JP2003301906A - Friction roller type transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To use a friction roller type transmission utilizing wedging operation as a speed increasing gear suitable for a high-speed rotation machine. <P>SOLUTION: A low speed side shaft 3 is rotatably supported by a housing 1, and an outer ring 32 is provided at one end of the low speed side shaft 3, while a high speed side shaft 17 is rotatably supported eccentrically from the low speed side shaft 3 and the outer ring 32. Two guide rollers 37a, 37b and a movable roller 38 to be moved during torque transmission are mounted between the outer ring 32 and the high speed side shaft 17. During positive rotation, the movable roller 38 is moved between the high speed side shaft 17 and the outer ring 32 in the direction of biting into a wedge to produce thrust for transmitting torque. During reverse rotation, the movable roller 38 is moved farther from the wedge to produce zero thrust making torque transmitting torque impossible. The bearing support of the high speed side shaft 17 is performed only by a set of two angular ball bearings 24, 25 in face-to-face combination. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a machine in which a high speed side shaft rotates at high speed, such as a turbo machine, a supercharger,
The present invention relates to a friction roller type transmission utilizing a wedge action which is suitable for a speed increasing machine such as a machine tool.

[0002]

2. Description of the Related Art Traction drive type transmissions have been developed for various industrial applications because they are quiet and smooth.
Furthermore, in recent years, attempts have been made to apply it to personal use such as automobiles and bicycles, and it is drawing attention as a next-generation power transmission system.

Unlike a gear transmission, a traction drive type transmission strongly presses at least two rotating bodies having smooth surfaces, and a lubricating oil film (for example, an EHL oil film) is interposed between them to drive power. It is a mechanism for transmission, and its basic formula is expressed by a simple friction formula Ft = μ · Fc (Ft: traction force). Where Fc
Is called pressing force, and various methods have been developed to generate this.

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 in this specification). The wedge roller type transmission is around the tip of the high speed side shaft and is eccentric to the high speed side shaft,
A rotatably provided outer ring exists between the driven-side cylindrical surface that is the outer peripheral surface of the high-speed side shaft and the drive-side cylindrical surface that is the inner peripheral surface of the outer ring, and has a radial width of a circle. A transmission provided in at least one guide roller and at least one movable roller, each outer peripheral surface of which is a cylindrical surface for power transmission, disposed in an annular space that is not uniform in the circumferential direction. . The movable roller is a roller that generates a pressing force by a wedge action, and is a roller that moves in the radial direction and the circumferential direction.

A conventional wedge roller type transmission A shown in FIG.
Includes a low speed side shaft 103 (outer ring side) and a high speed side shaft 117, and when the low speed side shaft 103 is the output side, acts as a speed reducer, while the low speed side shaft 103 is the input side Is designed to act as a gearbox. In addition, the wedge roller type transmission A
Transmits torque during normal rotation, while it transmits torque during reverse rotation.
Some have a one-way clutch function that idles and does not transmit torque, and some can transmit torque when rotating in both forward and reverse directions.

In the case of a speed increaser having the high speed side shaft 117 as the output side, the high speed side shaft 117 as the output shaft is
The high speed rotating machine X is mounted, and the high speed side shaft 117 is supported by two deep groove ball bearings 131a, 131b and the like at both ends separated from each other as shown in FIG.

[0007]

However, the wedge roller type transmission A is required to have "play" that allows a slight error in machining parts, an assembly error, and a slight movement of each part at the time of torque input. Therefore, the deep groove ball bearing 131b on the side of the wedge roller type transmission A is provided with an internal clearance, and the bearing and the hole 123 of the partition plate 102 are loosened (gap fitting) so that the bearing and the high speed side shaft 117 are separated from each other. Loose (gap fitting).

As a result, these gaps (plays) absorb machining and assembly errors and minute movements.

On the other hand, on the side of the high speed rotating machine X, the high speed side shaft 117 needs to be firmly supported, and the deep groove ball bearing 131a and the like cannot have an internal clearance or "play".

