JPS5919758A - Traction roller transmission gear - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention provides two traction surfaces that engage each other for the transmission of motion (a fixed ratio such that the applied contact force is dependent on the torque transmitted through the transmission). The present invention relates to a traction roller transmission device.

For example, a traction roller transmission device in which a large contact force is applied to prevent roller slippage is proposed by Harold A.
・“Mechanical Tesine Ant” by Rospert
Systems' Handbook, PP, 14-8 and 14
~9, McGraw-Hill, New York, 1964. The relatively simple arrangement of Figures 14.6 and 14.7 in which the outer ring is made slightly undersized to compress the roller arrangement (in both cases the surface pressure on the traction surface is always is the same, i.e. it is independent of the torque transmitted via the transmission (1 is always high). Also, if the contact pressure of the traction surfaces is Various transmission arrangements are also known, depending on the magnitude of the torque transmitted through the transmission. This type of transmission is disclosed in U.S. Pat.
, No. 212,462, No. 1,704,205, No. 1,
No. 956,934, No. 3,610,060 and Swedish Patent No. 281,542. A transmission including a disc spring on a sun roller or on a traction ring surrounding a planetary roller is disclosed in my earlier U.S. Pat. No. 4. ．． 2
No. 1-5,595.

In a traction roller transmission having coaxial input and output shafts, the sun roller assembly is supported by one of the shafts;
The traction rollers are arranged around the sun roller,
The pulling ring structure surrounds and is in contact with the pulling roller. At least one of the traction ring and the sun roller assembly is arranged between means for urging the disc springs toward each other to engage them with the traction roller and to engage the traction roller with the sun roller and the traction ring assembly. Contains multiple disc springs. The radial surface of the disc spring that engages the traction roller is rounded to reduce wear on the roller surface.

Disc springs are usually slightly conical in shape and when compressed, their radially outer region is under tension and their inner region is compressed so that its inner diameter decreases but its outer diameter increases. ing.

FIG. 1 basically shows a traction roller comprising a sun roller J disposed centrally within a traction ring assembly 3 and a traction roller 2 disposed in an annular passage between the sun roller 1 and the traction ring assembly 3. A roller transmission is shown.

The sun roller 1 is mounted by force or in rotation therewith on the input shaft 1''2, which is part of the input shaft 1''2. The input shaft 12 has a trunnion extending into the bore 22 of the output shaft 21. 14 and is supported by bearings 15.

The output shaft 21 has a flange 23 which, together with an opposite ring structure 24, supports the traction roller 2 in a roller bearing 2.
It is carried on 5.

Ring structure 24 may be connected to flange 23 by studs (not shown) for added stability.

The traction roller 2 is cylindrical and frictionally engaged with the central sun roller.

The traction ring assembly 3 consists of a housing link 31 containing two support ring assemblies 32 containing disc springs 30 with inner traction surfaces 33 engaged with the traction rollers 2. Both axial ends of the housing ring 31 (the two are inner
side cam rings, 35 (two adjacent outer cam rings 34
is installed, and a disc spring 30 is installed between the inner cam ring 35.
is engaged. Both surfaces of the outer cam ring 34 and the inner cam ring 35 have cam surfaces 36 and 37, and within the space C2 between these cam surfaces three rollers or holes are retained to accommodate the inner cam ring 35 and the inner cam ring 35. Housing ring 31 with outer cam link 34
The relative rotational movement with the disc spring 30 causes the inner cam ring 35 and the spring ring housing 32 to approach each other and compresses the disc spring 30 axially, which brings its inner surface 33 into tight engagement with the traction roller 2. It has become.

Reference is now made to my US Pat. No. 4,215,595 for a detailed description of the role features of this basic transmission.

As shown in this patent, the disc spring may be engaged with the sun roller.

The edges of disc springs are typically flat and blunt, and these sharp edges create high surface pressures on the traction roller and traction ring surfaces.

In addition, the core springs must be conically shaped to a certain degree so that they can obtain radial extension when pressed flat.

FIG. 2 shows a section of a conventional disc spring. Its width W
is half the difference between its outer and inner diameters. Its thickness is t, 11 is its deflection height or amount, and θ is the axial deflection angle required to press the disc spring flat. X is the distance between adjacent inner and outer centers of curvature, and y is the axial distance between the centers of curvature (circles) of the disc springs.

The change in width W during axial deflection of the spring ring is Δ.

1 to give a positive Δ, that is, an increase in W when the disc spring is deflected.
1 is y, l:! It turns out that ll must also be large. The maximum Δ that can be achieved for such an arrangement is Δmax = x (]-cos θ) −y sin θ
It is.

