JP2004239367A - Friction roller type transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To increase strength by suppressing the self-rotation of a movable roller support shaft to reduce stress concentration. <P>SOLUTION: A rotation stopping hole (roller shaft hole) 71 is radially formed in the support shaft 39b, and a projection 72 formed on one spring pin 51 is engaged with the rotation stopping hole (roller shaft hole) 71. Accordingly, the motion (auto rotating motion) of the support shaft 39b in the circumferential direction can be suppressed. As a result, when an oil hole 61 is formed in the supporting shaft 39b so that the center axis (oil hole axis) of the oil hole 61 (lubricant guide passage) is not positioned perpendicular to the neutral axis (neutral axis) thereof, the stress concentration produced in the supporting shaft 39b by the presence of the oil hole 61 can be reduced. <P>COPYRIGHT: (C)2004,JPO&NCIPI

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention is incorporated in, for example, a rotary drive portion of various mechanical devices such as a machine tool, a semiconductor manufacturing device, a water turbine, a windmill, and a supercharger, and transmits the rotation of the drive shaft to the driven side while reducing or increasing the rotation thereof. Then, the above-mentioned machine tool and the like can be rotationally driven, and can also be used for driving a drive unit or an auxiliary machine of an automobile, and is suitable for transmitting relatively high-speed rotation. About the machine.
[0002]
[Prior art]
The traction drive type transmission has been developed for various industrial uses because of its quietness and smoothness. In recent years, attempts have been made to apply it to personal use such as automobiles and bicycles, and it has attracted attention as a next-generation power transmission system. .
[0003]
Unlike a gear transmission, a traction drive type transmission is a mechanism for transmitting power by strongly pressing at least two rotating bodies having a smooth surface and interposing a lubricating oil film (for example, an EHL oil film) therebetween. The basic formula is represented by a simple friction formula of Ft = μ · Fc (Ft: traction force). Here, Fc is called a pressing force, and various methods have been developed for generating the pressing force.
[0004]
As one of the traction drive type transmissions, there is a friction roller type transmission utilizing a wedge action (hereinafter referred to as a wedge roller type transmission) as disclosed in Patent Document 1. . A wedge roller type transmission is an outer ring rotatably provided around an end of a high speed side shaft in an eccentric state with respect to the high speed side shaft, and a power transmission for an outer peripheral surface of the high speed side shaft. Each outer peripheral surface, which is located between a cylindrical surface and a power transmission cylindrical surface that is an inner peripheral surface of the outer ring, is disposed in an annular space having a radial width that is not uniform in the circumferential direction. It refers to a transmission having at least one guide roller and at least one movable roller as a transmission cylindrical surface. The movable roller is a roller that generates a pressing force by a wedge action, and is a roller that moves in a radial direction and a circumferential direction.
[0005]
In this wedge roller type transmission, during forward rotation, the movable roller moves in a direction to bite into the “wedge” between the high-speed side shaft and the outer ring, and generates a pressing force Fc. A traction force is generated by this Fc, and torque can be transmitted.
[0006]
On the other hand, at the time of reverse rotation, the movable roller moves in a direction away from the “wedge”, the pressing force Fc becomes zero, and the rotation of the input side stops being transmitted to the output side.
[0007]
When the low-speed side shaft (outer ring side) is used as the input side, the wedge roller type transmission acts as a gearbox with the high-speed side shaft as the output side, and the low-speed side shaft (outer ring side) is used as the output side. In such a case, it acts as a speed reducer with the high speed side shaft as the input side.
[0008]
Also, a wedge roller type transmission has a one-way clutch function that transmits torque during forward rotation, but idles and does not transmit torque during reverse rotation, and transmits torque during both forward and reverse rotation. There are things you can do.
