JP2003130090A - One-way clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a one-way clutch in which the breadthwise dimension is narrower than those of conventional cluches and the axial positioning structure is not required to be separately formed and further, which is easily built up, low in cost and practical. SOLUTION: The second track ring 1 made of tabular members in which a plurality of apertures 1a are circumferentially formed is disposed so as to be freely and relatively rotatable agaist the first track ring 2 in which two sheets of tabular circular members 2a are overlapped each other and a ball track face 2e is formed in the outer peripheral side, the inner peripheral side, or the radial intermediate part. A cum face 1d that the distance to the ball track face 2e gets narrow in a specified direction is formed in each aperture 1a, balls 3 brought into rolling contact with the ball track face 2e are contained in each aperture 1a, a viscous liquid VL is filled in the gap between each ball 3 and the ball track face 2e, the balls 3 are rotated together with the track rings during the relative rotation of the track rings 1 and 2, the width is made equal to the sum of the ball and two of tabular members 1a, a spring for urging the ball 3 can be omitted to save the component cost and setup cost.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a one-way clutch, and more particularly, to a compact one-way clutch having a small width, which is easy to assemble, inexpensive, and practical.

[0002]

2. Description of the Related Art As a one-way clutch that transmits relative rotation between a shaft and a housing in one direction and idles in the other direction,
A roller clutch having an axially parallel sectional view shown in FIG. 12 and an axially orthogonal sectional view shown in FIG. 13 is known. Such a roller clutch is often used, for example, in reels of fishing tackles and paper feed mechanisms of copying machines. Has been done.

This roller clutch holds an outer ring 10, a shaft 11 also serving as an inner ring, a plurality of rollers 12 interposed between the outer ring 10 and the shaft 11, and each of the rollers 12 at regular intervals in the circumferential direction. The cage 13 and the springs 14 that bias the rollers 12 in a fixed direction are used. A flange 10a is formed on the outer ring 10, and a plurality of cam surfaces 10b are formed on the inner peripheral surface of the outer ring 10 at a constant pitch. Each cam surface 10b is a surface in which the distance between the surface of the shaft 11 and the surface of the shaft 11 is gradually narrowed in a fixed direction in the circumferential direction (direction of arrow a in FIG. 13), and each roller 12 is fixed inside the outer ring 10. While being held by the retainer 13, the spring 14 is urged between the cam surface 10b and the outer peripheral surface of the shaft 11 in such a direction as to bite into the cam surface 10b, that is, in a direction in which the distance from the shaft 11 is narrowed. .
It is known that this type of roller clutch has a structure in which an inner ring is separately interposed between the roller and the shaft.

In the above structure, for example, when the shaft 11 rotates in the direction of arrow A in FIG. 13 with respect to the outer ring 10, the roller 12 which receives the rotational force resists the urging force of the spring 14 and forms the cam surface 10b. As a result of the displacement in the direction in which the distance from the shaft 11 becomes wider and the rollers 12 idling with respect to the outer ring 10, the rotational force of the shaft 11 is not transmitted to the outer ring 10 and the shaft 11 idling with respect to the outer ring 10. On the other hand, when the shaft 11 rotates in the direction of arrow B in FIG. 13 with respect to the outer ring 10, each roller 12 has a direction in which the gap between the cam surface 10b and the shaft 11 becomes narrow due to the rotational force and the biasing force of the spring 14. And is bitten between the cam surface 10b and the shaft 11, resulting in the shaft 1
The rotational force of 1 is transmitted to the outer ring 10, and the outer ring 10 rotates together with the shaft 11.

Here, in the above example, each roller 1
Although an example in which the same number of coil springs as balls are used as the spring 14 for pressing 2 is shown in consideration of reduction of the number of parts and ease of assembly process, the spring 14 is practically The structure shown in FIGS. 14 and 15 is often used.

FIG. 14 shows a combination of a resin-made cage 13 and an annular leaf spring 14. In this structure, the leaf spring 14 is inserted into each pocket 13a of the resin-made cage 13. Claws 14a for pressing each roller in a constant circumferential direction are integrally formed, and crimping claws 14b are integrally formed at both ends in the axial direction. The caulking claws 14b are crimped. As a result, the leaf spring 14 is incorporated inside the outer ring 10 in a state of being integrated with the resin cage 13.

