JP3465120B2 - Power transmission device using planetary roller transmission - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a power transmission device for transmitting the rotational power of one shaft to the other shaft by a planetary roller type speed change mechanism while increasing or decreasing the speed.

[0002]

As a power transmission apparatus using the Related Art planetary roller type transmission mechanism, there is shown in FIG. 10, for example. This structure has a fixed ring 2 held in the unit case 1, a small-diameter sun roller shaft 3a protruding from one end of the high-speed rotation shaft 3 and inserted on the central axis of the fixed ring 2, the fixed ring 2 and A plurality of planetary rollers 4 arranged in pressure contact between the sun roller shafts 3a and a planetary roller pin 5 rotatably supporting each planetary roller 4 constitute a planetary roller type speed change mechanism 6, and further a planetary roller pin. The power transmission device 8 is configured by including the low-speed rotating shaft 7 that holds the carrier No. 5 by the carrier flange 7a and the above-described high-speed rotating shaft 3.

The planetary roller type speed change mechanism 6 transmits the rotation to one of the sun roller shaft 3a and the planetary roller 4 by the rotation of one of the sun roller shaft 3a and the planetary roller 4 due to the shearing force of the oil film of the lubricating oil formed on the contact surfaces thereof. It uses a traction power transmission mechanism and functions as a speed increasing device when the low speed rotation shaft 7 that rotates in synchronization with the revolution of the planetary rollers 4 is the input side, and when the high speed rotation shaft 3 is the input side, it slows down. It is designed to function as a device.

In such a structure, the high-speed rotating shaft 3
Due to eccentricity between the low-speed rotation shaft 7 and the low-speed rotation shaft 7, and manufacturing errors of both rotation shafts 3 and 7 and the components of the planetary roller type speed change mechanism 6, the planetary roller 4 is misaligned and both rotation shafts 3 and 7 rotate. Since shake may occur and the entire device may vibrate, it is necessary to wrap the outer peripheral surfaces of the high-speed rotating shaft 3 and the sun roller shaft 3a to perform centering. Since and are long lengths, they are awkward to handle during the lapping process, and even when the sun roller shaft 3a and the planetary roller 4 are replaced due to wear over time, high speed is required. Since the whole including the rotating shaft 3 must be replaced, the replacement cost is high.

Therefore, for example, in Japanese Utility Model Laid-Open No. 4-39351, the sun roller shaft and the high-speed rotation shaft are formed separately,
By connecting the high-speed rotating shaft and the sun roller shaft by screwing, it is possible to easily handle the high-speed rotating shaft when performing the lapping process, and to reduce the replacement cost during the service life of the sun roller shaft at a low cost. I have to.

[0006]

However, in any of the above-mentioned conventional examples, since the basic type is a structure in which the high-speed rotating shaft and the low-speed rotating shaft are constrained in the unit case in the radial direction via bearings, power transmission is performed. When assembled as a device,
It is unavoidable that the high-speed rotating shaft and the low-speed rotating shaft or the three shafts including the sun roller shaft are misaligned, or any one of these shafts is tilted to give an inclination angle. Also, during operation, the high-speed rotating shaft and the low-speed rotating shaft resonate, and the radial load from the mounted parts such as pulleys, milling cutters, and grindstones mounted on the shaft ends of the high-speed rotating shaft and the low-speed rotating shaft,
There is a risk of causing shaft runout by acting as a bending moment for bending these rotary shafts or by forced vibration due to weight imbalance of the mounting component itself.

Further, the misalignment and the inclination angle of each shaft may be caused by uneven wear of the outer peripheral surface of the sun roller shaft or the planetary roller of the planetary roller type speed change mechanism. Angular and radial lateral loads and unbalanced loads due to bending moments act as an overload on the planetary roller type speed change mechanism, high-speed / low-speed rotating shafts, bearings, etc., causing separation and deformation on the outer peripheral surfaces of the sun roller shaft and the planetary roller. This may lead to problems such as an increase in vibration and noise during operation, and rapid wear of the entire device.

Furthermore, when the sun roller shaft and the planetary rollers of the speed change mechanism are replaced due to damage or the like, the entire apparatus must be disassembled and assembled, which requires a great deal of labor and time.

The present invention has been made in view of the above circumstances, and an object of the present invention is to make a manufacturing error of a member constituting a power transmission device and a misalignment of both rotary shafts generated during assembly or operation. Even if there is a tilting angle, a lateral load in the radial direction, or an unbalanced load due to mounted parts, the rotational power can be smoothly transmitted smoothly without causing tilting of the sun roller shaft, and the manufacturing accuracy of the constituent members Power using a planetary roller type speed change mechanism that can ease assembly and assembly accuracy, reduce manufacturing costs and improve durability, and easily disassemble and assemble when repairing or replacing parts in a short time. It is to provide a transmission device.

[0010]

