Friction resistance generator

A mechanism of a simple structure, in which always stable and discretionary frictional resistance can be produced even when the speed of rotary movements or rectilinear movements of the subject structure changes and, moreover, the magnitude of the frictional force can be easily controlled by changing the magnitude of a load. Namely, when a rotary member 1 is rotated while a load toward the axial direction is being applied, numerous rollers 2 make rolling motions in contact with the rotary member 1 and a passive member 3. The rollers 2 make rolling motions along a track of rotation of the rotary member 1. The rollers 2 are restrained to roll toward a direction being inclined by a prescribed angle by a cage 4. This results in producing a frictional force in proportion to the magnitude of the load being applied to the axial direction between the rollers 2 and the rotary member 1 nd between the rollers 2 and the passive member 3. At this time, since the rollers 2 slide while making rolling motions, sliding friction and rolling friction occur in combination to provide more stable resistance force.

BACKGROUND OF THE INVENTION 
1. Field of the Invention 
The present invention relates to a friction resistance generator for 
applying discretionary resistance by frictional force to rotary movement 
or rectilinear movement in various kinds of machines and equipment. 
2. Description of the Prior Art 
Bearings or guides being so far known as one type of mechanical elements 
can be broadly categorized into slide bearings or slide guides which are 
structured to support movable members through the aid of lubricating oil 
and roller bearings or roller guides which are structured to support the 
movable members through the aid of balls or rollers. They are intended to 
make the movable members always move smoothly diminishing the friction 
resistance between mating members as small as possible. Consequently, 
since conventional bearings or guides are not intended to apply resistance 
to moving members to control the moving force, additional attenuation 
means such as a shock absorber or damper becomes necessary when it is 
necessary to control the moving speed of the movable member to a constant 
level. 
Meanwhile, with slide bearings or slide guides using lubricating oil, 
although the frictional resistance can be diminished to an extremely low 
level if lubricating oil stays between mating members under an ideal 
state, under low speed movement or heavy load movement, oil film existing 
between the mating slide surfaces can be damaged resulting to intermittent 
occurrences of static friction and dynamic friction producing extremely 
unstable frictional force, thus tending to cause so called stick-slip 
phenomenon. 
Like aforesaid, among conventional machine elements, although there do 
exist machine elements that can provide smoother rotary or rectilinear 
motions, such a mechanical element as is capable of controlling the 
movement speed to a constant level without addition of particular external 
structures or as is capable of producing stable and easily controllable 
resistance force does not exist. Therefore, there is some margin for 
further development work being left in this technological field for 
provision of discretionary frictional resistance to rotary or rectilinear 
motions occurring in various kinds of machines and equipment. 
The present invention was conceived in view of the above problems. It is 
therefore an object thereof to provide a mechanism of a simple structure 
for generating always stable and discretionary frictional resistance to 
rotary movement or rectilinear movement of various material bodies at any 
moving speeds and, moreover, for easily controlling magnitude of said 
frictional force by changing the load. 
SUMMARY OF THE INVENTION 
In order to achieve the above object, the present invention provides a 
friction resistance generator comprising a rotary member which rotates on 
a prescribed axis of rotation, a passive member which faces the rotary 
member in the axial direction, numerous rollers being located between the 
rotary member and the passive member, said rollers making rolling motions 
in contact with the rotary member and the passive member, and a cage which 
maintains the rollers at prescribed intervals along a prescribed 
peripheral line around the axis of rotation of the rotary member while 
allowing free rolling of the rollers, in which axes of rolling of the 
rollers are so inclined to produce a prescribed angle between a plane 
containing the axis of rotation of the rotary member. 
With the aforesaid friction resistance generator, when the rotary member is 
rotated while applying a load toward the axial direction, respective 
rollers roll in contact with the rotary member and the passive member. 
Since the rollers roll along a track of rotation of the rotary member 
while being restricted by the cage to roll in a direction inclined by a 
prescribed angle to the track of rotation of the rotary member, frictional 
force commensurate with the load applied toward the axial direction occurs 
between the rollers and the rotary member, and between the rollers and the 
passive member. At this time, since the rollers slide while making rolling 
motions, sliding friction and rolling friction become combined to cause 
more stable frictional force. In this instance, by optional setting of the 
inclination angle of the axes of rolling of the rollers, frictional force 
corresponding to the preset inclination angle can be obtained. 
Also, with the aforesaid friction resistance generator, respective rollers 
are maintained, for free tilting, so that the inclination angle of the 
axes of rolling of respective rollers to the plane containing the axis of 
rotation of the rotary member when the rotary member rotates in one 
direction of rotation becomes different from an inclination angle of the 
axes of rolling of the rollers to the plane containing the axis of 
rotation of the rotary member when the rotary member rotates in the other 
direction of rotation. By this structure, it is possible, for example, to 
produce larger frictional force when the rotary member rotates in one 
direction of rotation and to produce smaller fractional force when the 
rotary member rotates in the other direction of rotation.

DESCRIPTION OF THE PREFERRED EMBODIMENTS 
FIG. 1 to FIG. 4 show a first preferred embodiment of this invention: FIG. 
1 being an exploded perspective view of a friction resistance generator of 
the first preferred embodiment; FIG. 2(a) being a partial enlarged view of 
a cross-section in the radial direction of the drawing in FIG. 1; FIG. 
2(b) being a partial enlarged view of a portion seen from the axial 
direction of the drawing in FIG. 1. 
The friction resistance generator comprises a rotary member 1 rotating on 
its axis of rotation, numerous rollers 2 disposed along a track of 
rotation of the rotary member 1, a passive member 3 which coaxially faces 
the rotary member 1 across the rollers 2, and a cage 4 which maintains the 
rollers 2 at prescribed intervals in freely rotatable state. 
Meanwhile, the aforesaid components are the minimum requirements for the 
friction resistance generator of this embodiment and, in an actual 
structure, the rotary member 1, the passive member 3 and the cage 4 must 
be housed in a housing or a similar structure being omitted from relevant 
drawings, which maintains said three components in coaxial co-relations. 
Also, the rotary member 1 is to be connected to a drive shaft and the 
passive member 3 is to be connected to another drive shaft or to be kept 
in a stationary state not to turn, indications of said external drive 
shafts also being omitted from relevant drawings. 
The rotary member 1 is in the form of a ring shape and its surf ace facing 
the passive rotary member 3 is a flat plane. Meanwhile, in descriptions 
for the first embodiment, the rotary member 1 is represented by a 
simplified shape since the descriptions mention only construction and 
movement of the friction resistance generator. 
The rollers 2 are in the form of a cylindrical shape extending straight in 
their axial direction and disposed at equal intervals along the peripheral 
direction of the rotary member 1. Also, both ends of the rollers 2 are 
rounded to a hemispherical shape to lessen friction occurring between the 
rollers 2 and the cage 4. 
The passive member 3 is in the form of a ring shape and its surface facing 
the rotary member 1 is a flat plane. Meanwhile, the passive member 3 is 
also represented by a simplified shape for the same reason as the rotary 
member 1. 
The cage 4 is in the form of a ring shape and its thickness in the axial 
direction is made thinner than the outer diameter of the rollers 2. The 
cage 4 is provided with numerous slots 4a, in which each roller 2 is kept 
in freely rotatable state in each slot 4a. Also, as shown in FIG. 2(b), 
each axis of rolling A of each roller 2 is inclined by angle .theta. to a 
plane B containing the axis of rotation of the rotary member 1. 
With the friction resistance generator of the aforementioned structure, as 
shown in FIG. 3, when the rotary member 1 is rotated while applying a load 
F toward the axial direction, respective rollers 2 make rolling motions 
being in contact with the rotary member 1 and the passive member 3, 
thereby the cage 4 also makes trailing rotation. At that time, as shown in 
FIG. 4, since the rollers 2 are forced to move along the track of rotation 
of the rotary member l(in the direction of the solid line) while their 
motivation to roll toward a direction inclined by angle .theta. from the 
track of rotation (in the direction of alternate long and short dash line) 
of the rotary member 1 are restricted by the cage 4, frictional force 
commensurate with the load F to the axial direction occurs between 
respective rollers 2 and the rotary member 1 and between the respective 
rollers 2 and the passive member 3. At this time, since the rollers 2 
slide while making rolling motions, sliding friction and rolling friction 
become combined to cause more stable resistance force. 
Thus, with the friction resistance generator of the first embodiment, since 
the axes of rolling of respective rollers 2 are inclined by a prescribed 
angle from the plane containing the axis of rotation of the rotary member 
1, the rolling movement of respective rollers 2 causes combined sliding 
friction and rolling friction, thereby making it possible to apply 
discretionary resistance force to the rotary movement of the rotary member 
1 in proportion to the load applied to the axial direction and, moreover, 
by varying the magnitude of the load applied to the axial direction, the 
resistance against the rotary member 1 can be controlled very easily. At 
this time, since said sliding friction occurs while the rollers 2 are 
making rolling motions, static friction which causes the stick-slip 
phenomenon does not occur, thus providing always stable resistance force. 
Also, by optional setting of the inclination angle .theta. of the axes of 
rolling of respective rollers 2, frictional force of discretionary 
magnitude fitting to respective purposes can be accurately obtained. 
FIG. 5 and FIG. 6 show a second preferred embodiment of this invention: 
FIG. 5 being an exploded perspective view of a friction resistance 
generator of the second preferred embodiment; FIG. 6(a) being a partial 
enlarged view of a cross-section in the radial direction of the drawing in 
FIG. 5; and FIG. 6(b) being a partial enlarged view of a portion seen from 
the axial direction of the drawing in FIG. 5. 
The friction resistance generator comprises a rotary member 10 rotating on 
its axis of rotation, numerous rollers 11 disposed along a track of 
rotation of the rotary member 10, numerous balls 12 similarly disposed 
along the track of rotation of the rotary member 10, a passive member 13 
which coaxially faces the rotary member 10 across the rollers 11 and the 
balls 12, and a cage 14 which maintains the rollers 11 and the balls 12 
individually at prescribed intervals in freely rotatable state. 
The rotary member 10 is in the form of a ring shape and its surface facing 
the passive member 13 is a flat plane. Also, in the flat plane of the 
rotary member 10, a circular groove 10a having a V-shaped cross-section is 
provided in continuation along the peripheral direction and the balls 12 
are individually engaging with the circular groove 10a in freely rotatable 
state. 
The rollers 11 are in the form of an cylindrical shape extending straight 
in their axial direction and disposed at equal intervals along the 
peripheral direction of the rotary member 10. Also, both ends of the 
rollers 11 are rounded to a hemi-spherical shape to lessen friction 
occurring between the rollers 11 and the cage 14. 
The balls 12 are disposed along the peripheral direction of the rotary 
member 10, being located alternately between each roller 11. 
The passive member 13 is also in the form of a ring shape and the surface 
facing the rotary member 10 is a flat plane. In the flat plane of the 
passive member 13, similar to the aforesaid rotary member 10, a circular 
groove 13a having a V-shaped cross-section is provided in continuation 
along its peripheral direction and the balls 12 are engaging individually 
with the groove 13a. 
The cage 14 is in the form of a ring shape and its thickness in the axial 
direction is made thinner than the outer diameter of the rollers 11. The 
cage 14 is provided with numerous slots 14a to maintain the rollers 11 
individually and numerous holes 14b to maintain the balls 12 individually. 
Each roller 11 is maintained in each slot 14a and each ball 12 is 
maintained in each hole 14b in freely rotatable state. The slots 14a for 
the rollers 11 are so disposed that axes of rolling of the rollers 11 are 
inclined to make a prescribed angle to a plane containing the axis of 
rotation of the rotary member 10, but toward opposite directions 
alternately. 
