WO2004010028A1

WO2004010028A1 - Stepless speed change device

Info

Publication number: WO2004010028A1
Application number: PCT/JP2003/009265
Authority: WO
Inventors: Suenori Tsujimoto
Original assignee: Suenori Tsujimoto
Priority date: 2002-07-22
Filing date: 2003-07-22
Publication date: 2004-01-29
Also published as: JP2006052739A; AU2003281545A1

Abstract

A stepless speed change device comprises power rollers (40) frictionally engaged between a pair of power wheels (30, 32) through inclined surfaces (40a, 40b) at the opposite ends and making an orbital motion around the center axis (C) of the power wheel while each rotating around its own axis, and planetary rollers (44) frictionally engaged with the peripheral surfaces of these power rollers and making an orbital motion around the center axis (C) of the power wheel while each rotating around its own axis. A guide surface (46) frictionally engaged with the peripheral surfaces of the planetary rollers supports the power rollers (40) urged in the direction of the center axis (C) of the power wheel by the pressing force produced by the pair of power wheels, through these planetary rollers (44), and holds the power rollers (40) and the planetary rollers (44) at peripherally equispaced intervals.

Description

Specification

Continuously variable transmission

Technical field

The present invention relates to a transmission, and more particularly, to a friction type transmission capable of changing a gear ratio steplessly.

Background art

In general, various types of friction type transmissions have been developed as continuously variable transmissions.

For example, in Japanese Patent Application Laid-Open No. 7-1333857, friction between the primary rotary plate connected to the input shaft and the secondary rotary plate connected to the output shaft is attached to the peripheral edges of these rotary plates. A forward / reverse continuously variable transmission in which a large number of small-diameter spheres are arranged is described. A large number of spheres of the continuously variable transmission extend in the radial direction of the rotating plate, and are supported by a fixed plate disposed between the pair of rotating plates so as to be tiltable with respect to the input shaft and the output shaft. It is rotatably held on a shaft. By tilting these rotating shafts at the same time, the positions where the peripheral edges of the primary side rotating plate and the secondary side rotating plate press against the outer surface of the sphere are changed. As a result, the rotational speed ratio between the primary side rotating plate and the secondary side rotating plate is steplessly changed.

However, since the continuously variable transmission rotates a small-diameter sphere at the periphery of the large-diameter rotary plate where the peripheral speed is highest, the rotation speed of the sphere becomes extremely high. For example, an automobile engine rotates at about 100 to 800 revolutions per minute, and an aircraft or marine turbine engine rotates at about several thousand to tens of thousands of revolutions per minute. The motor rotates at about 100 to 300 rotations per minute Is done. For this reason, even if forced lubrication is applied to the bearing portion of the rotating shaft that supports the sphere, a large power loss occurs in the bearing portion. Furthermore, since a large number of spheres arranged along the periphery of each rotating plate are moved at the same time, turbulence is likely to occur, and the load on the rotating shaft supporting the spheres and the control mechanism for controlling the tilt of the spheres increases. . This causes a problem in the durability of the rotating shaft supporting the spheres and the control mechanism, and also increases the cost of such a large number of spheres and the control mechanism.

Disclosure of the invention

The present invention has been made in view of such circumstances, and has a simple structure, high transmission efficiency, low weight, and low cost that can transmit large power. It is intended to provide a step transmission.

To achieve the above object, a transmission according to the present invention comprises: a first and a second power wheels having circular engagement portions provided at a distal end thereof arranged to face each other; and a first power wheel formed at a tapered end portion. , Frictionally engage with the engaging portions of these power wheels via the second inclined surface, and rotate while rotating along these engaging portions. A plurality of first rolling elements that revolve around the center axis of the wheel and frictionally engage with the peripheral surfaces of two adjacent first rolling elements, and the power wheel while rotating together with the first rolling elements; A plurality of second rolling elements orbiting about the central axis of the second rolling element, and frictionally engaging with the peripheral surface of the second rolling element, the center of the power wheel being pressed by the first and second power wheels. The first rolling element biased in the direction of the axis is supported via these second rolling elements, and the first rolling element and the second rolling element are separated from each other. And a support wheel for holding each at equal intervals in the circumferential direction. The first rolling element has a tilt with respect to the center axis and a tilt corresponding to the tilt in accordance with at least one axial position of the first and second power wheels and the support wheel. The distance between the engaging position of the engaging portion on the inclined surface of the and the rotating shaft is set. The rotation of the input shaft is transmitted to the first rolling element by one of the first and second power wheels and the supporting wheel via the second rolling element, and the rotation of the input shaft is performed by the first rolling element. The rotation output can be output to the output shaft via the other of the first and second power wheels.

According to this transmission, the first rolling elements are pressed against the first and second inclined surfaces disposed on both sides by the engaging portions of the first and second power wheels, respectively. Therefore, the power wheel is urged in the direction of the central axis. The peripheral surface of each of the first rolling elements is frictionally engaged with the peripheral surface of each of the two second rolling elements supported by the support wheel, so that the forces along the circumferential direction of the engaging portions are balanced. Further, each of the second rolling elements frictionally engages with two adjacent first rolling elements, so that a force along a circumferential direction of the engaging portion is balanced, and these first rolling elements are balanced. The rolling elements and the second rolling elements are respectively held at equal intervals in the circumferential direction along the engaging portion of the power wheel. And the first, second, and so on. When at least one of the wheel and the support wheel moves along the direction of the center axis, the inclination of the rotation axis of the first rolling element with respect to the center axis changes. As a result, the distance of each engagement portion from the rotation axis on the first and second inclined surfaces changes, and the first power wheel or the second rolling wheel is rotated. By being rotated by the body, the second power wheel that frictionally engages with the second engagement surface is rotated. The rotation of the input shaft is transmitted to the first rolling element by one of the first and second power wheels and the supporting wheel via the second rolling element, and the first rolling element is rotated by the first rolling element. Rotational output can be output to the output shaft via the other of the first and second power wheels.

The support wheel is formed of a central wheel provided on an input shaft concentric with the central axis, and the central wheel has a circumferential groove on the outer peripheral portion where the second rolling element rolls. Is preferred.

In this case, it is preferable that the driving force branched from the input shaft via the driving force branching mechanism is transmitted to one of the first and second power wheels. Instead, the first and second power wheels are preferably used. It is also possible to fix either one of them and the support wheel so that they do not rotate. When the rotation direction of one of the first and second wheels and the center wheel is in the opposite direction, the revolving speed of the first and second rolling elements is reduced, and the input shaft and, therefore, the start-up of the motor, that is, the start-up In this case, the load of potential energy at the time of rotation is reduced, thereby increasing the responsiveness to fluctuations in the rotation speed of the prime mover. Conversely, if the rotation direction of one of the first and second power wheels and the center wheel is in the same direction, the rotation speed of the first and _second rolling elements is reduced, and each of these rolling elements is reduced. The number of rolling stakes decreases, which increases transmission efficiency.

Also, an on-way clutch interposed between the driving force source and a center wheel, and a rotor connected to the center wheel A first motor generator; a second motor generator having a rotor connected to one of the first and second power wheels; an output shaft driven by the other of the first and second power wheels; And a clutch interposed between the shaft and a driven device operated by the shaft. By suitably switching between the first and second motor generators, even if the vehicle weight fluctuates greatly due to changes in the loaded cargo or the number of passengers, the kinetic energy and the electric energy can be efficiently converted. can do.