[0009]
[Patent Document 1]
Japanese Patent Application No. 2002-334016 [0010]
[Problems to be solved by the invention]
In the wedge roller type transmission disclosed in Patent Document 1, as shown in FIG. 8A, an oil hole 62 (a guide path for guiding a lubricant) is formed in a support shaft 39b of a movable roller 38. is there. The support shaft 39b of the movable roller 38 is rotatable (rotatable) in the circumferential direction.
[0011]
As shown in FIG. 8B, the wedge roller type transmission uses a preload spring 47 to prevent an initial slip from occurring on the contact surface between the low-speed side ring (outer ring) 32 and the movable roller 38. The movable roller 38 is pressed in the wedge direction. The preload spring 47 generates a compressive force F between the support shaft 39b and the bearing 42.
[0012]
In the conventional method, as shown in FIG. 8A, the support shaft 39b is rotatable (rotatable) in the circumferential direction. As a result, the support shaft 39b is moved between the oil hole 62 and the spring load (compression force) direction. The relationship may be as shown in FIG. That is, the central axis (oil axis) of the oil hole 62 may be perpendicular to the neutral axis (neutral axis). In such a case, stress concentration occurs at the maximum, and this may lead to a fatigue phenomenon of the material, leading to breakage and the like.
[0013]
SUMMARY OF THE INVENTION The present invention has been made in view of the above-described circumstances, and a friction roller type transmission capable of suppressing rotation of a support shaft of a movable roller, reducing stress concentration, and improving strength. The purpose is to provide.
[0014]
[Means for Solving the Problems]
To achieve the above object, a friction roller type transmission according to claim 1 of the present invention is rotatably supported by a housing and has a low-speed side shaft provided with an outer ring at one end, the low-speed side shaft and the outer ring. A high-speed side shaft eccentrically supported by the housing and rotatably supported by the housing; and at least one guide roller and at least one movable roller rotatably supported between the outer race and the high-speed side shaft. In a friction roller type transmission utilizing a wedge action consisting of
A support shaft that rotatably supports the movable roller,
Suppressing means for suppressing the rotation of the support shaft.
[0015]
Thus, according to the first aspect, the suppression means for suppressing the rotation of the support shaft of the movable roller is provided. Therefore, if the oil hole is formed in the support shaft so as not to make a right angle with the center axis (oil hole axis) of the oil hole (lubricant guideway) and the neutral axis (neutral axis), the oil hole supports the oil hole. Stress concentration occurring on the shaft can be reduced, and strength can be improved.
[0016]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, a friction roller type transmission according to an embodiment of the present invention will be described with reference to the drawings.
[0017]
First, the internal structure of the wedge roller type transmission will be described in detail, and then the embodiment will be described.
[0018]
Also, for convenience of description, a wedge roller type transmission using one movable roller will be described, and then a two-way power transmission type wedge roller type transmission using two movable rollers will be described.
[0019]
Further, when describing a method of transmitting power, a case where a wedge roller type transmission acts as a speed reducer is described as a representative. In the reduction gear, forward rotation is a direction in which power is transmitted from the high-speed shaft 17 to the outer ring 32, and reverse rotation is a direction in which the high-speed shaft 17 idles and stops transmission of torque (power) to the outer ring 32. It is.
[0020]
(Internal structure of wedge roller type transmission)
FIG. 1 is a longitudinal sectional view of a wedge roller type transmission according to the present invention.
[0021]
FIG. 2 is a cross-sectional view of a main part of the wedge roller transmission with the housing removed, and is a cross-sectional view of the wedge roller transmission having a one-way clutch function.
[0022]
FIG. 3 is a diagram illustrating the operation of a wedge roller type transmission as a speed reducer.
[0023]
FIG. 5 is a cross-sectional view of a main part of the wedge roller transmission with the housing removed, and is a cross-sectional view of the wedge roller transmission capable of transmitting torque (power) when rotating in both forward and reverse directions. is there.
[0024]
FIG. 4 is a diagram illustrating the operation of a wedge roller type transmission as a speed increasing device for reference.
[0025]
When the low-speed side shaft 3 (outer ring side) is the output side, the wedge roller type transmission A acts as a speed reducer with the high-speed side shaft 17 as the input side.
