Rotary power transmission apparatus

A rotary power transmission apparatus for transmitting a rotary power from an input rotary member to an output rotary member eccentric from the input rotary member. The rotary power transmission apparatus comprises: a ring member arranged around the outer circumferences of the input rotary member and the output rotary member and made rotatable on an axis eccentric from those input rotary member and output rotary member; a first intermediate rotary member for transmitting a torque between the input rotary member and the ring member; a second intermediate rotary member for transmitting the torque between the ring member and the output rotary member; and a relative phase changing mechanism for changing the relative phases in the direction of revolution between the first intermediate rotary member and the second intermediate rotary member along the inner circumference of the ring member.

BACKGROUND OF THE INVENTION 
1. Field of the Invention 
The present invention relates to an apparatus capable of transmitting a 
rotary power between an input rotary member and an output rotary member 
eccentric from each other and changing the eccentricity inbetween. 
2. Related Art 
In a rotary machining by a milling machine or the like, a plurality of 
diameters may be machined by a tool of one kind by changing the turning 
radius of the edge of the tool. In this case, not only the machining 
radius can be easily changed but also a complicated machining such as the 
cutting of a tapered face can be performed, if the structure, in which the 
edge is changed in position by attaching and detaching it to and from the 
tool body, is replaced by a mechanism for moving the edge radially of the 
tool body. 
The mechanism capable of changing the turning radius of the tool edge 
continuously is disclosed in Japanese Patent Laid-Open No. 51211/1989. In 
the apparatus disclosed, a cylindrical holder body, as mounted on the 
rotary spindle of a machine tool, is provided at its leading end portion 
with a radially directed slide guide, with which the tool is movably 
engaged. Moreover, the holder body is equipped therein with a motor and a 
feed screw mechanism to be actuated by the motor, so that the tool may be 
moved along the slide guide by the feed screw mechanism. In the disclosed 
apparatus, therefore, the tool is moved along the slide guide by 
energizing the motor so that the edge position in the radial direction of 
the rotary spindle can be continuously changed even while the rotary 
spindle is rotating. 
However, the aforementioned construction of the prior art is 
disadvantageously complicated because the motor and the feed screw 
mechanism have to be disposed in the rotary spindle. Since the center of 
rotation of the rotary spindle fails to be aligned with the center of 
gravity, moreover, the eccentric force for the eccentric load grows higher 
according to the increase in the number of rotation so that the number of 
rotation of the rotary spindle is disadvantageously restricted so as to 
prevent the vibration and to keep the rotating accuracy. In order to 
change the edge position or the cutting radius during the cutting 
operation, the motor in the rotating rotary spindle has to be energized. 
For this energization, contacts such as slip rings or brushes are mounted 
on the outer circumference of the rotary spindle. When this rotary spindle 
is turned at a high speed, however, insufficient contact or contact wear 
may probably occur to raise problems in the reliability and the 
durability. 
Here, the Oldham's coupling, a universal joint or a flexible cylinder is 
known as the mechanism for transmitting a torque between the input and 
output sides which are eccentric from each other. However, these 
mechanisms of the prior art may be restricted in the transmittable torque 
and the number of rotation and may have to change the spacing between the 
input side member and the output side member so as to change the 
eccentricity. If this eccentricity is to be changed during the rotation, 
moreover, the necessary mechanism is disadvantageously complicated. 
SUMMARY OF THE INVENTION 
An object of the invention is to provide a rotary power transmission 
apparatus capable of easily changing the eccentricity of an output rotary 
member to an input rotary member and turning the same at a high speed. 
According to the invention, therefore, there is provided a rotary power 
transmission apparatus for transmitting a rotary power from an input 
rotary member to an output rotary member made rotatable on an axis 
eccentric from that of the input rotary member, comprising: first drive 
means for turning the input rotary member on its center axis; a 
cylindrical member arranged around the outer circumferences of the input 
rotary member and the output rotary member and made rotatable on an axis 
eccentric from those of the input rotary member and the output rotary 
member; a first intermediate rotary member made rotatable on its axis in 
engagement with the outer circumference of the input rotary member and the 
inner circumference of the cylindrical member to transmit a torque between 
the input rotary member and the cylindrical member; a second intermediate 
rotary member made rotatable on its axis in engagement with the outer 
circumference of the output rotary member and the inner circumference of 
the cylindrical member to transmit the torque between the cylindrical 
member and the output rotary member; and a relative phase changing 
mechanism for changing the relative phases in the direction of revolution 
between the first intermediate rotary member and the second intermediate 
rotary member along the inner circumference of the cylindrical member. 