In order to achieve the above-mentioned object, the invention of claim 1 includes a stationary ring and a sun roller shaft projecting from one end of the high-speed rotating shaft and inserted through the central axis of the stationary ring. A plurality of planet rollers arranged in pressure contact between the sun roller shaft and the fixed ring and a planet roller pin that rotatably supports the planet rollers constitute a planet roller type speed change mechanism. The planetary rollers are connected to low-speed rotating shafts that rotate in synchronization with the revolutions of the planetary rollers through the planetary roller pins, and the high-speed rotating shaft and the sun roller shaft are divided so that the sun roller shaft and the sun roller shaft In a power transmission device using a planetary roller type speed change mechanism in which a rotating shaft is connected via a constant velocity universal joint, a first accommodating recess is formed in either one of the high speed rotating shaft and the constant velocity universal joint. hand A first female involute spline is engraved on the inner peripheral surface of the first accommodating recess, and a first male involute spline that meshes with the first female involute spline is engraved on the other outer peripheral surface, and the sun A second accommodating recess is formed in either one of the roller shaft and the constant velocity universal joint, and a second female involute spline is engraved on the inner peripheral surface of the second accommodating recess, and the outer peripheral surface of the other one is formed. Second mating with second female involute spline
Engraving male involute splines of the first and second male involute splines, and performing arc-shaped crowning processing on the tooth flank directions of the tooth crests and the tooth bottoms of both sides of the first and second male involute splines. Both side surfaces of the female involute spline and the tooth crest surface are formed linearly in the tooth trace direction,
Of the male spherical involute spline, a first spherical projection is projected on an end face of the first accommodating recess side of one of the high-speed rotating shaft and the constant velocity universal joint, and the first spherical surface is formed. The protruding portion is brought into contact with the bottom wall of the first accommodating recess, and the second accommodating recess side of either the sun roller shaft engraved with the second male involute spline or the constant velocity universal joint is provided. and projecting a second spherical projection on the end face, brought into contact a spherical projection of the second bottom wall of the second housing recess, the high-speed rotary
Inner and outer races are mounted on bearings that rotatably support the rolling shaft.
Using an angular ball bearing with a steel ball interposed between
Installed on the constant velocity power universal joint side of the angular ball bearing
The bearings that connect the steel balls to the contact points of the inner and outer races
Is a contact angle with the radial line of the high-speed rotation axis
With the straight line and the center axis of the constant velocity universal joint
On the straight line as the point of action,
Tute spline and first female involute spline
The reference contact point where the meshing pitch circles of
To be at the center of the tooth width of the involute spline
The solar roller shaft and the high-speed rotating shaft are connected by a constant velocity universal joint so as to swing and rotate.

The invention of claim 2 is the invention of claim 1.
At, the first spherical protrusion is centered on the point of action.
It is characterized in that it is formed in a spherical shape with a curvature,
Furthermore, the invention of claim 3 is the same as the invention of claim 1 or 2.
The power transmission device and the transmission mechanism unit
Three units, a rotary shaft unit and a low speed rotary shaft unit
It is not possible to divide it by converting it to a high-speed
In either one of the rotary shaft unit and the transmission mechanism unit,
Alternatively, it is characterized by being divided into both and incorporated . Characterized by the fact that it is pivotally supported with respect to the inclination
There is .

[0012]

[Operation] According to such a configuration, misalignment and inclination of the high-speed rotating shaft and the low-speed rotating shaft due to manufacturing errors of components such as the high-speed rotating shaft and the low-speed rotating shaft, bending moments and shaft runout due to mounted parts Since the constant velocity power universal joint absorbs or allows the angle, it is possible to suppress wear of the outer peripheral surface of the sun roller shaft or the planetary roller as much as possible without inclining the sun roller shaft. As a result, the durability of the planetary roller type speed change mechanism itself is improved, and the rotational power is transmitted reasonably and efficiently.

Further, since the power transmission device is divided into three parts, that is, the speed change mechanism unit, the high speed rotary shaft unit and the low speed rotary shaft unit, disassembly and assembly for repairing or replacing parts can be easily performed in a short time. Like

[0014]

Embodiments of the present invention will now be described in detail with reference to the drawings. It should be noted that the same reference numerals are given to the components common to the respective embodiments, and detailed description thereof will be omitted.

1 to 4 show a first embodiment to which the present invention is applied. A power transmission device 20 includes a unit case 24 in which both ends of a cylindrical case 21 are closed by side plates 22 and 23.
Both side plates 22, 23 are arranged on the central axis of the unit case 24.
Of the high-speed rotating shaft 25 and the low-speed rotating shaft 26 which are inserted through the shafts, the planetary roller type speed change mechanism 27 arranged with the both rotary shafts 25, 26 interposed, and the fixing ring 28 of the planetary roller type speed change mechanism 27. Sun roller shaft 2 arranged on the central axis
9 and a gear type coupling 30 that connects the sun roller shaft 29 and the high-speed rotation shaft 25.

Cylindrical housings 31 and 32 are fitted in the cylindrical case 21. The high speed rotating shaft 25 is mounted on the housing 31 via bearings 33 and 34, and the low speed rotating shaft 26 is mounted on the housing 32. They are rotatably supported via 35 and 36, respectively. In the bearings 33 to 36,
Angular ball bearings are used in consideration of the generation of thrust load. Cylindrical case 21, side plates 22 and 23, housings 31 and 3 constituting the unit case 24
2, a refueling passage 37 is continuously formed. Through the refueling passage 37, the high speed rotating shaft 25, the low speed rotating shaft 26,
Lubricating oil is supplied to the planetary roller type speed change mechanism 27, the gear type coupling 30, and the bearings 33 to 36.

A plurality of planet rollers 38 are arranged between the fixed ring 28 and the sun roller shaft 29. Each planetary roller 38 has a planetary roller pin 3 protruding from a carrier flange 26 a formed integrally with one end of the low speed rotation shaft 26.
9 is rotatably supported via a needle bearing 40. The planetary roller type speed change mechanism 27 described above includes a fixed ring 28, a sun roller shaft 29, and a plurality of planetary rollers 38.
And planetary roller pins 39.

In the planetary roller type speed change mechanism 27, the planetary roller 3 is provided on the outer periphery of the sun roller shaft 29 by an input from one of the sun roller shaft 29 and the planet roller pin 39.
8 is rotated and revolved to shift the input, and the sun roller shaft 2
9 and the planetary roller pin 39 are transmitted as an output to the other, and if the low-speed rotary shaft 26 that rotates in synchronization with the revolution of the planetary roller 38 is set as the input side, the power transmission device 20 increases the speed. Function as a high speed rotary shaft 25
Is the input side, the power transmission device 20 functions as a speed reducer.