With the friction resistance generator of the second embodiment, since the 
balls 12 are engaging individually with the circular grooves 10a and 13a 
of the rotary member 10 and passive member 13, respectively, there is no 
fear of displacement between the rotary member 10 and the passive member 
13 in the radial direction. In this instance, the balls 12 are engaging 
with the circular grooves 10a and 13a with slight clearance in order not 
to interfere the contacts between the rollers 11 and the rotary member 10 
and between the rollers 11 and the passive member 13. Also, since 
respective rollers 11 are inclined toward the opposite directions 
alternately, their resistance characteristics remain always same in either 
direction of rotation of the rotary member 10. Meanwhile, the principle of 
occurrence of the frictional force is the same as the preceding preferred 
embodiment of this invention. 
FIG. 7 and FIG. 8 show a third preferred embodiment of this invention: FIG. 
7 being an exploded perspective view of a friction resistance generator of 
the third preferred embodiment; FIG. 8(a) being a partial enlarged view of 
a cross-section in the radial direction of the drawing in FIG. 7; and FIG. 
8(b) being a partial enlarged view of a portion seen from the axial 
direction of the drawing in FIG. 7. 
The friction resistance generator comprises a rotary member 20 rotating on 
its axis of rotation, numerous rollers 21 disposed along a track of 
rotation of the rotary member 20, a passive member 22 which coaxially 
faces the rotary member 20 across the rollers 21, and a cage 23 which 
maintains the rollers 21 at prescribed intervals in freely rotatable 
state. 
The rotary member 20 is in the form of a ring shape and, as shown in FIG. 
8(a), its surface facing the passive member 22 is a rounded convex face in 
radial cross sections. 
The numerous rollers 21 are disposed at equal intervals along the 
peripheral direction of the rotary member 20 and their profile is such 
that the narrowed central part widens toward both ends gradually. Also, 
both ends of the rollers 21 are rounded to a hemi-spherical shape to 
lessen friction occurring between the rollers 21 and the cage 23. 
The passive member 22 is in the form of a ring shape and its surface facing 
the rotary member 20 is a rounded convex face in radial cross sections, 
similar to the surface of the rotary member 20. 
The cage 23 is in the form of a ring shape and its thickness in the axial 
direction is made thinner than the outer diameter of the rollers 21. The 
cage 23 is provided with numerous slots 23a to maintain the rollers 21. 
Each roller 21 is maintained in each slot 23a in freely rotatable state. 
Also, the slots 23a are so disposed that each axis of rolling of each 
roller 21 is inclined by a prescribed angle to a plane containing the axis 
of rotation of the rotary member 20. 
With the friction resistance generator of the third embodiment, since the 
peripheral surfaces of the rollers 21 are so shaped to properly fit to the 
rounded convex surface of the rotary member 20 and the passive member 22, 
occurrences of displacement in its axial direction of each roller 21 can 
be restricted, thereby preventing displacements in the radial direction 
between the rotary member 20 and the passive member 22. Also, the 
restriction against motions of the rollers 21 toward their axial direction 
by their center-narrowed profile and the effect of varying outer diameter 
toward both ends along the axial direction of each roller 21 produce extra 
frictional force, thereby providing greater resistance force. 
FIG. 9 and FIG. 10 show a fourth preferred embodiment of this invention: 
FIG. 9 being an exploded perspective view of a friction resistance 
generator of the fourth preferred embodiment; FIG. 10(a) being a partial 
enlarged view of a cross-section in the radial direction of the drawing in 
FIG. 9; and FIG. 10(b) being a partial enlarged view of a portion seen 
from the axial direction of the drawing in FIG. 9. 
The friction resistance generator comprises a rotary member 30 rotating on 
its axis of rotation, numerous rollers 31 disposed along a track of 
rotation of the rotary member 30, a passive member 32 which coaxially 
faces the rotary member 30 across the rollers 31, and a cage 33 which 
maintains the rollers 31 at equal intervals in freely rotatable state. 
The rotary member 30 is in the form of a ring shape and, as shown in FIG. 
10(a), its surface facing the passive member 32 is a rounded concave shape 
in radial cross sections. 
The numerous rollers 31 are disposed at equal intervals along the 
peripheral direction of the rotary member 30 and their profile is such 
that the thickened central part narrows toward both ends gradually. Also, 
both ends of the rollers 31 are rounded to a hemi-spherical shape to 
lessen friction occurring between the rollers 31 and the cage 33. 
The passive member 32 is in the form of a ring shape and, similar to the 
rotary member 30, its surface facing the rotary member 30 is a rounded 
concave shape in radial cross sections. 
The cage 33 is in the form of a ring shape and its thickness in the axial 
direction is made thinner than the outer diameter of the rollers 31. The 
cage 33 is provided with numerous slots 33a to maintain the rollers 31. 
Each roller 31 is maintained in each slot 33a in freely rotatable state. 
Also, the slots 33a are so disposed that each axis of rolling of each 
roller is inclined by a prescribed angle to a plane containing the axis of 
rotation of the rotary member 30. 
FIG. 11 to FIG. 14 show a fifth preferred embodiment of this invention: 
FIG. 11 being an exploded perspective view of a friction resistance 
generator of the fifth preferred embodiment; FIG. 12(a) being a partial 
enlarged view of a cross-section in the radial direction of the drawing in 
FIG. 11; and FIG. 12(b) being a partial enlarged view of a portion seen 
from the axial direction of the drawing in FIG. 11. 
The friction resistance generator comprises a rotary member 40 rotating on 
its axis of rotation, numerous rollers 41 disposed along a track of 
rotation of the rotary member 40, a passive member 41 coaxially facing the 
rotary member 40 across the rollers 41, a cage 43 which maintains the 
rollers 41 at equal intervals in freely rotatable state, and numerous 
springs 44 which push respective rollers 41 toward a prescribed peripheral 
direction of the rotary member 40. 
The rotary member 40 is in the form of a ring shape and its surface facing 
the passive member 42 is a flat plane. 
The numerous rollers 41 are in the form of a cylindrical shape extending 
straight in their axial direction and disposed at equal intervals along 
the peripheral direction of the rotary member 40. Also, both ends of the 
rollers 41 are rounded to a hemi-spherical shape to lessen friction 
occurring between the rollers 41 and the cage 43. 
The passive member 42 is in the form of a ring shape and its surface facing 
the rotary member 40 is a flat plane. Also, around the periphery of the 
passive member 42, a flange 42a to cover up the peripheral surface of the 
rotary member 40 is provided. 
The cage 43 is in the form of a ring shape and its thickness in the axial 
direction is made thinner than the outer diameter of the rollers 41. The 
cage 43 is provided with numerous openings 43a to maintain the rollers 41. 
Each roller 41 is maintained in each opening 43a in freely rotatable 
state. Each opening 43a is in the form of a fan-shape with its pivot 
matching to the position of one end of each roller 41. One side of each 
opening 43a extending from the pivot is designed in parallel with a plane 
containing the axis of rotation of the rotary member 40 and the other side 
of each opening 43a extending from the pivot is designed to incline by a 
prescribed angle to a plane containing the axis of rotation of the rotary 
member 40. Also, numerous elastic convexities 43b forming a corrugated 
ring are provided around the periphery of the cage 43. The numerous 
elastic convexities 4b are placed in elastically compressed contact with 
the inner peripheral surface of the flange 42a of the passive member 42. 
The springs 44 are attached beside respective openings 43a of the cage 43. 
One end of each spring 44 is fastened to the cage 43, and the other end of 
each spring 44 abuts to each roller 41, thereby pushing the rollers 41 to 
a position maintaining an inclination to the track of rotation of the 
rotary member 40. 
With the friction resistance generator of the aforementioned structure, as 
shown in FIG. 13, when the rotary member 40 is rotated in a prescribed 
direction (clockwise in the drawing) while applying a load in the axial 
direction, respective rollers 41 make rolling motions being in contact 
with the rotary member 40 and the passive member 42, consequently the cage 
43 trails to rotate together. At that time, since respective rollers 41 
are motivated to roll toward a direction being inclined from the track of 
rotation of the rotary member 40, similar to the case of the preceding 
preferred embodiment, a frictional force in proportion to the magnitude of 
the load applied toward the axial direction occurs between the rollers 41 
and the rotary member 40 and between the rollers 41 and the passive member 
42. 
Also, as shown in FIG. 14, when the rotary member 40 is rotated toward the 
opposite direction (counter-clockwise in the drawing), respective rollers 
41 make rolling motions being in contact with the rotary member 40 and 
with the passive member 42 and, at the same time, they tilt their position 
inside respective openings 43a of the cage 43 and the axes of rolling of 
respective rollers 41 come in parallel with a plane containing the axis of 
rotation of the rotary member 40. 
When this happens, since the axes of rolling of respective rollers 41 are 
not inclined to the track of rotation of the rotary member 40, sliding 
friction does not occur with respective rollers 41, thus allowing the 
rotary member 40 to rotate smoothly. 
Also, since the elastic convexities 43b being provided around the periphery 
of the cage 43 is in compressed contact with the flange 42a of the passive 
member 42, when the direction of rotation is changed, respective rollers 
41 are prompted to tilt their position to the other side of the openings 
43a inasmuch as the cage 43 always remain retarded from the rolling motion 
of respective rollers 41 due to the contact resistance with the passive 
member 42. Moreover, since respective rollers 41 are always motivated to 
stay at the position not making inclination to the track of rotation of 
the rotary member 40 whichever the direction of rotation may be, 
respective rollers 41 are tilted forcefully by respective springs 44 when 
the direction of rotation is turned to the direction wherein application 
of a resistance is required. 
Thus, with the friction resistance generator of the fifth embodiment, since 
respective rollers 41 are so designed to tilt between the direction where 
the axes of rolling of the rollers 41 come in parallel with the plane 
containing the axis of rotation of the rotary member 40 and the direction 
where the axes of rolling of the rollers 41 become inclined to the axis of 
rotation of the rotary member 40, resistance occurring from the frictional 
force of respective rollers 41 can be exerted to the rotation of the 
rotary member 40 in one direction of rotation and smooth rotation can be 
acquired in the other direction of rotation. 
FIG. 15 and FIG. 16 show a sixth preferred embodiment of this invention: 
FIG. 15 being an exploded perspective view of a friction resistance 
generator of the sixth preferred embodiment; FIG. 16(a) being a partial 
enlarged view of a cross-section in the radial direction of the drawing in 
FIG. 15; and FIG. 16(b) being a partial enlarged view of a portion seen 
from the axial direction of the drawing in FIG. 15. 
The friction resistance generator comprises a rotary member 50 rotating on 
its axis of rotation, numerous rollers 51 being disposed along a track of 
rotation of the rotary member 50, numerous balls 52 being similarly 
disposed along the track of rotation of the rotary member 50, a passive 
member 53 coaxially facing the rotary member 50 across the numerous 
rollers 51, a cage 54 which maintains the rollers 51 and the balls 52 at 
prescribed intervals in freely rotatable state, a disc spring 55 which 
pushes the rotary member 50 toward the axial direction as a pre-loading 
means, and a housing 56 to house all these parts. 
The rotary member 50 is in the form of a ring shape and its surface facing 
the passive member 53 is a flat plane. Also, around the periphery of the 
rotary member 50, a guide flange 50a is provided wherewith the outer 
diameter of the passive member 53 side is made slightly larger than the 
outer diameter of the other side. The balls 52 are engaging with the guide 
flange 50a in freely rotatable state. 
The rollers 51 are in the form of a cylindrical shape extending straight in 
the axial direction and they are disposed at equal intervals along the 
peripheral direction of the rotary member 50. Also, both ends of the 
rollers 51 are rounded to a hemi-spherical shape to lessen friction 
occurring between the rollers 51 and the cage 53. 