According to the invention, therefore, the first intermediate rotary member 
is made rotatable on its axis without being revolved. If the input rotary 
member is turned in this state, the input rotary member, the first 
intermediate rotary member and the cylindrical member construct a 
mechanism similar to the planetary gear mechanism so that the cylindrical 
member rotates backward of the input rotary member. On the other hand, the 
cylindrical member, the second intermediate rotary member and the output 
rotary member construct a mechanism similar to the planetary gear 
mechanism, and the cylindrical member receives the torque from the input 
rotary member and rotates, as described above, so that the output rotary 
member rotates backward of the cylindrical member, i.e., in the same 
direction of the input rotary member. Since the cylindrical member is 
eccentric from the input rotary member and since the output rotary member 
is eccentric from the cylindrical member, moreover, the output rotary 
member is held in an eccentric position relative to the input rotary 
member by making the individual directions of eccentricity different. As a 
result, the torque is transmitted from the input rotary member to the 
output rotary member in the eccentric states to each other. In this case, 
all the members rotate on their individual center axes to generate neither 
the eccentric load nor the centrifugal force, as might be caused by the 
eccentric load, so that the high speed rotation can be achieved. If one of 
the intermediate rotary members is revolved by the relative phase changing 
mechanism to change the relative phases of the two intermediate rotary 
members, moreover, the relative direction of eccentricity between the 
input rotary member and the cylindrical member and the relative direction 
of eccentricity between the output rotary member and the cylindrical 
member change thereby to change the relative eccentricity between the 
input rotary member and the output rotary member. In short, it is possible 
to change the eccentricity of the output rotary member. 
In addition to the construction described above, the invention can be 
equipped with a revolution mechanism for revolving the first and second 
intermediate rotary members at the same speed and in the same direction. 
With this construction, therefore, the cylindrical member rotates on the 
axis of the input rotary member when the first intermediate rotary member 
revolves around the axis of the input rotary member. This rotation of the 
cylindrical member is eccentric with respect to the axis of the input 
rotary member. Simultaneously with this, the second intermediate rotary 
member revolves in the same direction so that the output rotary member 
engaging with the second intermediate rotary member revolves around the 
axis of the input rotary member. As a result, the output rotary member can 
be revolved with a radius of the eccentricity to the input rotary member 
while being rotated on its axis. 
In addition to the construction described above, the invention can adopt a 
construction in which the relative phases in the direction of revolution 
between the first intermediate rotary member and the second intermediate 
rotary member while being the first and second intermediate rotary members 
being revolved in the same direction. 
With this construction, therefore, the output rotary member is revolved 
with the radius of the eccentricity to the input rotary member while being 
rotated on its axis, as in the aforementioned construction. During this 
revolution, moreover, the relative phases of the individual intermediate 
rotary members in the revolution direction are changed to change the 
eccentricity of the output rotary member to the input rotary member so 
that the radius of revolution is changed during the revolution. 
The above and further objects and novel features of the invention will more 
fully appear from the following detailed description when the same is read 
with reference to the accompanying drawings. It is to be expressly 
understood, however, that the drawings are for the purpose of illustration 
only and are not intended as a definition of the limits of the invention.

DESCRIPTION OF THE PREFERRED EMBODIMENT 
The invention will be described more specifically with reference to the 
accompanying drawings. First of all, the fundamental construction of the 
invention will be described with reference to FIGS. 1 and 2. In these 
Figures, reference numeral 1 designates an input shaft acting as an input 
rotary member. This input shaft 1 is rotatably supported by a base 2 and 
is connected to a power source such as a not-shown motor. A plurality of 
(e.g., three, as shown) rollers 3 or intermediate rotary members having 
center axes in parallel with the center axis O1 of the input shaft 1 and 
having different external diameters are arranged to contact with the outer 
circumference of the input shaft 1 in a torque transmittable manner. Of 
these rollers 3, more specifically, the two rollers 3 are given equal 
external diameters whereas the remaining one roller 3 is given a smaller 
external diameter, and these three rollers 3 are arranged equidistantly in 
the circumferential direction on the outer circumference of the input 
shaft 1. 
These rollers 3 are individually rotatably supported by support shafts 4, 
which are retained by a retaining member 5. In the shown example, the 
retaining member 5 is a cylindrical member, which is integrated at its one 
end portion with a side wall portion extended radially inward to mount the 
individual support shafts 4. Moreover, this cylindrical retaining member 5 
is so rotatably retained by the base 2 as to rotate on the axis common to 
the center axis O1 of the input shaft 1. 
Around the outer circumference of the input shaft 1 and on the inner 
circumference of the retaining member 5, there is rotatably arranged a 
cylindrical member 6 which corresponds to the ring member of the 
invention. Specifically, the cylindrical member 6 is so arranged on the 
outer circumferences of the three rollers 3 as to contact with them in a 
torque transmittable manner. Hence, the input shaft 1 and the cylindrical 
member 6 are made eccentric from each other by a predetermined size "x". 
The input shaft 1, rollers 3 and cylindrical member 6 thus far described 
construct a mechanism similar to the planetary gear mechanism, in which: 
the input shaft 1 corresponds to the sun gear; the rollers 3 correspond to 
the planetary pinions; and the cylindrical member 6 corresponds to the 
ring gear. When the input shaft 1 rotates with the revolutions of the 
rollers 3 being stopped, i.e., with the retaining member 5 retaining the 
individual support shafts 4 being fixed, therefore, the individual rollers 
3 rotate on their axes to transmit the torque to the cylindrical member 6 
so that the cylindrical member 6 rotates backward of the input shaft 1. 
