JPS63289363A - Rolling element constituting body for friction type rotational movement transmitting device - Google Patents

Abstract

PURPOSE:To provide a continuously variable transmission the drive efficiency of which is improved, by constituting a fundamental mechanism in which a rolling position between a member on the drive side and a rolling element and a rolling element and a member on the driven side is not moved. CONSTITUTION:Rotation of a rotor 22 rotated synchronously with an input shaft 20 is transmitted to a rolling element 30 through frictional transmission between transmission surfaces 22a and 30a, and receives the static friction force of a stationary rolling surface 13a of a stator 13 to revolve as it is rotated. The other rolling element 31 is also rotated and revolved by means of a rotor 23, and a revolving component rotates an output shaft 21 through rolling element first holding bodies 32 and 33, a rolling element second holding body 34, and a flange 36. The rolling elements 30 and 31 are rolled synchronously with each other through contact of second rolling surfaces 30b and 31b, and a gear can be shifted continuously variably in a range where, by changing an angle of rotation axes l1 and l2 and the rotors 22 and 23 with rolling points T1 and T2, in the case of alpha=0 deg., an output shaft angular speed ratio R is 1 and in the case of alpha=90 deg., R is 0. This constitution enables improvement drive efficiency through saving of a power loss.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a friction-type rotary motion transmission device suitable for use in general power devices such as transmissions, and particularly relates to improvements in the rotor structure thereof. .

[Conventional technology]

A toroidal system is well known as one of the conventional friction type rotary motion transmission devices. The typical principle mechanism is shown in Figure 13 (
The mechanism common to this method, as shown in a) and (b), is that the outer spherical surface of the rolling element operates as the rolling surface of the driving side member and the inner spherical surface of the driven side member as the rolling surface for friction-based rotational motion transmission. For example, in the one shown in FIG.
The rotary motion is transmitted from the driving side to the driven side by interposing the driving side in a freely rotatable state. In a device with such a configuration, a contact force peculiar to friction transmission acts on each rolling and moving surface, but in this case, the rolling element 3 is independently balanced against the contact force. , the contact pressure of the friction surface does not act on the bearing portion 4. However, both the driving side member l and the driven side member 2 are not individually balanced against the contact force on the friction surface, and the device outer box 7 to which the contact force is transmitted via the respective bearings 5.6. is balanced through.

In addition, in the device shown in FIG. 3B, since the shore side of the rolling element 3 is supported by the bearing 8 with respect to the bearing part 4, the driving side member l, Driven side member 2
The rollers 3 and 3 are not balanced on their own, but are also balanced through the device outer box 7 due to the action of contact pressure on the outer number O bearing 8 of the bearings 5 and 6.

[Problem that the invention seeks to solve]

By the way, among the above-mentioned systems that transmit power through friction, the system that rolls the pressure-contacting portion of the transfer element is called a traction drive system, and is distinguished from the belt transmission system. This traction drive system is said to not only have low power transmission efficiency because it causes a relatively large loss of work on the rolling surface.
Since most of the lost work is converted into thermal energy, there is a problem in that local cooling or cooling of the entire device is required to improve the functional strength of the rolling surface. Furthermore, in addition to this, this traction drive system also has the problem that the contact force of the rolling surface for generating the transmitted frictional force affects other components of the device.

In particular, in the device configuration described in FIGS. 13(a) and 13(b), the related components of the contact pressure acting on the bearings 5, 6 or the bearing 8 act as a load on each bearing, and have a large effect on power loss. do. Of course, the power loss in the traction drive mentioned above is unavoidable in principle when using this transmission method, but the power loss in the bearings as other components should be minimized as much as possible in the equipment. It is desirable to increase overall drive efficiency. However, no conventional device has yet been proposed that completely eliminates the influence of such contact pressure on other components from a mechanical standpoint, and the development of such a device is desired.

The present invention has been made in view of the above-mentioned circumstances, and includes a rotational motion transmission device using a traction drive system.
The contact force on the rolling surface required for friction transmission is applied without limit, and the influence is limited to the rolling surface, and the influence of contact pressure that causes power loss on other components, especially bearings, etc. is avoided. It is an object of the present invention to obtain a rolling element structure for a friction type rotary motion transmission device that can improve the driving efficiency of the entire device without any friction.