[0026]
In addition, as shown in FIG. 4, when the low speed side shaft 3 (outer ring side) is set as the input side, it acts as a gearbox with the high speed side shaft 17 as the output side.
[0027]
Further, as shown in FIG. 2, the wedge roller type transmission A using one movable roller 38 transmits torque (power) during normal rotation, and idles during reverse rotation to transmit torque (power). Although it has a one-way clutch function that does not transmit, as shown in FIG. 5, a wedge roller type transmission A using two movable rollers 38a and 38b transmits torque (power) during both forward and reverse rotations. can do.
[0028]
1 and 2, a wedge roller type transmission A has a housing 2 as a partition plate fixed to a substantially cylindrical housing 1. A low-speed side shaft 3 is rotatably supported by the housing 1, and a disk-shaped member 4 is provided at an end of the low-speed side shaft 3 in the housing 1. An outer ring 32 is attached.
[0029]
The high-speed side shaft 17 is eccentrically (offset) with respect to the low-speed side shaft 3 and the outer ring 32 and is rotatably provided in the housing 2 serving as a partition plate.
[0030]
As shown in FIG. 2, a large-diameter guide roller 37a, a small-diameter guide roller 37b, and a movable roller 38 that moves when transmitting torque (power) are interposed between the outer ring 32 and the high-speed side shaft 17. I am wearing it.
[0031]
As shown in FIG. 3, in the case of a speed reducer, the support shaft 39b that rotatably supports the movable roller 38 is configured to be movable between the high-speed side shaft 17 and the outer ring 32 in a direction in which the wedge bites. Further, the elastic member 47 (preload spring, see FIG. 2) such as a compression spring installed in the cylinder hole 46 is urged in a direction to bite into the “wedge”.
[0032]
As a result, at the time of normal rotation, the movable roller 38 moves between the high-speed side shaft 17 and the outer ring 32 in a direction to bite into the “wedge”, and generates a pressing force Fc. A traction force is generated by this Fc, and torque (power) can be transmitted.
[0033]
On the other hand, at the time of reverse rotation, the movable roller 38 moves in a direction away from the “wedge”, the pressing force Fc becomes zero, and the rotation of the input side stops being transmitted to the output side.
[0034]
As shown in FIG. 2, between the inner peripheral surface of the outer race 32 and the outer peripheral surface of the distal end portion of the high-speed shaft 17, there is provided an annular space 36 whose radial width is not uniform in the circumferential direction.
[0035]
In the annular space 36, two guide rollers 37a and 37b and one movable roller 38 are installed to constitute the wedge roller type transmission A. In FIG. 2, the movable roller 38 is partially cut away. Three support shafts 39a, 39a, 39b are provided in the annular space 36 for installing these rollers 37a, 37b, 38. Of the three support shafts 39a, 39a, 39b, the two support shafts 39a, 39a are press-fitted and fixed at both ends to fitting holes 40, 40 formed in the housing 2 and the connecting plate 14. . Therefore, the two support shafts 39a, 39a are not displaced in the circumferential direction or the diametric direction in the annular space 36. On the other hand, of the three support shafts 39a, 39a, 39b, the other one of the support shafts 39b has both ends in the circumferential direction and the diameter of the outer ring 32 with respect to the housing 2 and the connecting plate 14. It is supported to be slightly displaceable in the direction. For this purpose, a support hole 41 having an inner diameter larger than the outer diameter of the support shaft 39b is formed in a part of the housing 2 and the connecting plate 14 which is aligned with both ends of the one support shaft 39b. Both ends of the support shaft 39b are loosely engaged with these support holes 41.