Further, the support wheel is formed by a center wheel provided on a hollow shaft which is concentric with the center shaft and cannot rotate, and further comprises a motor having a rotor connected to one of the first and second power wheels. A generator may be provided, and an operating gear unit connected to the other of the first and second power wheels and the left and right drive shafts. In this case, the internal space of the motor generator can be used efficiently.

The center wheel is mounted on the input shaft so as to be immovable in the circumferential direction and slidable in the axial direction, and can control the inclination of the first rolling element with respect to the center axis.

The first and second power wheels can be connected to each other via a transmission having a constant speed ratio.

The support wheel is formed of a guide that surrounds the first and second rolling elements and frictionally engages with a peripheral surface of the second rolling element, and is provided between the other of the first and second power wheels and an output shaft. It may be through a clutch. In this case, the alignment between the first rolling element and the second rolling element can be further ensured. As described above, the rotation of the input shaft is transmitted to the first rolling element by one of the first and second power wheels and the supporting wheel via the second rolling element, and the first rolling element rotates. Instead of taking out the rotational output to the output shaft via the other of the first and second power wheels, the first and second power wheels are connected to each other via a speed change mechanism having a constant speed ratio. In addition, the rotation of the input shaft is transmitted to the first rolling element, and the rotation output from the center wheel rotated through the second rolling element can be taken out to the output shaft. In this case, for example, by rotating the input shaft with the blades of a wind turbine and driving the generator with the output shaft, it is possible to achieve a reduction in the size of the power generation device and an improvement in the power generation efficiency. You.

Brief description of the drawings ''

FIG. 1 is a longitudinal section of a transmission according to a first embodiment of the present invention. FIG. 2 is a sectional view of the transmission of FIG. 1 taken along line Π_Π.

FIG. 3 is a sectional view similar to FIG. 1 of a transmission according to a second embodiment.

FIG. 4 is an explanatory view of a state in which the transmission according to the third embodiment shown in FIG. 3 is formed for an automobile.

FIG. 5 is a longitudinal sectional view of a transmission according to a fourth embodiment formed for a hybrid vehicle.

FIG. 6 is a longitudinal sectional view of a transmission according to a fifth embodiment formed for an electric vehicle.

FIG. 7 is a cross-sectional view of the transmission of FIG. 6 taken along line W.

FIG. 8 is a longitudinal sectional view of a transmission according to a sixth embodiment. FIG. 9 is a cross-sectional view of the transmission of FIG. 8 taken along line X-IX.

FIG. 10 is a longitudinal sectional view of a transmission according to a seventh embodiment.

FIG. 11 is a longitudinal sectional view of a transmission according to an eighth embodiment formed for a wind turbine generator.

FIG. 12 is a longitudinal sectional view of a transmission according to a ninth embodiment.

FIG. 13 is a cross-sectional view of the transmission of FIG. 12 taken along the line Χ-ΠΙ. BEST MODE FOR CARRYING OUT THE INVENTION

1 and 2 show a transmission according to a first embodiment of the present invention.

This transmission is formed as a wide range of industrial continuously variable transmissions including, for example, automobiles, and is formed in a compact structure in which the entirety is housed in a housing 10.

As shown in FIG. 1, the housing 10 includes a cylindrical body 10a having both ends opened, and a lid 10b that closes both ends. 2 and the output shaft 14 penetrate these lids 10b along the central axis C common to both shafts, and are rotatably supported via appropriate bearings such as ball bearings. A suitable seal member is disposed at a portion where the input shaft 12 and the output shaft 14 penetrate to prevent leakage of lubricant and the like and prevent foreign substances from entering the housing 10. Further, in the present embodiment, the lid 10b through which the input shaft 12 penetrates is recessed inward, so that the entire axial length of the power transmission system can be shortened. It should be noted that “input” and “output” in the present specification are terms for convenience of explanation, and “input” and “output” may be reversed depending on how the transmission is used. The first drum 16 rotatably supported on the input shaft 12 and the second drum 18 coupled to the output shaft 14 are arranged inside the nozzle 10. . The first drum 16 has a disk-shaped portion 16a rotatably supported on the input shaft 12 via, for example, a ball bearing, and the second drum 18 has a hollow disk-shaped portion 18a. It is integrally connected to the output shaft 14 via the boss 14a. In the present embodiment, the distal end portion 12a of the input shaft 12 is inserted into the boss portion 14a, and is rotatably supported via bearings at two positions separated in the axial direction. I have.

Further, in order to offset thrust loads in opposite directions, the nozzle 10 extends beyond the outer peripheral portion of the second drum 18 toward the first drum 16, and the tip thereof extends to the first drum 16. A connecting member 20 fixed to the outer peripheral portion of the drum 16 is rotatably supported by a boss portion 14a of the output shaft via an axial bearing 22. By mounting the connecting member 20 rotatably on the boss portion 14a via the axial bearing 22 in this manner, the pressing force of a pair of power wheels described later can be reduced by the first drum 16. The axial bearing 22 acts as a force in the opposite direction via the second drum 18 and the second drum 18 to cancel each other. Thereby, the housing 10 can be formed in a lightweight structure. The boss portion 14a of the output shaft 14 is fixed to the disc-shaped portion 18a instead of being formed integrally with the disc-shaped portion 18a of the second drum 18. It can be formed as a separate member.

The first and ^second drums 16 and 18 have annular inner holes 26 and 28 opposed to each other at positions close to the outer peripheral portions thereof. In these annular bores, the first, second, and third wheels 30 and 32 can be moved only in the axial direction along the central axis C by, for example, a spline (not shown). Will be accommodated. The front ends of these power wheels 30 and 32 are formed with first and second engaging portions 30a and 32a, which are frictionally engaged with a power roller described later. Defines pressure chambers 26a, 28a in the respective annular bores 26, 28. These pressure chambers 26a, 28a are connected to the pressure fluid control device via appropriate pipes 36, 38, respectively, and the power wheel 30 is supplied by the fluid pressure supplied thereto. , 32 in opposite directions.

These nose. As shown in FIG. 2, in the present embodiment, the seven first rolling elements, that is, the power rollers 40, are located between the power wheels 40 and 32 at positions separated from the center axis C with respect to the rotation axis r. Is pressed from both sides. In other words, the No. 1 wheel 30,

3 2 engagement portion 3 that presses frictionally engage these power rollers 4 0 0 a, 3 2 a is Bruno, ⁰ Wah Russia over La 4 0 rotation axis r and between the center axis C of the It has a circular shape with a radius larger than the distance.

Such a thing. Each of the power rollers 40 sandwiched between the power wheels 30 and 32 has a hollow structure in which both ends are formed in a tapered or hemispherical shape. 1, 2nd inclined surface 40a, 40b Force S no.摩擦 Frictionally engages with the engaging portions 30a and 32a of the wheels 30 and 32. Each power roller

40 has a circumferential groove 42 which opens in the outer periphery. In the present embodiment, each of the seven second rolling elements, that is, the spherical planetary rollers 44, is arranged in the circumferential direction of two power rollers adjacent to each other. Fit into groove 42. Each of the planetary rollers 44 rolls along the circumferential groove 42 and frictionally engages with a circumferential surface formed on the bottom surface of the circumferential groove 42 at a contact point s (see FIG. 2). The rotation axis p passing through the center point of these planetary rollers 44 is closer to the center axis C, that is, radially inward than the straight line connecting the rotation axes r of the two adjacent power rollers 40. To position. Further, the rotation axis r of each power roller 40 is located radially outward from the center axis C with respect to a straight line connecting the rotation axes ρ of the two planetary rollers 44 adjacent to each other. The planetary rollers 44 are not limited to the spherical structure as shown, but may be formed in a plate-like or cylindrical structure.

