JPH0861450A - Power transmission using planetary roller type gear changing mechanism - Google Patents

Abstract

PURPOSE: To decrease the manufacturing and assembling accuracies of component members of a power transmission and to enable the power transmission to be disassembled and assembled in a short time during repair and replacement of parts by enabling torque to be transferred smoothly and efficiently, while permitting the manufacturing errors of members constituting the power transmission, their decentering and inclination angles, lateral loads in the radial direction, and localized loads produced by mounted parts, etc. CONSTITUTION: A high-speed rotating shaft 25 and a sun roller shaft 29 are split. The sun roller shaft 29 is connected to a geared coupling 30 by engagement of the male involute spline 29a of the sun roller shaft 29 with the female involute spline of the geared coupling 30. The geared coupling 30 is connected to the high-speed rotating shaft 25 by engagement of the male involute spline 30a of the geared coupling 30 with the female involute spline of the high-speed rotating shaft 25.

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]

2. Description of the Related Art As a power transmission device using a planetary roller type speed change mechanism, for example, there is one shown in FIG. 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. The lateral load in the radial direction and the eccentric load due to the bending moment 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 surface of the sun roller shaft and the planetary roller. However, problems such as vibration, noise during operation, and rapid wear of the entire device may occur.

Further, when the sun roller shaft or the planetary roller of the speed change mechanism is 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, in the first invention, a fixed ring, a sun roller shaft projecting from one end of a high-speed rotating shaft and inserted on the central axis of the fixed 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. In a power transmission device using a planetary roller type speed change mechanism in which a low speed rotating shaft that rotates in synchronization with the revolution of these planetary rollers is connected to a roller, the sun roller shaft and the high speed rotating shaft are divided, and the high speed rotating shaft is divided. And the sun roller shaft are connected by a constant velocity universal joint that can freely transmit power at a constant velocity, such as a gear type coupling, a constant velocity ball joint, a universal joint, and a flexible joint. .

In the second invention, the power transmission device is
The planetary roller type speed change mechanism, at least the high-speed rotating shaft, and a housing that accommodates one end side of the high-speed rotating shaft,
A high-speed rotating shaft mechanism including a bearing that rotatably supports the high-speed rotating shaft inside the housing, at least the low-speed rotating shaft, a housing that houses one end side of the low-speed rotating shaft, and inside the housing. The low-speed rotating shaft mechanism including a bearing that rotatably supports the low-speed rotating shaft is divided into three units, that is, a transmission mechanism unit, a high-speed rotating shaft unit, and a low-speed rotating shaft unit.
The constant velocity universal joint may be incorporated into either one of the high speed rotary shaft unit and the speed change mechanism unit, or separately into both the high speed rotary shaft unit and the speed change mechanism unit.

[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 invention to which the first invention is applied.
The 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.
And both side plates 22, on the central axis of the unit case 24,
A high-speed rotating shaft 25 and a low-speed rotating shaft 26 which are inserted through 23, a planetary roller type speed change mechanism 27 which is arranged so as to sandwich the two rotary shafts 25, 26, and the planetary roller type speed change mechanism 2
It has a sun roller shaft 29 arranged on the central axis of the fixing ring 28 of No. 7, and a gear type coupling 30 connecting 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 housing recess 25 is formed on one end surface of the high-speed rotating shaft 25.
a is formed, and a female involute spline 25b is engraved on the inner peripheral surface of the accommodation recess 25a. Inside the high-speed rotation shaft 25, there are oil supply holes 25c in the axial and radial directions.
Is provided so that the outer peripheral surface of the high-speed rotating shaft 25 and the housing recess 25a communicate with each other, and a part of the lubricating oil in the oil supply passage 37 is supplied to the housing recess 25a.