[0036]
The guide rollers 37a, 37b and the movable roller 38 are rotatable around the intermediate portions of the support shafts 39a, 39a, 39b supported as described above by radial needle bearings 42, 42, respectively. I support it. In order to connect and fix the connecting plate 14 to the housing 2, the projecting portions 27, 27 projecting from one side of the connecting plate 14 are provided with the respective guide rollers with respect to the circumferential direction of the connecting plate 14. 37a, 37b and between the movable roller 38. In other words, each of the protrusions 27 and 27 and each of the guide rollers 37a and 37b or the movable roller 38 are present alternately in the annular space 36 in the circumferential direction of the annular space 36. In addition, the outer peripheral surface of each of the guide rollers 37a, 37b or the movable roller 38 does not interfere with (rub against) the circumferential side surface of each of the protrusions 27, 27.
[0037]
In this way, the outer peripheral surfaces of the guide rollers 37a, 37b and the movable roller 38 rotatably supported between the housing 2 and the connecting plate 14 by the support shafts 39a, 39a, 39b, The transmission cylindrical surfaces 43a, 43a, 43b respectively correspond to a power transmission cylindrical surface 44, which is an outer peripheral surface of the distal end portion of the high-speed shaft 17, and a power transmission cylindrical surface 45, which is an inner peripheral surface of the outer ring 32. In contact. As described above, the width in the radial direction of the annular space 36 in which the guide rollers 37a and 37b and the movable roller 38 are installed is not uniform in the circumferential direction. As described above, the outer diameters of the guide rollers 37a and 37b and the movable roller 38 are made different by the amount of making the width of the annular space 36 unequal in the circumferential direction. That is, of the guide rollers 37a, 37b and the movable roller 38, the outer diameters of the movable roller 38 and the guide roller 37b located on the side where the tip of the high-speed side shaft 17 is eccentric with respect to the outer ring 32 are the same. And have a relatively small diameter. On the other hand, the outer diameter of the guide roller 37a located on the side opposite to the eccentric end of the high-speed shaft 17 with respect to the outer ring 32 is made larger than the outer diameters of the movable roller 38 and the guide roller 37b. ing. The power transmission cylindrical surfaces 43a, 43a, 43b, which are the outer peripheral surfaces of the guide rollers 37a, 37b and the movable roller 38, are brought into contact with the power transmission cylindrical surfaces 44, 45, respectively.
[0038]
Note that, of the guide rollers 37a, 37b and the movable roller 38, both ends of the support shafts 39a, 39a supporting the guide rollers 37a, 37b are, as described above, with respect to the housing 2 and the connecting plate 14 ( (Within the annular space 36). On the other hand, the support shaft 39b supporting the movable roller 38 causes a slight displacement in the circumferential direction and the diametric direction with respect to the housing 2 and the connecting plate 14 (in the annular space 36) as described above. We support as much as possible. Therefore, the movable roller 38 can also be slightly displaced in the annular space 36 in the circumferential direction and the diametric direction. A support shaft 39b supporting the movable roller 38 is rotatably supported by the support shaft 39b by an elastic member 47 (preload spring) such as a compression spring provided in the cylinder hole 46 of the housing 2 and the connecting plate 14. In order to move the movable roller 38, which is supported in the annular space 36, toward the narrow portion of the annular space 36, the movable roller 38 is elastically lightly pressed.
[0039]
In the case where the rotating shaft is rotationally driven by the wedge roller type transmission configured as described above (in the case of a reduction gear), the driving force is input to the high speed side shaft 17 at the time of normal rotation, so that the high speed side shaft 17 is driven. Rotate in the direction of the arrow in FIG. The rotation of the high-speed side shaft 17 is transmitted to the outer ring 32 via the guide rollers 37a and 37b and the movable roller 38, and rotates the outer ring 32 in the direction of the arrow in FIG.
[0040]
Power transmission between the outer ring 32 and the guide rollers 37a and 37b and the movable roller 38, and power transmission between the guide rollers 37a and 37b and the movable roller 38 and the high-speed shaft 17 are all performed by friction transmission. Therefore, noise and vibration generated during power transmission are low.
