the configuration example shown in FIG. 3 will be described. Electric power is supplied from the power supply device to the motor / generator MG2, and the motor / generator MG2 is driven as an electric motor. The planetary roller mechanisms 53 and 62 are supplied with the traction oil described above, and power is transmitted on the principle of traction drive (transmission). When the output torque of the motor / generator MG 2 is transmitted to the sun roller 54 of the planetary roller mechanism 53, the fixed carrier 57 becomes a reaction force element, and torque is output from the ring roller 55. Here, the direction of the torque of the ring roller 55 with respect to the sun roller 54 is opposite, and the rotational speed of the ring roller 55 is lower than the rotational speed of the sun roller 52, and the torque is amplified. Further, the torque of the ring roller 55 is input to the sun roller 65 of the planetary roller mechanism 62 via the hollow shaft 63. Then, the fixed sun roller 66 becomes a reaction force element, and torque is output from the carrier 68.

  At this time, the directions of torque of the sun roller 65 and the carrier 68 are the same, and the rotational speed of the carrier is lower than the rotational speed of the sun roller 65, and the torque is amplified. The torque of the carrier 68 is transmitted to the wheel 51, and a driving force is generated. As described above, also in the configuration example of FIG. 3, when the torque of the motor / generator MG <b> 2 is transmitted to the wheel 45, the planetary roller mechanisms 53 and 62 are decelerated, and a total of two stages of deceleration is performed. Therefore, the motor / generator MG2 can be downsized in the radial direction, and the motor / generator MG2 can be rotated at a high speed. Also in the configuration example of FIG. 3, the planetary roller mechanism 53 is disposed inside the coil end portion 19B in the radial direction centered on the rotation axis A1, and the planetary roller mechanism is disposed inside the coil end portion 19C. 62 is arranged. In addition, the arrangement area of the coil end portion 19B and the arrangement area of the planetary roller mechanism 53 overlap in the direction along the rotation axis A1, and the arrangement area of the coil end portion 19C and the arrangement of the planetary roller mechanism 62 are overlapped. The area overlaps. Therefore, the arrangement space for components is reduced in the direction along the rotation axis A1, and the transmission mechanism can be reduced in size.

  Further, in the configuration example shown in FIG. 3, the planetary roller mechanisms 53 and 62 are used, so that the thrust load generated in each rotating element is lower than that of the reduction gear using the helical gear, and the thrust bearing 59 is provided. 61, 71 can be reduced in size. In addition, a sliding bearing can be used instead of the thrust bearing, and the speed change mechanism can be further downsized in the direction along the rotation axis A1. The hollow shaft 63 is supported by a needle bearing 64 on one side in the axial direction and supported by thrust bearings 59 and 61 on the other side in the axial direction. That is, since the needle bearing 64 can be disposed inside the hollow shaft 63, the needle bearing 64 can be further downsized in the direction along the rotation axis A1. The configuration shown in FIG. 3 can be provided on each of the left and right front wheels and the left and right rear wheels. That is, in the configuration example shown in FIG. 3, the motor / generator MG <b> 2 is provided as a driving force source that transmits power to the wheels 72. That is, it can be used for an electric vehicle in which an engine is not provided as a driving force source.

  It is also possible to use a configuration example shown in FIG. 2 for the front wheels and a configuration example shown in FIG. The planetary roller mechanism 53 is configured so that the carrier 57 functions as a reaction force element and the rotational speed of the ring roller 55 as an output element is lower than the rotational speed of the sun roller 54 as an input element. The radius ratio is configured. In other words, the planetary roller mechanism 53 functions as a speed reducer in which the speed ratio is fixed to a value larger than “1”. As the planetary roller mechanisms 53 and 62, a transmission capable of changing the speed ratio may be used. In this case, the speed ratio can be changed by making the number of revolutions of the reaction force element of the planetary roller mechanism variable, and this technique is known. Further, in the configuration example of FIG. 3, it is possible to use a planetary gear type transmission instead of the planetary roller mechanism 62 as the second transmission. Also in this case, the gear ratio may be fixed or variable, and may be either a speed increaser or a speed reducer.

