JPS63289362A - Rolling element constituting body for friction type rotational movement transmitting device - Google Patents

Abstract

PURPOSE:To improve drive efficiency, by a method wherein a direct rolling portion between rolling elements is formed to a pair of rolling elements positioned symmetrically, and the contact pressure of a rolling portion to perform transmission of friction is balanced by means of the contact pressure of the portion. CONSTITUTION:The contact pressure of that, related to stators 13 and 14, of rolling contact points T1, T2, and T3 is balanced in a route shown by a broken line shown in a Fig A. A contact pressure related to rotors 22 and 23 is balanced in a route shown by a one-dotted line shown in Fig B. In which case, in a route A, a housing 10 is contained, but since the housing is formed in a manner to be secured to the stators 13 and 14, a relatively moving part is only the rolling contact points T1 and T3. In a route B, an input shaft 20 is contained, and is spline-joined with the rotors 22 and 23 by means of a screw. The spline joining is for a purpose to converting a rotation force into an axial parallel force, and a movement amount in an axial direction is nearly zero. A power loss due to slide is prevented from incurring, and a relatively moving part is only the rolling contact points T2 and T3.

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. 2(a), the rotor 3 is rotatably interposed between the inner spherical surfaces 1a and 2a of the driving side member l and the driven side member 2, so that the driving It is configured to transmit rotational motion from the side to the driven side. In a device with such a configuration, a contact force peculiar to friction transmission acts on each rolling 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 1 and the driven side member 2 are not individually balanced with respect to the contact force on the friction surface, and the device outer box 7 to which the contact force is transmitted through the respective bearings 5 and 6. is balanced through.

In addition, in the device shown in FIG. 3B, since one side of the rolling element 3 is supported by the bearing 8 with respect to the bearing portion 4, the driving side member 1 and Driven side member 2
The three components, ie, the rotor 3 and the rotor 3, are not balanced individually, but are also affected by contact pressure on the bearing 8 in addition to the bearings 5 and 6, and are balanced via the device outer box 7.

[Problem that the invention seeks to solve]

By the way, among the above-mentioned systems that transmit power using friction, the system that causes the pressure-contacting portions of the rolling elements to roll is called a traction drive system, and is distinguished from the belt transmission system. In this traction drive system, not only is the power transmission efficiency low because a relatively large amount of work loss occurs on the rolling surface, but also most of the loss 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 it is important to minimize the power loss in the bearings as other components as much as possible. It is desirable to increase the driving efficiency of the entire device. 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. The object of the present invention is to obtain a rotor structure for a friction-type rotary motion transmission device in which rotation is eliminated and the driving efficiency of the entire device is improved.

[Means for solving problems]

In order to achieve the above-mentioned object, the present invention 1f provides a rotation that does not move the transfer positions of the driving side member and the rolling element, and the rolling element and the driven side member in a traction drive type rotary motion transmission device. The basic mechanism structure as a rotor structure is adopted, and the three mechanism elements of the driving side member, the rolling element, and the driven side member are arranged symmetrically so that they work, and in particular, a pair of symmetrically arranged rollers. A direct rolling portion is provided between the rolling elements, and the contact pressure of this portion is used to balance the contact pressure of the rolling portion that performs friction transmission.

[Effect]

According to the present invention, rotational motion is transmitted from the input shaft to the output shaft at variable 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 13.14 are fixedly provided on the periphery, and side brackets 11.12 are connected to fastening means such as through bolts (not shown) so as to close the openings at both ends of the housing 10. It is integrally fixed by. 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 on the same axis via L5b.

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, and the rotors form a pair in a direction parallel to the axis of the input shaft 20. Elastic members 25a, 25
It is provided under the elastic force of b.

, 30, 31 are the stator 13, 14 and the rotor 2
2.23 are a pair of rolling elements arranged in sliding contact with each other, and these rolling elements 30.31 are, as is clear from FIGS. The holders 32 and 33 rotatably hold the rotor on a first axis (to be described later), and the second holder 34 rotates the rotor along the first axis via the second holders 32 and 33. It is rotatably held on a second orthogonal axis. 35 and 36 are flange members disposed on the outside of the rotor 22 and 23 and serving as a second rotor holder that is integrally formed with the second rotor holder 34 and the output shaft 21; One flange member 35 is rotatably supported on the input shaft 20 via a bearing 37a, and the other flange member 36 is provided on the output shaft 21 and supported by the bearing 15b. By being supported on the input shaft 20 via the bearing 37b, these components can be connected to the output shaft 20.
21 and 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 rotor 30.31.