[0041]
Further, the movable roller 38 tends to bite into the narrow portion of the annular space 36 with a force corresponding to the magnitude of the torque transmitted from the high-speed shaft 17 to the outer ring 32. Therefore, a contact portion between the power transmission cylindrical surface 45, which is the inner peripheral surface of the outer ring 32, and the power transmission cylindrical surfaces 43a, 43a, 43b, which are the outer peripheral surfaces of the guide rollers 37a, 37b and the movable roller 38, and The surface pressure of the contact portion between each of the power transmission cylindrical surfaces 43a, 43a, 43b and the power transmission cylindrical surface 44, which is the outer peripheral surface of the high-speed shaft 17, increases as the torque increases. Conversely, when the torque is small, the contact pressure of each contact portion is low. For this reason, the torque can be efficiently transmitted by setting the surface pressure of each contact portion to an appropriate value corresponding to the torque to be transmitted.
[0042]
That is, when rotating the high-speed shaft 17 in the direction of the arrow in FIG. 3, the movable roller 38 is driven by the power transmission cylindrical surface 45 that is the inner peripheral surface of the outer race 32 and the power transmission that is the outer peripheral surface of the high-speed shaft 17. It receives a force in the same direction as the pressing force of the elastic member 47 (preload spring) from the cylindrical surface 44 for use, and tends to move toward the narrow portion of the annular space 36.
[0043]
As described above, the force for moving the movable roller 38 toward the narrow portion of the annular space 36 changes according to the magnitude of the rotational driving force transmitted from the high-speed shaft 17 to the outer ring 32. As the force increases, the inner contact portion 48, which is the contact portion between the power transmitting cylindrical surfaces 43a, 43b and the power transmitting cylindrical surface 44, and the power transmitting cylindrical surfaces 43a, 43b and the power. The contact pressure of the outer contact portion 49, which is the contact portion with the transmission cylindrical surface 45, increases. Therefore, based on such an operation, the contact pressure according to the transmitted rotational driving force is automatically selected, and the transmission efficiency of the wedge roller type transmission A can be secured.
[0044]
In the case of the example shown in FIG. 2, the wedge roller type transmission A has a one-way clutch function, and in the case of a speed reducer, the rotation speed of the outer ring 32 matches the rotation speed of the high-speed side shaft 17, that is, If the rotation speed of the high-speed shaft 17 is higher than the speed obtained by multiplying the reduction ratio of the wedge roller type transmission A, the connection of the wedge roller type transmission A is disconnected. That is, in this case, the movable roller 38 is displaced toward the wider side of the annular space 36 against the elastic force of the elastic member 47 (preload spring). As a result, the contact pressure between the inner and outer contact portions 48 and 49 is reduced or lost, and the rotation of the high-speed side shaft 17 is not transmitted to the outer ring 32.
[0045]
Next, a description will be given of a wedge roller type transmission shown in FIG. 5 capable of transmitting torque when rotating in both the forward and reverse directions.
[0046]
FIG. 5 shows a structure in which the high-speed shaft 17 is rotatable in both clockwise and counterclockwise directions.
[0047]
In such a configuration of the present example, one guide roller 37 and two movable rollers 38a and 38b are used as three rollers constituting the wedge roller type transmission A. Among them, the roller installed in the widest part of the annular space 36 is a guide roller 37 having a relatively large diameter and the installation position does not change. On the other hand, a pair of rollers provided so as to sandwich the portion where the width of the annular space 36 becomes the narrowest is a movable roller 38a which has a relatively small diameter and enables a slight displacement in the circumferential and diametric directions. , 38b. The support shafts 39b and 39b supporting the movable rollers 38a and 38b are elastically pressed toward the narrowest portion of the annular space 36.
[0048]
In the case of the structure of the present embodiment configured as described above, when the high-speed side shaft 17 rotates clockwise in FIG. 5, the movable roller 38a bites into the narrowed portion of the annular space 36.