A male involute spline 29a is engraved on the outer periphery of one end of the sun roller shaft 29, and a spherical projection 29b is provided on one end of the sun roller shaft 29. The gear-type coupling 30 connecting the high-speed rotation shaft 25 and the sun roller shaft 29 has a male involute spline 30a engraved on the outer periphery on the one end side of the cylindrical body, and a spherical projection 30b provided on one end and the other end surface. Accommodation recess 30
c is formed, and a female involute spline 30d is engraved on the inner peripheral surface of the accommodation recess 30c.

The sun roller shaft 29 engages the male involute spline 29a with the female involute spline 30d of the gear-type coupling 30 while abutting the tip of the spherical projection 29b against the bottom wall of the accommodating recess 30c. The side is housed in the housing recess 30c, and the snap ring 41 is fitted to the opening end of the housing recess 30c to prevent the housing recess 30c from coming off. The gear type coupling 30 having the sun roller shaft 29 connected to the other end side is configured such that the male involute spline 30 a is meshed with the female involute spline 25 b of the high speed rotating shaft 25 while the tip of the spherical protrusion 30 b is engaged with the high speed rotating shaft 25.
The housing recess 25a is brought into contact with the bottom wall of the housing recess 25a so that one end is housed in the housing recess 25a, and the snap ring 42 is fitted to the open end of the housing recess 25a to prevent the housing recess 25a 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 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 ⁻¹ ε / 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 male involute spline 30a and the spherical projection 3 are provided on one end side of the gear type coupling 30.
0b and the oil supply groove 30e are provided in the same manner as in the first embodiment, and the male involute spline 30g, which is one size smaller than the one end side, is provided on the other end side of the gear type coupling 30.
A spherical projection 30h and an oil supply groove 30i are provided. On the other hand, one end surface of the sun roller shaft 29 has a housing recess 2
9d is formed to have a larger diameter than the arcuate male involute spline 30g of the gear type coupling 30, and the male involute spline 30g is formed in the accommodation recess 29d.
Planar female involute spline 29e that meshes with
Is engraved.

On the other end side of the gear type coupling 30, while inserting the male involute spline 30g into the female involute spline 29e of the sun roller shaft 29, the tip of the spherical projection 30h is accommodated in the sun roller shaft 29. The spacer 50 and the snap ring 51 are accommodated by abutting against the bottom wall of the recess 29d, and are accommodated at the open end of the recess 29d.
In this embodiment, the gear-type coupling 30 and the female involute splines 25b and 29e of the high-speed rotation shaft 25 and the sun roller shaft 29 are attached.
And constitute a constant velocity power universal joint 52.

The sun roller shaft 2 surrounding the accommodation recess 29d.
A radial oil drain hole 29f, which replaces the oil feed hole 30f of the gear type coupling 30 of the first embodiment, is provided on the peripheral wall of 9 in communication with the bottom of the housing recess 29d. While the lubricating oil in the oil supply passage 37 is forcibly introduced through the oil supply hole 25c of the high-speed rotation shaft 25, in the housing recess 29d, the lubricating oil at the bottom of the housing recess 29d is transferred between the sun roller shaft 29 and the gear type coupling 30. Due to the rotational centrifugal force, the oil is discharged from the oil drain hole 29f into the oil drop chamber 43 filled with oil drops or oil mist to make the bottom of the containing recess 29d a negative pressure, and the lubricating oil in the oil drop chamber 43 is opened into the containing recess 29d. It is introduced from the end and the lubricating oil is supplied to the male involute spline 30g and the female involute spline 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,
On the inner peripheral surface of the accommodation recess 60a of the joint receiver 60, the arc-shaped male involute spline 3 of the gear type coupling 30 is provided.
Straight female involute spline 6 meshing with 0a
0b is engraved with the gear type coupling 30 and the male involute spline 29a of the sun roller shaft 29.
And the female involute spline 60b of the joint receiver 60
The above constitutes the constant velocity universal joint 62 of the present embodiment.