  Further, it is possible to configure the power train shown in FIG. 4 by using the speed change mechanism shown in FIG. 3 instead of the speed change mechanism shown in FIG. Specifically, the carrier 68 shown in FIG. 3 is connected to the connecting drum 38 so that power can be transmitted. The configuration example of FIG. 4 forms a power train of a hybrid vehicle that can transmit the power of the engine 2 and the power of the motor / generator MG2 to the wheels 45. In the case of FIG. 4, the stator 16, the ring roller 66, and the carrier 57 of the motor / generator MG2 are fixed to the casing K1. Further, the rotor 17 and the hollow shaft 63 are arranged coaxially with respect to the input shaft 8. Further, the motor / generator MG2 is disposed between the end cover 14 of the casing K1 and the power distribution device 3 in a direction along the rotation axis A1. When the motor / generator MG2 shown in FIG. 4 is driven as an electric motor, the torque is transmitted to the connecting drum 38 via the planetary roller mechanism 53 and the planetary roller mechanism 62. In FIG. 4, the same function and effect as in FIG. 2 can be obtained for the same components as in FIG. 2, and the same effect as in FIG. 3 can be obtained for the same components as in FIG. 3. As the planetary roller mechanisms 53 and 62, a transmission capable of changing the speed ratio may be used. In this case, the speed ratio can be changed by making the number of revolutions of the reaction force element of the planetary roller mechanism variable, and this technique is known. Further, in the configuration example of FIG. 4, it is possible to use a planetary gear type transmission instead of the planetary roller mechanisms 53 and 62 as the second transmission. Also in this case, the gear ratio may be fixed or variable, and may be either a speed increaser or a speed reducer.

  Next, another configuration example of the speed change mechanism will be described with reference to FIG. The basic configuration of the configuration example shown in FIG. 5 is the same as the configuration shown in FIG. 3 except that the final reduction gear 74 is connected to the output side of the second reduction gear. It differs from the configuration. The final reduction gear 74 has a differential case 75 disposed inside the casing K2, and the differential case 75 is provided to be rotatable about the rotation axis A2. The differential case 75 is connected to the carrier 68 so that power can be transmitted. The differential case 75 is disposed between the planetary roller mechanism 62 and the end cover 70 in a direction along the rotational axis A2. The differential case 75 is provided with a pinion gear (not shown) supported by a pinion shaft (not shown) and a side gear (not shown) meshed with the pinion gear. The axle shaft is connected to the side gear. 76 is connected so that power transmission is possible. Two axle shafts 76 are provided, and one axle shaft 76 is disposed in the hollow shaft 63.

  The casing 52 is provided with radial bearings 77, 78, the differential case 76 is held by the radial bearing 77, and one axle shaft 76 is held by the radial bearing 78. The two axle shafts 76 are both rotatable about the rotation axis A2. In the arrangement layout of the configuration example of FIG. 5, the axle shaft 76 can be connected to the left and right front wheels or the left and right rear wheels. In this case, the rotation axis A2 is arranged along the left-right direction (width direction) of the vehicle. As another layout, the rotation axis A2 is arranged along the front-rear direction of the vehicle, and one axle shaft 76 is connected to a rear wheel via a front differential (not shown) so that power can be transmitted, It is also possible to connect the other axle shaft 76 to the rear wheels so as to be able to transmit power via a rear differential (not shown). In the configuration example of FIG. 5, as in the configuration example of FIG. 3, the torque of the motor / generator MG 2 is transmitted to the carrier 68 of the planetary roller mechanism 62, and the torque is transmitted to the axle via the final reduction gear 74. It is transmitted to the shaft 76. In the configuration example of FIG. 5 as well, the same effects as those of the configuration example of FIG. 3 can be obtained with respect to the same components as the configuration of FIG. In the configuration example of FIG. 5, a transmission that can change the gear ratio may be used as the planetary roller mechanisms 53 and 62. In this case, the speed ratio can be changed by making the number of revolutions of the reaction force element of the planetary roller mechanism variable, and this technique is known. Further, in the configuration example of FIG. 5, a planetary gear type transmission may be used as the second transmission instead of the planetary roller mechanisms 53 and 62. Also in this case, the gear ratio may be fixed or variable, and may be either a speed increaser or a speed reducer.