[0049]
On the other hand, when the high-speed side shaft 17 rotates counterclockwise in FIG. 5, the movable roller 38b cuts into the narrowed portion of the annular space 36.
[0050]
Further, in the case of this example, in order to support both ends of the support shafts 39b, 39b supporting these movable rollers 38a, 38b, support holes 41a, 41a (long grooves) formed in the housing 2 and the connecting plate 14 are formed. The length of the annular space 36 in the circumferential direction is regulated. Specifically, the position of the end of each of the support holes 41a, 41a (long groove) on the side where the width of the annular space 36 is wider than that of the case shown in FIG. It is close to the narrowest position. The movable rollers 38a and 38b are prevented from retreating excessively to the wide side of the annular space 36.
[0051]
In the case of the present embodiment configured as described above, in the case of a speed reducer, even when the high-speed side shaft 17 rotates in either the clockwise or counterclockwise direction, any of the movable rollers 38a (38b) is connected to the annular space. The movable roller 38a (38b) bites into the narrow portion of the movable roller 36, and the contact pressure of the inner and outer contact portions 48 and 49 with respect to the movable roller 38a (38b) is increased. On the other hand, the retractable amount of the movable roller 38b (38a) displaced in the direction of retracting from the narrow portion of the annular space 36 is also limited. As a result, with respect to both the movable rollers 38a and 38b and the guide roller 37, the contact pressures of the inner and outer contact portions 48 and 49 are sufficiently increased, and the power is efficiently transmitted from the high-speed shaft 17 to the outer ring 32. Can communicate. Except for enabling the transmission of power in both the clockwise and counterclockwise directions from the high-speed side shaft 17 to the outer ring 32 in this manner, it is the same as the case described above with reference to FIG. I do.
[0052]
(Embodiment of the present invention)
FIG. 6A is a cross-sectional view of a support shaft of a movable roller according to the embodiment of the present invention, and FIG. 6B is a partial schematic diagram of the movable roller and an outer ring. FIG. 7 is a cross-sectional view taken along the line BB of FIG.
[0053]
As shown in FIG. 6A, an oil hole (lubricant guide path) is formed in the support shaft 39b of the movable rollers 38, 38a, 38b. In the oil hole (lubricant guide path), an oil hole 61 is provided in the axial direction from the end surface of the support shaft 39b, and an oil hole 62 is provided from the oil hole 61 in a radial direction of the shaft. As a result, the lubricant flows from the oil hole 61 at the inflow port to the oil hole 62, and from the discharge port of the oil hole 62 to the contact surface between the support shaft 39b of the movable rollers 38, 38a, 38b and the needle bearing 42. , Lubricant is supplied.
[0054]
As shown in FIG. 7, a pair of spring pins 51 and 52 are provided to press the support pin 39b. The spring pins 51 and 52 are moved by the preload spring 47 in the direction in which the "wedge" becomes narrower. The support pin 39b is constantly urged in the direction in which the "wedge" becomes narrower, as described above.
[0055]
In the present embodiment, as shown in FIGS. 6 and 7, a rotation-preventing hole (roller shaft hole) 71 is formed in the support shaft 39b in the radial direction, and the rotation-preventing hole (roller shaft hole) is formed. ) 71 is engaged with a projection 72 formed on one spring pin 51.
[0056]
As described above, in the present embodiment, since the projection 72 of the spring pin 51 enters the rotation preventing hole (roller shaft hole) 71 of the support shaft 39b, the support shaft 39b rotates in the circumferential direction (rotational motion). ) Can be suppressed.
[0057]
That is, the positional relationship between the center axis (oil hole axis) of the oil hole 61 (lubricant guide path) and the neutral axis (neutral axis) is arbitrarily designated, and this position is maintained even during the rotational movement of the wedge roller type transmission. Relationships can be maintained.
[0058]
As a result, if the oil hole 61 is formed in the support shaft 39b so that the center axis (oil hole axis) of the oil hole 61 (lubricant guide path) and the neutral axis (neutral axis) do not make a right angle, Stress concentration on the support shaft 39b due to the presence of the oil hole 61 can be reduced.