A first accommodating recess 25a is formed on one end surface of the high-speed rotating shaft 25, and a first female involute spline 25b is formed on the inner peripheral surface of the accommodating recess 25a. Inside the high-speed rotation shaft 25, axial and radial oil supply holes 25c are provided to connect the outer peripheral surface of the high-speed rotation shaft 25 and the first accommodating recess 25a, and an oil supply passage 37 is provided.
Part of the lubricating oil is supplied to the first housing recess 25a.

The gear type coupling 30 connecting the high speed rotating shaft 25 and the sun roller shaft 29 has a first male involute spline 30a meshing with the first female involute spline 25b formed on the outer periphery of one end of the cylindrical body. The first spherical protrusion 30b is provided at one end.
A second male involute spline 29a is engraved on the outer circumference of one end of the sun roller shaft 29, and a second spherical projection 29b is provided on one end of the sun roller shaft 29. A second accommodating recess 30c is formed on the other end surface of the gear type coupling 30, and a second female involute spline 30d that meshes with the second male involute spline 29a is formed on the inner peripheral surface of the accommodating recess 30c. It is carved.

The sun roller shaft 29 has a second male involute spline 29a connected to the second coupling of the gear type coupling 30 .
While meshing with the female involute splines 30d, the distal end of the second spherical shaped projection 29b is brought into contact with the bottom wall of the accommodation recess 30c, one end of which is housed in the second housing recess 30c, the second housing A snap ring 41 is fitted to the open end of the recess 30c to prevent the snap ring 41 from coming off. The gear type coupling 30 having the other end side connected to the sun roller shaft 29 connects the first male involute spline 30 a to the high speed rotation shaft 25.
While engaging with the first female involute spline 25b, the tip of the first spherical protrusion 30b is attached to the high-speed rotating shaft 25.
Is brought into contact with the bottom wall of the first housing recess 25a, one end first
It is housed in the first housing recess 25a, and the snap ring 42 is fitted to the open end of the housing recess 25a to prevent it from coming off.

The tip surfaces of the spherical protrusions 29b and 30b are
The oil supply grooves 29c, 30e are provided in a radial or cross shape, and further, on the central axis of the gear type coupling 30, an oil supply hole 30f is provided so as to communicate both oil supply grooves 29c, 30e. Grooves 29c, 30e, oil supply hole 3
The lubricating oil in the oil supply passage 37 is passed through
5 is forcedly introduced into the bottom wall of the housing recesses 25a and 30c from the oil supply hole 25c, and the involute splines 25b, 30d, 30a and 29a of the male and female are lubricated by the rotational centrifugal force of the high speed rotary shaft 25 and the sun roller shaft 29. , Accommodation recess 2
The oil is discharged from the open ends of 5a and 30a into the oil drop chamber 43.

The snap rings 41 and 42 are provided at a distance from the sun roller shaft 29 and the male involute splines 29a and 30a of the gear type coupling 30, and the high speed rotary shaft 25, the sun roller shaft 29 and the gears. The mold coupling 30 is set so as to be relatively inclined at a certain angle.

High speed rotating shaft 25 and gear type coupling 30
In the female involute splines 25b and 30d, both side surfaces and tooth crests in the tooth trace direction are linear, whereas the sun roller shaft 29 and the male involute splines 29a and 30a of the gear type coupling 30 are respectively. Is crowned on both sides in the tooth trace direction, and when the eccentricity between the high-speed rotation shaft 25 and the sun roller shaft 29 or the relative inclination angle is large, the tooth tip surface and the tooth bottom surface tooth Arc-shaped crowning is applied to both ends in the line direction. These crowning processes are performed on the sun roller shaft 29.
And spherical projections 29b and 30b of the gear type coupling 30
Together with this, each of the high-speed rotation shaft 25, the sun roller shaft 29, and the gear type coupling 30 is allowed to relatively incline within the allowable range. The above-described structure in which the rotary shaft 25 and the sun roller shaft 29 are connected by an involute spline constitutes the constant velocity universal joint 44 of this embodiment.

Next, the mounting positional relationship between the bearing 34 that supports one end of the high-speed rotating shaft 25 and the gear-type coupling 30 that is arranged close to the bearing 34 will be described with reference to FIG.
Steel balls 34a, inner race 34b, and outer race 34 of the bearing 34
A straight line L1 connecting the contact points of c has a certain contact angle α with respect to a radial line such as the high speed rotating shaft 25 or the low speed rotating shaft 26, and the straight line L1 and the central axis CL of the gear type coupling 30. The point of intersection with is the point of action O1, and the male involute spline 30 of the gear type coupling 30 is on the straight line L1.
a and a female involute spline 25 of the high-speed rotating shaft 25
The reference contact point P where the meshing pitch circle of b intersects is the male involute spline 30a of the gear type coupling 30.
The relative positional relationship between the bearing 34 and the gear type coupling 30 is set so as to be at the center position of the tooth width W of. The spherical projection 30b of the gear-type coupling 30 is formed in a spherical shape having a curvature centered on the point of action O1, and when the high-speed rotating shaft 25 and the low-speed rotating shaft 26, which will be described later, are eccentric or inclined, the high speed rotating shaft The rotary shaft 25 and the gear-type coupling 30 make the point of action O1.
Is relatively oscillated around the fulcrum.