[Means for solving problems]

In order to achieve the above-mentioned object, the present invention provides a rolling element that does not move the transfer positions of the driving side member and the transfer element, and the transfer element and the driven side member in a traction drive type rotary motion transmission device. The basic mechanism configuration as a structural body is adopted, and all three mechanism elements of the driving side member, the rolling element, and the driven side member are arranged symmetrically and operated, and in particular, the rolling of a pair of symmetrically arranged transfer elements is A direct rolling portion is provided between the children, and the contact pressure of this portion is used to balance the contact pressure of the rolling portion that performs frictional transmission.

[Effect]

According to the present invention, rotational motion is transmitted from the input shaft to the output shaft with variable input and output shaft angular speeds by the rolling friction force between the three mechanical elements consisting of the driving side member, the rolling element, and the driven side member. A contact force acts to obtain the transmission friction force between these three mechanical elements, but this contact force is applied by a threaded spline etc. provided between the input shaft and the drive side member, and each As a result, the contact force acting on each sliding surface does not affect any other components other than the rolling surface, and the power of these other components is reduced. Efficient power transmission is possible by saving losses, and the input shaft angular velocity ratio can be automatically controlled by the rotational speed and transmission torque on the input or output side, and the control characteristics can be selected as appropriate based on the combination in the design. It is possible.

〔Example〕

Hereinafter, the present invention will be explained in detail using embodiments shown in the drawings.

1 to 3 show an embodiment of the friction type rotary motion transmission device according to the present invention, and in these figures, 10 is a housing having a generally cylindrical shape as a whole, and the inside of both ends of the housing 10 is approximately cylindrical. A pair of annular stators 13 and 14 are fixedly provided on the periphery, and side brackets 11 and 12 are fastened with through bolts (not shown) so as to close the openings at both ends of the housing 10. are integrally fixed by means. Furthermore, bearings 15a are provided in the solid shaft hole portions of these side brackets 11 and 12, respectively.

The input shaft 20 and the output shaft 21 are rotatably supported along the same axis via the shaft 15b.

22 and 23 are opposed to each other at a predetermined interval on the input shaft 20, the outer end of which is supported by the bearing 15a, and the inner end of which is extended to a position close to the other bearing 15b. The rotors are a pair of rotors arranged in such a manner that each female threaded spline 24a, 24a is threadedly engaged with a male threaded spline 24b, 24b on the input shaft 20, forming a pair in a direction parallel to the axis of the input shaft 20 of the bracket. Elastic members 25a, 25b
It is placed under the elastic force of.

30.31 are the stator 13.14 and the rotor 22.31.
As is clear from FIGS. 1 to 3, these transfer elements 30, 31 are arranged in sliding contact with the pair of roller first holders 32. 33 to be rotatably held about a first axis "2" (described later), and a second rotor holder 34, which is perpendicular to the first axis, It is rotatably held on two axes. 35 and 36 are arranged outside the rotor 22 and 23 and are the second rotor holder 3.
4 and a flange member integrally constructed with the output shaft 21, one of which flange members 35 is connected to the input shaft 20.
The other flange member 36 is provided on the output shaft 21 and supported by the bearing 15b, and is supported on the input shaft 20 via a bearing 37b. As a result, these components, including the output shafts 20 and 21, are coaxially supported.

Here, the stator 13.14 and the rotor 22.23
The stator rolling surface 13a is in sliding contact with the first rolling surfaces 30a, 31a of the transfer element 30.31.

14a and rotor rolling surfaces 22a and 23a are formed, and the pair of transfer elements 30 and 31 are arranged such that their second rolling surfaces 30b and 31b are in sliding contact with each other.