FIG. 7 is a fourth embodiment to which the first invention is applied, in which 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. The gear type coupling 70 divides the center of a cylindrical body 72, which is open at both ends, by a partition wall 72a to define two accommodating recesses 72b and 72c in the cylindrical body 72.
On the inner peripheral surface of c, a linear female involute spline 7
2d and 72e are engraved, and on the peripheral wall of the cylindrical body 72,
The oil drain holes 72f and 72g are formed so as to penetrate therethrough in the radial direction and communicate with the bottoms of the housing recesses 72b and 72c.

The male joint 71 has a fitting projection 71a for centering and a flange 71b for mounting on one end side, and a male involute spline 71c similar to the sun roller shaft 29 and a spherical projection on the other end side. The male joint 71 is provided with a portion 71d and an oil supply groove 71e. The male joint 71 fits the fitting protrusion 71a into a fitting recess 25d provided at the center of one end surface of the high-speed rotating shaft 25, and the flange 71b into the high-speed rotating shaft 25. Is fixed to one end surface of the with bolts 73.

The sun roller shaft 29 and the male joint 71 have male involute splines 29a and 71c and female involute splines 72d and 72 of the gear type coupling 70.
It is accommodated in the accommodating recesses 72b and 72c while meshing with the e, and the tips of the spherical projections 29b and 71d are brought into contact with the bottom walls of the accommodating recesses 72b and 72c, so that the accommodating recess 7
Snap ring 7 fitted to the open ends of 2b and 72c
It is retained at 4,75.

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 based on the first invention will be described with reference to FIGS. In this embodiment, a ball joint is used as the constant velocity universal joint 80 that connects the high speed rotating shaft 25 and the sun roller shaft 85e.

This constant velocity universal joint 80 has a cylindrical torque tube 81 and ball holes 81a, 81b formed in the torque tube 81 in two rows of three rows each in the circumferential direction.
, Three steel balls 82, 83 that are rotatably accommodated
An outer ring 84 attached to one end of the torque tube 81 so as to cover the three steel balls 82, and an outer ring 85 attached to the other end of the torque tube 81 to cover the three steel balls 83. There is.

The outer rings 84 and 85 are each formed in a bottomed cylindrical body, and guide shafts 84b and 85b are provided on the central axes of the cylindrical bodies 84a and 85a so as to project therefrom.
b, 85b and the cylindrical bodies 84a, 85a have recesses 84c, 84 having an arc-shaped cross section and long in the axial direction of the outer rings 84, 85.
Three sets of d, 85c, and 85d are provided facing each other inside and outside, and these recesses 84c, 84d, 85c, and 85 are provided.
Steel balls 82 and 83 are housed in d, respectively.

A fitting protrusion 84e for centering and a mounting flange 84f are integrally formed on the bottom of one outer ring 84, and a sun roller shaft 85e with a collar is formed on the bottom of the other outer ring 85. It is formed so as to integrally project. Further, a retaining ring 86 for retaining is fitted to the inner circumference of the opening of the cylindrical body 84a accommodating one end of the torque tube 81 in one outer ring 84, but this retaining ring is omitted in the other outer ring 85. In the constant velocity universal joint 80 before being assembled to the power transmission device 20, the torque tube 81 and the other outer ring 85 are in a temporarily assembled state in which they can be pulled out.

A housing recess 25 is formed on one end surface of the high-speed rotating shaft 25.
e is formed, and further, a fitting recess 25f is formed in the center of the bottom wall of the housing recess 25e.
The fitting protrusion 84e of one outer ring 84 is fitted into the fitting recess 25f of the high-speed rotating shaft 25, and the flange 84f is attached to the high-speed rotating shaft 2.
5, the sun roller shaft 85e integral with the outer ring 85 is fixed to the planetary roller type speed change mechanism 27 by being fixed to the bottom wall of the accommodation recess 25e of the No. 5 with a bolt 87 and arranged so as to project from the end surface of the high speed rotation shaft 25 to the oil drop chamber 43. It is arranged so as to project on the central axis of the ring 28. Since the plurality of planet rollers 38 are arranged in pressure contact with the outer periphery of the sun roller shaft 85e positioned on the central axis of the fixed ring 28, the assembled constant velocity universal joint 80 is
It becomes a non-separable fixed state.