  Here, the relationship between the configuration example shown in each figure and the present invention will be described. The configuration example in FIGS. 1 and 2 is an embodiment corresponding to the inventions of claims 1 to 6 and the invention of claim 9. It is. The configuration example of FIG. 3 is an embodiment corresponding to claim 1, claim 2, claim 7 and claim 8, and the configuration example of FIG. 4 is claim 1, claim 2 and claim 7. 5, and the configuration example of FIG. 5 is an embodiment corresponding to claim 1, claim 2, claim 7, and claim 8. The correspondence between the configuration shown in FIGS. 1 and 2 and the configuration of the present invention will be described. The motor / generator MG2 corresponds to the electric motor of the present invention, and the rotor 17 corresponds to the output of the present invention. The planetary roller mechanism 25 corresponds to the planetary roller mechanism and the first transmission of the present invention, the planetary gear mechanism 33 corresponds to the second transmission of the present invention, and the planetary roller mechanism 53 corresponds to the shaft. The planetary roller mechanism 62 corresponds to the first transmission of the invention, and the planetary roller mechanism 62 corresponds to the second transmission of the invention. Further, the sun roller 26 of the planetary roller mechanism 25, the sun gear 34 of the planetary gear mechanism 33, the rotor 17 of the motor / generator MG2, and the carrier 29 are “the planetary roller mechanism, the transmission, and the electric motor according to the present invention”. Corresponding to “parts to be configured”.

  The sun roller 26, the ring roller 27, and the carrier 29 correspond to “three rotating elements in the planetary roller mechanism 25” of the present invention, and the sun roller 54, the ring roller 55, and the carrier 57 correspond to the “planetary roller mechanism 53 of the present invention. The thrust bearing 44 corresponds to the load transmission mechanism and the thrust bearing of the present invention, the radial bearings 30 and 31 correspond to the radial bearing of the present invention, and the cylindrical portion 22 corresponds to this This corresponds to the cylindrical portion of the invention. The engine 2 corresponds to the power source of the present invention, the motor generator MG1 corresponds to the motor generator of the present invention, the coil end portion 19B corresponds to one end portion of the present invention, and the coil end portion 19C. Corresponds to the other end of the present invention, the carrier 7 corresponds to the input element of the power distribution device in the present invention, the sun gear 4 corresponds to the reaction force element of the power distribution device in the present invention, and the ring gear 5 The wheel 45 corresponds to the output element of the power distribution device in the present invention, and the wheel 45 corresponds to the driven member of the present invention. Further, in the configuration example of FIG. 3, the ring roller 55 corresponds to the output element of the first transmission in the present invention, and the sun roller 65 corresponds to the input element of the second transmission in the present invention. Further, in the configuration example of FIG. 4, the connecting drum 38, the wheel 45, and the final reduction gear 49 correspond to the driven members of the present invention.