According to the device having such a configuration, the rolling surfaces provided on each of the above-mentioned members are brought into rolling contact between the different members to generate rotational movement from the input shaft 20 side on the driving side to the output shaft 2 on the driven side.
It can be transmitted to the first side. Here, FIG. 4 is a block diagram showing the rotary motion transmission function of the above-mentioned component device, and each block represents the above-described device component member or a part thereof, and is given a corresponding number. Further, a portion where each block is connected by a solid line indicates a reliable transmission path of rotational motion, and a portion where two solid lines are connected represents a transmission path of rotational motion due to friction. As is clear from FIG. 2, the device of this embodiment is configured to transmit rotational motion through transmission paths by three sets of transfer elements 30, 31, etc., and the dotted chain line in FIG. Three sets of blocks shown are arranged in parallel.

According to such a configuration device, the rotational motion of one of the rotors 22 rotated in synchronization with the input shaft 20 is caused by frictional transmission between the rotor rolling surface 22a and the second rolling surface 30a. 30 to rotate it. Further, this transfer element 30 contacts the fixed rolling surface 13a of the stator 13 at another location on the second rolling surface 30a and receives static frictional force, so that it is rotated while rotating on its own axis. become.

This revolution component is transmitted to the first rotor holder 32, passes through the second rotor holder 34, and the flange 36, and rotates the output shaft 21. Similarly, the rotational movement of the other rotor 23 rotates the transfer element 31, and its revolution component rotates the output M21 via the transfer element first holder 33 and the second rolling element holder 34. I'm letting you do it. Here, □, the transfer elements 30 and 31 rotated in this way always perform a synchronous rolling motion, unlike other contact parts, due to the contact between the respective second rolling surfaces 30b and 31b. Ori,
A contact surface normal force is generated at this contact portion so as to balance the component parallel to the input axis 20 of the friction surface normal force generated in other contact portions due to friction transmission.

Now, the configuration of such an apparatus of the present invention will be explained in detail using FIG. 5 and subsequent figures.

FIG. 5 is for explaining the relationship between the first rolling surface 30a and the second rolling surface 30b in the transfer element 30,
In the figure, reference is a virtual axis passing through the transfer element 30 (hereinafter referred to as the first axis), and P is a fixed point on the rise of this -th axis. Both the first rolling surface 30a and the second rolling surface 30b are formed as surfaces of a puja body determined based on the first axis 9 and the fixed point P, and rl and θl are the same as the first rolling surface 30a and the second rolling surface 30b. - A first radius and a second angle that specify the rolling surface 30a, and r2 and 02 are a second radius and a second spherical angle that specify the second rolling surface 30b. Although this embodiment shows a case where the first radius rl and the second radius r2 are equal, there is no problem with the purpose of the present invention even if they are different. As a matter of course, the first spherical angle θl and the second arc angle θ2 are determined within a range that does not overlap, and the sum of these θ1 and 02 is set to be smaller than one circumferential angle. Ru.

Further, the spherical body portion having the first rolling surface 30a and the spherical body portion having the second rolling surface 30b are integrated via an axis portion 30c parallel to the second axis. Furthermore, 38a,
Reference numeral 38b denotes a bearing provided between the shaft core portion 30c and the boss portion 32a that is integrally provided on the first rotor holder 32, whereby the rotor 30 rotates about the first axis. It is held by the first rolling element holder 32 so as to be freely movable. The rotor first holder 32 also includes a support arm 32c having a support hole 32b with a bearing, and a sector gear 32.
d and a connecting portion 3 that connects these to the boss portion 32a.
2e is the -th axis! ! They are provided in pairs at symmetrical positions in terms of view.

Further, 5m is a virtual axis (hereinafter referred to as a second axis) connecting the centers of the pair of support holes 32b, 32b, and this second axis m is orthogonal to the -th axis line at the fixed point P. Reference numeral 40.40 is a support pin fixed to the second rolling element holder 34, whose center line is aligned with the second axis m, and whose tips are slidably fitted into the support holes 22b and 32b. engaged. As a result, the first rotor holder 32 is held by the second rotor holder 34 so as to be rotatably swingable on the second axis m. Here, the sector gear 32d integrally provided on the first rotor holder 32 has a side surface shape as shown in FIG. When the pitch line tooth profile is projected to be approximately equal to the second spherical arc and parallel to the second line m as shown in the figure, it has a fan-shaped range that approximately overlaps the second line m.