When the contact angle α of the bearing 34 is large, the ability to carry the thrust load in the axial direction is large. Further, as described above, the reference contact point P where the meshing pitch circle intersects the straight line L1 is placed at the center position of the tooth width W of the male involute spline 30a, so that the optimum position for the bearing 34 to receive the thrust load. Therefore, the thrust load generated due to the eccentricity and the inclination angle of the high-speed rotating shaft 25, the low-speed rotating shaft 26, and the like can be reasonably and effectively received by the bearing 34.

In a normal state where the high-speed rotating shaft 25 and the low-speed rotating shaft 26 have no eccentricity or inclination angle, no thrust load is generated. Therefore, the relative position between the bearing 34 and the tooth width W of the male involute spline 30a is determined. It doesn't matter what relationship you have. Further, in the present embodiment, the bearings 33 to 36
Since a single row angular contact ball bearing is used for the bearing 3,
By arranging 3, 34 and the bearings 35, 36 symmetrically, it is possible to deal with the thrust loads generated in the axial directions of the high-speed / low-speed rotating shafts 25, 26.

Next, the operation of the gear type coupling 30 will be described.
A description will be given based on FIGS. 1 and 3. Unit case 24
Misalignment in the axial direction during the manufacturing and processing of high-speed rotating shaft 25
Of eccentricity during manufacture, eccentricity during manufacture of the low-speed rotating shaft 26 and the planetary roller type speed change mechanism 27, or wear due to contact between the outer peripheral surface of the planetary roller 38 and the inner peripheral surface of the fixed ring 28 during long-term operation. Similarly, eccentricity may occur between the high-speed rotation shaft 25 and the sun roller shaft 29 due to wear due to contact between the outer peripheral surfaces of both the planet roller 38 and the sun roller shaft 29.

The amount of eccentricity ε is such that a plurality of planet rollers 38 are inscribed inside the fixed ring 28 which has been previously fixed with a strong and appropriate pressure, and on the central axis of the gear type coupling 30, Since the sun roller shaft 29 is in strong pressure contact with the planetary rollers 38 and there is no looseness between them, in the conventional structure, the radial direction eccentricity amount ε, the high speed / low speed rotating shafts 25 and 26 and the sun roller 38 are not used. Since the relative inclination angle of the shaft 29 cannot be tolerated, damage to the outer peripheral surfaces of the sun roller shaft 29 and the planetary roller 38, such as peeling and deformation, is unavoidable. Even if the gear-shaped coupling 30 is tilted, the distance L between the tooth width centers of the male involute splines 29a, 30a in which the sun roller shaft 29 and the gear-shaped coupling 30 are crowned by the inclination of the gear-shaped coupling 30.
2, the inclination angle γ of the gear type coupling 30 itself is
The inclination angle γ = tan-1ε / L2, and the maximum inclination is
The corner portion of the crowned male involute spline 30 a of the gear type coupling 30 is allowed until it hits the snap ring 42.

By inclining the gear type coupling 30 by an inclination angle γ, the male involute spline 2 having an arc shape is formed.
9a and the female involute spline 30d having a linear shape, and the male involute spline 30a having an arc shape.
And the meshing with the linear female involute spline 25b, a sliding phenomenon occurs in which the respective reference contact points P move to the point P'as the gear type coupling 30 rotates. 30 performs swinging rotation about the operating point O1 as the center of rotation and making one reciprocation while drawing a circular arc with an amplitude of 2 × (PP ′) across the reference contact point P.

A slight thrust load is generated by this sliding phenomenon, but this thrust load is damped / suppressed by the damper effect of the lubricating oil supplied to the male and female involute splines 25b, 30d, 29a, 30a. In this way, the eccentricity ε between the high-speed rotation shaft 25 and the sun roller shaft 29 is allowed by the oscillating rotation of the gear type coupling 30, and the rotational power is transmitted to the sun roller shaft 29 and the planetary roller 38 without difficulty. .

Next, the high-speed rotating shaft 25 and the low-speed rotating shaft 26 have natural vibrations that cause temporary vibrations when passing through the primary and secondary resonance points, and forced vibrations due to weight imbalance of each rotating component. The central axis of the rotary shaft 25 is the low-speed rotary shaft 2
A case of inclining at an inclination angle β relative to 6 and the central axis of the sun roller shaft 29 will be described with reference to FIG. 4.

At the inclination angle β between the high-speed rotating shaft 25 and the low-speed rotating shaft 26, the inner race 34b of the bearing 34 is moved to the high-speed rotating shaft 25.
This is allowed by following the inclination of the circular arc male involute spline 30a and the linear female involute spline 25b, and a sliding phenomenon occurs in which the reference contact point P moves to the position of point P '. , High speed rotating shaft 2
5 performs rocking rotation which makes one reciprocation while drawing a circular arc with an amplitude of 2 × (P−P ′) while sandwiching the reference contact point P while making the action point O1 an approximate rotation center. However, in reality, the gear type coupling 30 may also be inclined, and in this case, as shown in FIG. 3, a sliding phenomenon occurs in the meshing of the two positions of the male and female involute splines 25b, 30d, 29a, 30a. The high-speed rotation shaft 25 and the gear type coupling 30 respectively perform separate swing rotations with the point of action O1 as a substantially pivotal fulcrum, and the inclination angle β and the inclination angle of the gear type coupling 30 are allowed. The rotational power is reasonably transmitted to the sun roller shaft 29 and the planetary roller 38.

FIG. 5 is a second embodiment of the present invention showing a modification of the first embodiment. In this embodiment, the engagement of the male and female involute splines of the sun roller shaft 29 and the gear type coupling 30 is as described above. The relationship is opposite to that of the first embodiment.