It is a fragmentary sectional view showing an example of composition of a speed change mechanism of this invention. It is a skeleton figure which shows the power train of the vehicle which has the transmission mechanism of this invention. It is sectional drawing which shows the other structural example of the transmission mechanism of this invention. It is a skeleton figure which shows the power train of the vehicle which has the transmission mechanism of this invention. It is sectional drawing which shows the other structural example of the transmission mechanism of this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Vehicle, 2 ... Engine, 3 ... Power distribution device 7, 29, 57, 68 ... Carrier, 4, 34 ... Sun gear, 5, 35 ... Ring gear, 17 ... Rotor, 19 ... Coil, 19B, 19C ... Coil end Part, 22 ... cylindrical part, 25, 53, 62 ... planetary roller mechanism, 26, 54, 65 ... sun roller, 27, 55, 66 ... ring roller, 28, 56, 67 ... pinion roller, 33 ... planetary gear mechanism, 30 , 31 ... Radial bearings, 38 ... Connecting drums, 44 ... Thrust bearings, 45 ... Wheels, 49 ... Final reduction gears, A1, A2 ... Rotating axis, MG1, MG2 ... Motor generator.

Claims (10)

An electric motor that is energized in the coil and outputs power from the output shaft, and a planetary roller mechanism connected to the output shaft so as to be able to transmit power are provided. The planetary roller mechanism has three rotations capable of differential rotation. In the speed change mechanism in which the output shaft and the three rotating elements are arranged so as to be rotatable about the same rotation axis while having an element,
A speed change mechanism, wherein the planetary roller mechanism is arranged inside the coil in a radial direction centered on the rotation axis.   A transmission connected to the planetary roller mechanism so as to be able to transmit power is provided, and the components constituting the planetary roller mechanism, the transmission, and the electric motor are integrated with each other. The transmission mechanism according to 1.   The speed change mechanism according to claim 1 or 2, further comprising a load transmission mechanism that transmits a load applied to the output shaft to any one of the three rotation elements. The three rotating elements include a sun roller and a ring roller arranged on the same axis, and a carrier that holds a pinion roller that contacts the sun roller and the ring roller.
The transmission mechanism according to claim 3, wherein the load transmission mechanism is a thrust bearing that transmits a thrust load applied to the output shaft to the sun roller. The three rotating elements include a sun roller and a ring roller arranged on the same axis, and a carrier that holds a pinion roller that contacts the sun roller and the ring roller.
The speed change mechanism according to claim 1 or 2, wherein a radial bearing for receiving a radial load applied to the carrier is provided.   The output shaft has a cylindrical portion disposed on a circumference centered on the rotational axis, and the radial bearing is disposed inside the cylindrical portion in a radial direction centered on the rotational axis. The speed change mechanism according to claim 5, wherein An electric motor that energizes the coil and outputs power from an output shaft, and a first transmission coupled to the output shaft so as to be able to transmit power are provided, and the output shaft and the rotating element of the first transmission Are arranged on the same rotation axis,
A second transmission is provided in addition to the first transmission, and one end and the other end of the coil are arranged at different locations in the direction along the rotation axis, and the rotation axis is centered. The first transmission is disposed inside one end of the coil in the radial direction, and the second transmission is arranged inside the other end of the coil in the radial direction around the rotation axis. Is a speed change mechanism.   The transmission mechanism according to claim 7, wherein an output element of the first transmission and an input element of the second transmission are coupled so as to be able to transmit power. A power distribution device having a differentially rotatable input element and a reaction force element and an output element is provided, a power source is connected to the input element of the power distribution device, and a motor The generator is connected,
The output element of the transmission and the output element of the power distribution device are connected to a driven member so as to be able to transmit power in parallel.
3. The power source, the electric motor, the motor / generator, the planetary roller mechanism, and the rotating elements constituting the transmission are arranged so as to be rotatable about the rotation axis. 7. A transmission mechanism according to any one of claims 6 to 6. A power distribution device having a differentially rotatable input element and a reaction force element and an output element is provided, a power source is connected to the input element of the power distribution device, and a motor The generator is connected,
The output element of the second transmission and the output element of the power distribution device are coupled to the driven member so as to be able to transmit power in parallel.
The power source, the electric motor, the motor / generator, and the rotating elements constituting the first transmission and the second transmission are arranged to be rotatable about the rotation axis. The speed change mechanism according to claim 7 or 8.

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