The rolling element 30 and the rolling element first holder 32 as explained above
The structure formed by combining this with the rotor 31 and the first rotor holder 33, which are provided as a pair, has the same structure. The structures formed by these combinations are disposed opposite to each other so that the second rolling surfaces 30b and 31b formed thereon are in contact with each other, and the respective sector gears 32d and 32d are arranged in opposite directions. They are combined in an interlocking state. This state is shown in Figures 7 and 8 (a), (b), (c
) is shown.

Here, in FIG. 7, lines 1 and 2 are first axes, and these are positioned parallel to each other by the second roller holder 34. Pi and r2 are 11 and fL
, 2), the straight line passing through these fixed points P1 and r2 is configured to be orthogonal to the -th axis 1 and 2. ml and m2 are second axes that are orthogonal to the points 1 and 2 at the fixed points P1 and r2. No.-
Along with the axis line intersection l, the rolling element 30 is rotatable about the second axis line m1, and together with the second axis line 2, the transfer element 31 is able to rotate around the second axis line m1.
The sector gear 32b is rotatable about 2 as an axis, and the sector gear 32b is arranged such that the amount of mutual rocking thereof is always equal.

32d is engaged. Also, Fig. 8(a), (
b).

(c) shows a state in which the transfer elements 30 and 31 both have the same amount of rocking, but have different magnitudes of change.

Next, the rotational motion transmission effect of the device configured as described above will be explained. Figures 9(a), (b), and (c) are the first
This is a sectional view taken at the same position as in the figure, but showing a state in which the transfer elements 30, 31 have rotated and changed their positions with respect to their respective first axes.

First, in FIG. 9(a), T1 is the stator rolling surface 13.
a, the contact point between 14a and the first rolling surface 30a, 31a,
T2 is rotor rolling surface 22a, 23a and first rolling surface 30a
, 31a, T3 is the second rolling surface 30b, 31b
It is a point of contact with

In addition, the amount of rotation of the rolling elements 30a and 31a is determined by the straight line PIT2.
Or intersection of the straight line P 2T 2 and the −th axis 1 or 2
It is expressed as the angle formed by n is the common central axis of the input shaft 2o and the output shaft 21 (hereinafter referred to as the third axis), and a l.

a 2 is the distance of T I and T2 from n, and b 1° b 2 is the distance of TI and T2 from 11 or sentence 2. γ is the angle between TI and T2 at Pi or P2. Furthermore, when the angular velocity of the input shaft 20 is represented by ωi, the angular velocity of the output shaft 21 is represented by ωU, and the ratio of input and output shaft angular velocities is represented by R, it is assumed that R=ωU/ωi. Based on these conditions and according to the geometric figure shown in FIG. 9, this R is expressed by the following formula.

R= 1/(c/(sinyacot a-cos
y) + 1)...■ In this formula 0, C is the value of at/a2, which is determined as a constant once the device specifications are determined.

Further, the above equation 0 is a general equation, but if α=900 in the example of FIG. 9(a), it is transformed as follows.

R=17 (C@tan α+1) ”■Figure 9 (b
) is a state in which α=0° in a device where γ=80° as in FIG. In this state, input shaft 2
0 and the output shaft 21 have the same rotational speed, and rotational motion is transmitted thereto.

FIG. 9(C) shows α=90 in the same device as described above.
According to the above equation 0, the value of the input and output shaft angular velocity ratio H is 0. In this state, no rotational motion is transmitted to the output shaft 21 regardless of the rotational speed of the input shaft 20.

Therefore, in this embodiment device, the angle of α shown in FIG. 9(a) is changed from the state of α=06 shown in FIG. Setting an intermediate state, the input and output shaft angular velocity ratio H corresponds to the continuous and stepless change value of α.
It has the ability to continuously and steplessly change the value of from 1 to 0.

Fig. 1θ is a characteristic diagram of changes in R expressed in correlation with α, and the curve in the figure represents the value of the input and output shaft angular velocity ratio H that increases and decreases in correlation with the magnitude of the rotation angle α. ing.

Here, C is a constant a 1/a 2 determined for each device, as described in section 97, and in the embodiment shown in FIG. 9, C=0.
It is 8.