As described above, the requirements on the wedge roller type transmission A side and the requirements on the high speed rotating machine X side are incompatible with each other. Therefore, it is difficult to use the wedge roller type transmission A for the high speed rotating machine X. Met.

The present invention has been made in view of the above circumstances, and provides a friction roller type transmission utilizing a wedge action that can be used as a speed increaser suitable for a high speed rotating machine. It is in.

[0012]

In order to achieve the above object, a friction roller type transmission utilizing a wedge action according to a first aspect of the present invention has a housing in which a low speed side shaft is rotatably supported. An outer ring is provided at one end of the low speed side shaft, and is eccentric to the low speed side shaft and the outer ring to rotatably support the high speed side shaft. At least one outer ring is provided between the outer ring and the high speed side shaft. A guide roller and at least one movable roller that moves at the time of torque transmission;
It is characterized in that only one front combination of two angular ball bearings is used.

According to a second aspect of the present invention, in a friction roller type transmission utilizing a wedge action, a low speed side shaft is rotatably supported by a housing, and an outer ring is provided at one end of the low speed side shaft while the low speed side shaft is provided. At least one guide roller, which is eccentric to the shaft and the outer ring, rotatably supports the high-speed side shaft, moves between the outer ring and the high-speed side shaft, and moves at least 1
It is characterized in that a single movable double-row angular contact ball bearing is supported on the high-speed side shaft by interposing a plurality of movable rollers.

Further, in a friction roller type transmission utilizing a wedge action according to a third aspect, a low speed side shaft is rotatably supported in a housing, and an outer ring is provided at one end of the low speed side shaft while the low speed side shaft is provided. Eccentric with respect to the shaft and the outer ring, rotatably supports the high speed side shaft, and between the outer ring and the high speed side shaft, at least one guide roller and at least one movable member that moves during torque transmission. A roller is interposed, and the bearing of the high speed side shaft is supported by only one bearing.

As described above, according to the present invention, the bearing support of the high-speed side shaft is limited to one set of the front combination of the two angular ball bearings.

On the side of the wedge roller type transmission, two angular ball bearings are combined in front even if there is no internal clearance or play in the bearing, so the shaft on the high speed side has a small angular rigidity and an angular direction. Can swing slightly to
It is possible to absorb machining and assembly errors and minute movements.

The high-speed side shaft is supported not only by these two angular ball bearings but also by the rollers on the transmission side, and is substantially supported at two points. Therefore, the high-speed side shaft is firmly supported on the high-speed rotating machine side without causing a defect such as a missile movement.

Therefore, according to the present invention, it is possible to satisfy the requirements of the wedge roller type transmission and the requirements of the high-speed rotating machine, which are not contradictory to each other in the past, and provide a speed increaser suitable for the high-speed rotating machine. be able to.

Further, when the bearing support of the high-speed side shaft is only one double-row angular contact ball bearing of the front combination, and when the bearing support of the high-speed side shaft is only one bearing, it is substantially the same as above. Has the effect of.

[0020]

BEST MODE FOR CARRYING OUT THE INVENTION A wedge roller type transmission according to an embodiment of the present invention will be described below with reference to the drawings.

First, the internal structure of the wedge roller type transmission common to the respective embodiments will be described in detail, and then the first embodiment and the second embodiment will be described.

(Internal structure of wedge roller type transmission) FIG.
FIG. 3 is a sectional view of a wedge roller type transmission according to the embodiment of the present invention. 2 is a sectional view of the wedge roller type transmission having a one-way clutch function taken along the line bb of FIG. 1, FIG. 3 is a diagram for explaining the operation of the wedge roller type transmission, and FIG. FIG. 3 is a cross-sectional view of a wedge roller type transmission that can transmit torque when rotating in opposite directions.

In the present embodiment, the wedge roller type transmission A acts as a speed increaser with the low speed side shaft 3 (outer ring side) as the input side and the high speed side shaft 17 as the output side.
However, the present invention can also be applied to a speed reducer having the low speed side shaft 3 (outer ring side) as the output side.