The number of rotations of the cylindrical member 6 in this case is 
determined by the ratio of the external diameter of the input shaft 1 and 
the internal diameter of the cylindrical member 6. Since this ratio is 
smaller than "1", the cylindrical member 6 is decelerated with respect to 
the input shaft 1 so that it rotates backward of the input shaft 1. 
The cylindrical member 6 is extended to the front side (or to the right of 
FIG. 1) of the leading end portion of the input shaft 1, and three rollers 
7 having a construction identical to that of the aforementioned rollers 3 
are arranged on the inner circumference of the extension of the 
cylindrical member 6 at the leading end side of the input shaft 1. 
Specifically, two rollers 7 of a larger diameter and one roller 7 of a 
smaller diameter are arranged at a predetermined interval. At the center 
of the space enclosed by those three rollers 7, moreover, there is 
arranged an output shaft 8 which is in contact with the three rollers 7 in 
a torque transmittable manner. 
This output shaft 8 corresponds to the output rotary member of the 
invention, and the three rollers 7 at the side of the output shaft 8 
correspond to the second intermediate rotary members of the invention. 
These three rollers 7 are rotatably supported by support shafts which are 
directed in parallel with the axis of the input shaft 1. Hence, the output 
shaft 8 has a center axis O8 in parallel with the center axis O1 of the 
input shaft 1. 
The support shafts 9 supporting the rollers 7 are individually retained by 
a retaining member 10 which can rotate on an axis aligned with the center 
axis O1 of the cylindrical member 6. Moreover, this retaining member 10 is 
rotatably fitted in the inner circumference of the first-named retaining 
member 5 having a cylindrical shape. On the other hand, the output shaft 8 
rotatably extends through the retaining member 10. As a result, the 
retaining member 5 on the side of the input shaft 1 is rotatably retained 
by the base 2 to retain the retaining member 10 on the side of the output 
shaft 8 in a rotatable manner, and the output shaft 8 is rotatably 
retained by the retaining member 10. 
The output shaft 8, the rollers 7 and the cylindrical member 6 construct a 
mechanism similar to the planetary gear mechanism, in which: the output 
shaft 8 corresponds to the sun gear; the rollers 7 correspond to the 
planetary pinions; and the cylindrical member 6 corresponds to the ring 
gear. When the cylindrical member 6 rotates with the revolutions of the 
rollers 7 being stopped, i.e., with the retaining member 10 retaining the 
individual support shafts 9 being fixed, therefore, the individual rollers 
7 rotate on their axes to transmit the torque from the rollers 7 to the 
output shaft 8 so that the output shaft 8 rotates backward of the 
cylindrical member 6. The number of rotations of the output shaft 8 in 
this case is determined by the ratio of the external diameter of the 
output shaft 8 and the internal diameter of the cylindrical member 6. 
Since this ratio is smaller than "1", the output shaft 8 is accelerated 
with respect to the cylindrical member 6 so that it rotates backward of 
the cylindrical member 6. 
There are further provided turning units 11 and 12 for turning those 
retaining members 5 and 10, respectively. These turning units 11 and 12 
are given functions to turn the individual retaining members 5 and 10 at 
the same speed in the same direction and to turn one retaining member 5 
relative to the other retaining member 10 thereby to change the rotary 
phases of the two, i.e., the relative phases in the direction of 
revolution. Hence, these turning units 11 and 12 correspond to a relative 
phase changing mechanism of the invention. These turning units 11 and 12 
also correspond to a revolution mechanism of the invention because they 
revolve the output shaft 8 and changes the eccentricity of the output 
shaft 8, as will be described hereinafter. 
In the structure thus far described, the input shaft 1, the rollers 3, the 
cylindrical member 6, the rollers 7 and the output shaft 8 are constructed 
to contact with one another in an arcuate plane thereby to transmit the 
torque. As a result, the transmittable torque is restricted by their 
contact pressure, and it is desired transmitting the demanded torque to 
raise the contact pressures of those members. These contact pressures 
between the members are desirably raised by press-fitting or shrinking the 
individual rollers 3 and 7, the input shaft 1 and the output shaft 8 in 
the cylindrical member 6. Since these members construct a mechanism 
corresponding to the planetary gear mechanism, as described hereinbefore, 
they can be individually replaced by gears. Specifically: the input shaft 
1 and the output shaft 8 may be replaced by external gears; the individual 
rollers 3 and 7 may be replaced by pinion gears; and the cylindrical 
member 6 may be replaced by an internal gear (or a ring gear). Hence, it 
should be understood that the terminologies "outer circumferential 
portion" or "inner circumferential portion", as defined in Claims, contain 
both the outer circumference or inner circumference for transmitting the 
torque frictionally and the external or internal teeth meshing with each 
other for the torque transmissions. 