The control means, which has not been discussed in the above explanation, will be explained below. That is, in order to change the output shaft angular velocity ratio R, various means can be considered to give the rotational swing angle α to the transfer element 30, 31, examples of which include:
There is a control means that uses rotational centrifugal force acting on the components of the device. To explain this in detail, in this device, the rotors 30, 31 and the first rotor holder 32, 33 are supported by the second rotor holder 34, and are located at a common center together with the output shaft 21. When rotating around axis n, it is naturally affected by centrifugal force related to this n.

In order to correlate this centrifugal force with the amount of rotation α, the centers of gravity of the transfer element 30.31 and the first rotor holder 32.33 are intentionally placed at positions off the second axes ml and m2. It is. FIG. 11 explains the control of the rotation angle α by this centrifugal force, and Q indicates the point where the total mass of the rotor 30 and the first rotor holder 32 is located, that is, the center of gravity. Roller 3
1 and the center of gravity of the first roller holder 33 is also indicated by Q. If the center of gravity Q or the perpendicular line drawn from the center of gravity Q to Ut or intersection 2 is Pg, then this Pg point is the -th axis line statement 1
Or the first rolling surface 3 is higher than the fixed point P1 or P2 on the vertical position 2.
It is configured to be located biased toward the 0a and 31a sides. F is the vector of centrifugal force, Mf is the centrifugal force F is the second axis m
This is the rotational moment given with respect to l or m2 (which overlaps fixed point P1 or P2 in the figure). In addition, in the figure, 50 is a spiral spring, whose both ends are engaged with the outer periphery of the support arms 32c and 33c of the transfer elements 30 and 31, respectively.
A rotational moment MS due to the elastic force is applied in the direction shown in the figure. The rotational moment due to centrifugal force is in the direction of decreasing the output shaft angular velocity ratio R, and the rotational moment due to the elasticity of the spiral spring 50 is in the direction of increasing R.

The device of this embodiment, in which the rotational moment due to centrifugal force and elastic force acts in the directions as described above, is equipped with an automatic control function for the output shaft angular velocity ratio H based on the output shaft angular velocity ωU. Such an automatic control function can be effectively applied to, for example, a rotational motion transmission device that keeps the output shaft angular velocity ωU substantially constant regardless of the magnitude of the input shaft angular velocity ω i.

, FIG. 12 is for explaining the path in which the contact pressure for friction transmission is balanced, and among the rolling contact points T1, T2, and T3 provided in this device, the stator 13
．． The contact force related to 14 is balanced along the path indicated by the broken line indicated by A in the figure. Further, the contact forces related to the rotors 22 and 23 are balanced along the path indicated by the dashed-dotted line indicated by B in the figure. The characteristics of these balanced paths A and B are that ``the number of components included in this path other than mechanical elements with rolling surfaces is kept to a minimum,'' and ``the path avoids all bearings.'' ``That is.'' Here, the path A includes the housing IO, which is configured to be fixed to the stator 13, 14, so that the only parts that move relative to each other are the rolling contact points Tl and T3. Path B also includes an input shaft 20, which is connected to the rotor 22.23 by a threaded spline. The amount of movement is almost zero, no power loss occurs due to sliding, and the only relatively moving parts are the rolling contact points T2 and T3. In particular, there is an advantage that all the bearings are not subjected to the contact pressure of the friction rolling portion, and as a result, there is no need to use thrust bearings, angular contact bearings, etc., and normal settings can be made.

Note that the present invention is not limited to the structure of the embodiment described above, and the shape, structure, etc. of each part of the device may be modified or changed as appropriate. For example, in the embodiment described in , transferee 30.3
Although we have shown a device using three sets of transfer children, one pair being 1,
The number of sets is not limited and may be freely determined based on the device configuration. In addition, although a configuration has been shown in which the rotation moment due to the centrifugal force acting on the transfer element 30, 31 is opposed by the rotation moment due to the elastic force of the spiral spring 50, the type and shape of the elastic member is not limited to this. It can be selected as follows.