The balls 52 are disposed between the outer peripheral surface of the 
rotary member 50 and the housing 56 at equal intervals along the 
peripheral direction of the rotary member 50. 
The passive member 53 is in the form of a ring shape and its surface facing 
the rotary member 50 is a flat plane. Also, around the periphery of the 
passive member 53, numerous keys 53a extending toward the axial direction 
are provided at prescribed intervals along the peripheral direction. 
The cage 54 is in the form of a ring shape and its thickness in the axial 
direction is made thinner than the outer diameter of the rollers 51. The 
cage 54 is provided with numerous slots 54a to maintain the rollers 51. 
Each roller 51 is maintained in each slot 54a in freely rotatable state. 
Also, the slots 54a are so disposed that the axes of rolling of the 
rollers 51 become inclined by a prescribed angle to a plain containing the 
axis of rotation of the rotary member 50. Also, around the periphery of 
the cage 54, numerous holes 54b to maintain the balls 52 are provided. 
Each hole 54b is maintaining each ball 52 in freely rotatable state. 
The disc spring 55 is inserted in compressed state between the passive 
member 53 and the inside of the housing 56, thus pushing the passive 
member 53 toward the rotary member 50 side constantly with a certain 
springing force. 
The housing 56 is in the form of a cylindrical shape and numerous key 
grooves 56a which engage with the keys 53a of the passive member 53 are 
provided on the inner peripheral surface of the housing 56. Also, a ring 
groove 56b in continuation around the inner periphery is provided in the 
inner peripheral surface of the housing 56 with which the balls 52 are 
individually engaging in freely rotatable state. Namely, inside the 
housing 56, as shown in FIG. 16(a), the passive member 53 is housed in a 
compressed state toward the rotary member 50 side by function of the disc 
spring 55 and, at the same time, the balls 52 being maintained 
individually by the cage 54 are engaging with the ring groove 56b provided 
in the bore surface of the housing 56 and the guide flange 50a of the 
rotary member 50. By this structure, dislocation toward the outside of the 
axial direction of the rotary member 50 is restricted, thus the rotary 
member 50 and the passive member 52 are compressed to each other across 
the rollers 51 under a certain pressure. 
With the friction resistance generator of the aforementioned structure, the 
frictional force occurring from respective rollers 51 can always keep at a 
certain level by the pre-load applied to the rotary member 50. Also, by 
application of a load in the axial direction to the rotary member 50, in 
addition to the pre-load of the disc spring 55, the frictional force can 
be optionally augmented. 
FIG. 17 represents a seventh preferred embodiment of this invention: FIG. 
17(a) being a partial enlarged view of a cross-section in the radial 
direction of a friction resistance generator of the seventh preferred 
embodiment; and FIG. 17(b) being a partial enlarged view of a portion seen 
from the axial direction of the friction resistance generator. 
The friction resistance generator comprises a rotary member 60 rotating on 
its axis of rotation, numerous rollers 61 disposed along a track of 
rotation of the rotary member 60, numerous balls 62 similarly disposed 
along the track of rotation of the rotary member 60, a guide ring 63 which 
rotates integrally with the rotary member 60, a cage 64 which maintains 
the rollers 61 and the balls 62 at prescribed intervals in freely 
rotatable state, a disc spring 65 which works as a pre-loading means to 
push the rotary member 60 toward the axial direction, and a housing 66 to 
house all these parts. 
The rotary member 60 is in the form of a ring shape and its surface on one 
side is a flat plane. Also, the other surface side of the rotary member 60 
is provided with a cylindrical structure. The outer peripheral surface of 
said cylindrical structure is provided with numerous keys 60a being formed 
at prescribed intervals in the peripheral direction. 
The rollers 61 are in the form of a cylindrical shape extending straight in 
the axial direction and they are disposed at equal intervals along the 
peripheral direction of the rotary member 60. Also, both ends of the 
rollers 61 are rounded to a hemi-spherical shape to lessen friction 
occurring between the rollers 61 and the cage 63. 
The balls 62 are located between the outer peripheral surface of the guide 
ring 63 and the inner peripheral surface of the housing 66 at equal 
intervals along the peripheral direction of the rotary member 60. 
The guide ring 63 is in the form of a ring shape and in its inner 
peripheral surface, numerous key grooves 63a to engage with the keys 60a 
of the rotary member 60 are provided. Also, the external periphery of the 
guide ring 63 is formed into a guide surface 63b wherewith the outer 
diameter at the rotary member 60 side is made slightly larger than the 
remaining sections. The balls 62 are engaging with the guide surface 63b 
in freely rotatable state. 
The cage 64 is in the form of a ring shape and its thickness in the axial 
direction is made thinner than the outer diameter of the rollers 61. The 
cage 64 is provided with numerous slots 64a to maintain the rollers 61. 
Each roller 61 is maintained in each slot 64a in freely rotatable state. 
Also, the slots 64a are so laid out that the each of rolling of each 
roller 61 becomes inclined by a prescribed angle to a plane containing the 
axis of rotation of the rotary member 60. Moreover, around the periphery 
of the cage 64, numerous holes 64b to maintain the balls 62 individually 
are provided. Each ball 62 is maintained in each hole 64b in freely 
rotatable state. 
The disc spring 65 is inserted in compressed state between the rotary 
member 60 and the inside of the guide ring 63, thus pushing the rotary 
member 60 toward the housing 66 side constantly with a certain springing 
force. 
The housing 66 is in the form of a cylindrical shape and its inside surface 
facing the rotary member 60 is formed to become a passive surface 66a. 
Also, a ring groove 66b in continuation around peripheral direction is 
provided in the inner peripheral surface of the housing 66 with which the 
balls 62 are individually engaging in freely rotatable state. Namely, in 
the housing 66, as shown in FIG. 17(a), the rotary member 60 is housed in 
a state being compressed toward the passive surface 66a side by the 
function of the disc spring 65 and, at the same time, the balls 62 being 
maintained by the cage 64 are engaging with the ring groove 66b provided 
in the bore surface of the housing 66 and the guide surface 63b of the 
guide ring 63. By this structure, dislocation toward the outside of the 
axial direction of the rotary member 60 is restricted, thus the rotary 
member 60 is compressed to the passive surface 66a of the housing 66 
across the balls 61 under a certain force. 
FIG. 18 and FIG. 19 show an eighth preferred embodiment of this invention: 
FIG. 18 being an exploded perspective view of a friction resistance 
generator of the eighth preferred embodiment; FIG. 19(a) being a partial 
enlarged view of a cross-section in the radial direction of the drawing in 
FIG. 18; and FIG. 19(b) being a partial enlarged view of a portion seen 
from the axial direction of the drawing in FIG. 18. 
The friction resistance generator comprises a rotary member 70 rotating on 
its axis of rotation, numerous rollers 71 disposed along a track of 
rotation of the rotary member 70, numerous balls 72 similarly disposed 
along the track of rotation of the rotary member 70, a guide ring 73 which 
rotates integrally with the rotary member 70, a roller cage 74 which 
maintains the rollers 71 at prescribed intervals in freely rotatable 
state, a ball cage 75 which maintains the balls 72 at prescribed intervals 
in freely rotatable state, numerous coil springs 76 which work as a 
pre-loading means to push the rotary member 70 toward the axial direction, 
and a housing 77 which houses all these parts. 
The rotary member 70 is in the form of a ring shape and its surface on one 
side is a flat plane. Also, the other surface side of the rotary member 70 
is provided with a cylindrical structure. The outer periphery of said 
cylindrical structure is provided with numerous keys 70a being formed at 
prescribed intervals in the peripheral direction. 
The rollers 71 are in the form of a cylindrical shape extending straight in 
the axial direction and they are disposed at equal intervals along the 
peripheral direction of the rotary member 70. Also, both ends of the 
rollers 71 are rounded to a hemi-spherical shape to lessen friction 
occurring between the rollers 71 and the cage 74. 
The balls 72 are located between the outer periphery of the guide ring 73 
and the inner periphery of the housing 77 at equal intervals along the 
peripheral direction of the rotary member 70. 
The guide ring 73 is in the form of a ring shape and in its inner 
peripheral surface, numerous key grooves 73a to engage with keys 70a of 
the rotary member 70 are provided. Also, the external periphery of the 
guide ring 73 forms a guide surface 73b wherewith the outer diameter of 
the rotary member 70 side is made slightly larger than the remaining 
sections. The balls 72 are engaging with the guide surface 73b in freely 
rotatable state. 
The roller cage 74 is in the form of a ring shape and its thickness in the 
axial direction is made thinner than the outer diameter of the rollers 71. 
The roller cage 74 is provided with numerous slots 74a to maintain the 
rollers 71. Each roller 71 is maintained in each slot 74a in freely 
rotatable state. Also, the slots 74a are so laid out that each axis of 
rolling of each roller 71 becomes inclined to a plane containing the axis 
of rotation of the rotary member 70. 
The ball cage 75 is in the form of a ring shape and its thickness in the 
axial direction is made thinner than the outer diameter of the balls 72. 
The ball cage 75 is provided with numerous holes 75a to maintain the balls 
72. Each ball 72 is maintained in each hole 75a in freely rotatable state. 
The coil springs 76 are inserted in compressed state between the rotary 
member 70 and the inside of the guide ring 73, thus pushing the rotary 
member 70 toward the housing 77 side constantly with a certain springing 
force. 
The housing 77 is in the form of a cylindrical shape and its inside surface 
facing the rotary member 70 is formed to become a passive surface 77a. 
Also, a ring groove 77b in continuation around the inner periphery is 
provided in the inner peripheral surface of the housing 77 with which the 
balls 72 are individually engaging in freely rotatable state. 
Namely, in the housing 77, as shown in FIG. 19(a), the rotary member 70 is 
housed in a state being compressed toward the passive surface 77a side of 
the housing 77 by the function of the coil springs 76 and, at the same 
time, the balls 72 maintained by the ball cage 75 are engaging with the 
ring grooves 77b provided in the bore surface of the housing 77 and the 
guide surface 73b of the guide ring 73. By this structure, dislocation 
toward the outside of the axial direction of the rotary member 70 is 
restricted, thus the rotary member 70 is compressed to the passive surface 
77a of the housing 77 across the rollers 71 under a certain force. 
Meanwhile, the motions occurring in the friction resistance generator of 
the eighth embodiment and effects thereof are the same as those of the 
preceding preferred embodiment of this invention. 
FIG. 20 and FIG. 21 show a ninth preferred embodiment of this invention: 
FIG. 20 being an exploded perspective view of a friction resistance 
generator of the ninth preferred embodiment; FIG. 21(a) being a partial 
enlarged view of a portion seen from the radial direction of the drawing 
in FIG. 20; and FIG. 21(b) being a partial enlarged view of a 
cross-section along the axial direction of the drawing in FIG. 20. 
The friction resistance generator comprises a rotary member 80 rotating on 
its axis of rotation, numerous rollers 81 disposed along a track of 
rotation of the rotary member 80, a pair of passive member 82 and 83 
covering the rotary member 80 from outside across the rollers 81, a cage 
84 which maintains the rollers 81 at prescribed intervals in freely 
rotatable state, a disc spring 85 which works to apply pre-load from the 
rotary member 80 and from the passive members 82 and 83 to each roller 81. 
The rotary member 80 is in the form of a ring shape and its peripheral 
surface facing the inner peripheral surfaces of the passive members 82 and 
83 curves along the axial direction so that the outer diameter thereof 
gradually becomes smaller from both ends to its center in the axial 
direction. 