Further, as shown in FIG. 2, the wedge roller type transmission A has a one-way clutch function of transmitting torque during forward rotation but not idling and transmitting torque during reverse rotation. As shown in FIG. 4, torque may be transmitted during both forward and reverse rotations.

In the wedge roller type transmission A according to the embodiment of the present invention, in FIGS. 1 and 2, a housing 2 which is a partition plate is fixed to a substantially cylindrical housing 1. A low speed side shaft 3 is rotatably supported by the housing 1, and at the end of the low speed side shaft 3 in the housing 1,
A disc-shaped member 4 is provided, and an outer ring 32 is attached to the outer edge portion of the disc-shaped member 4.

A 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 which is a partition plate.

As shown in FIG. 2, a large-diameter guide roller 37a is provided between the outer ring 32 and the high-speed shaft 17.
A guide roller 37b having a small diameter and a movable roller 38 that moves when torque is transmitted are interposed.

As shown in FIG. 3, the support shaft 39b for rotatably supporting the movable roller 38 is constructed so as to be movable between the high speed side shaft 17 and the outer ring 32 in the direction of biting into the "wedge". Further, it is urged by an elastic material 47 (see FIG. 2) such as a compression spring installed in the cylinder hole 46 in a direction to bite into the “wedge”.

As a result, as shown in FIG. 3, during normal rotation, the movable roller 38 includes the high speed side shaft 17 and the outer ring 32.
It moves in a direction that bites into the "wedge" between and, and generates a pressing force Fc. Traction force is generated by this Fc, and torque can be transmitted.

On the other hand, during reverse rotation, the movable roller 38 is
Move in the direction away from the "wedge" and press force Fc =
It becomes 0, the outer ring 32 spins, and torque cannot be transmitted to the high speed side shaft 17.

As shown in FIG. 2, between the inner peripheral surface of the outer ring 32 and the outer peripheral surface of the distal end portion of the high speed side shaft 17, there is provided an annular space 36 having a radial width which is different in the circumferential direction. .

The wedge roller type transmission A is constructed by installing two guide rollers 37a and 37b and one movable roller 38 in such an annular space 36.
In the figure, the movable roller 38 is partially cut away and is shown. In order to install each of these rollers 37a, 37b, 38, three support shafts 39a,
39a and 39b are provided. These three support shafts 39
Two support shafts 39a, 39 of a, 39a, 39b
a is the housing 2 and the connecting plate 14 at both ends thereof.
It is press-fitted and fixed in the fitting holes 40, 40 formed in 1. Therefore, the two support shafts 39a, 39a are not displaced in the annular space 36 in the circumferential direction or the diametrical direction. On the other hand, the above three support shafts 39a, 39a, 39b
Of the remaining one of the supporting shafts 3 located on the upper left side of FIG.
9b supports both ends of the outer ring 32 with respect to the housing 2 and the connecting plate 14 so as to be slightly displaceable in the circumferential direction and the diametrical direction. For this reason, a support hole 41 having an inner diameter larger than the outer diameter of the support shaft 39b is formed in a portion of the housing 2 and the connecting plate 14 aligned with both ends of the one support shaft 39b. Both ends of the support shaft 39b are loosely engaged with the respective support holes 41.

Then, each support shaft 39 supported as described above.
The guide rollers 37a, 37b and the movable roller 38 are rotatably supported by bearings such as radial needle bearings 42, 42 (the bearings of the movable roller are not shown) around the intermediate portions of a, 39a, 39b. is doing. In order to connect and fix the connecting plate 14 to the housing 2, the protrusions 27, 27 projectingly provided on one surface of the connecting plate 14 have the guide rollers in the circumferential direction of the connecting plate 14. It exists between 37a, 37b and the movable rollers 38. In other words, the protrusions 27, 27 and the guide rollers 37a are provided in the annular space 36.
37b or movable rollers 38 are alternately present in the circumferential direction of the annular space 36. Further, the outer peripheral surface of each of the guide rollers 37a and 37b or the movable roller 38 and the circumferential side surface of each of the protrusions 27 and 27 do not interfere (rub) with each other.