That is, the first male involute spline 30a, the first spherical projection 30b and the oil supply groove 30e are provided on one end side of the gear type coupling 30 as in the first embodiment, and On the other end side of the gear type coupling 30, a second male involute spline 30g, which is one size smaller than the one end side, a second spherical protrusion 30h, and an oil supply groove 3 are provided.
0i are provided. On the other hand, a second accommodating recess 29d is formed on one end surface of the sun roller shaft 29 so as to have a diameter larger than that of the arc-shaped male involute spline 30g of the gear type coupling 30, and the accommodating recess 29d has a male involute. A second planar female involute spline 29e that meshes with the spline 30g is engraved.

The other end of the gear type coupling 30 has a second
30g of male involute spline with sun roller shaft 2
The second spherical protrusion 30h is inserted into the second female involute spline 29e while being brought into contact with the bottom wall of the second accommodation recess 29d of the sun roller shaft 29 while being accommodated therein. A spacer 50 and a snap ring 51 are attached to the open end of the accommodating recess 29d to prevent them from coming off. In the present embodiment, the gear type coupling 30, the high speed rotation shaft 25 and the sun roller shaft 29 are provided. The involute splines 25b and 29e form a constant velocity power universal joint 52.

On the circumferential wall of the sun roller shaft 29 surrounding the second accommodation recess 29d, a radial oil drain hole 29f is provided instead of the oil feed hole 30f of the gear type coupling 30 of the first embodiment.
Is provided so as to communicate with the bottom of the second accommodation recess 29d. In the first accommodation recess 25a, the lubricating oil in the oil supply passage 37 is forcedly introduced through the oil supply hole 25c of the high-speed rotation shaft 25. contrast, in the second accommodation recess 29d, the lubricating oil of the housing recess 29d bottom, by centrifugal force of the sun roller shaft 29 and the gear-type couplings 30, fills the oil droplets and oil mist from the oil discharge hole 29f oil The oil is discharged into the drip chamber 43, and the bottom of the second accommodating recess 29d is made to have a negative pressure.
3 of the lubricating oil introduced from the open end of the housing recess 29d,
A second male involute splines 30g supplies lubricating oil to the second female involute splines 29e.

FIGS. 6 and 7 show third and fourth embodiments using gear type couplings, as in the first and second embodiments. In the third embodiment of FIG. 6, a separate joint receiver 60 is fixed to one end of the high speed rotation shaft 25 with a bolt 61,
A linear first female involute spline 60b that meshes with the arc-shaped first male involute spline 30a of the gear type coupling 30 is formed on the inner peripheral surface of the first accommodating recess 60a of the joint receiver 60. Thus, the gear type coupling 30, the second male involute spline 29a of the sun roller shaft 29, and the first female involute spline 60b of the joint receiver 60 constitute the constant velocity universal joint 62 of the present embodiment. To be done.

FIG. 7 shows a fourth embodiment to which the present invention is applied.
A gear type coupling 70 and a male joint 71 are used to connect the high-speed rotating shaft 25 and the sun roller shaft 29. In the gear type coupling 70, the center of a cylindrical body 72 having openings at both ends is partitioned by a partition wall 72a to define a first accommodating recess 72b and a second accommodating recess 72c in the cylindrical body 72. First
A linear first female involute spline 72d is engraved on the inner peripheral surface of the accommodation recess 72b of the cylindrical body 7
In the peripheral wall of No. 2, the oil drain hole 72f is formed to penetrate in the radial direction,
It communicates with the bottom of the first accommodating recess 72b. A linear second female involute spline 72e is formed on the inner peripheral surface of the second accommodating recess 72c, and the cylindrical body 72
An oil drain hole 72g is formed in the peripheral wall of the container in the radial direction so as to communicate with the bottom of the second housing recess 72c.

The male joint 71 is provided with a fitting projection 71a for centering and a flange 71b for attachment on one end side, and a first male involute spline 71c similar to the sun roller shaft 29 on the other end side. The male joint 71 includes a first spherical protrusion 71d and an oil supply groove 71e.
Fitting recess 25d provided at the center of one end surface of the high-speed rotation shaft 25
And the flange 71b is fixed to one end surface of the high-speed rotating shaft 25 with a bolt 73.

In the male joint 71, the first male involute spline 71c is meshed with the first female involute spline 72d of the gear type coupling 70, and the first male involute spline 71c is meshed with the first female involute spline 71c.
Of the first spherical projection 71d.
The snap ring 7 fitted to the open end of the housing recess 72b by bringing the tip of the housing into contact with the bottom wall of the first housing recess 72b.
It is prevented from coming off at 4. The sun roller shaft 29 is housed in the second housing recess 72c while meshing the second male involute spline 29a with the second female involute spline 72e of the gear-type coupling 70, and the second spherical projection 29b. The tip end of the second housing recess 72c is brought into contact with the bottom wall of the second housing recess 72c, and the snap ring 75 fitted to the opening end of the housing recess 72c prevents it from coming off.

In this embodiment, the gear type coupling 70 is used.
And the sun roller shaft 29 and the male involute splines 29a and 71c of the male joint 71.
In addition, both the third and fourth embodiments have the same effects as the first embodiment.

In the first to fourth embodiments, the involute spline is used as the fitting element of the constant velocity power universal joints 44, 52, 62, 76, but other than this, a square spline or serration may be used. In this case, the male side splines and serrations are crowned on both sides in the tooth trace direction, and if a larger amount of eccentricity or inclination angle is allowed, the tooth flank direction of the tooth crest and the tooth bottom should be considered. By subjecting both ends to arc-shaped crowning, it becomes possible to reasonably allow for misalignment and inclination.