Using the constant velocity universal joint 80 of the present embodiment, for example, a case will be described in which rotational power is transmitted from one outer ring 84 on the high speed rotating shaft 25 side to the other outer ring 85 on the sun roller shaft 85e side. The rotational power of the outer ring 84 is transmitted to the torque tube 81 from the recess 84c of the guide shaft 84b through the three steel balls 82, and the torque tube 81
Is transmitted from the recess 85c of the guide shaft 85b to the other outer ring 85 via the three steel balls 83.

Further, the high speed rotating shaft 25 and the sun roller shaft 85
When a misalignment or a relative tilt angle occurs with e, the torque tube 81 of the constant velocity universal joint 80 tilts to allow this. The allowable amount is determined by the gap C1 between the cylindrical body 84a and the guide tube 81 and the gap C2 between the guide shaft 84b and the guide tube 81 in the one outer ring 84 (see FIG. 11), and the other outer ring 85. Is determined by the gap C3 between the cylindrical body 85a and the guide tube 81 and the gap C4 between the guide shaft 85b and the guide tube 81 (see FIG. 9).

In this embodiment, since the ball joint is used as the constant velocity universal joint 80, the high speed rotary shaft 2
5 and the sun roller shaft 85e are allowed to be misaligned with each other and a relative inclination angle, and rotational power can be smoothly transmitted smoothly. Moreover, since the second moment of inertia of the constant velocity universal joint 80 is small, the transmission loss of rotational power is small,
Efficient transmission can be achieved.

Further, the constant velocity power universal joint 80 of the present embodiment.
Since the retaining ring is omitted on the other outer ring 85, by disengaging the sun roller shaft 85e from the planetary roller type speed change mechanism 27, the constant velocity universal joint 80 becomes a separable temporary assembled state again. Therefore, the constant velocity universal joint 80 can be easily maintained, which is preferable.

As shown in FIG. 8, also in this embodiment, the steel ball 34a of the angular type ball bearing 34 and the operating point O are used.
By locating the center of the steel ball 82 of the constant velocity universal joint 80 on the straight line L1 connecting 1 to 1, the high speed rotation shaft 25 and the sun roller shaft 85e are misaligned or relative to each other, as in the first embodiment. It is desirable that the bearing 34 can reasonably and effectively receive the thrust load generated at a large inclination angle.

Next, a sixth embodiment to which the first invention is applied,
It will be described with reference to FIG. In this embodiment, a double cross joint type universal joint is used as the constant velocity universal joint 90 that connects the high-speed rotating shaft 25 and the sun roller shaft 93a. Constant velocity power universal joint 90
Has two shafts 92, 93 pivotally supported at cross points O2, O3 of the intermediate body 91 so as to be swingable with respect to a relative inclination, and one shaft 92 has a fitting shaft 92a. And a flange 92b are integrally formed, and a sun roller shaft 93a is integrally formed on the other shaft body 93.

A large-diameter housing recess 25g and a small-diameter fitting recess 25h are connected to one end surface of the high-speed rotation shaft 25. Male and female involute splines are engraved on the fitting recess 25h of the high-speed rotating shaft 25 and the fitting shaft 92a of the shaft 92. The fitting shaft 92a is press-fitted into the fitting recess 25h and spline fitted to a position where the fitting shaft 92a abuts the bottom wall of the housing recess 25g. A sun roller shaft 93 a, which is integral with the body 93, is arranged so as to project on the central axis of the fixed ring 28 of the planetary roller type speed change mechanism 27.