Here will be described the actions of the mechanism thus far described. The 
first description will be made on the transmission of the torque from the 
input shaft 1 to the output shaft 8. When the not-shown power source such 
as the motor is started, the input shaft 1 rotates on its axis because it 
is rotatably retained by the base 2. In this case, the rollers 3 are 
rotated on their axes by the rotation of the input shaft 1 if the 
individual turning units 11 and 12 are stopped to fix the retaining 
members 5 and 10 thereby to stop the revolutions of the individual rollers 
3 and 7. In accordance with the rotations of the rollers 3, the 
cylindrical member 6 corresponding to the ring member rotates backward of 
the input shaft 1 on its center axis O6. The ratio between the numbers of 
rotations of the input shaft 1 and the cylindrical member 6 in this case 
is a reduction ratio based on the ratio between the external diameter of 
the input shaft 1 and the internal diameter of the cylindrical member 6. 
On the side of the output shaft 8, the cylindrical member 6 rotates with 
the revolution of the rollers 7 corresponding to the second intermediate 
rotary member being stopped. As a result, the torque is transmitted 
through the rollers 7 to the output shaft 8 so that the output shaft 8 
rotates on its center axis O8. The ratio between the numbers of rotations 
of the cylindrical member 6 and the output shaft 8 in this case is an 
acceleration ratio based on the ratio between the internal diameter of the 
cylindrical member 6 and the external diameter of the output shaft 8. As a 
result, the deceleration is established between the input shaft 1 and the 
cylindrical member 6 whereas the acceleration is established between the 
cylindrical member 6 and the output shaft 8, so that the numbers of 
revolutions of the input shaft 1 and the output shaft 8 are hardly 
different even with the difference in the internal and external diameters 
among the input shaft 1, the output shaft 8 and the cylindrical member 6. 
More specifically, the input shaft 1 and the output shaft 8 rotate at the 
same number of rotation, if they have the same external diameter, but the 
acceleration/deceleration occurs according to the ratio of the external 
diameters of the input shaft 1 and the output shaft 8 if these external 
diameters are different. 
Here will be described the actions for changing the eccentricity between 
the input shaft 1 and the output shaft 8. FIGS. 1 and 2 show the state in 
which the eccentricity takes the maximum. In the shown example, the 
maximum eccentricity is "2x" because the input shaft 1 and the output 
shaft 8 have the same external diameter. In short, the cylindrical member 
6 is eccentric by the predetermined size "x" with respect to the input 
shaft 1. The rollers 7 on the side of the output shaft 8 are revolved 
around the cylindrical member 6. 
These revolutions of the rollers 7 are performed by turning the retaining 
member 10 retaining the support shafts 9 of the rollers 7. Since the 
center axis of the retaining member 10 is aligned with that of the 
cylindrical member 6, however, the retaining member 10 and the output 
shaft 8 supported by the rollers 7 revolve around the center axis O6 of 
the cylindrical member 6. Specifically, the output shaft 8 moves on a 
circle of the radius "x" around the center axis O6 of the cylindrical 
member 6. Since the input shaft 1 and the cylindrical member 6 are 
eccentric by the predetermined size "x", on the other hand, the output 
shaft 8 revolves by 180 degrees from the shown position so that the center 
axis O8 of the output shaft 8 comes into alignment with the center axis O1 
of the input shaft 1. By thus turning one retaining member 10 relative to 
the other retaining member 5, that is, by moving the rollers 7 
corresponding to the second intermediate rotary member in the direction of 
revolution relative to the rollers 3 corresponding to the first 
intermediate rotary member to change their relative phases, the spacing 
(or eccentricity) between the center axis O1 of the input shaft 1 and the 
center axis O8 of the output shaft 8 changes in the range of 0 to "2x". 
Here, the change in the eccentricity of the output shaft 8 with respect to 
the input shaft 1 can be made by turning either or both of the retaining 
members 5 and 10 by the aforementioned turning units 11 and 12 thereby to 
make their rotary phases different. 
Here will be described the actions to revolve the output shaft 8. The 
individual retaining members 5 and 10 are turned at the same speed and in 
the same direction by the turning units 11 and 12. This is similar to the 
state in which the individual retaining members 5 and 10 are integrally 
connected and turned together. Thus, the rollers 3 and 7, as retained by 
the retaining members 5 and 10, respectively, through the support shafts 4 
and 9, are revolved while keeping their relative positional relations 
without any change in their relative phases. As a result, the shown 
apparatus rotates as a whole on the center axis O1 of the input shaft 1 so 
that the rotating locus of the output shaft 8 is a circuit having a center 
on the center axis O1 of the input shaft 1 and the relative eccentricity 
as its radius. In short, the output shaft 8 revolves along the 
circumference of such circle. 