In this way, the support shafts 39a, 39 are formed.
The guide rollers 37a, 3a rotatably supported between the housing 2 and the connecting plate 14 by a and 39b.
7b and the outer peripheral surface of the movable roller 38, the power transmission cylindrical surfaces 43a, 43a, 43b are driven side cylindrical surfaces 44 which are the outer peripheral surfaces of the tip of the high speed side shaft 17, respectively.
And the drive side cylindrical surface 45 which is the inner peripheral surface of the outer ring 32. As described above, each of the guide rollers 37
The radial widths of the annular space 36 in which the a and 37b and the movable roller 38 are installed are different in the circumferential direction. As described above, the guide rollers 37a and 37b are equal in width to the annular space 36 in the circumferential direction.
Also, the outer diameter of the movable roller 38 is different. That is, of the guide rollers 37a, 37b and the movable roller 38, 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 (upper side in FIG. 2). The outer diameter is the same as each other and is relatively small. On the other hand, the outer diameter of the guide roller 37a located on the opposite side (lower side in FIG. 2) of the outer ring 32 to which the tip of the high-speed shaft 17 is eccentric is set to the movable roller 38 and the guide roller 37b. Larger than the outer diameter of. Then, 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 driven-side and driving-side cylindrical surfaces 44 and 45, respectively.

Among the guide rollers 37a, 37b and the movable roller 38, the guide rollers 37a, 37 are used.
Both ends of the support shafts 39a, 39a supporting b are fixed to the housing 2 and the connecting plate 14 (in the annular space 36) as described above. On the other hand, the support shaft 39b that supports the movable roller 38 does not move relative to the housing 2 and the connecting plate 14 (the annular space 3) as described above.
In (6), a slight displacement in the circumferential direction and the diametrical direction is possible. Therefore, the movable roller 38 also
Within the annular space 36, some displacement is possible in the circumferential direction and the diametrical direction. Then, the housing 2 and the connecting plate 1
A support shaft 39 that supports the movable roller 38 by an elastic material 47 such as a compression spring installed in the cylinder hole 46 of No. 4
b is elastically lightly pressed to move the movable roller 38 rotatably supported by these support shafts 39b toward the narrow portion of the annular space 36.

When the rotary shaft is rotationally driven by the wedge roller type transmission according to the present invention having the above-mentioned structure, the driving force is input to the low speed side shaft 3 so that the outer ring 32 can be driven.
Is rotated clockwise in FIG. The rotation of the outer ring 32 is transmitted to the high speed side shaft 17 via the guide rollers 37a and 37b and the movable roller 38, and rotates the high speed side shaft 17 in the counterclockwise direction in FIG. The power transmission between the outer ring 32 and the guide rollers 37a and 37b and the movable roller 38, and the power transmission between the guide rollers 37a and 37b and the movable roller 38 and the high speed side shaft 17 are both friction. Since it is performed by power transmission, noise and vibration generated during power transmission are low.

The movable roller 38 is the outer ring 32.
The width of the annular space 36 is narrowed by a force corresponding to the magnitude of the torque transmitted from the high speed side shaft 17 to the high speed side shaft 17 (see FIG. 2).
The upper middle part of the) tends to cut into. Therefore, the contact portion between the driving side cylindrical surface 45 which is the inner peripheral surface of the outer ring 32 and the power transmission cylindrical surface 43a, 43a and 43b which is the outer peripheral surface of the guide rollers 37a and 37b and the movable roller 38, and , These power transmitting cylindrical surfaces 43a, 43
The surface pressure of the abutting portion between a and 43b and the driven side cylindrical surface 44 which is the outer peripheral surface of the high speed side shaft 17 becomes higher as the torque increases. Conversely, when this torque is small, the surface pressure of each of the contact portions is low. Therefore, the surface pressure of each of these contact portions is set to an appropriate value according to the torque to be transmitted, and the torque can be efficiently transmitted.