Next, a fifth embodiment to which the present invention is applied is shown in FIG.
8 and FIG. 9. In addition, this embodiment is described above.
The first embodiment is applied, and if necessary, the first embodiment
Please refer to the description of FIGS. 1 to 4 as appropriate. Power transmission device 1
10 is a high-speed rotating shaft provided in the unit case 111
A unit 112 and low speed shaft unit 113, both Yoo
A gearbox unit incorporated between the units 112, 113.
Consists of three assembly units,
It is

The high speed rotary shaft unit 112 has a side plate with an outer end.
On the central axis of the cylindrical housing 116 closed by 115
In addition, one end of the high-speed rotation shaft 25 has a pair of bearings 33 and 34.
It is rotatably supported via. One end of high-speed rotating shaft 25
In the first accommodation recess 25a of the
The first female involute spline 25b
The high-speed rotary shaft unit 112 is
The gear type coupling 30 is snapped onto the high speed rotating shaft mechanism.
Even the structure restrained by the ring 42 is assembled in advance as an assembly.
It is assembled .

The low speed rotary shaft unit 113 has an outer end.
Inside the cylindrical housing 118 in which the side plate 117 is closed
On the mandrel, one end side of the low speed rotation shaft 26 is provided with a pair of bearings 35,
One end of the low-speed rotation shaft 26, which is rotatably supported via 36.
An accommodation recess 1 for accommodating the speed change mechanism unit 114 at the front.
The low-speed rotating shaft mechanism having the structure of 19 is previously assembled and
And then assembling .

On the other hand, the transmission mechanism unit 114 includes
Roller type transmission mechanism 27 and carrier flange 120.
ing. The planetary roller type speed change mechanism 27 is the same as that of the first embodiment.
Similarly, the fixed ring 28, the sun roller shaft 29, and
It has a star roller 38 and a planet roller pin 39.
A pair of guide rings 12 are provided on both sides of the fixed ring 28.
1, 122 are fixed with bolts 123,
Lubricating oil from the passage 37 is injected by the guide ring 121.
Needle bear on the inner circumference of the planetary roller 38 through the hole 121a
Supply to the ring 40 and both guide rings 121,
At 122, the axial movement of the planetary roller 38 is restricted.
There is .

A second male cable is attached to one end of the sun roller shaft 29.
Involute spline 29a and second spherical protrusion 29
b and an oil supply groove 29c are provided, the sun roller shaft
29 is a stepped portion 29g and a plurality of planets surrounding the outer circumference.
By contact with the roller 38 , transfer to the low speed rotation shaft 26 side
Holds on the central axis of the fixed ring 28 while being restricted in movement
To be done. In addition, the planet roller protruding from the planet roller 38
The outer end of the pin 39 is separated from the low speed rotary shaft unit 113.
Is press-fitted into the plate-shaped carrier flange 120
It

Further, the high speed rotation shaft 2 of the planetary roller pin 39
Fix the cap 124 with the bolt 125 to the shaft end on the 5 side.
As a result, the planetary flange including the carrier flange 120
The locking pin 39 is not locked in the transmission mechanism unit 114.
However, they are integrated into a unit .

The transmission mechanism unit 114 described above is a carrier.
Attach the flange 120 to one end of the low-speed rotary shaft 26
Secure the low speed rotary shaft unit 113 by fixing it with the bolt 126.
It is attached to the container part 119 and further has a high-speed rotating shaft and a low-speed rotating shaft.
The units 112 and 113 of the second are the second rollers of the sun roller shaft 29.
The male involute spline 29a of the
Second female involute spline 30d of ring 30
While engaging with each other, both cylindrical housings 116, 11
8 butts together the housings 116, 118 into a plurality of
It is fixed with a bolt 127 and is integrally connected .

Further , the constant velocity universal joint 128 of the present embodiment.
Is formed on the high-speed rotating shaft 25 of the high-speed rotating shaft unit 112.
A first female involute spline 25b
High speed rotary shaft unit 112 that meshes with the spline 25b.
Gear type coupling 30 assembled to the
Second integrally formed on the sun roller shaft 29 of the knit 114
The male involute spline 29a
The high-speed rotating shaft unit 112 and the transmission mechanism unit 11
By connecting with 4, the constant velocity power universal joint 128 described above is connected.
Configure .

The power transmission device 110 of this embodiment has a high
The high speed rotary shaft unit 112 and the low speed rotary shaft unit 113
Three assembly units with transmission mechanism unit 114
Since it is divided into two parts, it has the same power transmission capability, that is,
Even with the same motor capacity, there is no need to change the output speed.
If it occurs, replace the transmission mechanism unit 114.
The planetary roller 38, the fixed ring 28, and the solar
The rotation ratio with the rotary shaft 29, that is, the gear ratio, can be changed very easily.
can do. In addition, the planetary roller transmission 27
Is a failure of the outer peripheral surfaces of the planetary roller 38 and the sun roller shaft 29.
However, even in this case, the transmission mechanism unit 114
Can be dealt with by exchanging. In addition, other repairs and
Easy to disassemble and assemble the power transmission device
Therefore, the workability in the field is excellent.
There is .

Furthermore, this unitization makes it possible to
Storage management has become easier. In the case of the past, in the case of an emergency
Since it was necessary to replace the entire power transmission device,
Keep the main parts and the finished product of the power transmission device.
However, in the present embodiment, a user with a high failure frequency
It was only necessary to put knits on the stock .

As described above, according to the above-mentioned first to fifth embodiments.
If so, the high-speed rotation axis tilts, and the high-speed rotation axis and the sun roller axis
May tilt relative to each other,
With a constant velocity power universal joint interposed between the high speed rotating shaft and
As the sun roller shaft itself will not tilt,
It is possible to smoothly and efficiently transfer rolling power.
You will be able to .