Here, the transmission of the torque from the input shaft 1 to the output 
shaft 8, the change in the eccentricity of the output shaft 8 relative to 
the input shaft 1, and the revolutions of the output shaft 8, as have been 
described hereinbefore, can be performed in the individually superposed 
manners. In other words, the output shaft 8 can be turned while changing 
its eccentricity or revolved, or can be rotated or revolved while changing 
its eccentricity. For these actions, the individual retaining members 5 
and 10 are turned or caused to establish relative rotations by controlling 
the individual turning units 11 and 12 while driving the input shaft 1. 
FIG. 3 schematically shows one embodiment of the spindle head of a cutting 
machine employing the apparatus thus far described. Here, the portions in 
FIG. 3, as identical to those of FIGS. 1 and 2, are designated by the 
reference numerals employed in FIGS. 1 and 2, and their description will 
be omitted. 
On the base 2, there is fixed a spindle motor 15, to which the input shaft 
1 is connected. Here, the construction may be modified such that the 
output of the spindle motor 15 is used as the input shaft. On the other 
hand, the output shaft 8 is extended long in the opposite direction to the 
input shaft 1 and is equipped with a chuck 16 for chucking a (not-shown) 
cutting tool such as a milling cutter. Hence, the output shaft 8 is 
constructed as a tool shaft. Moreover, the retaining member 10 on the side 
if the output shaft 8 is formed into a relatively long cylindrical member 
extended axially like the output shaft 8. 
With the outer circumference of the retaining member 5 on the side of the 
input shaft 1, on the other hand, there is integrated a driven pulley 17, 
and a drive pulley 18 is arranged outside of the outer circumference and 
in parallel with the driven pulley 17. Moreover, a timing belt 19 is made 
to run on those driven pulley 17 and drive pulley 18. 
This drive pulley 18 is equipped with shafts protruded in the axial 
direction to the two sides, and the lefthand shaft, as seen in FIG. 3, is 
connected to a revolution shaft motor 20. Here, this lefthand shaft may be 
replaced by the output shaft of the revolution shaft motor 20. On the 
other hand, the righthand shaft, as seen in FIG. 3, is connected to a sun 
gear 22 in a planetary gear mechanism 21. This planetary gear mechanism 21 
is constructed to include: the sun gear 22; a plurality of pinion gears 23 
meshing with the sun gear 22 for rotations and revolutions; a carrier 24 
retaining those pinion gears 23; and a ring gear 25 meshing with the 
pinion gears 23. Moreover, the carrier 24 is connected to a phasing motor 
26. This phasing motor 26 is provided for setting the eccentricity of the 
output shaft 8 with respect to the input shaft 1, as will be described 
hereinafter, and may preferably be exemplified by a motor such as a step 
motor capable of setting the rotary phase finely and accurately. Here, 
this phasing motor 26 is mounted on a predetermined stationary portion of 
the base 2. 
With the portion, as located at the radially outer side of the planetary 
gear mechanism 21, of the outer circumference of the retaining member 10 
on the side of the output shaft 8, on the other hand, there is integrated 
an external gear 27, which is meshed by an internal gear 28 made rotatable 
on the center axis of the input shaft 1. This internal gear 28 provides a 
driven pulley whereas the aforementioned ring gear 25 provides a drive 
pulley. Thus, a timing belt 29 is made to run on these internal gear 28 
and ring gear 25. 
When the input shaft 1 is turned by the spindle motor 15 in the spindle 
head, as shown in FIG. 3, the output shaft 8 rotates on its axis in the 
same direction as that of the input shaft 1. The ratio of the numbers of 
rotations in this case is determined by the ratio between the external 
diameters of the input shaft 1 and the output shaft 8, as has been 
described hereinbefore. When the torque is to be transmitted by means of 
the gears, the ratio between the numbers of rotations of the input shaft 1 
and the output shaft 8 is determined by the ratio between the tooth number 
of the input shaft 1 and the tooth number of the output shaft 8. 
When the revolution shaft motor 20 is started, on the other hand, its 
torque is transmitted to rotate the retaining member 5 on the side of the 
input shaft 1 through the drive pulley 18, the timing belt 19 and the 
driven pulley 17. The torque of the revolution shaft motor 20 is 
transmitted on the other hand to rotate the sun gear 22 of the planetary 
gear mechanism 21. In this planetary gear mechanism 21, therefore, the sun 
gear 22 acts as the input element whereas the ring gear 25 acts as the 
output element. Thus, the torque is transmitted from the ring gear 25 
through the timing belt 29 to the external gear 28 and further from this 
external gear 28 to the internal gear 27 so that the retaining member 10 
on the side of the output shaft 8 rotates. In other words, the rollers 7 
on the side of the output shaft 8 revolve. 
In this case, the retaining member 5 on the side of the input shaft 1 
rotates while being accelerated/decelerated according to the ratio between 
the external diameters of the drive pulley 18 and the driven pulley 17 (or 
the ratio between the numbers of gears meshing with the timing belt 19). 