The rollers 81 are in the form of a cylindrical shape and they are disposed 
at equal intervals in the peripheral direction of the rotary member 80. 
Also, both ends of the rollers 81 are rounded to a hemi-spherical shape to 
lessen friction occurring between the rollers 81 and the cage 84. 
The passive members 82 and 83 are in the form of ring shapes and their 
surfaces facing the outer peripheral surface of the rotary member 80 
curves along the passive surface of the rotary member 80. The passive 
members 82 and 83 are provided with numerous keys 82a and key grooves 83a 
extending toward the axial direction on their outer and inner periphery, 
respectively, and they are coupled by engagement of these keys 82a and key 
grooves 83a for free sliding in the axial direction. 
The cage 84 is in the form of a ring shape and its peripheral surface 
curves along the axial direction so that its diameter becomes smaller from 
both ends to its center in the axial direction. The cage 84 is provided 
with numerous slots 84a to maintain the rollers 81 in freely rotatable 
state. Also, the slots 84a are so laid out that each axis of rolling of 
each roller 81 becomes inclined by a prescribed angle to a plane 
containing the axis of rotation of the rotary member 80. 
The disc spring 85 is in the form of a ring shape being made of a disc 
shaped spring material having elasticity toward the axial direction. The 
disc spring 85 is inserted between the two passive members 82 and 83 in 
compressed state pushing the two passive members 82 and 83 toward the 
axial direction, respectively. 
With the friction resistance generator of the ninth embodiment, when the 
rotary member 80 is rotated, the rollers 81 make rolling motions in 
contact with the rotary member 80 and with the two passive members 82 and 
83, consequently the cage 84 also makes trailing rotation. 
At that time, similar to the case of the preceding embodiment of this 
invention, since the rollers 81 are forced to move along the track of 
rotation of the rotary member 80 while their motivation to roll toward a 
direction being inclined by a prescribed angle from the track of rotation 
of the rotary member 80 are restricted by the cage 84, sliding friction 
occurs between the rollers 81 and the rotary member 80 and between the 
rollers 81 and the passive members 82 and 83. 
At this time, since the two passive members 82 and 83 are motivated to move 
toward separating directions by the springing force of the disc spring 85, 
both ends of each roller 81 are pressed onto the rotary member 80. By 
occurrence of said movements, the rollers 81, the rotary member 80 and the 
passive members 82 and 83 are pressed toward each other, thus producing a 
certain frictional force in proportion to the magnitude of the pre-load 
applied by the disc spring 85. 
FIG. 22 and FIG. 23 show a tenth preferred embodiment of this invention: 
FIG. 22 being an exploded perspective view of a friction resistance 
generator of the tenth preferred embodiment; FIG. 23(a) being a partial 
enlarged view of a portion seen from the radial direction of the drawing 
in FIG. 22; and FIG. 23(b) being a partial enlarged view of a 
cross-section along the axial direction of the drawing in FIG. 22. 
The friction resistance generator comprises a pair of rotary members 90 and 
91 rotating on their axis of rotation, a guide ring 92 which maintains the 
rotary members 90 and 91, numerous rollers 93 disposed along a track of 
rotation of the rotary members 90 and 91, numerous balls 94 similarly 
disposed along the track of rotation of the rotary members 90 and 91, a 
passive member 95 which is positioned to cover the outer peripheries of 
the rotary members 90 and 91 across the rollers 93 and the balls 94, a 
cage 96 which maintains the rollers 93 and the balls 94 at prescribed 
intervals in freely rotatable state, and a disc spring 97 which works to 
apply pre-load from the rotary members 90 and 91 and from the passive 
member 95 to the rollers 93. 
The rotary members 90 and 91 are in the form of ring shapes. A portion of 
the peripheral surface of one 90 of the pair of rotary members and the 
whole peripheral surface of the other rotary member 91 which face the bore 
surface of the passive member 95 are formed to a concave cross sectional 
shape along the axial direction. Also, in the remaining peripheral surface 
of the one 90 of the rotary members, a ring groove 90a is formed in 
continuation in the peripheral direction and the balls 94 are engaging 
with the ring groove 90a in freely rotatable state. 
The guide ring 92 is in the form of a ring shape being provided with a 
flange 92a exerting outward at its one end. The guide ring 92 is located 
inside the rotary members 90 and 91, and one 90 of the pair of rotary 
members is fastened to the other end of the guide ring 92 by bolts 92b. 
Also, in the outer periphery of the guide ring 92, numerous keys 92c 
extending toward the axial direction are formed, and in the inner 
periphery of the other rotary member 91, numerous key grooves 91a 
extending toward the axial direction are formed. The keys 92c and the key 
grooves 91a are engaging together to couple the guide ring 92 and the 
rotary member 91 for free slides in the axial direction. 
The rollers 93 are in the form of a cylindrical shape being disposed at 
equal intervals along the peripheral direction of the rotary members 90 
and 91. Also, both ends of the rollers 93 are rounded to a hemispherical 
shape to lessen frictional resistance occurring between the rollers 93 and 
the cage 96. The balls 94 are located between one 90 of the rotary members 
and the passive member 95 at equal intervals along the peripheral 
direction of the rotary members 90 and 91. 
The passive member 95 is in the form of a ring shape, and a portion of its 
inner peripheral surface facing the combined concave surfaces including of 
the combination of a portion of the outer peripheral surface of one 90 of 
the pair of rotary members and the whole outer peripheral surface of the 
other rotary member 91 is formed to a convex cross sectional shape along 
the axial direction. In the remaining inner peripheral surface of the 
passive member 95, a ring groove 95a is formed in continuation in the 
peripheral direction. The balls 94 are engaging with the ring groove 95a 
in freely rotatable state. 
The cage 96 is in the form of a ring shape and a portion facing the outer 
periphery of the other rotary member 91 of its bore surface is formed to a 
convex cross sectional shape along the outer periphery of the rotary 
member 91. Also, the cage 96 is provided with numerous slots 96a and 
numerous holes 96b to maintain the rollers 93 and the balls 94. Each 
roller 93 is maintained in each slot 96a and each ball 94 is maintained in 
each hole 96b, respectively. Also, the slots 96a are so laid out that each 
axis of rolling of each roller 93 becomes inclined by a prescribed angle 
to a plane containing the axis of rotation of the rotary members 90 and 
91. 
The disc spring 97 is in the form of a ring shape being made of a disc 
shaped spring material having elasticity toward the axial direction. The 
disc spring 97 is inserted between the rotary member 91 and the flange 92a 
of the guide ring 92 in compressed state, pushing the rotary member 91 
toward the axial direction. 
With the friction resistance generator of the tenth embodiment, since the 
rotary member 91 is motivated to approach the rotary member 90 by the 
springing force of the disc spring 97, thereby both ends of each roller 93 
are depressed to the passive member 95. By occurrence of said movements, 
the rollers 93, the rotary members 90 and 91 and the passive member 95 are 
depressed each other, thus producing a certain frictional force in 
proportion to the magnitude of the pre-load applied by the disc spring 97, 
similar to the case of the preceding embodiment of this invention. 
Also, since the balls 94 are engaging with respective ring grooves 90a and 
95a of the rotary member 90 and the passive member 95, dislocations in the 
axial direction of the rotary members 90 and 91 and the passive member 95 
are prevented. 
FIG. 24 and FIG. 25 show an eleventh preferred embodiment of this 
invention: FIG. 24 being an exploded perspective view of a friction 
resistance generator of the eleventh preferred embodiment; FIG. 25(a) 
being a partial enlarged view of a portion seen from the radial direction 
of the drawing in FIG. 24; FIG. 25(b) being a partial enlarged view of a 
cross section along the radial direction of the drawing in FIG. 24; and 
FIG. 25(c) being a partial enlarged view of a portion seen from the axial 
direction of the drawing in FIG. 24. 
The friction resistance generator comprises a rotary member 100 rotating on 
its axis of rotation, a guide ring 101 which maintains the rotary member 
100, numerous rollers 102 disposed along a track of rotation of the rotary 
member 100, a passive member 103 which is positioned to cover the outer 
periphery of the rotary member 100 across the rollers 102, a cage 104 
which maintains the rollers 102 at prescribed intervals in freely 
rotatable state, a pair of ring springs 105 which work to apply pre-load 
from the rotary member 100 and the passive member 103 to the rollers 102. 
The rotary member 100 is in the form of a split structure, into radially 
two halves, and its outer periphery facing the inner peripheral surface of 
the passive member 103 is formed to a concave cross sectional shape along 
the axial direction. Also, on the inner peripheral surface of the rotary 
member 100, plural projections 100a are provided at prescribed intervals 
along the peripheral direction. 
The guide ring 101 is in the form of a ring shape and the rotary member 100 
is installed around the outer periphery of the guide ring 101 in freely 
movable state in the radial direction. Also, around the outer peripheral 
surface of the guide ring 101, dents 101a mating the projections 100a of 
the rotary member 100 are provided. 
The rollers 102 are disposed at equal intervals along the peripheral 
direction of the rotary member 100, and are in the form of a barrel shape, 
namely the largest outer diameter at the center gradually becomes smaller 
toward both ends. Also, both ends of the rollers 102 are rounded to a 
hemispherical shape to lessen frictional resistance occurring between the 
rollers 102 and the cage 104. 
The passive member 103 is in the form of a ring shape carrying a flat cross 
sectional bore surface shape along the axial direction. 
The cage 104 is in the form of a ring shape and its inner peripheral 
surface is formed to a convex cross sectional shape along the axial 
direction matching the concave cross sectional shape of the outer 
peripheral surface of the rotary member 100. 
The cage 104 is provided with numerous slots 104a to maintain the rollers 
102 in freely rotatable state, and the slots 104a are so laid out that the 
axes of rolling of the rollers 102 become inclined by a prescribed angle 
to a plane containing the axis of rotation of the rotary member 100. 
The ring springs 105 are in the form of ring shapes being made of a 
wave-formed spring material having elasticity toward the radial 
directions. The ring springs 105 are inserted between the inner periphery 
of the rotary member 100 and the outer periphery of the short sleeves at 
both ends of the guide ring 101 in compressed state, pushing the rotary 
member 100 toward the outside in the radial direction. 
With the friction resistance generator of the eleventh embodiment, since 
the rollers 102 are in the form of barrel-shapes and their surface shape 
is matching the concave outer peripheral surface of the rotary member 100, 
sliding friction occurring from the uneven outer diameter of the rollers 
102 can also be acquired in addition to the sliding friction occurring 
from the inclination of the axes of rolling of the rollers 102, thus 
providing even greater resisting force. 
FIG. 26 shows a twelfth preferred embodiment of this invention: FIG. 26(a) 
being a partial enlarged view of a portion seen from the radial direction 
of a friction resistance generator of the twelfth preferred embodiment; 
FIG. 26(b) being a partial enlarged view of a cross section along the 
radial direction of the friction resistance generator; and FIG. 26(c) 
being a partial enlarged view of a portion seen from the axial direction 
of the friction resistance generator. 
The friction resistance generator comprises a rotary member 110 rotating on 
its axis of rotation, numerous rollers 111 disposed along a track of 
rotation of the rotary member 110, a passive member 112 which is 
positioned to face the outer periphery of the rotary member 110 across the 
rollers 111, a guide ring 113 which maintains the passive member 112, a 
cage 114 maintains the rollers 111 at prescribed intervals in freely 
rotatable state, and a pair of ring springs 115 which work to apply 
pre-load from the rotary member 110 and the passive member 112 to the 
rollers 111. 
The rotary member 110 is in the form of a ring shape and the outer 
peripheral surface of the rotary member 110 facing the inner peripheral 
surface of the passive member 112 is formed to a convex cross sectional 
shape along the axial direction. 