That is, when the outer ring 32 rotates clockwise in FIG. 2 and the high speed side shaft 17 also rotates counterclockwise, the movable roller 38 causes the outer ring 32 to rotate.
From the driving side cylindrical surface 45 which is the inner peripheral surface of the above and the driven side cylindrical surface 44 which is the outer peripheral surface of the high speed side shaft 17, a force in the same direction as the pressing force by the elastic material 47 is received and the annular space 36 2 tends to move toward the narrow part, that is, toward the center of the upper part of FIG.

As a result, the power transmission cylindrical surface 43b, which is the outer peripheral surface of the movable roller 38, is replaced by the drive side cylindrical surface 45.
And the driven side cylindrical surface 44 are strongly pressed. And
This power transmission cylindrical surface 43b and the driven side cylindrical surface 44
The contact pressure of the inner diameter side contact portion 48, which is the contact portion with the drive force, and the outer diameter side contact portion 49, which is the contact portion between the power transmission cylindrical surface 43b and the drive side cylindrical surface 45, are high. Become. In this way, both the inner diameter side and outer diameter side contact portions 4 of the movable roller 38 are
When the abutting pressure of 8, 49 is increased, the high-speed side shaft 17 and the outer ring 32, which are pressed by the power transmission cylindrical surface 43b that is the outer peripheral surface of the movable roller 38, have a diameter due to elastic deformation and assembly clearance. Slightly displaced in the direction. As a result, the contact pressures of the inner diameter side and outer diameter side contact portions 48 and 49 with respect to the guide rollers 37a and 37b are increased. Then, both of these inner diameter side and outer diameter side contact portions 48,
Based on the frictional engagement at 49, the rotational force of the outer ring 32 can be transmitted to the high speed side shaft 17 via the guide rollers 37a and 37b and the movable roller 38.

As described above, the force for moving the movable roller 38 toward the narrow portion of the annular space 36 is large as the rotational driving force transmitted from the outer ring 32 to the high speed side shaft 17. It changes according to the size. And
As this force increases, both the inner diameter side and outer diameter side contact portions 4
The contact pressure of Nos. 8 and 49 becomes high. Therefore, based on such an action, the contact pressure corresponding to the transmitted rotational driving force is automatically selected, and the transmission efficiency of the wedge roller type transmission A can be secured.

In the case of the example shown in FIG. 2, the wedge roller type transmission A has a one-way clutch function,
When the rotation speed of the high-speed side shaft 17 becomes higher than the rotation speed of the outer ring 32, that is, the rotation speed of the outer ring 32 multiplied by the speed increasing ratio of the wedge roller type transmission A, The connection of this wedge roller type transmission A is disconnected. That is, in this case, the movable roller 38
However, against the elasticity of the elastic material 47, the annular space 36
Is displaced to the wider side (lower left side in FIG. 2). As a result,
The contact pressure between the inner diameter side and outer diameter side contact portions 48, 49 is reduced or lost, and the rotation of the outer ring 32 is not transmitted to the high speed side shaft 17.

Next, the wedge roller type transmission shown in FIG. 4 capable of transmitting torque when rotating in both forward and reverse directions will be described.

FIG. 4 shows the high speed side shaft 17 (see FIG. 1).
Shows a structure which can be rotationally driven in both directions of a clock and a counterclockwise. Therefore, the structure of this example is implemented in combination with the high-speed rotating machine X (see FIG. 1) whose rotational direction is freely convertible. In the combination of the structure of this example, one guide roller 37 and two movable rollers 38a and 38b are conveniently used as the three rollers forming the wedge roller type transmission A. . Of these, the roller installed in the widest part of the annular space 36 is a guide roller 37 whose diameter is relatively large and whose installation position does not change. On the other hand, a pair of rollers provided with the narrowest portion of the annular space 36 sandwiched therebetween are movable rollers 38a each having a relatively small diameter and capable of slight displacement in the circumferential direction and the diametrical direction. , 38b. Then, the support shafts 39b, 39 supporting the movable rollers 38a, 38b, respectively.
b is elastically pressed toward the narrowest part of the annular space 36.