In the planetary gear mechanism 21, moreover, the output rotation, i.e., 
the number or direction of rotation of the ring gear 25 is determined by 
the number and direction of rotation of the carrier 24. Moreover, a speed 
change is made between the ring gear 25 and the external gear 28 and 
between the external gear 28 and the internal gear 27. By turning the 
carrier 24 in a predetermined direction and at a predetermined number of 
rotation by the phasing motor 26, therefore, the gear ratio of the torque 
transmission path from the revolution shaft motor 20 to the retaining 
member 10 on the side of the output shaft 8 is equalized to that of the 
torque transmission path from the revolution shaft motor 20 to the 
retaining member 5 on the side of the input shaft 1. With this setting, 
the rollers 3 on the side of the input shaft 1 and the rollers 7 on the 
side of the output shaft 8 revolve in the same direction and at the same 
speed so that the output shaft 8 revolves around the center axis of the 
input shaft 1. 
By changing the relative rotary phases between the rollers 3 on the side of 
the input shaft 1 and the rollers 7 on the side of the output shaft 8, as 
has been described in connection with the fundamental construction shown 
in FIGS. 1 and 2, moreover, the eccentricity of the output shaft 8 to the 
input shaft 1 is changed. If, therefore, a relative rotation of one of the 
revolution shaft motor 20 and the phasing motor 26 to the other is caused 
with the individual retaining members 5 and 10 being turned in the same 
direction and at the same speed by the motors 20 and 26 or with both the 
motors 20 and 26 being stopped to interrupt the rotations of the retaining 
members 5 and 10, relative revolutions of the rollers 3 or 7 to those of 
the other rollers are caused to change the rotary phases of the two so 
that the eccentricity of the output shaft 8 to the input shaft 1 
increases/decreases. The change in the eccentricity thus made can be made 
in the state in which the output shaft 8 is being revolved or not. Thus, 
the mechanism including the revolution shaft motor 20 and the phasing 
motor 26 for turning the individual retaining members 5 and 10 and the 
timing belts 19 and 29 for transmitting the torques of the motors 20 and 
26 corresponds to the revolution mechanism of the invention. 
In the spindle head adopting the apparatus of the invention shown in FIG. 
3, therefore, the revolution radius of the cutting tool can be changed to 
work holes of different diameters with a single tool thereby to improve 
the working efficiency and to lower the cost for the tool. In the spindle 
head shown in FIG. 3, moreover, the output shaft 8 can be changed in its 
revolution radius while being revolved, so that the revolution radius of 
the tool can be changed during the cutting operation. By making use of 
this function, it is possible to facilitate a complicated working such as 
the cutting of a tapered hole or the recessing for increasing the internal 
diameter in an intermediate portion of a hole. 
Especially the spindle head, shown in FIG. 3, is constructed by combining 
the simple rotary members so that a high-speed rotation can be achieved 
with little restriction on the number of rotation by the centrifugal force 
even in the centering operation for which the tool is revolved while being 
rotated on its axis. As a result, a cutting apparatus embodying the 
invention can improve the working efficiency for the centering operation 
better than the prior art. 
FIG. 4 shows another embodiment of the spindle head using the rotary power 
transmission apparatus of the invention. The shown embodiment employs a 
differential mechanism as the mechanism for changing the revolution 
radius. Specifically, a revolution shaft 30 corresponding to the 
aforementioned retaining member is formed into a hollow shaft and is 
rotatably retained in a housing 31 by a plurality of bearings. In this 
revolution shaft 30, moreover, there is rotatably held by a plurality of 
bearings the input shaft 1, to which a spindle turning motor M1 is 
connected. 
Moreover, the revolution shaft 30 is radially enlarged at its leading end 
portion (as located at the lefthand side of FIG. 4), and the rotary power 
transmission apparatus according to the invention is arranged in that 
radially large portion. Specifically, the cylindrical member 6 is arranged 
in alignment with the revolution shaft 30, and the plurality of rollers 3 
of different external diameters are press-fitted between the inner 
circumference of the cylindrical member 6 and the outer circumference of 
the leading end portion of the input shaft 1. In other words, the rollers 
are so held in close contact with the input shaft 1 and the cylindrical 
member 6 as to transmit the torque. Moreover, the support shafts 4 
supporting the rollers 3 rotatably are mounted on the revolution shaft 30 
so that the rollers 3 revolve around the revolution shaft 30 as this 
revolution shaft 30 rotates. 
Moreover, a spindle 32 corresponding to the output shaft 8 is inserted at 
its trailing end portion into the cylindrical member 6, and the plurality 
of rollers 7 of different external diameters are press-fitted like the 
rollers 3 between the outer circumference of the spindle 32 and the inner 
circumference of the cylindrical member 6. The support shafts 9 supporting 
the rollers 7 rotatably are connected to gears 33 which are rotatably 
arranged on the outer circumference of the spindle 32 through bearings. On 
the outer circumference of the spindle 32, moreover, there are rotatably 
fitted through bearings radius changing shafts 34 to which the gears 33 
are connected by means of pins. 