[0059]
Thereby, the breakage and breaking strength of the support shaft 39b can be significantly improved as compared with the case where the central axis (oil hole axis) of the oil hole 61 and the neutral axis (neutral axis) are at right angles.
[0060]
This is to clarify the unclear factor concerning the support shaft 39b, which leads to an optimal design with respect to breakage and breaking strength, and can also extend the life.
[0061]
The present invention is not limited to the above-described embodiment, but can be variously modified.
[0062]
【The invention's effect】
As described above, according to the first aspect, the suppression means for suppressing the rotation of the support shaft of the movable roller is provided. Therefore, if the oil hole is formed in the support shaft so as not to make a right angle with the center axis (oil hole axis) of the oil hole (lubricant guideway) and the neutral axis (neutral axis), the oil hole supports the oil hole. Stress concentration occurring on the shaft can be reduced, and strength can be improved.
[Brief description of the drawings]
FIG. 1 is a longitudinal sectional view of a wedge roller type transmission according to the present invention.
FIG. 2 is a cross-sectional view of a main part of the wedge roller transmission with a housing removed, and is a cross-sectional view of the wedge roller transmission having a one-way clutch function.
FIG. 3 is a diagram illustrating the operation of a wedge roller type transmission as a speed reducer.
FIG. 4 is a diagram illustrating the operation of a wedge roller type transmission as a speed increasing device.
FIG. 5 is a cross-sectional view of a main part of the wedge roller type transmission with the housing removed, and is a cross-sectional view of the wedge roller type transmission capable of transmitting torque (power) when rotating in both forward and reverse directions. is there.
FIG. 6A is a cross-sectional view of a support shaft of a movable roller according to the embodiment of the present invention, and FIG. 6B is a partial schematic diagram of the movable roller and an outer ring.
FIG. 7 is a sectional view taken along line BB of FIG. 6 (b).
FIG. 8A is a partial schematic diagram of a movable roller and the like according to Patent Document 1, and FIG. 8B is a partial schematic diagram of a movable roller and an outer ring and the like according to Patent Document 1.
FIG. 9A is a partial schematic view of a movable roller and an outer ring according to Patent Literature 1, and illustrates a center axis (oil hole axis) of an oil hole (lubricant guide path) and a neutral axis (neutral axis). ) And (b) are cross-sectional views along line bb in (a).
[Explanation of symbols]
1 housing 2 housing (partition plate)
3 Low-speed side shaft 4 Disc-shaped member 14 Connecting plate 17 High-speed side shaft 27 Projection 32 Outer ring (low-speed side shaft)
36 Annular space 37a, 37b Guide roller 38 Movable roller 37 Guide roller 38a, 38b Movable roller 39a Support shaft 39b for guide roller Support shaft 40 for movable roller Fitting holes 41, 41a Support hole 42 Radial needle bearing 43a Guide Power transmitting cylindrical surface 43b for roller Power transmitting cylindrical surface 44 for movable roller Power transmitting cylindrical surface 45 Power transmitting cylindrical surface 46 Cylinder hole 47 Elastic material (preload spring)
48 Inside contact part 49 Outside contact part 51, 52 Spring pin 61 Lubricating oil guide path (oil hole)
62 Lubricating oil guideway (oil hole)
71 Anti-rotation hole (roller shaft hole, suppression means)
72 Projection (suppression means)
A Wedge roller type transmission

Claims (1)

A low-speed side shaft rotatably supported by the housing and having an outer ring at one end; a high-speed side shaft eccentrically supported by the housing and eccentric to the low-speed side shaft and the outer ring; In a friction roller type transmission using a wedge action, which is rotatably supported between a high-speed side shaft and includes at least one guide roller and at least one movable roller,
A support shaft that rotatably supports the movable roller,
A friction roller type transmission comprising: a suppression unit that suppresses rotation of the support shaft.

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