Also in this embodiment, one shaft 9
It is desirable that the second cross point O2 coincides with the action point O1 of the bearing 34 so that the bearing 34 can reasonably and effectively receive the thrust load generated by the misalignment and the relative inclination angle.

FIGS. 13 and 14 show a seventh embodiment to which the first invention is applied. A flexible joint is used as the constant velocity universal joint 100. The constant velocity universal joint 100 is
Couplings 101 and 102 and both couplings 10
It is composed of a power transmission material 103 which is sandwiched between 1 and 102.

The couplings 101 and 102 are made of a rigid material such as metal and have three claw pieces 101a and 102a which are fitted alternately. One of the couplings 101 has a housing recess 25 for the high-speed rotating shaft 25.
flange 10 attached to the bottom wall of i with bolts 104
1b is integrally formed, and the other coupling 102 is
The sun roller shaft 102b is integrally formed.

The power transmission material 103 is made of tetrafluoroethylene resin, polyurethane rubber, silicone rubber, acrylic rubber or the like having oil resistance, elasticity, allowable surface pressure, and heat resistance.
It is formed in the shape of a plate-shaped star and has couplings 101, 1
The two claw pieces 101a and 102a of No. 02 can be compressed and deformed according to the misalignment between the high-speed rotation shaft 25 and the sun roller shaft 102b and the relative inclination angle.

When the constant velocity universal joint 100 is assembled to the power transmission device 20, the power transmission material 103 is used.
It is preferable to match the width center O4 of the above with the point of action O1 on the straight line L1 from the same idea as in the above-described respective embodiments.

Next, an eighth embodiment to which the second invention is applied,
A description will be given based on FIGS. 15 and 16. The present embodiment is an application of the above-described first embodiment, and FIGS. 1 to 4 of the first embodiment should be appropriately referred to as necessary. Power transmission device 1
Reference numeral 10 includes three assembly units including a high-speed rotary shaft unit 112 and a low-speed rotary shaft unit 113 provided in the unit case 111, and a transmission mechanism unit 114 incorporated between the units 112 and 113.

The high-speed rotating shaft unit 112 is rotatably supported by one end of the high-speed rotating shaft 25 via a pair of bearings 33, 34 on the central axis of a cylindrical housing 116 whose outer end is closed by a side plate 115. ing. A female involute spline 25b with which the gear-type coupling 30 meshes is engraved in the housing recess 25a at one end of the high-speed rotating shaft 25. The high-speed rotating shaft unit 112 includes the gear-type coupling 30 in the high-speed rotating shaft mechanism. The structure up to which the snap ring 42 is constrained is assembled in advance as an assembly.

Further, the low-speed rotation shaft unit 113 has a pair of bearings 35 on one end side of the low-speed rotation shaft 26 on the central axis of a cylindrical housing 118 whose outer end is closed by a side plate 117.
An accommodation recess 1 that rotatably supports the transmission mechanism unit 114 and accommodates the transmission mechanism unit 114 in front of one end of the low-speed rotation shaft 26.
The low-speed rotating shaft mechanism having the structure of 19 is preassembled as an assembly.

On the other hand, the speed change mechanism unit 114 is composed of a planetary roller type speed change mechanism 27 and a carrier flange 120. The planetary roller type speed change mechanism 27 has a fixed ring 28, a sun roller shaft 29, a plurality of planetary rollers 38 and a planetary roller pin 39, as in the first embodiment.
A pair of guide rings 12 are provided on both sides of the fixed ring 28.
1, 122 are fixed by bolts 123, and the lubricating oil from the oil supply passage 37 is supplied to the needle bearing 40 on the inner circumference of the planetary roller 38 through the oil supply injection holes 121a of the guide ring 121. ，
At 122, the movement of the planetary roller 38 in the axial direction is restricted.