The rollers 111 are disposed at equal intervals along the peripheral 
direction of the rotary member 110, and are in the form of shapes 
wherewith the smallest outer diameter at their center gradually becomes 
larger toward both ends. Also, both ends of the rollers 111 are rounded to 
a hemi-spherical shape to lessen frictional resistance occurring between 
the rollers 111 and the cage 114. 
The passive member 112 is in the form of a split structure, into radially 
two halves, and its inner peripheral surface facing the outer periphery of 
the rotary member 110 is formed to a concave cross sectional shape along 
the axial direction. Also, on the outer peripheral surface of the passive 
member 112, plural projections 112a are provided at prescribed intervals 
along the peripheral direction. 
The guide ring 113 is in the form of a ring shape and the passive member 
112 is installed around the inner periphery of the guide ring 113 in 
freely movable state in the radial direction. Also, around the inner 
peripheral surface of the guide ring 113, dents 113a to mate the 
projections 112a of the passive member 112 are provided. 
The cage 114 is in the form of a ring shape and its thickness in the radial 
direction is made thinner than the outer diameter of the rollers 111. The 
cage 114 is provided with numerous slots 114a to maintain the rollers 111 
in freely rotatable state, and the slots 114a are so disposed that the 
axes of rolling of the rollers 111 become inclined by a prescribed angle 
to a plane containing the axis of rotation of the rotary member 110. 
The ring springs 115 are in the form of ring shapes being made of a 
wave-formed spring material having elasticity toward the radial 
directions. The ring springs 115 are inserted between the outer periphery 
of the passive member 112 and inner periphery of the short sleeves at both 
ends of the guide ring 113 in compressed state, pushing the passive member 
112 toward the inside in the radial direction. 
With the friction resistance generator of the twelveth embodiment, since 
the concave shaped surface of the rollers 111 is matching the convex outer 
peripheral surface of the rotary member 110 and convex inner peripheral 
surface of the passive member 112, similar to the case of the preceding 
embodiment of this invention, sliding friction occurring from the uneven 
outer diameter of the rollers 111 can also be acquired in addition to the 
sliding friction occurring from the inclination of the axes of rolling of 
the rollers 111, thus providing even greater resisting force. 
FIG. 27 and FIG. 28 show a thirteenth preferred embodiment of this 
invention: FIG. 27 being an exploded perspective view of a friction 
resistance generator of the thirteenth preferred embodiment; FIG. 28(a) 
being a partial enlarged view of a portion seen from the radial direction 
of the drawing in FIG. 27; and FIG. 28(b) being a partial enlarged view of 
a cross section along the radial direction of the drawing in FIG. 27. 
The friction resistance generator comprises a rotary member 120 rotating on 
its axis of rotation, numerous rollers 121 disposed along a track of 
rotation of the rotary member 120, numerous balls 122 similarly disposed 
along the track of rotation of the rotary member 120, a pair of passive 
members 123 and 124 which are positioned to cover the outer periphery of 
the rotary member 120 across the rollers 121 and the balls 122, a cage 125 
which maintains the rollers 121 and the balls 122 at prescribed intervals 
in freely rotatable state, and a disc spring 126 which works to apply 
pre-load from the rotary member 120 and one 123 of the pair of passive 
members to the rollers 121. 
The rotary member 120 is in the form of a ring shape and the portion of its 
outer peripheral surface facing the bore surface of the one 123 of the two 
passive members is in the form of a conical shape. The remaining outer 
peripheral surface facing the bore surface of the passive member 124 is 
provided with a ring groove 120a tracing in continuation along the 
peripheral direction. The balls 122 are in engagement with the ring groove 
120a in freely rotatable state. 
The rollers 121 are in the form of a conical shape being disposed at equal 
intervals along the peripheral direction of the rotary member 120. The 
rollers 121 are so directed that their smaller diameter ends come to the 
smaller diameter side of the conically shaped part of the rotary member 
120 and their larger diameter ends come to the larger diameter side of the 
conically shaped part of the rotary member 120. Also, as shown in FIG. 
28(b), each roller 121 is so positioned that an intersecting point X of 
the lines extended along both sides of its conical body surfaces toward 
the axial direction does not coincide with the axis of rotation 
(indication being omitted from the drawing) of the rotary member 120. 
The balls 122 are located between the rotary member 120 and the passive 
member 124 at equal intervals in the peripheral direction of the rotary 
member 120. 
The passive members 123 and 124 are in the form of ring shapes, one 123 of 
the pair of passive members carries conical shaped surface on a plane 
facing the rotary member 120 and the other passive member 124 carries flat 
shaped surface on the plane facing the rotary member 120. 
The passive members 123 and 124 are provided with numerous keys 123a and 
key grooves 124a extending toward the axial direction in the outer 
periphery and inner periphery, respectively, and they are coupled by 
engaging the keys 123a and the key grooves 124a for free movement in the 
axial direction. 
Also, the passive member 124 is provided with a ring groove 124b tracing in 
continuation along the peripheral direction, similar to the rotary member 
120. The balls 122 are also in engagement with the ring groove 124b in 
freely rotatable state. 
The cage 125 is in the form of a ring shape and its portion facing one 123 
of the passive members is formed to a conical shape. The cage 125 is 
provided with numerous slots 125a and numerous holes 125b to individually 
maintain the rollers 121 and the balls 122, respectively, and the slots 
125a to maintain the rollers 121 are located along the conically shaped 
portion of the surface of the case 125. 
The disc spring 126 is in the form of a ring shape being made of a disc 
shaped spring material having elasticity toward the axial direction. The 
disc spring 126 is inserted between the passive members 123 and 124 in 
compressed state, pushing the passive members 123 and 124 apart from each 
other toward the axial direction. 
With the friction resistance generator of the thirteenth embodiment, when 
the rotary member 120 is rotated, the rollers 121 make rolling motions in 
contact with the surfaces of the rotary member 120 and one 123 of the 
passive members, consequently the cage 125 also makes trailing rotation. 
At that time, since the balls 122 are engaging with the ring grooves 120a 
of the rotary member 120 and the ring groove 124b of the passive member 
124, respectively, dislocation toward the axial direction of the rotary 
member 120 and the passive member 124 are prevented. 
Also, since each roller 121 is so positioned that the intersecting point X 
of the lines extended along both sides of its conical body surfaces toward 
its axial direction does not coincide with the axis of rotation of the 
rotary member 120, when respective rollers 121 roll between the rotary 
member 120 and the passive member 123, the revolution difference occurring 
between the larger diameter end and the smaller diameter end of respective 
rollers 121 does not coincide with the revolution difference occurring 
between the larger diameter side and smaller diameter side of the rotary 
member 120. Consequently, sliding friction occurs between the rollers 121 
and the rotary member 120, and between the rollers 121 and the passive 
member 123, thus providing resistance to the rotary movement of the rotary 
member 120. At this time, since the rollers 121, the rotary member 120 and 
the passive member 123 are depressed by the function of the disc spring 
126, a certain frictional force in proportion to the magnitude of the 
pre-load of the disc spring 126 can be produced here. 
FIG. 29 shows a fourteenth preferred embodiment of this invention: FIG. 
29(a) being a partial enlarged view of a portion seen from the radial 
direction of a friction resistance generator of the fourteenth preferred 
embodiment; and FIG. 29(b) being a partial enlarged view of a cross 
section along the radial direction of the friction resistance generator. 
The friction resistance generator comprises a rotary member 130 rotating on 
its axis of rotation, numerous rollers 131 disposed along a track of 
rotation of the rotary member 130 in two lines, a pair of passive members 
132 and 133 facing the rotary member 130 from outside in the radial 
direction across the rollers 131, a cage 134 which maintains the rollers 
131 at prescribed intervals in freely rotatable state, and a disc spring 
135 which works to apply preload from the rotary member 130 and from the 
passive members 132 and 133 to the rollers 131. 
The rotary member 130 is in the form of a ring shape and its outer 
peripheral surface facing the passive members 132 and 133 is formed to a 
combination of two conical profiles, the outer diameter thereof becoming 
smaller toward the center in the axial direction from the two largest 
outer diameters at both ends. 
The rollers 131 are in the form of a conical shape being disposed at equal 
intervals along the peripheral direction of the rotary member 130. The 
rollers 131 are so directed that their smaller diameter ends come to the 
smaller diameter side of the conically shaped part of the rotary member 
130 and that their larger diameter ends come to the larger diameter side 
of the conically shaped part of the rotary member 130. Also, as shown in 
FIG. 29(b), each roller 131 is so positioned that an intersecting point X 
of the lines extended along both sides of its conical body surfaces toward 
the axial direction does not coincide with the axis of rotation 
(indication being omitted from the drawing) of the rotary member 130. 
The passive members 132 and 133 are in the form of ring shapes and their 
inner peripheral surfaces facing the rotary member 130 are formed to 
conical profiles matching the combined conical profiles of the outer 
peripheral surface of the rotary member 130. 
The passive members 132 and 133 are provided with numerous keys 132a and 
numerous key grooves 133a extending toward the axial direction in the 
outer peripheral surface of the passive member 132 and in a portion of the 
inner peripheral surface of the passive member 133, respectively. The 
passive members 132 and 133 are coupled by engagement of the keys 132a and 
the key grooves 133a for free movement in the axial direction. 
The cage 134 is in the form of a ring shape including a combination of two 
conical profiles, the outer diameter thereof becoming smaller toward the 
center in the axial direction from the two largest diameters at both ends. 
Also, the cage 134 is provided with numerous slots 134a in axially two 
lines in the radial direction to maintain the rollers 131 individually in 
freely rotatable state. Said two lines of slots 134a are alternately 
shifted in their relative positions. 
The disc spring 135 is in the form of a ring shape being made of a disc 
shaped spring material having elasticity toward the axial direction. The 
disc spring 135 is inserted between the passive members 132 and 133 in 
compressed state, pushing the passive members 132 and 133 apart from each 
other toward the axial direction. 
With the friction resistance generator of the fourteenth embodiment, since 
the rollers 131 are located in axially two lines, larger frictional force 
can be acquired. The principle of occurrence of the frictional force is 
same as the case of the preceding embodiment of this invention. 
FIG. 30 and FIG. 31 show a fifteenth preferred embodiment of this 
invention: FIG. 30 being an exploded perspective view of a friction 
resistance generator of the fifteenth preferred embodiment; FIG. 31(a) 
being a partial enlarged view of a portion seen from the radial direction 
of the drawing in FIG. 30; and FIG. 31(b) being a partial enlarged view of 
a cross section along the radial direction of the drawing in FIG. 30. 
The friction resistance generator comprises a pair of rotary members 140 
and 141 rotating on their axes of rotation, numerous rollers 142 disposed 
in axially two lines in the radial direction along a track of rotation of 
the rotary members 140 and 141, a passive member 143 covering the outer 
peripheries of the rotary members 140 and 141 in the radial direction 
across the rollers 142, a cage 144 which maintains the rollers 142 
individually at prescribed intervals in freely rotatable state, a disc 
spring 145 which works to apply pre-load from the rotary members 140 and 
141 and from the passive member 143 to the rollers 142. 
The rotary members 140 and 141 are in the form of ring shapes and their 
outer peripheral surfaces facing the inner peripheral surface of the 
passive member 143 are formed to conical profiles, the outer diameters 
thereof becoming larger toward the center in the axial direction from the 
two smallest outer diameters at both ends, under the status where the 
rotary members 140 and 141 are coupled together. 
The rotary members 140 and 141 are provided with numerous keys 140a and 
numerous key grooves 141a extending toward the axial direction in a 
portion of the outer peripheral surface of the rotary member 140 and in 
the inner peripheral surface of the rotary member 141, respectively. The 
rotary members 140 and 141 are coupled by engagement of the keys 140a and 
the key grooves 141a for free movement in the axial direction. 