When the first wheels 30 and 32 are pressed in the directions facing each other by the pressures in the respective pressure chambers 26 a and 28 a, the respective first rollers 40 become the first and second inclined surfaces 4. By the action of 0 a and 40 b, it is urged radially inward toward the central axis C. Each planetary roller 44 receives two equalizing forces from two sides, each having an equal magnitude, and applies radially inward toward the center axis C. Urged. In this embodiment, the planetary roller 44 urged inward in the radial direction is supported by a support wheel 46 which is a central wheel formed integrally with the input shaft 12 in this embodiment. Can be A circumferential groove formed on the outer peripheral surface of the support wheel 46 is provided with a guide groove 46 a that frictionally engages with the planetary roller 44 to prevent axial movement and guides in the circumferential direction. It works. With this, no ,. Circumferential forces acting on the word rollers 40 and the planetary rollers 44 cancel each other out and are held at equal intervals in the circumferential direction about the center axis C. In the present embodiment, the circumferential groove 42 formed on the power roller 40 and the guide groove 46 a of the support wheel 46 are formed by a smooth annular curved surface. The axial movement of the power roller 4 ◦ and the support wheel 46 is prevented. Due to this, no. When the wheels 30 and 32 move in the same direction along the central axis C while pressing the power rollers 40 sandwiched therebetween from both sides, the power rollers 40 move more than the rotation axis r. Engagement parts 30a, 3

It is pressed by 2a and tilts all together about the contact point s with the adjacent planetary roller 44. As a result, the engagement positions of the engagement portions 30a and 32a on the inclined surfaces 40a and 40b move, and the distance from the rotation axis r changes. In other words, the distance between the engagement position of the engagement portions 30a, 30b on the inclined surfaces 40a, 40b and the rotation axis r is: It is set at an angle of inclination centered on the contact s of the warlor 40. ·

In this embodiment, the power wheels 30 and 32 have pressure chambers 26 a and 28 a partitioned into annular bores 26 and 28, respectively, and the pipelines 36 and 28.

A speed ratio changing means is formed by the pressure fluid control device supplied through the pressure fluid control device 38 and the pressure chambers 26 a and 28 a from a pressure fluid source (not shown) through the pressure fluid control device. By controlling the pressure of the pressurized fluid supplied to the inside and the amount thereof, the amount by which the power wheels 30 and 32 project from the inner holes 26 and 28, that is, the engaging portions 30 a and 32 a It is possible to adjust the inclination angle of the rotation axis r with respect to the center axis C of the rotation axis r.

Further, in this embodiment, a part of the driving force is divided from the input shaft 12. There is provided a driving force branching mechanism 50 for transmitting the power to the first drum 16 at a divergent speed. The driving force splitting mechanism 50 of the present embodiment includes an external gear 52 provided on the outer periphery of the input shaft 12 and a support shaft 54 projecting from the inner surface of the lid 10b on the input shaft 12 side. An intermediate gear 56 that is rotatably mounted and mates with the external gear 52, and an internal gear that is provided on the disk-shaped portion 16a of the first drum 16 and mates with the intermediate gear 56. 5 8 and. Since the intermediate gear 5 6 is interposed between the external gear 52 and the internal gear 58, the speed of the external gear 52 and the internal gear 58 is inversely proportional to the number of teeth. Rotate in opposite directions by the ratio.

Next, the operation of the above-described transmission will be described.

In this transmission, the first power wheel 30 and the support wheel 46 rotate the input shaft 12 in rotation. The speed-changed rotation output transmitted to the power roller 40 and output from the second power wheel 32 can be output to the output shaft 14. The driving force extracted from the output shaft 14 can be transmitted to a driven device such as a propeller shaft of an automobile, for example.

Specifically, when the input shaft 12 is driven by, for example, an engine which is a driving force source (not shown) connected via a spline joint, the center wheel 46 is driven by a power roller via a planetary roller 44. Rotate 40 in the same direction as this center wheel 46. On the other hand, the internal gear 58 through the external gear 52 of the input shaft 12 and the intermediate gear 10 causes the first drum 16 to rotate in the opposite direction to the input shaft 12 at a predetermined speed ratio. Rotate.

Each power roller ₄₀ has a first and a second power wheel from both sides. The first drum 16 and the center wheel 46 cause the input shaft 12 to be pressed by the center wheels 46 through the planetary rollers 44 and pressed by the rollers 30 and 32. The rotation is transmitted to the power roller 40. As a result, each power roller 40 rotates while revolving around the center wheel 46. As a result, the second power wheel 32 becomes the first power wheel. It rotates in the same direction as the wheel 30, and the driving force is transmitted to the output shaft 14 through the second drum 18.

Here, for convenience of explanation, each engaging portion of the power roller 40 is described.

The trajectory radii drawn by 30a and 3Ob around the rotation axis r are represented by rl and r2.

As shown in FIG. 1, when the rotation axis r of the power roller 40 is parallel to the center axis C, r 2 = r 1. The wheel 30 rotates the second wheel 32 at a constant speed, and the rotational drive is shifted to the output shaft 14 through the second drum 18 at the speed ratio by the driving force branching mechanism 50. Power is transmitted.

On the other hand, when the first and second power wheels 30 and 32 are moved to the output shaft 14 side by the pressure fluid control device, each power roller is moved.

40 is inclined to the output shaft 14 side so that r 2> r 1, and the peripheral speed of the engaging portion 32 a becomes higher than that of the engaging portion 30 a. Therefore, the second nozzle wheel 32 rotates at an increased speed, and the reduced rotational driving force is transmitted to the output shaft 14 through the second drum 18. Conversely, the first, second,. When the wheels 30 and 32 are moved to the input shaft 12 side, the respective power rollers 40 are inclined to the input shaft 12 side so that r 2 <r 1, and the engagement portion 32 a Peripheral speed is lower than engagement part 30a And Thus, the second wheel, the second power wheel 32, is rotated at a reduced speed, and the reduced driving force is transmitted to the output shaft 14 through the second drum 18.

In the transmission described above, the input of the driving force is performed through both the first drum 16 and the center wheel 46 via the planetary rollers 44, and the input is lower than the conventional one-way input. The speed ratio can be reduced with respect to rotation. The pair of power wheels 30 and 32 that press the roller 40 rotate with each of the drums 16 and 18. Driving force can be efficiently transmitted without hindering rotation and revolution of the word rollers 40, and transmission loss can be significantly reduced.

Further, since the engaging portion 30a of the first power wheel 30 that transmits the driving force by changing the speed is frictionally engaged with the power roller 40 near the maximum radial position of the transmission, It is possible to simultaneously reduce the size and weight while increasing the workload. In addition, since the central wheel 46 is arranged along the central axis C, the speed change device can be made robust and the durability can be improved. In addition, the power roller 40 and the planetary roller 44 can be used. Are maintained at equal intervals around the center wheel 46 without requiring a special support mechanism, thereby reducing the loss of driving force due to rotation and further improving transmission efficiency. Can be done.