14a and rotor rolling surfaces 22a and 23a are formed, and the pair of rollers 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. Furthermore, a portion connected by a single solid line between each block indicates a reliable transmission path of rotational motion, and a portion connected by two solid lines indicates a transmission path due to friction of rotational motion. In the device of this embodiment, as is clear from FIG. 2, three sets of rolling elements 30. , 31, etc., and three sets of blocks shown by the dashed lines in FIG. 4 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. It is transmitted to child 30 and rotates it. Further, since the rolling 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, it is rotated while rotating on its own axis. It turns out.

Then, this revolution component is transmitted to the second rolling element holder 32, and rotates the output shaft 21 through the second rolling element holder 34 and the flange 36, which is the third rolling element holder. Similarly, the rotational movement of the other rotor 23 is caused by the rotation of the rotor 31.
is rotated, and its revolution component rotates the output shaft 21 via the first rotor holder 33 and the second rotor holder 34. Here, the rotor 30.31 rotated in this way
The contact between the respective second rolling surfaces 30b and 31b causes a rolling motion that is always synchronized, unlike other contact parts, and this contact part has a friction force for transmitting friction to other contact parts. Input axis 2 of the friction surface normal force occurring on
A contact surface normal force is generated to balance the component parallel to zero.

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 rolling element 30,
In the same figure, P indicates a virtual axis passing through the rolling element 30 (hereinafter referred to as the first axis), and P indicates a fixed point on which the -th axis rises. The first rolling surface 30a and the second rolling surface 30b are both formed as surfaces of a spherical body determined based on the second axis line and the fixed point P, and rl and 01 are the surfaces of the second rolling surface 30a and the second rolling surface 30b.
The first radius and first spherical angle that specify the rolling surface 30a, and r
2 and 02 are the second radius and 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. Note that, as a matter of course, the first spherical arc θ1 and the second spherical arc θ2 are determined within a range that does not overlap, and these θ
The sum of 1 and 02 is set to be smaller than one circumferential angle. Further, a spherical body portion having a first rolling surface 30a and a second rolling surface 3
The spherical body portion having 0b is integrated through an axis portion 30c parallel to the −th axis line. Furthermore, 38a, 3
Reference numeral 8b denotes a bearing provided between the shaft core portion 30c and the boss portion 32a provided integrally with the rotor holder 32, whereby the rotor 30 rotates with respect to the first axis. It is held by the first rolling element holder 32 so as to be freely movable. The first rotor holder 32 also includes a support arm 32c having a support hole 32b with a bearing, and a sector gear 32d.
and a connecting portion 32 that connects these to the boss portion 32a.
e are provided in pairs at symmetrical positions with respect to the -th axis 1Jiu.

Further, m 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 axis m as shown in the figure, it has a fan-shaped range that approximately overlaps the second axis 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 arranged oppositely 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 FIGS. 7 and 8(a), (b), and (c).

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 1 and 2
- A straight line passing through the fixed points Pi and r2 is configured to be orthogonal to the -th axis intersection 1 and the vertical line 2. ml and m2 are second axes that are perpendicular to the points 1 and fL2 at the fixed points P1 and r2. First axis fL
1 and the rotor 30 are rotatable about the second axis m1, and the rotor 31 and the second axis 2 are rotatable about the second axis m2. sector gear 32b so that they are always equal.

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

(c) shows a state in which both the rotors 30 and 31 have the same swing lid, 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 cross-sectional view taken at the same position as in the figure, but shows a state in which the rolling elements 30 and 31 have been rotated about the straight line connecting fixed points P1 and P2 (hereinafter referred to as the third axis) and have changed their positions. It shows.

First, in FIG. 9(a), T1 is the stator rolling surface 13.
a, the contact point between 14a and the -th rolling surface 30a, 31a, T
2 is the rotor rolling surface 22a, 23a and the -th rolling surface 30a,
The point of contact with 31a, T3 is the point of contact with the second rolling surfaces 30b, 31b.

In addition, the amount of rotation of the rolling elements 30a and 31a is determined by the straight line PIT2.
Alternatively, it is expressed by the angle formed by the straight line P 2T 2 and the -th axis m or intersection 2, and this is indicated by α. n is the common central axis of the input shaft 20 and the output shaft 21 (hereinafter referred to as the fourth axis), and a1゜a2 are TI and T2
The distance from n, b 1゜b 2 is T 1 and T2
It is the distance from 11 or 2. γ is PI or P
It is the angle formed by T1 and T2 in 2. Furthermore, the angular velocity of the input shaft 20 is ω i, and the angular velocity of the output shaft 21 is ωU.
, when the input and output shaft angular velocity ratio is represented by R, R=ωU/ω
Suppose that i. Based on these conditions, the ninth
According to the geometric figure shown in the figure, this R is expressed by the following formula.

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

Further, the above equation 0 is a general equation, but when α=800 in the example of FIG. 9(a), it is transformed as follows.