In the case of the structure of the present embodiment configured as described above, when the outer ring 32 rotates clockwise in FIG. 4, the movable row 38a on the left side in FIG. I will cut into the part that became. On the other hand, the outer ring 3
When 2 rotates in the counterclockwise direction in FIG. 4, the movable roller 38b on the right side in FIG. 4 bites into the narrowed portion of the annular space 36. Further, in the case of this example, support shafts 39b and 39b supporting the movable rollers 38a and 38b, respectively.
In order to support both ends of the annular space 36, the lengths of the support holes 41a formed in the housing 2 and the connecting plate 14 in the circumferential direction of the annular space 36 are regulated. Specifically, of the support holes 41a, 41a, the annular space 36 is
The position of the end on the wide side (lower side in FIG. 4) is closer to the position where the width of the annular space 36 is narrower than that in the case shown in FIG. The movable rollers 38a, 38b are prevented from retreating excessively to the wider side of the annular space 36.

In the case of the present embodiment configured as described above, even if the outer ring 32 rotates in either the clockwise or counterclockwise direction, any movable roller 38a (38b) causes the width of the annular space 36 to change. Of the movable roller 38
Inner diameter side and outer diameter side contact portions 48, 4 related to a (38b)
Increase the contact pressure of 9. On the other hand, the movable roller 38b is displaced in the direction of retracting from the narrow portion of the annular space 36.
With respect to (38a) as well, the retreat amount is limited. As a result, with respect to both the movable rollers 38a, 38b and the guide roller 37, the contact pressures of the contact portions 48, 49 on the inner diameter side and the outer diameter side are sufficiently increased, and from the outer ring 32 to the high speed side shaft 17, Motion can be transmitted efficiently. As described above, except that the power can be transmitted from the rotating outer ring 32 to the high-speed side shaft 17 in both the clockwise and counterclockwise directions, the same parts as those described above with reference to FIG. Omit it. (First Embodiment) Next, the first embodiment will be described. FIG. 1 is a sectional view of a wedge roller type transmission according to a first embodiment of the present invention. 2 is a cross-sectional view of the wedge roller type transmission having a one-way clutch function taken along line bb of FIG. 1, FIG. 3 is a diagram for explaining the operation of the wedge roller type transmission, and FIG. FIG. 3 is a cross-sectional view of a wedge roller type transmission that can transmit torque when rotating in opposite directions. FIG. 5A is an enlarged cross-sectional view of an example in which two angular ball bearings are combined in front, and FIG. 5B is an enlarged cross-sectional view of an example in which two angular ball bearings are combined in back.

Two holes are provided in the hole 23 of the partition plate (housing) 2.
One set of angular contact ball bearings 24 and 25 in which individual pieces are combined in front
And a seal member 29 is provided by the preload member 26.
It is firmly fixed with. The preload member 26 presses the outer rings of the bearings 24 and 25 in the axial direction to apply preload so as to eliminate the inner clearance of the bearing.

No bearing is provided on the high-speed rotating machine X side. This is because if the high-speed side shaft 17 is supported by two bearings that are distant from each other, it becomes impossible to slightly swing in the angular direction.

As described above, in the present embodiment, the bearing support of the high-speed side shaft 17 is made up of only one set of two angular ball bearings 24, 25 that are assembled in front.

On the side of the wedge roller type transmission A, as shown in FIG.
As shown in (a), angular contact ball bearings (24, 25)
Since the two are combined in the front direction, the action point distance d can be made smaller than in the case of the rear combination in FIG. Therefore, the angular rigidity of the high-speed side shaft 17 can be reduced, the high-speed side shaft 17 can be slightly swung in the angular direction, and processing errors, assembling errors, and minute movements can be absorbed.

In the case of the back face combination shown in FIG. 5B, the action point distance d is large, the angular rigidity of the high speed side shaft 17 cannot be reduced, and the high speed side shaft 17 cannot be swung in the angular direction.

The high speed side shaft 17 is not only supported by these two angular ball bearings (24, 25), but also the rollers 37a, 3 on the side of the wedge roller type transmission A.
It is also supported by 7b and 38, and is substantially supported at two points. Therefore, the high-speed side shaft 17 is firmly supported on the high-speed rotating machine side X without causing a defect such as a misalignment motion.