FIG. 3 shows a transmission according to a second embodiment. Since various embodiments described below are basically the same as the above-described embodiments, similar parts are denoted by the same reference numerals, and detailed description thereof will be omitted. In this embodiment, the driving force branching mechanism 50 is formed by a planetary gear set, and the first drum 16 and the first drum 16. The present embodiment differs from the above-described embodiment only in that the wheel 30 is rotated in the same direction as the input shaft 12. In this driving force branching mechanism 50, a support shaft 54 for supporting the intermediate gear 56 is provided on the disk-shaped portion 16a of the first drum 16 and the internal gear 58 is connected to the input shaft 12 side. Provided on the lid 10b of the camera.

According to this transmission, each of the power rollers 40 is rotationally driven in the same direction by both the center wheel 46 and the first power wheel 30 with the rotary shaft interposed therebetween, so that the rotation speed thereof is reduced. Be confused Thereby, the rolling resistance of each power roller 40 is reduced, and the transmission efficiency is improved.

In the first and second embodiments described above, the speed ratio of the rotation speed of the output shaft 14 to the rotation speed of the input shaft 12 is the first and second nose. Various settings can be made according to the effective diameter of each of the wheel 30, 32, the center wheel 46, and the power roller 40, that is, the diameter actually formed by the engaging portion of each member. Regarding the rotation direction of the output shaft 14, a forward rotation region that rotates in the same direction as the input shaft 12 and a reverse rotation region that rotates in the opposite direction to the input shaft 12 can be provided. For example, when used in a motorcycle, it is preferable to set only the forward rotation region in which the output shaft 14 rotates in the same direction as the input shaft 12. When used for marine applications, it is preferable that the forward rotation region and the reverse rotation region be in a one-to-one relationship, and that the intermediate point be a neutral position. Further, when used for construction equipment such as bulldozers, it is preferable to set the ratio of the forward or forward rotation region to the reverse or reverse rotation region to be 2 to 3. When it is used as a vehicle tractor, it is preferable that the ratio of the forward area to the reverse area is about 5 to 2. Thus, it is easy to change the speed ratio of the speed change device according to the application, and the efficiency and convenience of the speed change device are improved.

FIG. 4 shows a transmission according to a third embodiment.

In this embodiment, the transmission shown in FIG. 3 is optimized for an automobile, so that the forward rotation region for forward movement is expanded, and the output shaft 14 and the propeller shaft 60 as a driven device are enlarged. Between them, an intervening clutch mechanism 62 is interposed.

Such a combined clutch mechanism 62 for connecting or separating the output shaft 14 and the propeller shaft 58 can be formed in an appropriate structure. The combined clutch mechanism 62 of the present embodiment includes a cam block 64 non-rotatably connected to the output shaft 14 by a suitable means such as a screw, for example, and a propeller shaft 60. And a shifter 68 that is non-rotatably mounted on the top and is movable in the axial direction by a shift lever 66. Both ends of the shifter 68 are formed with teeth or ridges extending in the radial direction, and are combined with the teeth or ridges formed on the cam block 64 and the control housing 10c. I can.

When the shift lever 66 is positioned at the position D indicated by the solid line, the shifter 168 engages with the cam block 64, thereby connecting the input shaft 14 and the propeller shaft 60. Is done. On the other hand, when the shift lever 66 is located at the position P indicated by the dotted line, the shift lever 68 is engaged with the control housing 10 c, whereby the propeller shaft 60 is separated from the input shaft 14. This propeller shaft 60 is It is fixed to the housing 10 c to prevent rotation of the propeller shaft. When the shift lever 66 is located at the middle position N, the opening shaft 60 is separated from both the input shaft 14 and the control housing 10c.

By providing such a joint clutch mechanism 62 between the output shaft 14 and the propeller shaft 60, the shift lever 66 can be arranged at the P position or the N position. Only then can a mechanical or electrical interlocking mechanism be provided to allow the engine to start. As a result, when the crankshaft of the engine is connected to the propeller shaft 60 via the transmission, the engine cannot be started, and an excessive load on the engine is prevented. At the same time, runaway of the vehicle when the engine is started can be reliably prevented. When the shift lever 66 is located at the position P, the propeller shaft 60 is made unrotatable, so that braking during parking can be secured and the movement of the vehicle can be prevented. Further, in a state where the shift lever 66 is located at the N position, even when the transmission is at a position other than the neutral position, the propeller shaft 60 can freely rotate to secure the rotation of the engine trouble and the like. It is possible to secure the movement of the vehicle, for example, by towing when the vehicle is unable to run.

FIG. 5 shows a transmission according to a fourth embodiment.

This embodiment is formed for a hybrid vehicle, and the first drum 16 is driven to rotate by a motor generator instead of the driving force branching mechanism 50 in the above-described embodiment. can do. In this embodiment, the coupling 72 is attached to the end of the input shaft 12 via a one-way clutch 70, and the rotor 76 of the first motor generator 74 is connected to the nut 78. It is fixed with. This one-way clutch 70 is preferably formed by a coupling with a damper for damping the rotational vibration of an engine connected via a spline joint, for example. When the number of revolutions is equal to or less than the number of revolutions of the drive shaft of the engine connected via the power ring 72, these input shafts 12 and the drive shaft are connected. Further, the rotor 82 of the second motor generator 80 is fixed to the connecting member 20. The stators 75, 81 of these first and second motor generators 74, 80 are fixed inside the body 10a of the housing, respectively, and the rotors 76, 82 are Opposite to the stator, permanent magnets 76a and 82a, for example, neodymium magnets, are arranged at equal intervals along the periphery thereof, and are formed as a so-called PM motor. The housing 10 housing such motor generators 74 and 80 preferably has a liquid-tight interior.

These first and second motor generators 74 and 80 act as drive motors which are rotated by electric power from a battery as necessary by a motor generator controller (not shown). Or act as a generator to power the battery, so that kinetic and electrical energy can be maintained even when the weight of the vehicle fluctuates significantly due to the load or the number of passengers. Can be converted efficiently. For example, it increases the acceleration force when starting a car and increases the energy efficiency when decelerating. By recovering at a low rate, fuel efficiency can be reduced.

The transmission equipped with the two motor generators 74 and 80 can be operated in various modes according to the situation of the vehicle. Will be described. If the remaining amount of the battery is insufficient, the vehicle is brought into a braking state in advance, and the shift lever 66 is arranged at the position D. In addition, the first and second motor generators 74 and 80 are brought into a power generation state via the motor generator control device. In this state, when the input shaft 12 is rotated by an engine (not shown), the rotor 76 of the first motor generator 74 is rotated at the same speed in the same direction as the drive shaft, and charges the battery. Since the propeller shaft 60 is being braked, the second drum 18 and the second power wheel 32 remain stationary, and the lower roller 40 has its second inclined surface 40 b Is frictionally engaged with the engagement portion 32 a, and revolves while rotating along the second wheel 32. This causes the first power wheel 30 and the first drum 16 to rotate the rotor 82 of the second motor generator 80 on the first inclined surface 40a, thereby removing the battery. Charge.

If the engine is stopped and the rotor 76 of the first motor generator 74 is braked while the battery is charged, the input shaft 12 is fixed to the housing 10 and does not rotate. When the braking of the vehicle is released and the second motor generator 80 is driven, the power roller 40 rolls along the engaging portion 30a of the first power wheel 3◦, thereby Then, the second No. 3 wheel 32 is rotated at a speed relative to the first power wheel, and 2 Drum 18, output shaft 14 and propeller shaft 60 rotate. The driving by the second motor generator 80 is controlled by controlling the rotation of the second motor generator 80 when the running resistance of the vehicle is the smallest. The speed can be changed from a state in which the vehicle is started forward or backward to the cruising speed, and therefore, it is possible to travel with the minimum power by the second motor generator 80 having a small output. Obviously, it is also possible to move the first and second power wheels 30, 32 in the axial direction if necessary.