〔Effect of the invention〕

As described below, according to the rolling element structure of the friction type rotary motion transmission device according to the present invention, the drive side member, the transfer element,
In addition, we adopted a basic mechanism configuration that does not move the transfer position between the transfer element and the driven side member, and is configured so that the contact pressure acting on each rolling surface does not adversely affect other components, saving power loss. It is possible to obtain a device, improve its driving efficiency, and have various excellent effects such as, for example, it is possible to obtain a continuously variable transmission device that can automatically control the angular velocity ratio of the output shaft depending on the rotational speed of the output shaft. be. Further, according to the present invention, it can be used, for example, for driving an automobile engine auxiliary machine that requires keeping the output shaft rotational speed constant regardless of the input shaft rotational speed, or for long-term unmanned operation. The benefits are great, as it has many other valuable applications in driving wind power generators.

[Brief explanation of the drawing]

FIG. 1 is a schematic sectional view showing an embodiment of a friction type rotary motion transmission device to which a rolling element structure according to the present invention is applied, and FIGS. 2 and 3 are II-II, m- 4 is a block diagram showing the rotary motion transmission function of the device of this embodiment; FIG. 5 is a partial sectional view illustrating the rolling element;
Figure 6 is a side view seen from the arrow ■ direction in Figure 5, Figure 7 is a sectional view taken along the line ■-■ in Figure 1, and Figures 8 (a) and (b).
, (c) is an explanatory diagram of the operation taken along the line ■-■ in Fig. 7,
Figure 9(a). (b) and (c) are operation explanatory diagrams of the device according to the present invention, the first
Fig. 0 is a functional characteristic diagram of the device of the present invention, Fig. 11 is an explanatory diagram of a mechanism related to rotor rotation angle control, Fig. 12 is a schematic diagram showing a balanced path of contact pressure at rolling contact points, and Fig. 13. (a)
, (b) is a schematic sectional view for explaining a conventional device. 10... Cylindrical housing, 13.14... Stator, 20... Input shaft, 21... Output shaft, 22° 23... Rotor, 30.31... ...Roller, 30
a, 31a--first rolling surface, 30b, 3l
b...second rolling surface, 32.33...roller first holder, 34...roller second holder, 11. u 2
...First axis line, ml, m2...Second axis line, ■・
...Third axis. Figure 1 ■ 10: Hakuji -7 = 22, 23: View #2
1-, k direction @ 34; *,
971-) i 2 'r#, bamboo 4-4th- 2 Figure 4 Figure 6 Figure 7 Figure 8 Figure 9 (a) Figure 9 (b) Figure 9 (C) Figure 10 □α (deg) Figure 11 Figure 13 (a) Figure 13 (b) Procedural amendment (voluntary) 21 Name of invention Roller structure 3 of friction type rotary motion transmission device, Amendment person case and Relationship of patent applicant address: 2-2-3 Marunouchi, Chiyoda-ku, Tokyo. Name (601) Mitsubishi Electric Corporation Representative Moriya Shiki 4, Agent 5, Subject of amendment (1) Detailed explanation of the invention in the specification (2) Brief explanation of the drawings in the specification ( 3) Contents of amendment to Drawing 6 (1) Lines 14-15 of page 2 of the specification: "The outer spherical surface...the inner spherical surface" and "the outer spherical surface and the inner spherical surfaces of the driving side member and the driven side member" and correct it. (2) On page 3, line 5, ``act'' is amended to ``influence.'' (3) On page 3, line 8, "transmitted device outer box" is corrected to "transmitted, device outer box." (4) "In addition to bearings 5 and 6," on page 3, line 14, is corrected to "In addition to bearings 5 and 6." (5) On page 4, line 10, "to other component parts of the device" is corrected to "to other component parts of the device". (6) On page 4, lines 14-15, "Each bearing is affected." is corrected to "It becomes an undesirable load on each bearing, causing power loss." (7) Same page 5, line 3, “Inai Mono de,” is replaced with “I don’t know,”