FIG. 3 shows an improved Belleville spring in which the half, radially inner and outer ends of the Belleville spring are rounded with radii of curvature r and r2 (y=0), respectively, in accordance with the present invention. Contact between the disc spring and the housing ring or planetary roller occurs along a radiused area. In the arrangement shown in FIG. 3 (2), when θ is zero, i.e. when the spring is pressed flat, Δ is at its maximum value Δmax = x (1-cos θ).

However, X, and therefore Δ, depends on r and r2 since X decreases as rl and r2 increase. rl
For −r2 and x = 0, Δ becomes zero.

However, Δ should be large for a given axial motion, and rl and r2 should be relatively large to provide a relatively small surface pressure and a relatively long life of the transmission.

Figure 4 shows that the radially inner and outer surfaces of the disc spring are formed into a slightly conical shape so that the axially farthest edge of the disc spring contacts the inner roller and outer ring surface in order to provide a relatively large Δ. Give an example. This contacting edge is slightly rounded with radii r and r2 to reduce surface pressure. The maximum radial extension that can be achieved in this example is Δmax = x (1−cosθ
)+ysinθ, which is much thicker than x(1−cosθ) that could be achieved in the example of FIG.

In the example of FIG. 5, r,=r2 and X is equal to zero. However, the centers of curvature are axially C2 apart from each other by y such that the maximum radial extension is Δl1laX ” y Sjnθ.

In this example, the radius of curvature at both contact surfaces is as large as possible, so that the load-carrying capacity of the traction surface is high.

What is shown in FIG. 5 is r,=r2, but other combinations are also possible. For example, rl in the transmission housing link may be very small, and the area of radius r2 in contact with the roller may be relatively large.

If rl is very small, r2 should be close to the value of W so as to reduce the surface pressure on the pulling roller side and provide a very large load capacity.

As shown in FIG. 6, when rl is extremely small and r2 is large but smaller than w-rl, X appears again and the maximum radial extension becomes Δmax = x (1, - CO3θ) + ySinθ. In order to have a long service life of the transmission, the radius of the rolling contact surface should be as large as possible, but the maximum value of r2 is such that when the disc spring is pressed flat, the contact area of the core spring is on the edge of the disc spring. You shouldn't get too close, h
.

It depends on the shape and dimensions of the disc spring, such as t and w. As mentioned above, rl need not be as large as γ2 if it is a region with radius r2 that provides rolling contact with the planetary rollers.

[Brief explanation of drawings]

Fig. 1 is a sectional view of a traction roller transmission device, Fig. 2 is a partial sectional view of a normal disc spring, and Figs. 3 to 6 are partial sectional views of each embodiment of the disc spring. There is a diagram C illustrating various curved shapes. [Explanation of symbols of main parts] 1. Sun roller 2. Traction roller 3..-Traction ring assembly 30. Disc spring

Claims (1)

[Scope of Claims] (1) a traction ring structure having an inner traction surface; a sun roller having a circumferential traction surface disposed centrally within the traction ring structure and spaced apart from the traction surface of the traction ring structure; in the space between the rollers and the traction ring structure (consisting of two supported planetary traction rollers and engagement means for engaging said traction roller with said traction ring structure and said sun roller; At least 1,
The length of the disc spring is 1 m J, 9, and a torque is applied through the transmission to cause a radial extension of the disc spring to bring it into firm frictional engagement with an adjacent traction roller. means for axially compressing the disc spring during transmission, the disc spring having a radial end surface curved in the axial direction C2 to provide rolling contact with the planetary traction roller. 2. In claim 1, the container spring has one of its radially inner and outer surfaces in contact with the support surface and the other in rolling contact with the traction roller; One side is slightly conical in the axial direction of the disc spring (the two-stage protruding edge is in contact with the adjacent roller and the support surface, and the edge in contact with the roller surface is shaped so as to at least reduce wear). 3. A traction-radial transmission device having rounded edges.3 In claim 1, the radially inner and outer surfaces of the Belleville spring are axially C-curved, and the center of curvature of the radially inner and outer surfaces is C-curved. A traction roller transmission device which is spaced apart from each other in the axial direction. In claim 3, the axial distance between the centers of the curved wheels is smaller than the thickness of the disc spring, and the centers are located at two positions within the disc spring. 5. A traction roller transmission device according to claim 4, wherein the radial position of the center of curvature within the disc spring is approximately at the center between the radially inner and outer surfaces of the disc spring. Roller transmission device.6 In claim 2, the radial surface of the disc spring in contact with the traction roller is curved and the central circle of curvature of the radial surface of the opposite...1j defines it. 7. In claim 6: A traction roller transmission, wherein a radial spacing of the center circles of curvature of each of the curved contact surfaces adjacent to the traction roller is at least half the radial width of the disc baffle.