R=1/(C*tanα+1) -----■Figure 9 (
Similarly to (a) in the same figure, b) is a state in which α=0° in the apparatus where γ=80°, and by the above equation 0, input,
The value of the output shaft angular velocity ratio R is 1. In this state, rotational motion is transmitted to the input shaft 20 and the output shaft 21 at the same rotational speed.

Figure 9(C) shows α-80 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 α shown in FIG. 9(a) is changed from the state of α=0° shown in FIG. In response to the continuous and stepless change value of α, the output shaft angular velocity ratio R
It has the ability to continuously and steplessly change the value of from 1 to 0.

FIG. 10 is a change characteristic diagram of R expressed in correlation with the above-mentioned α, and the curve in the figure represents the value of the input and output shaft angular velocity ratio R 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 FIG. 9, and in the embodiment shown in FIG. 9, C=0.
It is 8.

The control means not mentioned 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 rotor 30, 31 a rotational swing angle α. There are control means using rotational centrifugal force acting. To explain this in detail, in this device, the rolling element 3
0°31 and the first rolling element holder 32,33 are supported by the second rolling element holder 34 and rotate together with the output shaft 21 about the common central axis n. It is under the action of 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 rotor 30.31 and the first rotor holder 32.33 were intentionally removed from the second axes m 1 and m 2 . It's in position. 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.

Similarly, the center of gravity of the rolling element 31 and the first rolling element holding body 33 is Q.
It is shown in If the center of gravity Q or the perpendicular line drawn from the center of gravity Q to the intersection 1 or 2 is Pg, then this Pg point is the -th point.
It is configured to be located on the axis 111 or 2 so as to be biased toward the -th rolling surface 30a, 31a side with respect to the fixed point P1 or P2. F is the vector of the centrifugal force, and Mf is the rotational moment that the centrifugal force F gives with respect to the second axis m1 or m2 (which overlaps the fixed point P1 or P2 in 1 in the figure). In addition, 50 in the same figure is a spiral spring, and the rolling element 30.
31, both ends of which are engaged with the outer periphery of each of the support arms 32c and 33c, and the rotation moment MS is generated by the elastic force of the support arms 32c and 33c.
is applied in the direction shown. The rotational moment due to centrifugal force is in the direction of reducing the output shaft angular velocity ratio R,
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 the centrifugal force and the elastic force acts in the directions as described above, is equipped with an automatic control function for the input and output shaft angular velocity ratio R 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 where the contact pressure for friction transmission is balanced, and shows the transfer contact points T1 provided in this device. Among T2 and T3, 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 10, 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 T1 and T3. Path B also includes an input shaft 20, which is connected to a rotor 22. '23 is joined by a threaded spline, but the purpose of this threaded spline is to convert rotational force into axis-parallel force, and the amount of movement in the axial direction is almost zero, so there is no power loss due to sliding, and the relative The only 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 above, the rolling element 30.
'31 is shown as a pair of rolling elements, but the number of pairs is not limited, and the device configuration is
- can be freely determined from -. In addition, the rolling element 30
．． Although a configuration has been shown in which the rotation moment due to the centrifugal force acting on the spiral spring 31 is opposed by the rotation moment due to the elastic force of the spiral spring 50, the configuration is not limited to this, and the type and shape of the elastic member may be freely selected. It is something.

[Effects of the Invention] □ As explained above, according to the rolling element structure of the friction type rotational motion transmission device according to the present invention, the relationship between the driving side member and the rolling element, and the rolling element and the driven side member is By adopting a basic mechanism configuration that does not move the transfer position, and configuring it so that the contact pressure acting on each rolling surface does not adversely affect other components, a device that saves power loss is obtained, and its drive efficiency is improved. In addition, there are various excellent effects such as being able to obtain a continuously variable transmission device that can automatically control the input and output shaft angular velocity ratios depending on the rotational speed of the output shaft. 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 drawings]

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 m-line cross-sectional view,
FIG. 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, and FIG. 6 is a side view seen from the direction of the arrow ■ in FIG. 5. Fig. 7 is a sectional view taken along the line ■-■ in Fig. 1, and Fig. 8 (a), (b), (
c) is an explanatory view of the operation taken along the line ■-■ in FIG. 7, and FIG. 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. 30a, 31a---first rolling surface, 30b, 3
l b'23... Second rolling surface, 32. 33... Roller first holder, 34... Roller second holder, 35, 36.
...Flange member (roller third holder), Jll. Sentence 2...First axis, ml, m2...Second axis, P IP 2...Third axis, n...Fourth axis.

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 and a second rotor holder are rotated and oscillated about a third axis perpendicular to the second axis on a plane that includes the first axis and is perpendicular to the second axis. a third rotor holder having means for freely holding the rotor, the third holder being parallel to the third axis and larger than at least either the first radius or the second radius; 1. A rotor structure for a friction-type rotary motion transmission device, characterized in that it is provided so as to be rotatable about a fourth axis that is separated by a certain distance from the third axis.