As a result, the torque of the input shaft 1 is transmitted to the 
cylindrical member 6 through the rotations of the rollers 3 contacting 
with the outer circumference of the input shaft 1, and the torque of the 
cylindrical member 6 is transmitted to the spindle 32 through the 
rotations of the other rollers 7 closely contacting with the inner 
circumference of the cylindrical member 6. Moreover, the individual 
rollers 3 and 7 revolve relative to each other to change the eccentricity 
of the spindle 32 to the input shaft 1, i.e., the revolution radius of the 
spindle 32. As the input shaft 1 rotates, the individual rollers 3 and 7, 
the cylindrical member 6 and the spindle 32 rotate so that the spindle 32 
rotates on its axis. 
A cylindrical revolution shaft 35 is rotatably fitted around the outer 
circumference of the radius changing shaft 34 through bearings. The 
trailing end portion of the revolution shaft 35 and the leading end 
portion of the revolution shaft 30 are opposed to each other at a spacing 
around the outer circumferences of the gears 33, and a plurality of 
intermediate gears 36 meshing with the gears 33 are arranged between the 
end portions of those revolution shafts 35 and 30. The intermediate gears 
36 revolve around the axis of the input shaft 1 and are exemplified by a 
plurality of gears having different external diameters matching the 
eccentricity of the spindle 32 to the input shaft 1. 
Support shafts 37 supporting those intermediate gears 36 are fitted in the 
individual revolution shafts 30 and 35 so that these revolution shafts 30 
and 35 are so connected by the support shafts 37 as to revolve integrally 
with each other. Moreover, the individual intermediate gears 36 mesh with 
a revolution radius changing gear 38 or an internal gear. This revolution 
radius changing gear 38 is formed in the inner circumference of the 
leading end portion of a cylindrical shaft 39. Moreover, this cylindrical 
shaft 39 is arranged around the outer circumference of the revolution 
shaft 30 and fitted in alignment with the input shaft 1 and are rotatably 
retained by a bearing. On the other hand, the revolution shaft 35 on the 
leading end side is rotatably supported by the housing 31 through a 
bearing fitted on its outer circumference. 
A revolution shaft gear 40 is fixed on the outer circumference of the 
revolution shaft 30, as located around the outer circumference of the 
input shaft 1, and an intermediate shaft gear 41, as arranged adjacent to 
the revolution shaft gear 40, is fixed on the cylindrical shaft 39. The 
revolution shaft gear 40 meshes with an input gear 43 in a differential 
mechanism 42, and the intermediate shaft gear 41 meshes with an output 
gear 44 in the differential mechanism 42. 
Here will be described the differential mechanism 42. This deferential 
mechanism 42 is constructed to include: a pair of circular splines 45 and 
46 splined in their inner circumferences; a flexible spline 47 of a 
flexible cylinder splined in its outer circumference to mesh with the 
circular splines 45 and 46; and a wave generator 48 having a ball bearing 
fitted on the outer circumference of an elliptic cam and fitting the 
flexible spline 47 on the outer circumference thereof 
One circular spline 45 and the flexible spline 47 are set to have equal 
tooth numbers (e.g., 200), and the circular spline 45 is fixedly fitted in 
the inner circumference of the input gear 43. On the other hand, the other 
circular spline 46 is set to have a slightly larger tooth number (e.g., 
202) than that of the flexible spline 47 and is fixedly fitted in the 
inner circumference of the output gear 44. Moreover, the wave generator 48 
is fixedly fitted on an adjusting shaft 49, which is connected to a radius 
changing motor M2. 
In this differential mechanism 42, therefore, the flexible spline 47 
rotates at the same number of rotation as that of the input gear 43 when 
this input gear 43 is turned with the wave generator 48, i.e., the 
adjusting shaft 49 being fixed, because the tooth number of the circular 
spline 45 fixed on the input gear 43 is equal to that of the flexible 
spline 47. Since the tooth number of the circular spline 46 fixed on the 
output gear 44 is larger than that of the flexible spline 47, on the 
contrary, the output gear 44 is turned while being decelerated according 
to its tooth number difference. In this embodiment, the output gear 44 is 
turned at the deceleration of 200/202=100/101, because the flexible spline 
47 has the tooth number of "200" whereas the circular spline 46 has the 
tooth number of "202". 
Thus, the numbers of rotation become different, but the tooth number ratio 
between the input gear 43 and the revolution shaft number 40 and the tooth 
number ratio between the output gear 44 and the intermediate shaft number 
41 are so set that the revolution radius of the spindle 32 may not change 
even with the difference in the numbers of rotation. In case the input 
gear 43 has a tooth number of "100" whereas the revolution shaft gear 40 
has a tooth number of "200", for example, the tooth number of the output 
gear 44 is set to "101", and the tooth number of the intermediate shaft 41 
is set to "200". With this construction, the output gear 44 rotates at 100 
RPM, and the revolution shaft gear 40 revolves at 101/2 RPM, when the 
input gear 43 is rotated at 101 RPM, for example, with the adjusting shaft 
49, i.e., the wave generator 48 being fixed. Since the output gear 44 
rotates at 100 RPM, moreover, the intermediate shaft gear 41 meshing with 
it rotates at 100.times.101/299=101/2 RPM. In short, the revolution shaft 
gear 40 and the intermediate shaft gear 41 rotate at the same speed. 