The rollers 142 are in the form of a conical shape being laid out at equal 
intervals along the peripheral direction of the rotary members 140 and 
141. The rollers 142 are so directed that their smaller diameter ends come 
to the smaller diameter side of the conically shaped part of the rotary 
member 140 and their larger diameter ends come to the larger diameter side 
of the conically shaped part of the rotary member 140. 
Also, similar to the case of the preceding embodiment, each roller 142 is 
so positioned that an intersecting point of the lines extended along both 
sides of its conical body surfaces toward the axial direction does not 
coincide with the axis of rotation of the rotary member 140. 
The passive member 143 is in the form of a ring shape and its inner 
peripheral surface facing the outer peripheral surfaces of the rotary 
members 140 and 141 is formed to a combination of two conical profiles, 
the outer diameter thereof becoming larger toward the center in the axial 
direction from the two smallest diameters at both ends. 
The cage 144 is in the form of a ring shape including two conical profiles, 
the outer diameter thereof becoming larger toward the center in the axial 
direction from the two smallest diameters at both ends. The cage 144 is 
provided with numerous slots 144a in axially two lines in the radial 
direction to maintain the rollers 142 individually in freely rotatable 
state. Said two lines of slots 144a are positioned symmetrically each 
other. 
The disc spring 145 is in the form of a ring shape being made of a disc 
shaped spring material having elasticity toward the axial direction. The 
disc spring 145 is inserted between the rotary members 140 and 141 in 
compressed state, pushing the rotary members 140 and 141 apart from each 
other toward the axial direction. 
With the friction resistance generator of the fifteenth embodiment, similar 
to the case of the preceding embodiment, since the rollers 142 are 
disposed in axially two lines in the radial direction along the track of 
rotation of the rotary members 140 and 141, larger frictional force can be 
acquired. The principle of occurrence of the frictional force is the same 
as the case of the preceding embodiment. 
FIG. 32 shows a sixteenth preferred embodiment of this invention: FIG. 
32(a) being a partial enlarged view of a portion of a friction resistance 
generator of the sixteenth preferred embodiment seen from the radial 
direction; and FIG. 32(b) being a partial enlarged view of a cross section 
along the radial direction of the friction resistance generator. 
The friction resistance generator comprises a pair of rotary members 150 
and 151 rotating on their axes of rotation, numerous rollers 152 disposed 
in axially two lines in the radial direction along tracks of rotation of 
the rotary members 150 and 151, a passive member 153 which covers the 
outer peripheries of the rotary members 150 and 151 in the radial 
direction, a cage 154 which maintains the numerous rollers 152 
individually at prescribed intervals in freely rotatable state, a disc 
spring 155 which works to apply pre-load from the rotary members 150 and 
151 and from the passive member 153 to the rollers 152. 
The rotary members 150 and 151 are in the form of ring shapes and their 
outer peripheral surfaces facing the inner peripheral surface of the 
passive member 153 are formed to conical profiles, the outer diameter 
thereof becoming larger toward the center in the axial direction from the 
two smallest outer diameters at both ends, under the status where the two 
rotary members are coupled together. 
The rotary members 150 and 151 are provided with numerous keys 150a and 
numerous key grooves 151a extending toward the axial direction in a 
portion of the outer peripheral surface of the rotary member 150 and in 
the inner peripheral surface of the rotary member 151, respectively. The 
rotary members 150 and 151 are coupled by engagement of the keys 150a and 
key grooves 151a for free movement in the axial direction. 
The rollers 152 are in the form of a conical shape being laid out at equal 
intervals along the peripheral direction of the rotary members 150 and 
151. The rollers 152 are so directed that their smaller diameter ends come 
to the larger diameter side of the conically shaped part of the rotary 
member 150 and their larger diameter ends come to the smaller diameter 
side of the conically shaped part of the rotary member 150. Also, as shown 
in FIG. 32(b), each roller 152 is so positioned that an intersecting point 
X of the lines extended along both sides of its conical body surfaces 
toward the axial direction does not coincide with the axis of rotation 
(indication being omitted from the drawing) of the rotary member 150. 
The passive member 153 is in the form of a ring shape and its inner 
peripheral surface facing the outer peripheral surfaces of the rotary 
members 150 and 151 is formed to a combination of two conical profiles, 
the outer diameter thereof becoming larger toward the center in the axial 
direction from the two smallest diameters at both ends. 
The cage 154 is in the form of a ring shape including two conical profiles, 
the outer diameter thereof becoming larger toward the center in the axial 
direction from the two smallest diameters at both ends. 
The cage 154 is provided with numerous slots 154a in axially two lines in 
the radial direction to maintain the rollers 152 individually in freely 
rotatable state. Said two lines of slots 154a are positioned symmetrically 
each other. 
The disc spring 155 is in the form of a ring shape being made of a disc 
shaped spring material having elasticity toward the axial direction. The 
disc spring 155 is inserted between the rotary members 150 and 151 in 
compressed state, pushing the rotary members 150 and 151 apart from each 
other in the axial direction. 
With the friction resistance generator of the sixteenth embodiment, since 
the rollers 152 are so directed that their smaller diameter ends come to 
the larger diameter side of the conically shaped part of the rotary member 
150 and their larger diameter ends come to the smaller diameter side of 
the conically shaped part of the rotary member 150, the intersecting point 
X of the lines extended along both sides of the conical body surfaces 
toward the axial direction comes farther away from the axis of rotation of 
the rotary member 150 as compared with the case of the preceding 
embodiment, thus providing larger sliding friction between the rollers 152 
and the rotary members 150 and 151 and between the rollers 152 and the 
passive member 153. Meanwhile, the principle of occurrence of the 
frictional force is the same as the case of the preceding embodiment. 
FIG. 33 to FIG. 36 show a seventeenth preferred embodiment of this 
invention: FIG. 33 being an exploded perspective view of a friction 
resistance generator of the seventeenth preferred embodiment; FIG. 34(a) 
being an enlarged view of a portion seen from the top of the drawing in 
FIG. 33; and FIG. 34(b) being an enlarged view of a cross section seen 
from the front side of the drawing in FIG. 33. 
The friction resistance generator comprises a sliding member 160 which is 
designed to slide in rectilinear directions, numerous rollers 161 disposed 
along a track of movement of the sliding member 160, numerous balls 162 
similarly disposed along the track of movement of the sliding member 160, 
a passive member 163 which faces the sliding member 160 across the rollers 
161 and the balls 162, a cage 164 which maintains the rollers 161 and the 
balls 162 at prescribed intervals in freely rotatable state. 
These parts are the minimum requirements to constitute the friction 
resistance generator of this embodiment. In actual applications, the 
sliding member 160 is to be connected to a driving mechanism or the like, 
indication thereof being omitted from the drawing, and the passive member 
163 is to be fastened to a stationary state. 
The sliding member 160 is in the form of a plate shape and the center 
section of its surface facing the passive member 163 (the bottom surface) 
is formed to a flat plane. Also, on both sides of the bottom surface, a 
groove 160a each of a V-shaped cross section is provided in continuation 
along the longitudinal direction. The balls 162 are in engagement with a 
pair of said grooves 160a in freely rotatable state. Meanwhile, since the 
explanations are made only on the structure of the friction resistance 
generator and on occurring movements therein, the sliding member 160 is 
represented by a simplified shape of a short length. 
The rollers 161 are in the form of a cylindrical shape extending straight 
toward their axes of rolling and they are disposed at equal intervals 
along the longitudinal direction of the sliding member 160. Also, both 
ends of each roller 161 are rounded to a hemispherical shape to lessen 
friction occurring with the cage 164. 
The balls 162 are disposed at equal intervals in two lines along the 
longitudinal direction of the sliding member 160 putting the rollers 161 
in between the two lines. 
The passive member 163 is in the form of a plate shape and the center 
section of its surface facing the sliding member 160 (the upper surface) 
is formed to a flat plane. Also, on both sides of the upper surface of the 
passive member 163, a pair of said groove 163a of a V-shaped cross section 
are provided in continuation along the longitudinal direction. The balls 
162 are in engagement with the grooves 163a in freely rotatable state. 
Meanwhile, similar to the case of the aforesaid sliding member 160, the 
passive member 163 is represented by a simplified shape. 
The cage 164 is in the form of a plate shape and its thickness is made 
thinner than the outer diameter of the rollers 161. The cage 164 is 
provided with numerous slots 164a to maintain the rollers 161 individually 
and with numerous holes 164b to maintain the balls 162 individually. Each 
slot 164a and each hole 164b maintain each roller 161 and each ball 162, 
respectively in freely rotatable state. Also, as shown in FIG. 34(a), each 
slot 164a is so directed that each axis of rolling of each roller 161 
becomes inclined by an angle .theta. from the plane B perpendicular to the 
sliding direction of the sliding member 160. 
With the friction resistance generator of the aforementioned structure, as 
shown in FIG. 35, when the sliding member 160 is slided in the rectilinear 
directions with a load F applied toward the passive member 163, the 
rollers 161 make rolling motions in contact with the surfaces of the 
sliding member 160 and the passive member 163, thus the cage 164 also 
trails to move forward. 
At that time, as shown in FIG. 36, since the rollers 161 are forced to move 
along the track of movement of the sliding member 160 (along the direction 
of the solid line) while their motivation to roll toward a direction 
inclined by the angle .theta. from the track of movement (in the direction 
of the alternate long and short dash line) of the sliding member 160 are 
restricted by the cage 164, frictional force commensurate with the load F 
to the axial direction occurs between the rollers 161 and the sliding 
member 160 and between the rollers 161 and the passive member 163. At this 
time, since the rollers 161 cause sliding friction while making rolling 
motions, static friction does not occur and stable resistance force 
exerted by dynamic friction can always be acquired. Even if the static 
friction may occur during initial stage, rolling motion of the rollers 161 
immediately causes shifts to dynamic friction. 
Also, situations without production of the frictional force can also be 
obtained optionally by releasing the load applied through the sliding 
member 160. Moreover, since the balls 162 are in engagement with the 
grooves 160a and 163a of the sliding member 160 and the passive member 
163, respectively, dislocation toward the crosswise direction of the 
sliding member 160 or the passive member 163 is prevented. In this 
instance, the balls 162 leave slight clearance when engaging with the 
grooves 160a and 163a in order not to interfere the contact between the 
rollers 161 and the sliding member 160 and between the rollers 161 and the 
passive member 163. 
Thus, with the friction resistance generator of the seventeenth embodiment, 
since sliding friction is produced while the rollers 161 are rolled along 
by inclining the axes of rolling of the rollers 161 by a prescribed angle 
to a plane perpendicular to the sliding direction of the sliding member 
160, discretionary resistance force in proportion to the load applied 
toward the passive member 163 can be exerted to the rectilinear movement 
of the sliding member 160 and, furthermore, the resistance force exerted 
to the rectilinear movement of the sliding member can be very easily 
controlled by changing the magnitude of said load. 
With the friction resistance generator, since the aforesaid sliding 
friction is produced pursuant to the rolling motions of the rollers 161, 
stable resistance force can be always acquired without fear of occurrences 
of static friction which causes so-called stick-slip phenomenon. 
Meanwhile, the balls 162 can be omitted when necessary. 
FIG. 37 shows an eighteenth preferred embodiment of this invention: FIG. 