At one end of the sun roller shaft 29, a male involute spline 29a, a spherical projection 29b, and an oil supply groove 2 are provided.
9c is provided, and the sun roller shaft 29 is fixed while being prevented from moving toward the low-speed rotation shaft 26 by the contact between the step portion 29g and the plurality of planet rollers 38 surrounding the outer circumference. It is held on the central axis of the ring 28. Further, the outer end of the planetary roller pin 39 protruding from the planetary roller 38 is press-fitted into a plate-shaped carrier flange 120 separated from the low speed rotation shaft unit 113.

Further, the high-speed rotating shaft 2 of the planetary roller pin 39
By fixing the cap 124 to the shaft end on the fifth side with the bolt 125, the planetary roller pin 39 including the carrier flange 120 is integrally held while being retained by the transmission mechanism unit 114.

The above-described transmission mechanism unit 114 has the carrier flange 120 fixed to one end of the low speed rotation shaft 26 with a plurality of bolts 126, and is assembled in the housing recess 119 of the low speed rotation shaft unit 113. And the units 112 and 113 of the low-speed rotation shaft, the male involute splines 29a of the sun roller shaft 29 are meshed with the female involute splines 30d of the gear-type coupling 30, while the cylindrical housings 116 and 118 are butted to each other. , 118 with multiple bolts 12
It is fixed at 7 and connected integrally.

Further, the constant velocity universal joint 128 of the present embodiment.
Is a female involute spline 25b formed on the high-speed rotating shaft 25 of the high-speed rotating shaft unit 112, a gear-type coupling 30 which is engaged with the high-speed rotating shaft unit 112 by meshing with the spline 25b, and a transmission mechanism unit 114. It is composed of a male involute spline 29a integrally formed with the sun roller shaft 29, and the above-mentioned constant velocity universal joint 128 is constituted by connecting the high speed rotary shaft unit 112 and the speed change mechanism unit 114.

Since the power transmission device 110 of this embodiment is divided into three assembly units, that is, the high-speed rotation shaft unit 112, the low-speed rotation shaft unit 113, and the speed change mechanism unit 114, the power transmission device 110 has the same power transmission capability. That is, when the output rotation speed needs to be changed even with the same motor capacity, the transmission mechanism unit 114 is replaced to change the rotation ratio of the planet roller 38, the fixed ring 28, and the sun roller shaft 29, that is, The gear ratio can be changed extremely easily. Further, in the planetary roller type speed change mechanism 27, the outer peripheral surfaces of the planetary roller 38 and the sun roller shaft 29 are relatively frequently damaged.
Can be dealt with by exchanging. Furthermore, for other repairs and maintenance, the power transmission device can be easily disassembled and assembled, and therefore workability is particularly excellent in the field.

Further, this unitization facilitates inventory / storage management. Further, in the conventional case, since it was necessary to replace the entire power transmission device in an emergency, it was necessary to store the main parts and finished products of the power transmission device, but in the present embodiment, It became possible to focus on the inventory of units with high failure frequency.

As described above, according to the above-described first to eighth embodiments, even if the high-speed rotation shaft tilts and the high-speed rotation shaft and the sun roller shaft tilt relatively, the sun roller shaft The sun roller shaft itself is not tilted by the constant velocity universal joint interposed between the high speed rotary shaft and the high speed rotary shaft, so that the rotary power can be smoothly and efficiently transmitted.

In the eighth embodiment in which the second invention has been described with reference to FIGS. 15 and 16, the constant velocity universal joint is divided into the high speed rotary shaft unit and the transmission mechanism unit. Depending on the structure of the power universal joint, the entire power universal joint may be incorporated into either the high speed rotary shaft unit or the speed change mechanism unit. Further, as described in the present embodiment as an application example of the first embodiment, similarly in the above-mentioned second to seventh embodiments, the unit case is divided into two, and the high-speed rotating shaft including one of the divided unit cases. Unit, a low-speed rotary shaft unit including the other of the split unit cases, and a speed change mechanism unit incorporated between the two units, and is further divided into three assembly units. It is also possible to divide and install in one or both of the mechanical units.