When the rotor 82 of the second motor generator 80, that is, the first drum 16 is braked and the first motor generator 74 is driven, the output shaft 14 rotates. Furthermore, the first, is rotated synchronously with the second Motor generators 7 4, 8 0, Nono ⁰ Waro over La 4 0 does not rotate, therefore, the output shaft 1 4 same as the input shaft 1 2 speed And the speed ratio becomes 1: 1. Since the movable member of the continuously variable transmission transmits the rotation of the input shaft 12 to the output shaft 14 and the propeller shaft 60 without rotating relatively, the transmission efficiency is highest. In addition, the first and second power wheels 30 and 32 are moved through the speed ratio changing means, and are notched. As in the above-described embodiment, the speed ratio between the input shaft 12 and the output shaft 14 can be changed over a wide range by setting the tilt position of the word roller 40.

By combining this transmission with an engine, a hybrid drive suitable for an automobile is formed. If integrated into a car, through a suitable motor generator control It can be operated as follows.

When the vehicle starts or runs at low speed, the input shaft 12 is driven by the first motor generator 74. The one-way clutch 70 separates the drive shaft of the engine from the input shaft 12. Then, the rotation of the first drum 16 is stopped, the electric power is supplied to the first motor generator 74, and the input shaft 12 is driven to rotate. The motor generator control device rotationally drives the first motor generator 74 with an output corresponding to a signal requested by the driver, which is sent based on, for example, an accelerator pedal (not shown). If the output of the first motor generator 74 is insufficient, the second motor generator 80 is further driven to rotate, and the output shaft 14 is rotated by the driving force required by the driver.

When the vehicle travels at a speed that is efficient for driving by the engine, the motor generator controller reduces the power supplied to the first and second motor generators 74, 80, and the engine, which is the main driving force source, To rotate the output shaft 1 2. Also, when the driver decelerates the accelerator pedal when decelerating the car, the rotation speed of the engine decreases, and the on-way clutch 70 separates the input shaft 12 from the engine. Then, the first motor generator 74 is operated as a generator, recovers kinetic energy associated with the deceleration of the vehicle as electric energy, and stores it in the knotter. Further, when the kinetic energy due to the deceleration of the vehicle cannot be recovered only by the first motor generator 74, the second motor generator 80 is also operated as a generator, and the first and second motor generators are also operated. By changing the axial position of one wheel 30, 32, the speed ratio of this transmission can be increased. Then, the braking force is increased, thereby increasing the amount of power generated by the first and second motor generators 74, 80 and hence the braking force.

Therefore, the transmission according to the fourth embodiment, like the transmissions according to the above-described embodiments, not only exhibits quick response and high transmission efficiency, but also has a large acceleration force when starting and accelerating. Thus, energy can be recovered with high efficiency at the time of deceleration, thereby making it possible to reduce the fuel consumption of the vehicle. It should be noted that the number of motor generators is not limited to two, but may be one or three or more.

FIG. 6 shows a transmission according to a fifth embodiment formed for an electric vehicle.

In this embodiment, a non-rotatable hollow shaft 13 having one end fixed to the housing 10 extends coaxially with the center axis C in place of the input shaft 12 in the above-described embodiment, and the other end is a boss. 14 a and a hollow output shaft 14. The first and second drums 16 and 18, the boss 14 a and the output shaft 14 are rotatably supported on the hollow shaft 13.

The connecting member 20 extends over substantially the entire length of the body 10a of the housing 10 and is supported by the second drum 18 via an axial bearing 22 instead of the boss 14a. A large number of permanent magnets 84 are fixed to the outer periphery of the connecting member 20, and a stator coil 86 is fixed to the inner peripheral surface of the body 10 a opposed thereto. Accordingly, the connecting member 20 functions as a rotor of the motor generator 88, and drives the first drum 16 and thus the first power wheel 30 to rotate. This motor energy In order to make the radiator 88 have a liquid-tight structure, it is necessary to place the first drum 16 between the fixed shaft 13 and the connecting member 20 and the partition plate 11 in the housing 10 respectively A seal member is provided.

Further, a planetary gear set 90 functioning as a final reduction mechanism is arranged in the housing 10 around the output shaft 14 and the rotational output of the output shaft 14 is transmitted to the left and right drive shafts. A differential gear device 92 for transmitting to 94 and 96 is arranged. In the present embodiment, the left and right drive shafts 94, 96 are rotatably supported in the hollow shaft 13. Further, the planetary gear set 90 and the differential gear set 92 are interlocked with each other via a carrier 91 of the planetary gear set 90 and laid out.

In this transmission, when the motor generator 88 is driven, the first drum 16 and the first drum 16 are driven through the rotor, that is, the connecting member 2.ホイール Wheel 30 rotates. Since the center wheel 46 does not rotate, the power roller 40 revolves around the central axis C while rotating, and rotates the second power wheel 32.

In here, the first Pawaro over La 4 0, the second inclined surface 4 0 a, 4 O b in Nono ⁰ Wahoiru 3 0, 3 2 of the engaging portion 3 0 a, 3 2 a; a ^ rotation axis r The trajectory radii drawn at the center are denoted by r 1 and r 2. When the rotation axis r of each roller 40 is parallel to the center axis C, r 2 = r 1, and the first node. The power wheel 30 rotates the second power wheel 32 at a constant speed.

When the first and second power wheels 30 and 32 are moved rightward by the above-described speed ratio changing means, the respective power rollers 40 are inclined rightward so that r 2> r 1. The peripheral speed of the engaging part 3 2a is The speed becomes larger than 30a, and the second No. 3 wheel 32 is accelerated. Conversely, first and second. When the wheels 30 and 32 are moved to the left, the respective power rollers 40 are inclined to the left, so that r 2 <r 1, and the peripheral speed of the engaging portion 32 a becomes the engaging portion 30 a As it becomes smaller, the second power wheel 32 is decelerated and rotates.

When the second power wheel 32 and the second drum 18 rotate, the output shaft 14 rotates, and the planetary gear unit 90 reduces the speed to a predetermined reduction ratio to support a plurality of planetary gears. The differential gear device 9 2 is driven via the carrier 91. In this differential gear device 92, a planetary gear 93 rotatably supported by a carrier 91 revolves around a center axis C, and a sun gear 95 connected to a left drive shaft 94. And the internal gears 9 7 and 9 7 fixed to the right drive shaft 9 6 are rotationally driven.

The axial ball bearing 22 of the present embodiment cancels the reaction force of each of the power wheels 30 and 32 pressing the power roller 40 and also reduces the thrust load acting on the housing 10. . During operation, when the first and second power wheels 30 and 32 rotate at a constant speed, only the thrust load acts on the axial ball bearing 22. The first and second no-wheels 30 and 32 rotate in synchronism with the rotational speed difference generated according to the tilt angle, and large-capacity bearings are mounted on the left and right sides of the housing as in the conventional case. The transmission efficiency is improved by greatly reducing the loss as compared with the case of mounting.

In particular, the latest PM motors for electric vehicles that use permanent magnets are more efficient in the low-speed rotation range than conventional electric vehicle motors. Is excellent, but the starting torque is small, and there is a problem that the efficiency is extremely reduced in the field of weakening in the constant output region and in the high-speed rotation region. The transmission according to the fifth embodiment overcomes the problems of the motor for PM electric vehicles, and satisfies the demands for a highly efficient continuously variable transmission for electric vehicles.