Therefore, according to the present invention, it is possible to satisfy the requirements of the wedge roller type transmission A side and the requirements of the high speed rotating machine X side which are conventionally incompatible with each other, and the high speed rotating machine X can be satisfied.
It is possible to provide a speed increaser (or a speed reducer) suitable for.

(Second Embodiment) FIG. 6 shows a second embodiment of the present invention.
It is a sectional view of a wedge roller type gearbox of an embodiment. A sectional view of the wedge roller type transmission taken along the line bb is shown in FIG.
Since it is equivalent to FIG. Moreover, the same components as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

In this embodiment, the partition plate (housing)
No bearing is provided in the hole 23 of No. 2, and two sets of two angular ball bearings 24 and 25, which are frontally combined, are provided on the high speed side shaft 1.
It is provided at the other end of 7.

Also in this case, as shown in FIG.
Since the two angular ball bearings (24, 25) are combined in the front direction, the working point distance d can be made smaller than in the case of the rear combination in FIG. 5 (b). Therefore,
The angular rigidity of the high speed side shaft 17 can be reduced, the high speed side shaft 17 can be slightly swung in the angular direction, and processing errors, assembly errors, and minute movements can be absorbed. Further, the high speed side shaft 17 is not only supported by these two angular ball bearings (24, 25),
Wedge roller type transmission A side rollers 37a, 38b, 3
8 (see FIG. 2), and is substantially supported at two points. Therefore, the high-speed side shaft 17 does not cause a defect such as a scouring motion, and the high-speed rotating machine side X
Then, it is firmly supported.

(Third Embodiment) FIG. 7 shows a third embodiment of the present invention.
FIG. 3 is a cross-sectional view of the wedge roller type transmission according to the embodiment. A cross-sectional view of the wedge roller type transmission taken along the line bb is the same as FIGS. Moreover, the same components as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

In the present embodiment, one double-row angular contact ball bearing 30 combined in front is used instead of one set of two angular contact ball bearings 24, 25 combined in front.

Also in this case, since the front combination is used, the working point distance can be made smaller than that in the rear combination. Therefore, the angular rigidity of the high-speed side shaft 17 can be reduced, the high-speed side shaft 17 can be slightly swung in the angular direction, and processing errors, assembling errors, and minute movements can be absorbed. Also, the high speed side shaft 17
Is a double-row angular contact ball bearing 3 combined with this front
Not only is it supported by 0, but it is also supported by rollers 37a, 37b, 38 (see FIG. 2) on the side of the wedge roller type transmission A, and is supported at substantially two points. Therefore,
The high-speed side shaft 6 is firmly supported on the high-speed rotating machine X side without causing a defect such as a missile movement.

(Fourth Embodiment) FIG. 8 shows a fourth embodiment of the present invention.
FIG. 3 is a cross-sectional view of the wedge roller type transmission according to the embodiment. A cross-sectional view of the wedge roller type transmission taken along the line bb is the same as FIGS. Moreover, the same components as those in the first embodiment are designated by the same reference numerals, and the description thereof will be omitted.

In the present embodiment, a deep groove ball bearing 31 is used in place of the pair of two angular ball bearings 24 and 25 that are combined in front.

In this case, since angular rigidity is not imparted, it can be applied if the rotational speed condition is not so high.

The present invention is not limited to the above-described embodiments, but can be modified in various ways.

[0063]

As described above, according to the present invention,
The bearing support for the high-speed side shaft is limited to one set of two frontal combinations of angular ball bearings.

On the side of the wedge roller type transmission, two angular ball bearings are combined in front even if there is no internal clearance or play in the bearing, so the high-speed side shaft has small angular rigidity and Can swing slightly to
It is possible to absorb machining and assembly errors and minute movements.

The high speed side shaft is supported not only by these two angular ball bearings but also by the rollers on the transmission side, and is supported at substantially two points. Therefore, the high-speed side shaft is firmly supported on the high-speed rotating machine side without causing a defect such as a missile movement.