Further, as a high speed rotating shaft mechanism constituting the high speed rotating shaft unit, at least a high speed rotating shaft, a housing accommodating one end side of the high speed rotating shaft, and a high speed rotating shaft rotatably supported inside the housing. Bearing and
Further, as a low speed rotating shaft mechanism constituting the low speed rotating shaft unit, at least a low speed rotating shaft, a housing that accommodates one end side of the low speed rotating shaft, and a bearing that rotatably supports the low speed rotating shaft inside the housing. Shall be included.

[0074]

According to the power transmission device of the present invention, 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 the constant velocity universal joint, so that the high speed rotation is achieved. Shaft and low-speed rotary shaft manufacturing error during manufacturing, eccentricity and inclination angle of both rotary shafts due to variations in each component that occur during device assembly, primary of high-speed rotary shaft and low-speed rotary shaft at start / stop of operation・ Even if there is bending of the shaft end due to resonance when passing the secondary resonance frequency, or radial runout applied to the shaft end of a high-speed rotating shaft or a low-speed rotating shaft, or shaft run-out due to weight unbalance, etc. Since the constant velocity power joint absorbs or allows the defective movement, it becomes possible to smoothly and efficiently transmit the rotational power smoothly without giving an inclination to the sun roller shaft.

Further, since the inclination of the sun roller shaft due to the eccentricity and inclination of the high-speed rotating shaft and the low-speed rotating shaft is avoided, there is no overload on the outer peripheral surfaces of the sun roller shaft and the planetary rollers, and the planetary roller type speed change mechanism is not affected. The durability is improved. Further, since it is possible to relax the processing precision and the assembly precision of each member constituting the power transmission device, it is possible to significantly reduce the production cost of the entire power transmission device. In addition, the number of locations that require precise processing precision such as lapping and heat treatment is reduced, and parts that use expensive materials such as special alloy steel can be shortened, so that handling at the time of production can be easily performed.

Further, since the above-mentioned power transmission device is divided into three units, that is, the high-speed rotating shaft side, the low-speed rotating shaft side, and the planetary roller type speed change mechanism, in case of failure or change of gear ratio, the unit is replaced. It can be handled with an extremely simple work of just doing. Further, since other repairs and maintenance can be performed easily, the workability in the field is particularly excellent. Further, it suffices to focus on inventory and storage management of units that are frequently replaced, and there is no need to store main parts and finished products of power transmission devices as in the conventional case.

[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 is a sectional front view of a constant velocity power universal joint used in a fifth embodiment.

10 is a sectional view taken along line XX of FIG.

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

FIG. 12 is a sectional front view of a power transmission device showing a sixth embodiment of the present invention.

FIG. 13 is a sectional front view of a power transmission device showing a seventh embodiment of the present invention.

FIG. 14 is an exploded perspective view of a constant velocity power universal joint used in a seventh embodiment.

FIG. 15 is a sectional front view of a power transmission device showing an eighth embodiment of the present invention.

16 is a sectional front view of the power transmission device of FIG. 15 disassembled into three units.