In addition, a space is formed in the rotor of a conventional PM motor for electric vehicles using permanent magnets. The transmission of the present embodiment utilizes the internal space effectively by being housed in this internal space together with the final reduction gear 90 and the differential gear 92. In particular, it is suitable as a drive device for an electric vehicle of an FF (front engine drive / front wheel drive) vehicle which is limited by space.

8 and 9 show a transmission according to a sixth embodiment. In this transmission, the first and second power wheels 30 and 32 are formed integrally with the first and second drums, respectively, and the first and second power wheels 30 and 3 are formed integrally with the first and second drums. the tilting of Nono ⁰ word b over La 4 0 that supported by two rows cormorants also Ru Nodea axial movement of the central wheel Lumpur 4 6.

In the transmission of the present embodiment, a slide-shaped slider 98 that is slidable in the axial direction and relatively non-rotatable is mounted on the input shaft 12 by, for example, a spline. , Through the planetary rollers 4 4. The center wheel 46 supporting the roller 40 is formed integrally with the slider 98.

The slider 98 has a flange portion 98a formed at the end of the input shaft 12 side, and the outer periphery of the input shaft 12 has the flange portion 98a. A cylindrical box portion 100 for receiving 98a is provided. The flange 98a is accommodated in the annular space of the box 100, and the open end of the box 100 is closed with the cover 102. Accordingly, the annular space in the box portion 100 is divided into two pressure chambers 104a and 104b, each of which is formed in a liquid-tight manner. By controlling the pressure fluid supplied from the pressure flow control device to these pressure chambers 104 a and 104 b, the slider 98 and the central wheel 46 become central axes. Move along C, and tilt the power roller 40 about its swing center q. In other words, no. The first and second inclined surfaces 40a and 40b of the word roll 40 form a part of a circle having the swing center q as a base point. In the present embodiment, the box portion 100 is disposed in a concave portion 16b formed in the disk-shaped portion 16b of the first drum 16, and a roller bearing is provided. Thus, the first disk 16 is rotatably supported. The thrust load acting on the first disk 16 is applied to the housing via the support cylindrical portion 106 and the axial bearing 108 connected to the disk-shaped portion 16a. Transmitted to 10 On the other hand, the thrust load acting on the second disk 18 on the opposite side is transmitted from the disk-shaped portion 18a to the boss portion 14 via the ball cam 110 and axially It is transmitted to the housing 10 via the bearing 1 1 2. The pole cam 110 is formed of a normal pressure cam, and generates an axial thrust load according to the size of the tonnolek, and the second disk 18 and therefore the second disk. Automatically adjusts the pressing force of power wheel 40 against power wheel 40. This acts on the first and second disks 16 and 18. These thrust loads cancel each other out in the housing 10 to form a compact and lightweight transmission.

Furthermore, in the present embodiment, a shaft portion 19a extends from the disk-shaped portion 18a of the second disk 18 in the direction of the input shaft 12 and is inserted into the recess of the input shaft 12 to be rotatable. It is supported by. The shaft 18b extending toward the output shaft 14 is inserted into the boss 14a and the output shaft 14 1. Thus, the second disk 18 is supported by the rotation axis on the center axis C together with the input shaft 12 and the output shaft 14. The coil spring 114 accommodated in the boss portion 14 does not act on the second disk when the pressing force of the cam 110 is not acting, that is, when the output shaft 14 is stopped. 1 8 and the second power wheel 3 2 are pressed, whereby all of the nozzles are pressed. Maintain the alignment of the warr rollers 40 and the planetary rollers 44 and secure the torque at the beginning of driving.

This transmission operates in the same manner as the second embodiment shown in FIG. 3, except that the tilting of the power roller 40 is performed through the axial movement of the central wheel 46.

FIG. 10 shows a transmission according to a seventh embodiment.

In the transmission of the present embodiment, the first and second power wheels 30 and 32 and thus the first and second drums 16 and 18 are connected to each other via a transmission mechanism 120 having a constant gear ratio. I have. The boss portion 14a is formed in a solid structure, and the shaft portion 14b is inserted into the concave portions of the center wheel 46 and the input shaft 12, and is rotatably supported. You.

The transmission mechanism 120 in this embodiment is provided outside the output shaft 14. An intermediate gear 1 2 which is rotatably mounted on an external gear 1 2 2 provided on the periphery and a support shaft 1 2 4 protruding from the wall of the connecting member 20, and which is combined with the external gear 1 2 2. 6 and an internal gear 1 28 provided on the output shaft 14 b of the nosing 10 on the side of the output shaft 10 b and corresponding to the intermediate gear 12 6. Thus, the first power wheel 30 functions as a driving force combining mechanism that combines the torque of the first drum 16 and the torque of the output shaft 14.

Therefore, the transmission of the present embodiment is different from the transmission of the second embodiment shown in FIG. 3 in that the driving force splitting mechanism 50 is replaced by a driving force combining mechanism 120 and a first drum 16 and an output shaft 14. The input shaft 12 and the output shaft 14 of the transmission shown in FIG. 3 are reversed. By changing the speed ratio of the transmission mechanism, that is, the driving force synthesizing mechanism 120, it can be used for various applications.

FIG. 11 shows a transmission according to an eighth embodiment.

The transmission according to this embodiment is formed for a wind power generator, and a plate 13 2 of a wind turbine 130 is fixed to an input shaft 12 by, for example, a nut 13 4. . The input shaft 12 is formed integrally with the first drum 16, and the tip 12 a is inserted into the boss 14 a forming the center wheel 46, and is rotatably supported and supported. .

The second wheel 18 is rotatably mounted on the boss 14a via a ball bearing, and projects inward from the lid 10b on the output shaft 14 side of the housing 10. It is rotatably supported on an annular tubular portion 10 c via an axial bearing 22. This The axial bearing 22 supports not only the thrust load of the second drum 18 but also the thrust load of the plate 13 2 acting via the input shaft 12. On the other hand, the thrust load and the radial load acting on the input shaft 12 in the opposite direction are supported by the axial bearing 23 interposed between the input shaft 12 and the lid 10b on the input shaft side. .

The second drum 18 and the input shaft 12 are connected by a driving force branching mechanism 50 which is a speed changing mechanism having a constant speed ratio. A rotatable support shaft 54 is provided on the connecting member 20 fixed integrally with the second drum 18. Therefore, when the input shaft 12 rotates, the intermediate gear 56 is combined with the external gear 56 provided on the input shaft 12 and the internal gear 58 provided on the cover member 10b. Then, it revolves around the central axis C while revolving, and rotates the second drum 18. As a result, the power roller 40 is the first and second nodes. The rotation of the input shaft 12 is transmitted via the wheel 3G, 32, and revolves along the circumferential groove 46a of the central wheel 46 while revolving, via the planetary rollers 44. Rotating the center wheel 4 6, and thus the output shaft 14.

The second drum 18 that transmits the rotation of the input shaft 12 to the power roller 40 together with the first drum 16 has a coil spring 29 disposed in its annular inner hole 28. The coil spring 29 keeps the second power wheel 32 pressed against the power roller 40 with a constant pressing force at all times, and maintains a state in which the power roller 40 and the planetary roller 44 are arranged at equal intervals. As a result, the torque at the initial Can be secured.