The fifth embodiment described with reference to FIGS.
Let's move the constant-velocity universal joint to the high-speed rotary shaft unit
Although it was provided separately to the mechanical unit, it is a constant velocity universal joint.
Depending on the configuration of the
Or even if it is built into one of the transmission mechanism units
Good. In addition, this embodiment will be described as an application example of the first embodiment.
As described above, the units of the second to fourth embodiments described above are also similar.
The split case is divided into two, and one of the split unit cases is included.
The high-speed rotary shaft unit and the other of the split unit cases
Built-in between the low speed rotary shaft unit including
3 speed change gear units and 3 assembly units
Separately, further install a constant velocity power universal joint as needed
And the transmission mechanism unit or both
It can also be removed .

Furthermore, the height of the high-speed rotary shaft unit is increased.
As a high-speed rotating shaft mechanism, at least a high-speed rotating shaft and the high-speed rotating shaft
A housing for accommodating one end side of the rotating shaft, and the housing
Bearings that rotatably support the high-speed rotating shaft inside the
The low-speed rotary shaft mechanism that constitutes the low-speed rotary shaft unit
As at least the low speed rotation shaft and one end side of the low speed rotation shaft
And a housing that accommodates the
And a bearing that rotatably supports the rolling shaft .

[0057]

The power transmission device of the present invention includes a high-speed rotating shaft and
The sun roller shaft is divided into the sun roller shaft and the high-speed rotating shaft.
By connecting and via a universal joint for constant velocity power,
Manufacturing error during manufacturing and processing of high-speed rotating shaft and low-speed rotating shaft
Both rotating shafts due to variations in each part that occur during assembly
Eccentricity and tilt angle, high-speed rotation axis when starting / stopping operation
Resonance when passing the primary and secondary resonance frequencies of the low-speed rotating shaft
Deflection of the shaft end due to, or the shaft of high-speed rotating shaft or low-speed rotating shaft
For radial load and weight imbalance applied to the end
Even if there is shaft runout, etc., these defective movements can be performed at a constant speed.
The power coupling absorbs or tolerates tilting on the sun roller shaft.
Rotation force without any trouble
You will be able to communicate to Moose .

Further , the eccentricity and tilt of the high-speed rotating shaft and the low-speed rotating shaft
Since the tilt of the sun roller shaft due to the inclination is avoided,
Roller shaft and the outer surface of the planetary roller are not overloaded,
The durability of the gear shift mechanism is improved. In addition, the power transmission
The manufacturing and assembly precision of each member that composes the equipment is eased.
Manufacturing cost of the entire power transmission device
Can be significantly reduced. Also, precise processing such as lapping
A special alloy that requires less precision and heat treatment
Since parts that use expensive materials such as steel can be shortened,
Handling at the time of production is easy .

Further, the power transmission device described above is rotated at high speed.
Shaft side, low speed rotation shaft side and planetary roller type speed change mechanism
Due to the separate formation in the unit, failure or change in transmission ratio
It is very easy to replace the unit
Can respond. Also, other repairs and maintenance
Since it can be performed easily and easily, especially in the field.
It has excellent workability. In addition, the unit with high replacement frequency
Inventory and storage management should be focused on
It is necessary to keep finished parts of main parts and power transmission devices
There is no .

[Brief description of drawings]

FIG. 1 is a sectional front view of a power transmission device showing a first embodiment of the present invention.

FIG. 2 is an enlarged view of a main part of FIG.

FIG. 3 is an enlarged view of a main part when the high-speed rotating shaft and the sun roller shaft in FIG. 1 are eccentric.

FIG. 4 is an enlarged view of a main part when the high-speed rotating shaft in FIG. 1 is inclined with respect to the low-speed rotating shaft and the sun roller shaft.

FIG. 5 is a sectional view of a main portion of a power transmission device showing a second embodiment of the present invention.

FIG. 6 is a sectional view of an essential part of a power transmission device showing a third embodiment of the present invention.

FIG. 7 is a cross-sectional view of the main parts of a power transmission device showing a fourth embodiment of the present invention.

FIG. 8 is a sectional front view of a power transmission device showing a fifth embodiment of the present invention.

FIG. 9 shows the power transmission device of FIG . 8 disassembled into three units.
Sectional front view

FIG. 10 is a sectional front view showing a conventional power transmission device .

[Explanation of symbols]