and correct it. (8) Lines 9 to 17 of page 6, “possible, . The contact force is applied by a threaded spline or the like provided between the drive side member and the raceway member, and is applied to each rolling surface in a sufficient and balanced manner.Then, this contact force is applied to components that involve relative movement other than the rolling surface. The power loss of these other components is saved and efficient power transmission is possible. (9) From page 7, line 19 to page 8, line 2, “At a predetermined interval...
・Threaded together," is defined as "a pair of rotors disposed facing each other with a predetermined interval, the female thread splines 22b and 23b each having a counter threaded direction, and the male thread splines 22b and 23b having mutually counter threaded threads on the input shaft 20. It is corrected by screwing into the splines 24a and 24b. (10) Same page 8, line 7, “suri contact” is changed to “transfer contact”
and correct it. (11) ``Slide contact'' on page 9, line 7, is changed to ``transfer contact''.
and correct it. (12) On page 9, line 10, ``Sliding contact'' is corrected to ``Relocation contact''. (13) Lines 14 to 15 of page 9, “By making contact... with something that can transmit” was changed to “By making contact with the input shaft 20 on the drive side.
"It is capable of transmitting rotational motion from the output shaft 21 side to the output shaft 21 side on the driven side." (14) ``In contact and receiving static friction force'' on page 13, line 9, is corrected to ``in contact.'' (15) Same page 13, line 9 [Support hole 22b, J is corrected as "Support hole 32b, J." (16) Same page 14, line 8 r32d, 32dJ, r32d
, 33dJ. (17) From page 14, line 11 to page 15, line 6, "Here, Figure 7 shows..." is corrected as follows. "Here, in Figure 7, intersection 1 and vertical 2 are the first axes,
These are positioned so that they are always in the same plane by the second roller holder 34. Pl and P2 are fixed points on 11 and 2, respectively, and ml and m
2 is a second axis line that is orthogonal to Sentence 1 and Sentence 2 at the fixed points P1 and P2. Transferee 3 along with 1st axis line view
0 is rotatable and swingable around the second axis vjml, and the rotor 31 is rotatable and swingable around the second axis m2 along with the second axis 2, so that the mutual swing amounts are always equal. Sector gears 32d and 33d are meshed with each other. Moreover, FIGS. 8(a), 8(b), and 8(c) show states in which the rolling elements 30 and 31 both have the same amount of rocking, but change values of different magnitudes. ” (18) Same page 19, line 1, line r, first axis ni” wo, correct to “second axis ml, m2”. (19) Same page 15 line 17 “Rollers 30a, 31a”
"Correct as rolling elements 30 and 31J. (20) Correct "C to at/a2J" and "C to a2/a14" on page 16, line 13. (21) Correct as page 16, line 16 "α=90"``is'' is changed to ``γ
=906, which is J. (22) Correct "constant al/a2" on page 17, line 19, to "constant a2/all." (23) Correct "the perpendicular line" to "perpendicular leg" on page 19, line 1
and correct it. (24) On page 21, line 6, “Settings” should be corrected to “Bearing settings.” (25) ``As a shape'' on page 21, lines 17-18, ``
The shape is corrected. (26) "Continuously variable transmission" in lines 8 and 9 on page 22 is corrected to "continuously variable transmission." (27) ``Cylindrical housing,'' on page 23, line 13, is changed to ``
Housing,” he corrected. (28) Figure 1, Figure 4, Figure 5, Figure 6, Figure 7, Figure 8 (a) to (C), Figure 9 (a) to (C), Figure 11 and Correct Figure 12 as shown in the attached sheet. Figure 9 (a) Figure 9 (b) Figure 9 (C) Figure 11

Claims (1)

[Claims] Based on the first axis and a fixed point on this first axis, the first rolling surface by the spherical surface of the spherical body specified by the first radius and the first spherical arc, and the first axis and the fixed point. a second rolling surface by a spherical surface of a spherical body specified by a second radius having a length that is the same as or different from the first radius, and a second spherical arc that does not overlap the first spherical arc; and holding the rolling element rotatably about the first axis without disturbing the continuity of the uniform spherical surface over the entire surface of each of the first and second rolling surfaces. a first rotor holder having a means for holding the first rotor; a second rotor holder, which is included in a plane perpendicular to the second axis at the fixed point and extends a certain distance larger than at least both of the first and second radii. A rolling element structure of a friction type rotary motion transmission device, characterized in that it is configured to be rotatable about a third axis between it and a second axis.