On the output shaft 14, a rotor 13 formed by winding a coil 13 around a core 13 is fastened and fixed with a nut 15. The circumference of the rotor 13 is A compact power generator is formed together with a stator 1339 fixed to the inner surface of the body 10a of the housing 10 with a predetermined gap disposed in the housing. This transmission is rotatably mounted on the top of the table T via a turntable 140 so that the blade 132 can always be arranged in the direction of the wind.

According to this transmission, a large thrust load acting via the blade of the wind turbine is transmitted to the axial bearing 22 via the input shaft 12, so that the rotating shaft for the wind turbine and This eliminates the need for thrust bearings, thereby simplifying the power generation device and reducing noise, weight and cost. In addition, the output shaft 14 also functions as a rotating shaft of the generator, thereby reducing the number of parts of the power generation device and reducing the cost. The whole can be reduced in size. Moreover, by moving the first and second power rollers 30 and 32 in the axial direction to control the inclination angle of the power roller 40 with respect to the center axis C, it is possible to respond to the constantly changing wind force. By rotating the rotor 1338 at the optimum gear ratio, the power generation efficiency of the power generator can be improved.

FIGS. 12 and 13 show a transmission according to a ninth embodiment.

In this transmission, the input shaft 12 is formed into a relatively short hollow structure, and the end wall 14 2 provided at the end on the output shaft 14 side is formed. The dry ling 144 extends from the outer edge to form a gap between the outer periphery of the first drum 16. A guide 144 that covers the gap between the first and second power wheels 30 and 32 is formed at the tip of the driving ring 144. The guide 1 46 supports a planetary roller 44 formed in an annular plate-like structure in the present embodiment through a guide groove 1 46 a having an arcuate cross section formed on the inner surface thereof. Further, the planetary roller 44 is supported by a circumferential groove 42 of the power roller 40 and a ridge 42a projecting from a side wall thereof. Therefore, the guide 146 acts as a support wheel that holds the power roller 40 and the planetary roller 44 at equal intervals in the circumferential direction.

In Fig. 13, this guide 1 46 is the planetary roller 4 4 and the nozzle.示す As shown in a state supporting one roller 40, each planetary roller 44 frictionally engages with the peripheral surface formed by the bottom surface of the circumferential groove 42 at the contact point s. The rotation axis p of these planetary rollers 44 is more radially away from the center axis C than the straight line connecting the rotation axes r of the two adjacent power rollers 40. Also, the rotation axis r of each power roller 40 is located further radially outward from the center axis C than the straight line connecting the rotation axes p of the two planetary rollers 44 adjacent to each other.

Each node. When the water roller 40 is urged radially inward toward the center axis C by the action of the first and second inclined surfaces 40a and 40b, the planetary rollers 44 are adjacent to each other. The two power rollers 40 receive equal force from both sides from both sides, and in the radial direction away from the central axis, opposite to the power roller 40 It is urged outward. Then, the planetary roller 44 urged radially outward in this manner frictionally engages with the guide groove 144a and is supported by the guide 144. With this, no ,. Circumferential forces acting on the word rollers 40 and the planetary rollers 44 cancel each other out, and are kept at equal intervals in the circumferential direction about the central axis C.

When the wheels 30 and 32 move in the same direction along the central axis C, each power roller 40 engages a portion separated from the central axis C with respect to the rotation axis r. It is pressed by 30a and 32a, and rotates about the contact point s with the adjacent planetary roller 44. As a result, the engagement portions on the inclined surfaces 40a and 40b

The engagement position of 30a and 32a moves, and the distance from the rotation axis r changes.

Further, the inclination angle of the rotation axis r of each power roller 40 with respect to the center axis C is simultaneously changed to the same angle, and at the same time, the circumferential groove is formed.

Each planetary roller 44 fitted to 42 is also urged by the power roller 40 via the ridge 42a, and the adjacent power roller while maintaining frictional engagement with the guide groove 144a. Rotate all around the same angle around the contact s with 40. As a result, the rotation axis r of the power roller 40 and the rotation axis p of the planetary roller 44 are disposed at substantially the same angle with respect to the center axis C.

Further, in this embodiment, the connecting member 20 extends from the center of the first drum 16 along the center axis C, is connected to the boss 14a, and the nut 17 is placed on the boss 14a. It is connected to the second drum 18 via an axial bearing 22 fixed at the position. Also, A transmission mechanism 120 acting as a driving force synthesizing mechanism for the first and second drums 16 and 18 is disposed in the concave portion of the second drum 18 so that the intermediate gear 12 26 can rotate freely. A supporting shaft 124 supports the second drum 18 and the axial bearing 22 mechanically. The speed change mechanism 120 has an intermediate gear 122 mounted rotatably on a support shaft 124, an external gear 122 provided on a pos part 14a, and a housing 10 provided on a housing 110. And the first and second drums 16 and 18 at a constant speed ratio as a planetary gear device that revolves around the center axis C while rotating. Rotate.

In order to prevent the intermediate gears 126 that are rotatably mounted on the support shafts 124 from falling off, and to prevent the support shafts 124 from moving in the axial direction, the conical shaft bearings of the axial bearings 22 are used. Ring to be accommodated 1 2 5 Force S Screwed to this support shaft 1 2 5

Further, in this transmission, a vane clutch 70 is disposed between the inner peripheral side of the input shaft 12 and the spline shaft 148 connecting the drive shaft of the engine. On the outer peripheral side of the input shaft 12, a motor generator 150 for driving the above-mentioned guide 144 is provided. This motor generator 150 is preferably formed by a PM motor, and a number of permanent magnets 152 are fixed to the inner peripheral side of the extension portion 148 of the driving ring 144, and this is combined with the motor generator 150. The stator coils 154 facing each other with a predetermined gap are attached to a cylindrical support portion 156 projecting inward from the housing lid 1 Ob.

The transmission according to this embodiment shifts in substantially the same manner as the transmission shown in FIG. However, the transmission shown in FIG. While the roller 44 rotates in the opposite direction to the input shaft 12, the transmission of the present embodiment has the idler roller 44 inscribed in the guide groove 144 a of the guide 146. The idler roller 4 rotates in the same direction as the input shaft 12.

In this transmission, the first and second nose urge the power roller 40 from both sides.ホイール Wheels 30 and 32 for power output. The forces are balanced on both sides of the word roller 40 and the planetary rollers 44, so that the alignment of the near roller 40 and the planetary rollers 44 can be ensured. Further, by forming the one-way clutch 70 integrally with the input shaft 12, the connection of the drive shaft such as an engine to the input shaft 12 can be made compact. ·

In addition, since the permanent magnets 152 of the motor generator 150 are arranged on the inner peripheral side of the extension portion 148 of the dry ring 144, the permanent magnets are prevented from being separated and scattered by centrifugal force. It can be prevented reliably. As a result, the motor generator 150 can be rotated at a high speed, the operating radius of the magnetic force can be increased, and the output of the motor generator 150 can be increased, which is suitable for automobiles. It is possible to form a hybrid drive device.

When such a motor generator 150 is incorporated in an automobile, it can be operated as follows through a suitable motor generator control device.

When the vehicle starts and runs at low speed, the fuel consumption is extremely poor due to the low engine speed. For this reason, the motor generator 150, which exhibits high efficiency at low speeds, is supplied from the battery. It is driven by the supplied power. When the engine speed rises above the speed of the input shaft 12 and the drive shaft and the input shaft 12 are connected via the one-way clutch 70, the motor generator The power supply to 70 can be stopped, and the input shaft 12 can be rotationally driven by the engine.