20 ... Power transmission device, 21 ... Cylindrical case, 24 ... Unit case, 25 ... High speed rotating shaft, 25a ... High speed rotating shaft 25
A first accommodating recess 25b, a first female involute spline formed on the inner peripheral surface of the first accommodating recess 25a,
26 ... Low speed rotating shaft, 27 ... Planetary roller type speed change mechanism, 28
... a fixed ring of the planetary roller type speed change mechanism 27, 29 ... a sun roller shaft, 29a ... a second male involute spline, 29b ... a second spherical projection, 29c, 30e ... an oil supply groove, 29d ... a second accommodating recess. , 29e ... Second female involute spline, 29f ... Oil drain hole, 30 ... Gear type coupling, 30a ... First male involute spline, 30b ... First spherical projection, 30c ... Second accommodating recess, 30d ... second female involute spline, 30
f ... Refueling hole, 30g ... Second male involute spline, 30h ... Second spherical protrusion, 30i ... Refueling groove, 3
3, 34, 35, 36 ... Bearing, 37 ... Oil supply passage, 38 ...
Planetary rollers, 39 ... planet roller pin, 40 ... Needle bearing, 41 ... snap ring, 43 ... Aburashizukushitsu, 44 ... constant velocity power universal joint, 52 ... constant velocity power universal joint, 60 ... receiving fittings, 60a ... first 1 receiving recess, 60b
... first female involute spline, 62 ... constant velocity power universal joint, 70 ... gear type coupling, 71 ... male joint,
72 ... Cylindrical body, 72a ... Partition wall, 72b ... 1st accommodation recess, 72c ... 2nd accommodation recess , 72d ... 1st female involute spline, 72e ... 2nd female involute
Splines , 72f, 72g ... Oil drain holes, 71a ... Centering fitting projections, 71b ... Mounting flanges, 71c ...
1st male involute spline, 71d ... 1st spherical surface-shaped protrusion, 74, 75 ... Snap ring, 110 ... Power transmission device, 111 ... Unit case, 112 ... High-speed rotating shaft unit, 113 ... Low speed Rotating shaft unit, 114 ... Transmission mechanism unit, 116, 118 ... Housing, 119
... Receiving recess, 120 ... Carrier flanges, 121, 12
2 ... Guide ring, 123, 124, 125, 126,
127 ... Bolt, L1 ... Straight line connecting the contact points of the steel ball 34a of the bearing 34, the inner race 34b, and the outer race 34c, L2 ...
The distance between the tooth width centers of the male involute splines 29a, 30a, the angle of the straight line L1 with respect to the radial line of the high speed rotating shaft 25, the low speed rotating shaft 26, etc., CL ... the central axis of the gear type coupling 30, O1 ... the straight line L1 And the central axis CL intersects with each other at the point of intersection P, the straight line L1, the first male involute spline 30a of the gear type coupling 30 and the second female involute spline 25b of the high speed rotation shaft 25 .
Contact point where the meshing pitch circles of W intersect, W ... tooth width of the first male involute spline 30a, ε ... eccentric amount of the high-speed rotation shaft 25 and the sun roller shaft 29, γ ... inclination angle of the gear-type coupling 30 , Β ... Inclination angle between the high-speed rotating shaft 25 and the low-speed rotating shaft 26

Continuation of front page (56) Reference JP-A-49-13557 (JP, A) JP-A-55-126146 (JP, A) JP-A 64-87923 (JP, A) JP-A 58-211022 (JP , A) Japanese Unexamined Patent Publication No. 50-35558 (JP, A) Actually opened 4-39351 (JP, U) Actually opened 50-509411 (JP, U) Actually opened 3-32241 (JP, U) Actually opened 53-97249 (JP, U) Actually opened 60-103744 (JP, U) Actually opened 59-35759 (JP, U) JP-B 34-6151 (JP, B1) JP-B 45-24724 (JP, B1) (58) Fields investigated (Int.Cl. ⁷ , DB name) F16H 13/08 F16D 3/18

Claims (3)

(57) [Claims] 1. A fixed ring, a sun roller shaft projecting from one end of a high-speed rotation shaft and inserted through the center axis of the fixed ring, and arranged in a pressure contact state between the sun roller shaft and the fixed ring. A plurality of planet rollers and a planet roller pin that rotatably supports the planet rollers constitute a planetary roller type speed change mechanism, and the plurality of planet rollers have a low-speed rotation shaft that rotates in synchronization with the revolution of the planet rollers. A planetary roller type speed change mechanism in which the high speed rotating shaft and the sun roller shaft are divided and the sun roller shaft and the high speed rotating shaft are connected through a constant velocity universal joint, while being connected via the planetary roller pin. In a power transmission device using the above, a first accommodating recess is formed in one of the high-speed rotating shaft and the constant velocity universal joint, and a first female involute spline is formed on an inner peripheral surface of the first accommodating recess. The first male involute spline that meshes with the first female involute spline is engraved on the outer peripheral surface of the other, and the second housing is provided on either one of the sun roller shaft and the constant velocity universal joint. A recess is formed, a second female involute spline is engraved on the inner peripheral surface of the second accommodating recess, and a second male involute spline that meshes with the second female involute spline is formed on the other outer peripheral surface. Engraving is performed on both side surfaces of the first and second male involute splines, the tooth crests and the tooth bottoms in an arc-shaped crowning direction, and both sides of the first and second female involute splines. A first surface of the high speed rotary shaft and a constant velocity power universal joint in which the first male involute spline is engraved. A first spherical projection is provided on the end surface on the accommodation recess side to project the first spherical projection.
The spherical projection of the second housing recess is brought into contact with the bottom wall of the first housing recess, and the second housing recess of any one of the sun roller shaft engraved with the second male involute spline and the constant velocity universal joint. A bearing that rotatably supports the high-speed rotation shaft by projecting a second spherical protrusion on the side end surface, abutting the second spherical protrusion on the bottom wall of the second accommodating recess. In the inner race
Ball bearings with steel balls between the outer race and the outer race
A constant velocity power universal joint among the angular ball bearings
The bearings on the side are made of steel balls and inner and outer races.
The straight line connecting the contact points is to the radial line of the high-speed rotation axis.
It has a certain contact angle and is a universal joint for constant velocity power with the straight line.
The point of intersection with the central axis of
Male involute spline and first female involute
The reference contact point where the meshing pitch circles of the spline intersect,
The center position of the tooth width of the first male involute spline
A power transmission device using a planetary roller type speed change mechanism, characterized in that the sun roller shaft and the high-speed rotation shaft are swingably and rotatably connected by a constant velocity universal joint. 2. The first spherical projection has the point of action
The power transmission device using a planetary roller type speed change mechanism according to claim 1, wherein the power transmission device is formed in a spherical shape having a center of curvature . 3. A transmission mechanism unit for the power transmission device.
And a high speed rotary shaft unit and a low speed rotary shaft unit
Unitized and separable, the constant velocity universal joint
Is either a high-speed rotating shaft unit or a speed change mechanism unit.
The power transmission device using the planetary roller type speed change mechanism according to claim 1 or 2, wherein the power transmission device is incorporated into one or both .