FIG. 17 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 ... Receiving recessed portion of high-speed rotating shaft 25 25b ... Female involute spline 25e formed on inner peripheral surface of receiving recessed portion 25a ... Receiving recessed portion 25f ... Fitting Fitting recess 25g ... Receiving recess 25h ... Fitting recess 26 ... Low speed rotation shaft 27 ... Planetary roller type speed change mechanism 28 ... Fixed ring of planetary roller type speed change mechanism 27 ... Sun roller shaft 29a ... Male involute spline 29b ... Spherical protrusion 29c, 30e ... Oil supply groove 29d ... Housing recess 29e ... Female involute spline 29f ... Oil drain hole 30 ... Gear type coupling 30a ... Male involute spline 30b ... Spherical projection 30c ... Housing recess 30d ... Female involute spline 30f ... Oil supply hole 30g ... Male involute spline 0h ... Spherical projection 30i ... Oil supply groove 33, 34, 35, 36 ... Bearing 37 ... Oil supply passage 38 ... Planetary roller 39 ... Planetary roller pin 40 ... Needle bearing 41, 42 ... Snap ring 43 ... Oil drop chamber 44 ... Constant velocity Power universal joint 52 ... Constant velocity universal joint 60 ... Joint receiver 60a ... Housing recess 60b ... Female involute spline 62 ... Constant velocity universal joint 70 ... Gear type coupling 71 ... Male joint 72 ... Cylindrical body 72a ... Partition walls 72b, 72c ... Accommodation recesses 72d, 72e ... Female involute splines 72f, 72g ... Oil drain holes 71a ... Centering fitting projections 71b ... Mounting flange 71c ... Male involute splines 71d ... Spherical projections 74, 75 ... Snap rings 80 ... Constant velocity power universal joint 81 ... Torque tube 81a, 81b ... Ball hole 2, 83 ... Steel balls 84, 85 ... Outer rings 84a, 85a ... Cylindrical bodies 84b, 85b ... Guide shafts 84c, 84d, 85c, 85d ... Recesses 84e ... Fitting projections 84f ... Mounting flange 86 ... Retaining rings 85e ... Sun roller shaft 90 integrated with outer ring 85 ... Constant velocity universal joint 91 ... Intermediate body 92, 93 ... Shaft body 92a ... Fitting shaft 92b ... Flange 93a ... Sun roller shaft 100 integral with shaft body 93 ... Coupling 101, 102 ... Coupling 103 ... Power transmission material 101a, 102a ... Claw piece 101b ... Flange 102b ... Sun roller shaft 110 integrated with coupling 102 ... 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 ... Housing recess 120 ... Carrier flange 121, 122 ... 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 ... Teeth of the male involute splines 29a, 30a Width center-to-center distance α ... Angle of straight line L1 with respect to radial line of high-speed rotating shaft 25, low-speed rotating shaft 26, etc. CL ... On the straight line L1, the reference contact point where the meshing pitch circle of the male involute spline 30a of the gear type coupling 30 and the female involute spline 25b of the high-speed rotating shaft 25 intersects W ... The tooth width of the male involute spline 30a ε ... High-speed rotation Amount of eccentricity between the shaft 25 and the sun roller shaft 29 γ ... Inclination angle β of the gear type coupling 30 Inclination angle between the high-speed rotation shaft 25 and the low-speed rotation shaft 26 C1 ... Gap between the cylinder 84a and the guide tube 81 C2 ... Gap between the guide shaft 84b and the guide tube 81 C3 ... Gap between the cylinder 85a and the guide tube 81 C4 ... Gap between guide shaft 85b and guide tube 81 O2, O3 ... Cross point O4 ... Center of width of power transmission member 103

Claims (2)

[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. In a power transmission device using a connected planetary roller type speed change mechanism, 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 via a constant velocity universal joint. A power transmission device using a planetary roller type speed change mechanism. 2. The power transmission device, the planetary roller type speed change mechanism, at least the high-speed rotating shaft, a housing for accommodating one end side of the high-speed rotating shaft, and rotating the high-speed rotating shaft inside the housing. A high-speed rotating shaft mechanism including a bearing that supports the low-speed rotating shaft, a housing that houses one end side of the low-speed rotating shaft, and a low-speed rotating shaft that is rotatably supported inside the housing. The low-speed rotary shaft mechanism including the bearing can be divided into three units, that is, a speed change mechanism unit, a high-speed rotary shaft unit, and a low-speed rotary shaft unit, and can be divided, and the constant velocity universal joint can be divided into a high-speed rotary shaft unit. The power transmission device using a planetary roller type speed change mechanism according to claim 1, wherein the speed change mechanism unit is incorporated into either one or both of them separately.