37(a) being an enlarged plan view of a portion of a friction resistance 
generator of the eighteenth preferred embodiment; and FIG. 37(b) being an 
enlarged view of a cross-section perpendicular to the longitude of the 
friction resistance generator. Similar to the preceding embodiment, the 
friction resistance generator comprises a sliding member 170, numerous 
rollers 171, numerous balls 172, a passive member 173 and a cage 174. The 
balls 172 and the rollers 171 are disposed alternately along a single line 
one after another. Meanwhile, the movements occurring in the friction 
resistance generator of this embodiment and the effects thereof are the 
same as those of the preceding embodiment. 
FIG. 38 shows a nineteenth preferred embodiment of this invention: FIG. 
38(a) being an enlarged plan view of a portion of a friction resistance 
generator of the nineteenth preferred embodiment; and FIG. 38(b) being an 
enlarged view of a cross-section perpendicular to the longitude of the 
friction resistance generator. 
Similar to the preceding embodiment, the friction resistance generator 
comprises a sliding member 180, numerous rollers 181, numerous balls 182, 
a passive member 183 and a cage 184. The rollers 181 are disposed 
alternately in opposite directions which are inclined by a prescribed 
angle to a plane perpendicular to the sliding direction of the sliding 
member 180. Consequently, the friction resistance generator of this 
embodiment exhibits always equal resistance characteristics in either 
sliding direction of the sliding member 180. The principle of producing 
the frictional force is the same as that of the preceding embodiment. 
FIG. 39 shows a twentieth preferred embodiment of this invention: FIG. 
39(a) being an enlarged plan view of a portion of a friction resistance 
generator of the twentieth preferred embodiment of this invention; FIG. 
39(b) being an enlarged view of a cross-section perpendicular to the 
longitude of the friction resistance generator. 
The friction resistance generator comprises a sliding member 190 which 
slides in the rectilinear directions, numerous rollers 191 disposed along 
a track of movement of the sliding member 190, numerous balls 192 disposed 
similarly along the track of movement of the sliding member 190, a passive 
member 193 which faces the sliding member 190 across the rollers 191, and 
a cage 194 which maintains the rollers 191 and the balls 192 at prescribed 
intervals in freely rotatable state. 
The sliding member 190 is in the form of a plate shape and its surface 
facing the passive member 193 is formed to a flat plane. Also, in both 
side surfaces of the sliding member 190, a groove 190a each of a V-shaped 
cross section is formed in continuation along the longitudinal direction. 
The balls 192 are in engagement with a pair of said grooves 190a in freely 
rotatable state. 
The rollers are of a cylindrical shape extending straight toward their axes 
of rolling and they are disposed at equal intervals along the longitudinal 
direction of the sliding member 190. Also, both ends of the rollers 191 
are rounded to a hemi-spherical shape to lessen friction occurring between 
the rollers 191 and the cage 194. 
The balls 192 are disposed at equal intervals along the longitudinal 
direction of the sliding member 190 in two lines along both side surfaces. 
The passive member 193 is in the form of a tray shape with walls rising up 
from both sides and its surface facing the sliding member 190 (the bottom 
surface) is made to a flat plane. Also, in the inside surfaces of walls on 
both sides of the passive member 193, a groove 193a each of a V-shaped 
cross section is formed in continuation along the longitudinal direction. 
The balls 192 are engaging with the pair of grooves 193a in freely 
rotatable state. 
The cage 194 is in the form of a U-shape with both sides being bent upward 
matching the inner profile of the passive member 193 and its thickness is 
made thinner than the outer diameter of the rollers 191. The cage 194 is 
provided with numerous slots 194a to maintain the rollers 191 at its 
bottom along the centerline thereof, in which the rollers 191 are 
maintained in freely rotatable state. The slots 194a are so disposed that 
the axes of rolling of the rollers 191 becomes inclined by a prescribed 
angle to a plane perpendicular to the sliding direction of the sliding 
member 190. 
Also, in the upright walls on both sides of the cage 194, numerous holes 
194b are opened in continuation along the longitudinal direction. The 
holes 194b on both sides maintain the balls 192 individually in freely 
rotatable state. 
With the friction resistance generator of the twentieth embodiment, since 
the balls 192 are in engagement with the grooves 190a and 193a, 
dislocation not only toward the cross-wise direction but also toward the 
vertical direction of the sliding member 190 and the passive member 193 is 
fully prevented. 
FIG. 40 and FIG. 41 show a twenty-first preferred embodiment of this 
invention: FIG. 40 being an exploded perspective view of a friction 
resistance generator of the twenty-first preferred embodiment of this 
invention; FIG. 41(a) being an enlarged plan view of a portion of the 
friction resistance generator of the twenty-first embodiment; and FIG. 
41(b) being an enlarged view of the cross-section perpendicular to the 
longitude of the friction resistance generator. 
The friction resistance generator comprises a sliding member 200, numerous 
rollers 201 disposed at prescribed intervals along a track of movement of 
the sliding member 200, numerous balls 202 similarly disposed in two lines 
along the track of movement of the sliding member 200, a passive member 
203 facing the sliding member 200 across the rollers 201 and the balls 
202, and a cage 204 which maintains the rollers 201 and the balls 202 at 
prescribed intervals in freely rotatable state. 
The sliding member 200 is in the form of a plate shape and the center 
section of its surface facing the passive member 203 is formed to a 
concave cross-sectional plane. Also, on both sides of the surface of the 
sliding member 200 facing the passive member 203, a groove 200a each of a 
V-shaped cross-section is formed in continuation along the longitudinal 
direction. The balls 202 are engaging with a pair of said grooves 200a in 
freely rotatable state. 
The rollers 201 are disposed at equal intervals along the longitudinal 
direction of the sliding member 200. The rollers 201 are in the form of a 
barrel shape, namely the largest outer diameter at the center thereof 
becoming gradually smaller toward both ends. Also, both ends of the 
rollers 201 are rounded to a hemi-spherical shape to lessen friction 
occurring between the rollers 201 and the cage 204. 
The balls 202 are disposed at equal intervals along the longitudinal 
direction of the sliding member 200 in two lines holding the line of the 
rollers 201 in between. 
The passive member 203 is in the form of a plate shape and the center 
section of its surface facing the sliding member 200 is formed to a 
concave cross-sectional plane. Also, on both sides of said surface of the 
passive member 203 facing the sliding member 200, a groove 203a each of a 
V-shaped cross section is formed in continuation along the longitudinal 
direction. The balls 202 are engaging with a pair of said grooves 203a in 
freely rotatable state. 
The cage 204 is in the form of a plate shape and its thickness is made 
thinner than the outer diameter of the rollers 201. The cage 204 is 
provided with numerous slots 204a and numerous holes 204b to maintain the 
rollers 201 and the balls 202, respectively. Each roller 201 and each ball 
202 are maintained in each slot 204a and each hole 204b, respectively, in 
freely rotatable state. Also, the slots 204a to maintain the rollers 201 
are so disposed that the axes of rolling of the rollers 201 become 
inclined by a prescribed angle to a plane perpendicular to the moving 
direction of the sliding member 200. 
With the friction resistance generator of the twenty-first embodiment, 
since the barrel shaped surface of each roller 201 is in contact with 
matchingly shaped surfaces of the sliding member 200 and the passive 
member 203, the motivation of respective rollers 201 to move toward their 
axes of rolling is restricted. Moreover, the outer diameter of the rollers 
201 varies along their longitudes. These facts cause additional frictional 
force, thus making it possible to acquire even larger resistance force. 
FIG. 42 shows a twenty-second preferred embodiment of this invention: FIG. 
42(a) being an enlarged plan view of a portion of a friction resistance 
generator of the twenty-second preferred embodiment; and FIG. 42(b) being 
an enlarged view of a cross section perpendicular to the longitude of the 
friction resistance generator. 
Similar to the preceding embodiment, the friction resistance generator 
comprises a sliding member 210, numerous rollers 211, numerous balls 212, 
a passive member 213, and a cage 214. The rollers 211 are in the form of a 
shape wherewith the smallest outer diameter at their center in the axial 
direction gradually becomes larger toward both ends. Meanwhile, the 
movements occurring in the friction resistance generator of the 
twenty-second embodiment and the effects thereof are the same as those of 
the preceding embodiment. 
FIG. 43 and FIG. 44 show a twenty-third preferred embodiment of this 
invention: FIG. 43 being an exploded perspective view of a friction 
resistance generator of the twenty-third preferred embodiment; FIG. 44(a) 
being an enlarged plan view of a portion of the friction resistance 
generator; and FIG. 44(b) being an enlarged view of a cross section 
perpendicular to the longitude of the friction resistance generator. 
The friction resistance generator comprises a sliding member 220 which is 
designed to slide in rectilinear directions, numerous rollers 221 disposed 
along a track of movement of the sliding member 220, numerous balls 222 
similarly disposed along the tack of movement of the sliding member 220, a 
passive member 223 which faces the sliding member 220 across the rollers 
221 and the balls 222, and a cage 224 which maintains the rollers 221 and 
the balls 222 at prescribed intervals in freely rotatable state. 
Both sides of the sliding member 220 are bent downward and its surface 
facing the passive member 223 is formed to a flat plane. Also, both sides 
of the sliding member 220 are formed to ball-guides 220a in continuation 
along the longitudinal direction of the sliding member. The balls 222 are 
engaging with the ball-guides 220a in freely rotatable state. 
The rollers 221 are in the form of cylindrical shapes extending straight 
toward their longitude and they are disposed at equal intervals along the 
longitudinal direction of the sliding member 220. Also, both ends of the 
rollers 221 are rounded to a hemi-spherical shape to lessen friction 
occurring between the rollers 221 and the gage 224. 
The balls 222 are disposed at equal intervals along the longitudinal 
direction of the sliding member 220 in two lines along both sides. 
Both sides of the passive member 223 are bent downward before bent up at 
both edges. Its surface facing the sliding member 220 is formed to a flat 
plane. Also, the outside surfaces on both sides of the passive member 223 
are formed to ball-guides 223a. The balls 222 are engaging with the 
ball-guides 223a in freely rotatable state. Both sides of the cage 224 are 
bent downward and its thickness is made thinner than the outer diameter of 
the rollers 221. Also, the cage 224 is provided with numerous slots 224a 
to maintain the rollers 221 in its center plane. Each roller 221 is 
maintained in each slot 224a in freely rotatable state. The slots 224a are 
so disposed that the axes of rolling of the rollers 221 become inclined by 
a prescribed angle to a plane perpendicular to the moving direction of the 
sliding member 220. Also, through both side walls of the cage 224, 
numerous holes 224b are opened to maintain the balls 222. Each ball 222 is 
maintained in each hole 224b in freely rotatable state. 
The sliding member 220 and the passive member 223 of the friction 
resistance generator of the twenty-third embodiment are press-formed 
plates. The movements occurring in the friction resistance generator and 
effects thereof are the same as those of the preceding embodiment. 
FIG. 45 shows a twenty-fourth preferred embodiment of this invention: FIG. 
45(a) being an enlarged plan view of a portion of a friction resistance 
generator of the twenty-fourth preferred embodiment; and FIG. 45(b) being 
an enlarged view of a cross section perpendicular to the longitude of the 
friction resistance generator. 
Similar to the preceding embodiment, the friction resistance generator 
comprises a sliding member 230, numerous rollers 231, numerous balls 232, 
a passive member 233, and a cage 234. 
The passive member 233 of the friction resistance generator of this 
embodiment is so shaped that, in its independent state as indicated by the 
alternate long and short dash line, the center plane, namely the plane 
contacting the rollers 231, is slightly elevated than in the assembled 
state as indicated by solid line in the cross sectional view. 
Consequently, the rollers 231 are always depressed upward onto the sliding 
member 230 under a certain pressure by the elastic deformation of the 
passive member 233 when it has been assembled. Thus, a pre-load is applied 
to the rollers 231 and the friction force produced by respective rollers 
231 can always be maintained constant. 