As a result, the number of revolution of the revolution shaft 30 and the 
number of rotation of the cylindrical shaft 39 are equalized so that the 
revolution radius changing gear 38 formed on the cylindrical shaft 39, the 
intermediate gears 36 meshing with the gear 38 and the gears 33 meshing 
with the gears 36 rotate altogether. In short, the phases of the 
individual rollers 3 and 7 in the revolution direction kept constant. 
Because of the difference in the tooth number between the flexible spline 
47 and the circular spline 46 on the side of the output shaft 44, on the 
other hand, the circular spline 46 is decelerated with respect to the 
rotation of the flexible spline 47 at a deceleration rate according to the 
difference in the tooth number. With the tooth number difference of "2" in 
this embodiment, therefore, the circular spline 46 is decelerated at a 
ratio of 2/200=1/100 with respect to the rotation of the flexible spline 
47. In other words, the circular spline 46 rotates with -1 RPM when the 
flexible spline 47 is rotated at 100 RPM together with the adjusting shaft 
49. Here, no difference arises in the number of rotation between the 
circular spline 45 on the side of the input gear 43 and the flexible 
spline 47 because these splines have the equal tooth number. After all, a 
difference occurs between the rotary phases of the input gear 43 and the 
output gear 44 when the flexible spline 47 is rotated together with the 
adjusting shaft 49. Specifically, relative rotations can be established 
between the input shaft 43 and the output gear 44 at the rotary speed of 
1/100 of the number of rotation of the adjusting shaft 49. 
These relative rotations appear as those between the revolution shaft 30 
and the gears 33, i.e., the relative revolution speeds between the 
individual rollers 3 and 7. Since the eccentricity of the spindle 32 to 
the input shaft 1, i.e., the revolution radius is changed by the relative 
revolutions between the individual rollers 3 and 7, moreover, the spindle 
head thus far described can adjust the revolution radius finely with ease. 
Here, reference numeral 50 appearing in FIG. 4 designates a revolution 
gear meshing with the input gear 43. This revolution gear 50 is connected 
to a revolution motor M3. 
As in the embodiment shown in FIG. 3, moreover, the spindle head shown in 
FIG. 4 can not only turn the spindle 32 at a high speed but also revolve 
the spindle 32 while rotating it on its axis and can change the radius of 
the spindle 32 during the revolution. As a result, it is possible to 
perform the cutting of tapered holes, the working of a plurality of bores 
of different diameters and the recessing with ease. 
Here, the invention should not be limited to the specific embodiments thus 
far described, but the revolution mechanism for revolving the intermediate 
rotary member on the input side and the intermediate rotary member on the 
output side may be other than the transmission means using the motors 20 
and 26 and the timing belt, and the planetary gear mechanism, as shown in 
FIG. 3. On the other hand, the rotary power transmission apparatus of the 
invention can be applied not only to the spindle head of the cutting 
machine but also to a variety of machines for transmitting the torque. 
Moreover, the intermediate rotary member of the invention should not be 
limited to the single one for transmitting the torque by engaging it 
simultaneously with the input rotary member or the output rotary member 
and the ring member but may be composed of a plurality of rotary members 
which are connected in a torque transmittable manner. 
Here will be summarized the advantages to be achieved by the invention. 
According to the invention, as has been described hereinbefore, the input 
rotary member and the output rotary member, as eccentric from each other, 
are arranged on the inner circumference of the ring member, and the 
intermediate rotary members for rotating to transmit the torque are 
individually arranged between the ring member and the input rotary member 
and between the ring member and the output rotary member. As a result, the 
torque can be transmitted from the input rotary member to the output 
rotary member through those intermediate rotary members and the ring 
member. By revolving at least one of the intermediate rotary members, 
moreover, it is possible to change the relative eccentricity between the 
input rotary member and the output rotary member. These functions to 
transmit the torque and to change the eccentricity are performed by 
turning the rotors such as the intermediate rotary members and the ring 
member so that any excessive centrifugal force is generated even at the 
large number of rotation for the torque transmission. According to the 
invention, therefore, it is possible to achieve far higher rotations than 
those of the prior art. If the relative phases of the individual 
intermediate rotary members in the revolution direction are changed, on 
the other hand, the eccentricity of the output rotary member can be 
changed to change/set the eccentricity easily. 
According to the invention, moreover, the output rotary member is revolved 
by revolving both the intermediate rotary members so that the revolutions 
accompanied by the rotation of the output rotary member can be easily 
performed to achieve the high speed rotations, because there arises no 
special rotation obstructing cause such as the centrifugal force. 
According to the invention, still moreover, while the output rotary member 
is revolving, its eccentricity, i.e., the revolution radius can be changed 
to facilitate the various motions of the output rotary member. By making 
use of these functions, the rotary cutting tool is rotated on its axis and 
revolved to facilitate the complicated cutting operations.