Therefore, according to the present invention, it is possible to satisfy the requirements of the wedge roller type transmission side and the requirements of the high speed rotating machine side, which are not contradictory to each other in the past, and provide a speed increaser suitable for the high speed rotating machine. be able to.

Further, when the bearing support of the high-speed side shaft is only one double-row angular contact ball bearing in the front combination, and when the bearing support of the high-speed side shaft is only one bearing, it is substantially the same as above. Has the effect of.

[Brief description of drawings]

FIG. 1 is a sectional view showing an internal structure of a wedge roller type transmission according to a first embodiment of the present invention.

FIG. 2 is a sectional view taken along line bb of FIG.

FIG. 3 is a diagram illustrating an operation of a wedge roller type transmission.

FIG. 4 is a sectional view of a wedge roller type transmission according to the present invention capable of transmitting torque when rotating in both forward and reverse directions.

5A is an enlarged cross-sectional view of an example in which two angular ball bearings are combined in front, and FIG. 5B is an enlarged cross-sectional view of an example in which two angular ball bearings are combined in back.

FIG. 6 is a sectional view of a wedge roller type transmission according to a second embodiment of the present invention.

FIG. 7 is a sectional view of a wedge roller type transmission according to a third embodiment of the present invention.

FIG. 8 is a sectional view of a wedge roller type transmission according to a fourth embodiment of the present invention.

FIG. 9 is a cross-sectional view of a conventional wedge roller type transmission.

[Explanation of symbols]

1, 101 housing 2,102 housing (partition plate) 3,103 Low speed side shaft 4 Disc-shaped member 14 Connection plate 17,117 High speed side shaft 22 Thrust needle bearing 23, 123 holes 24, 25 angular contact ball bearing 26 Preload member 27 Projection 28 Volts 29 Seal member 30 Double Row Angular Contact Ball Bearing 31, 131a, 131b Deep groove ball bearings 32 outer ring (low speed side shaft) 33 retaining ring 34 Volts 36 annular space 37, 37a, 37b Guide roller 38, 38a, 38b Movable roller 39a, 39b Support shaft 40 fitting hole 41, 41a Support hole 42 radial needle bearing 43 Cylindrical surface for power transmission 44 Driven side cylindrical surface 45 Drive side cylindrical surface 46 Cylinder hole 47 Elastic material 48 Inner diameter side contact part 49 Outer diameter side contact part A wedge roller type transmission X high speed rotating machine

   ─────────────────────────────────────────────────── ─── Continued front page    F term (reference) 3J051 AA01 BA03 BB08 BC01 BD01                       BE04 EC01 FA06 FA07                 3J063 AA25 AA40 AB35 AC01 BA04                       BA09 BB25 CB57 CD02 XB06

Claims (3)

[Claims] 1. A low speed side shaft is rotatably supported by a housing, and an outer ring is provided at one end of the low speed side shaft, while the high speed side shaft is rotatably eccentric with respect to the low speed side shaft and the outer ring. At least one guide roller that supports and that moves between the outer ring and the high-speed side shaft when torque is transmitted.
It has one movable roller and supports the bearing of the high-speed side shaft with the angular ball bearing 2
A friction roller type transmission utilizing a wedge action, characterized in that only one front combination is provided. 2. A low speed side shaft is rotatably supported by a housing, and an outer ring is provided at one end of the low speed side shaft, while the high speed side shaft is rotatably eccentric with respect to the low speed side shaft and the outer ring. And at least one guide roller and at least one movable roller that moves during torque transmission between the outer ring and the high-speed side shaft, and the bearing support for the high-speed side shaft A friction roller type transmission utilizing the wedge action, which is characterized by having only one double-row angular contact ball bearing. 3. A low speed side shaft is rotatably supported by a housing, and an outer ring is provided at one end of the low speed side shaft, while the high speed side shaft is rotatably eccentric with respect to the low speed side shaft and the outer ring. And at least one guide roller between the outer ring and the high speed side shaft, and at least one movable roller that moves during torque transmission, and one bearing for supporting the high speed side shaft. Friction roller type transmission utilizing the wedge action, which is characterized in that it is only.