FIG. 46 to FIG. 48 show a twenty-fifth preferred embodiment of this 
invention: FIG. 46 being an exploded perspective view of a friction 
resistance generator of the twenty-fifth preferred embodiment of this 
invention; FIG. 47(a) being an enlarged plan view of a portion of the 
friction resistance generator; and FIG. 47(b) being an enlarged view of a 
cross section perpendicular to the longitude of the friction resistance 
generator. 
The friction resistance generator comprises a sliding member 240, numerous 
rollers 241 disposed along a track of movement of the sliding member 240, 
numerous balls 240 similarly disposed along the track of movement of the 
sliding member 240, a passive member 243 facing the sliding member 240 
upward from below across the rollers 241, a cage 244 which maintains the 
rollers 241 and the balls 242 individually at prescribed intervals in 
freely rotatable state, and numerous coil springs 245 pushing the rollers 
241 toward a prescribed sliding direction of the sliding member 240. 
The sliding member 240 is in the form of a plate shape and its surface 
facing the passive member 243 is formed to a flat plane. Also, in the 
surfaces on both sides of the sliding member 240, a groove 240a each of a 
V-shaped cross section is formed in continuation along the longitudinal 
direction of the sliding member 240. The balls 242 are engaging with a 
pair of said grooves 240a in freely rotatable state. 
The rollers 241 are in the form of a cylindrical shape extending straight 
along their axes of rolling and they are disposed at equal intervals along 
the longitudinal direction of the sliding member 240. Also, both ends of 
the rollers 241 are rounded to a hemi-spherical shape to lessen friction 
occurring between the rollers 241 and the cage 244. 
The balls 242 are disposed at equal intervals along the longitudinal 
direction of the sliding member 240 in two lines along both sides. 
The passive member 243 is in the form of a tray shape with walls rising up 
from both sides and its surface facing the sliding member 240 is formed to 
a flat plane. Also, in the inner side surfaces of walls on both sides of 
the passive member 243, a groove 243a each of a V-shaped cross section is 
formed in continuation along the longitudinal direction of the passive 
member 243. The balls 242 are in engagement with a pair of said grooves 
243a in freely rotatable state. 
The cage 244 is in the form of a U-shape with both sides being bent upward 
matching the inner profile of the passive member 243 and its thickness is 
made thinner than the outer diameter of the rollers 241. The cage 244 is 
provided with numerous openings 244a to maintain the rollers 241. Each 
roller 241 is maintained in each opening 244a in freely rotatable state. 
Each opening 244a is in the form of a fan-shape with its pivot matching to 
the position of one end of each roller 241. One side extending from said 
pivot is designed in parallel with a plane perpendicular to the moving 
direction of the sliding member 240 and the other side extending from said 
pivot is so designed to incline by a prescribed angle to the plane 
perpendicular to the moving direction of the sliding member 240. 
Also, in the upright walls on both sides of the cage 244, numerous holes 
244b are opened in continuation along the longitudinal direction of the 
cage 244. The holes 244b on both sides maintain the balls 242 individually 
in freely rotatable state. 
Moreover, the upright walls on both sides of the cage 244 are formed to 
corrugated spring structures having numerous elastic convexities 244c at a 
prescribed intervals. The elastic convexities 244c are pressing the inside 
surface of the passive member 243 by their springing force in a state of 
contact. 
The coil springs 245 are individually installed beside respective openings 
244a of the cage 244, and one end of the coil springs 245 are fastened to 
the bottom surface of the cage 244. The other end of the coil springs 245 
is hooked to each roller 241, pushing the roller 241 onto the side being 
inclined to the plane perpendicular to the trace of movement of the 
sliding member 240. 
With the friction resistance generator of the aforementioned structure, as 
shown in FIG. 48(a), when the sliding member 240 is moved toward a 
prescribed direction (the upward direction in the drawing), the rollers 
241 make rolling motions in contact with the sliding member 240 and the 
passive member 243, then the cage 242 trails to move along. At this time, 
since the rollers 241 are motivated to move toward the direction being 
inclined to the track of movement of the sliding member 240, similar to 
the case of the preceding embodiment, friction force in proportion to a 
load applied in the axial direction occurs between the rollers 241 and the 
sliding member 240 and between the rollers 241 and the passive member 243. 
On the other hand, as shown in FIG. 48(b), if the sliding member 240 is 
moved toward the opposite direction (the downward direction in the 
drawing), the rollers 241 tilt inside the openings 244a until their axes 
of rolling come in parallel with the plane perpendicular to the moving 
direction of the sliding member 240, while making rolling motions in 
contact with the sliding member 240 and the passive member 243. When this 
occurs, since the axes of rolling of the rollers 241 are not inclined to 
the plane perpendicular to the track of movement of the sliding member 
240, sliding friction does not occur with respective rollers 241, thus 
allowing the sliding member 240 slide smoothly. 
Also, since the elastic convexities 244c provided along the walls on both 
sides of the cage 244 are pushing the inside surfaces of the upright 
structures of the passive member 243, when the sliding direction of the 
sliding member 240 is shifted, the cage 244 is always late in shifting the 
direction of movement than the tiling motions of the rollers 241 because 
of the aforesaid contact resistance with the inside wall surfaces of the 
passive member 243, thus the rollers 241 can tilt their directions 
promptly inside the openings 244a. 
Moreover, since respective rollers 241 are always motivated to stay at the 
direction not being inclined to the plane perpendicular to the trace of 
movement of the sliding member 240 whichever direction they may be rolling 
for, the rollers 241 are tilted forcefully by the coil springs 245 when 
heading for the direction, which is deemed necessary to exert a 
resistance. 
Thus, with the friction resistance generator of this embodiment, since it 
is so structured that the axes of rolling of the rollers 241 can be tilted 
between the side becoming in parallel with the plane perpendicular to the 
sliding direction of the sliding member 240 and the side becoming inclined 
to the plane perpendicular to the sliding direction of the sliding member 
240, in a prescribed sliding direction, a resistance occurring from the 
frictional force of the rollers 241 can be applied to the rectilinear 
movement of the sliding member 240, while in the other sliding direction, 
the rectilinear movement of the sliding member 240 can be made smoothly 
without application of said resistance. 
FIG. 49 and FIG. 50 show a twenty-sixth preferred embodiment of this 
invention: FIG. 49 being an exploded perspective view of a friction 
resistance generator of the twenty-sixth preferred embodiment; FIG. 50(a) 
being an enlarged plan view of a portion of the friction resistance 
generator; and FIG. 50(b) being an enlarged view of a cross section 
perpendicular to the longitude of the friction resistance generator. 
The friction resistance generator comprises a sliding member 250 which 
moves along its axis of rectilinear movement, numerous rollers 251 
disposed along s track of movement of the sliding member 250, numerous 
balls 252 being similarly disposed along the track of movement of the 
sliding member 250, a passive member 253 facing the sliding member 250 
upward fro m below across the rollers 251, a cage 254 which maintains the 
rollers 251 and the balls 252 at prescribed intervals in freely rotatable 
state, numerous coil springs 255 which work as the means of application of 
a pre-load pushing the passive member 253 toward the sliding member 250, 
and a housing 256 to house all these components. 
The sliding member 250 is in the form of a plate shape with its upper 
center section being raised to a higher elevation and with its surface 
facing the passive member 253 (the bottom surface) being formed to a flat 
plane. Also, in the both lower elevation side surfaces on the upper side 
of the sliding member 250, a groove 250a each of a V-shaped cross section 
is formed in continuation along the longitudinal direction of the sliding 
member 250. The balls 252 are in engagement with a pair of said grooves 
250a in freely rotatable state. 
The rollers 251 are in the form of a cylindrical shape extending straight 
toward their axes of rolling and they are disposed at equal intervals 
along the longitudinal direction of the sliding member 250. Also, both 
ends of the rollers are rounded to a hemi-spherical shape to lessen 
friction occurring between the rollers 251 and the cage 254. 
The balls 252 are disposed at equal intervals along the longitudinal 
direction of the sliding member 250 in two lines along both sides. 
The passive member 253 is in the form of a plate shape and its surface 
facing the sliding member 250 (the upper surface) is formed to a flat 
plane. Also, numerous guide rods 253a extending downward and numerous 
holes 253b to accept the upper ends of the coil springs 255 are provided 
on the bottom plane of the passive member 253, in continuation in the 
longitudinal direction. 
Both sides of the cage 254 is bent upward before further bent inward and 
its thickness is made thinner than the outer diameter of the rollers 251. 
Numerous slots 254a to maintain the rollers 251 are opened through the 
bottom of the cage 254. Each roller 251 is maintained in each slot 254a in 
freely rotatable state. 
The slots 254a are so disposed that the axes of rolling of the rollers 251 
become inclined by a prescribed angle to the plane perpendicular to the 
sliding direction of the sliding member 250. Also, in the side structure 
at an upper elevation than the bottom surface of the cage 254, numerous 
holes 254b are opened to maintain the balls 252. Each ball 252 is 
maintained in each hole 254b in freely rotatable state. 
The coil springs 255 are inserted between the passive member 253 and the 
housing 256 in compressed state, pushing up the passive member 253 toward 
the sliding member 250 at a constant springing force. 
The housing 256 extends its walls on both sides upward before extending 
them toward inside to cover both sides of the upper open space. In the 
bottom surface of the housing 256, numerous holes 256a whereto the guide 
rods 253a of the passive member 253 are inserted for free sliding and 
numerous holes 256b whereto the lower ends of the coil springs 255 are 
inserted. Through the bottom of each hole 256b for inserting the lower end 
of each coil spring 255, an adjusting screw 257 each is screwed in, whose 
head contacts the bottom end of each coil spring 255, thus providing an 
adjusting means of the springing force of each coil spring 255 by screwing 
the adjusting screws 257 in or out. Also, in the ceiling surfaces of the 
structure covering both sides of the upper open space of the housing 256, 
a groove 256c each of a V-shaped cross section is formed in continuation 
along the longitudinal direction of the housing 256. The balls 252 are 
engaging with a pair of said grooves 256c in freely rotatable state. 
Namely, as shown in FIG. 50(b), in the housing 256, the passive member 253 
is housed in a state being pushed upward by the coil springs 255 toward 
the sliding member 250, and the balls 252 maintained by the cage 254 are 
engaging with the grooves 256c of the housing 256 and the grooves 250a of 
the sliding member 250. 
By this structure, dislocation of the sliding member 250 toward outside of 
its axis of rectilinear movements is prevented, and the sliding member 250 
and the passive member 253 are depressed each other by a constant force 
across the rollers 251. 
With the friction resistance generator of this embodiment, since the 
springing force of the coil springs 255, in other words, the pre-load 
applied to the rollers 251, can be adjusted by the adjusting screws 257, 
the frictional force occurring from the pre-load can be optionally 
adjusted. 
PROSPECTS FOR INDUSTRIAL APPLICATIONS 
As aforementioned, the friction resistance producing mechanism of this 
invention can produce always stable and discretionary frictional 
resistance even when its speed of rotary movements or rectilinear 
movements of the subject structure changes. Moreover, the magnitude of the 
frictional force can be easily controlled by changing the magnitude of the 
load, or the discretionary frictional force can be produced only in a 
prescribed direction of rotary movement or rectilinear movement of the 
subject structure. Under such circumstances, optional friction force 
fitting to individual purposes can be obtained, by optionally setting of 
the inclination angle of the rolling axes of respective rollers. 
Consequently, the friction resistance generator of this invention can be 
effectively applied to various machines and equipment requiring the 
aforesaid functions, and its simple structure can provide extremely 
effective advantage to reduction of the production costs and down sizing 
of machines and equipment.