During normal driving, the input shaft 12 is mainly driven by the engine. When the remaining amount of the battery is low, the power supplied to the motor generator 70 is suppressed, and the battery is charged by operating the motor generator 70 as a generator to charge the battery. Prepare to operate the data generator 70. When accelerating during driving, the motor generator 70 is operated as a motor, and the driving force of the motor generator 70 is added to the driving force of the engine. Can also respond to the acceleration required by the driver.

When the vehicle is decelerated, the motor generator 70 operates as a generator, and the power generated at this time is stored in a battery. That is, when the vehicle is decelerated, the accelerator pedal is loosened, and when the rotation speed of the engine is reduced, the one-way clutch 70 separates the drive shaft 60 from the input shaft 12, which causes Then, all the rotating forces acting on the input shafts 12 act on the motor generator 70 as generated energy, and are converted into electric power. The braking energy converted to this electric power is stored in the notifier.

Therefore, similarly to the transmissions in the above-described embodiments, the transmission according to the present embodiment not only exhibits quick responsiveness and high transmission efficiency, but also has a great performance when starting and accelerating. It forms an accelerating force and recovers energy with high efficiency during deceleration, which makes it possible to reduce the fuel consumption of automobiles. Further, by utilizing the pressure difference in the housing 10 to circulate the lubricating oil to the lubricant cooling device 86, there is no need to provide a circulating pump for cooling. The overall structure of the device can be simplified and the weight can be reduced.

The description of the operation in each of the above-described embodiments is an example, and the first and second power wheels 30 and 32, the idle roller 44, the power roller 40, the support wheel, that is, the center wheel 46 or It is clear that various changes can be made depending on the size, size, shape, etc. of guide 146.

Industrial applicability

As described above, according to the transmission of the present invention, a continuously variable transmission that has a simple structure, high transmission efficiency, and is capable of transmitting large power while being lightweight is manufactured at low cost. can do. This makes it possible to support an extremely wide range of industrial uses such as automobiles, ships, construction machinery, agriculture, and power generation.

While the present invention has been described in connection with the preferred embodiments illustrated in the various figures, other similar embodiments may be used to perform the functions of the present invention without departing from the invention. Or, it is clear that the above-described embodiment can be modified and added to it. Therefore, the present invention is not limited to any single embodiment, but has its width and range defined by the claims.

Claims

Range of request

1. The first and second power wheels (30, 30) in which the circular engaging portions (30a, 32a) provided at the tip end are arranged to face each other.

3 2)

It frictionally engages with the engaging portions of these power wheels via the first and second inclined surfaces (40a, 40b) formed at the tapered end portion, and follows these engaging portions. A plurality of first rolling elements (40) that revolve around the center axis (C) of the power wheel while rotating, and frictionally engage with the peripheral surfaces of two first rolling elements adjacent to each other. The plurality of second rolling elements (4) revolving around the center axis (C) of the power wheel while rotating together with the first rolling elements.

4) and

The first rolling elements (44) are frictionally engaged with the peripheral surfaces of the first and second rolling elements (44). The first rolling elements urged in the direction of the center axis (C) of the power wheel by the pressing force of the power wheels (30, 32) are supported via these second rolling elements, A support wheel (46) for holding each of the rolling elements and the second rolling elements at equal intervals in the circumferential direction;

The first rolling element (40) corresponds to at least one axial position of the first and second power wheels (30, 32) and the supporting wheels (46). The inclination with respect to the central axis (C), the engagement position and rotation of the engagement portions (30a, 32a) on the respective inclined surfaces (40a, 40b) corresponding to the inclination. Axis

(r) The distance between and is set, and

One of these first and second power wheels (30, 32) And the supporting wheel (46) via the second rolling element (44) transmits the rotation of the input shaft (12), which is rotationally driven by the driving force source, to the first rolling element (40). The rotation output can be output to the output shaft (14) via the other of the first and second noisy wheels (30, 32) rotated by the first rolling element. A transmission characterized by the following.

2. The support wheel (46) is formed by a center wheel provided on an input shaft (12) concentric with the center shaft (C), and the center wheel is provided with a second rolling element. Guide grooves that roll

The transmission according to claim 1, wherein (46a) is provided on an outer peripheral portion.

3. The driving force branched from the input shaft (12) via the driving force branching mechanism (50) is applied to the first and second power wheels (30,

3. The transmission according to claim 2, wherein the transmission is transmitted to one of (3) and (2).

4. A one-way clutch (70) interposed between the driving force source and a center wheel (46), and a motor (76) connected to the center wheel A first motor generator (74); and the first and second nodes. A second motor generator (80) in which a rotor (82) is connected to one of the power wheels (30, 32); and the other of the first and second power wheels (30, 32). And a clutch (62) interposed between an output shaft (14) driven by the motor and a driven device (60) operated by the output shaft. The transmission according to claim 2, wherein:

5. The support wheel is concentric with the center axis (C). A motor generator (8) formed of a central wheel (46) provided on a non-rotatable hollow shaft, and further having a rotor connected to one of the first and second power wheels (30, 32). 8) and a differential gear device connected to the other of the first and second power wheels (30, 32) and the left and right drive shafts (94, 96).

The transmission according to claim 1, characterized in that:

6. The center wheel (46) is mounted on the input shaft (12) so as to be immovable in the circumferential direction and slidable in the axial direction, and the center shaft (C) of the first rolling element (40) is 3. The transmission according to claim 2, wherein the inclination of the transmission is controlled.

7. The first and second power wheels (30, 32) are interconnected via a speed change mechanism (122) having a constant speed change ratio. 3. The transmission according to claim 1.

8. The support wheel is formed of a guide that surrounds the first and second rolling elements and frictionally engages with the -circumferential surface of the second rolling element, and the other of the first and second power wheels and the output shaft. The transmission according to claim 7, wherein a clutch is interposed between and.

9. First and second power wheels (30, 32) in which the circular engagement portions (30a, 32a) provided at the distal end are arranged to face each other;

It frictionally engages with the engaging portions of these power wheels via the first and second inclined surfaces (40a, 40b) formed on the tapered end, and follows these engaging portions. A plurality of first rolling elements (40) that revolve around the center axis (C) of the wheel, while rotating A plurality of second rolling elements (44) that frictionally engage with the peripheral surfaces of two adjacent first rolling elements and revolve around the center axis of the power wheel while rotating with the first rolling elements. ), And frictionally engage with the peripheral surfaces of these second rolling elements (44). The first rolling elements urged in the direction of the center axis (C) of the power wheel by the pressing force of the power wheels (30, 32) are supported via these second rolling elements, A center wheel (46) coaxially arranged with the center axis, for holding each of the rolling elements and the second rolling elements at equal intervals in the circumferential direction;

The first rolling element (40) is responsive to at least one axial position of the first and second power wheels (30, 32) and the support wheel (46). The inclination with respect to the central axis (C), and the engagement position and rotation of the engagement portions (30a, 32a) on the respective inclined surfaces (40a, 40b) corresponding to the inclination. Axis

(r) The distance between and is set, and

The first and second power wheels are connected to each other via a transmission mechanism having a constant speed ratio, transmit the rotation of the input shaft to the first rolling element, and are rotated via the second rolling element. A transmission that can output rotational output from the center wheel to the output shaft.

10. The transmission according to claim 9, wherein the input shaft is connected to a blade of a windmill, and the output shaft is connected to a rotor of a generator.