In FIG. 15, a retainer and a spring are integrally formed of resin, and a pawl 13b for pressing each roller 12 into each pocket 13a of the retainer 13 is integrally formed. It is formed to project.

[0008]

By the way, in the roller clutch as described above, due to processing restrictions and the like,
The roller 12 requires a certain length or more, and naturally there is a limit in reducing the overall width dimension (axial dimension). The same can be said for a one-way clutch that uses a scrub as a power transmission member instead of the roller.

In the roller clutch described above, the structure of the spring for urging each roller 12 is shown in FIG.
As shown in FIG. 13 and FIG. 13, it becomes complicated, which is one of the reasons for increasing the cost. Further, when a force is intermittently applied due to the repeated operation of rotation transmission / idling of the one-way clutch, the spring and the retainer may have a complicated shape and may be easily damaged.

Further, in the above-mentioned roller clutch, since there is no axial positioning means with respect to the shaft 11, there is a problem that a separate positioning mechanism must be provided.

The present invention has been made in view of the above circumstances, and the width dimension can be made narrower than that of a conventional one-way clutch such as a roller clutch, and an axial positioning mechanism is separately provided. It is not necessary to provide, and from this point as well, the widthwise dimension as a whole can be significantly narrowed compared to the conventional roller clutch, and a complicated spring for urging the power transmission member is not required, The purpose is to provide a practical one-way clutch with low cost and high durability.

[0012]

In order to achieve the above object, a one-way clutch according to a first aspect of the present invention comprises two bearing rings arranged concentrically, and the relative rotation of each bearing ring is controlled. It is a one-way clutch that transmits only in one direction and idles in the other, and stacks two plate-shaped annular members,
A first race having a ball raceway surface formed by a curved portion formed on the outer edge side or the inner edge side of each of the annular members, or on a radially intermediate portion, and two annular members of the first race. There is provided a second bearing ring between which a plurality of windows are formed and which is composed of a plate-shaped member which is arranged so as to be rotatable relative to the first bearing ring, and the inner circumference of each window is provided. The surface is formed with a cam surface whose gap is gradually narrowed in a certain direction with respect to the ball raceway surface, and the first race and the second raceway are provided in the gap between the ball raceway surface and the ball. It is characterized by being filled with a viscous fluid that causes each ball to rotate when the wheels rotate relative to each other.

Further, in order to achieve the same object, a second aspect of the present invention is provided.
The one-way clutch according to the invention includes two orbital rings that are concentrically arranged in the same manner as described above, and the one-way clutch that transmits the relative rotation of each orbital ring in only one direction and idles in the other. There are two plate-shaped annular members,
A first race having a ball raceway surface formed by a curved portion formed on the outer edge side or the inner edge side of each of the annular members, or on a radially intermediate portion, and two annular members of the first race. A second recess formed of a plate-shaped member disposed between the first raceway ring and rotatable relative to the first raceway ring, and having a plurality of recesses opened toward the ball raceway surface along the circumferential direction. A raceway is provided, and a cam surface having a gradually narrowing interval with respect to the ball raceway surface is formed on the bottom surface of each recess, and a first gap is formed in the gap between the ball raceway surface and the ball. It is characterized by being filled with a viscous fluid that causes the balls to rotate together when the first bearing ring and the second bearing ring rotate relative to each other.

Here, in the present invention, grease or oil for lubricating the space between the ball raceway surface and the ball can be suitably adopted as the viscous fluid (claim 3).

According to the present invention, as the power transmission member (rolling element) interposed between the outer ring and the inner ring or shaft, balls are used without using rollers or sprags, and plate members are used as the outer ring and the inner ring. Moreover, this is not necessary for the spring that biases each ball in a certain direction, and the desired viscosity can be obtained by causing the ball to rotate with the bearing ring due to the viscosity of the viscous fluid filled in the gap between the ball raceway surface and the ball. It achieves the purpose.

That is, according to the present invention, a first race having two plate-shaped annular members superposed on each other and a plate-shaped member relatively rotatable between the two ring-shaped members are provided. Two orbital rings are used. If the first bearing ring is the inner ring,
When a curved portion is formed on the outer edge portion or the radial intermediate portion of two plate-shaped annular members to form a ball raceway surface, and when the first race is also used as an outer ring, two plate-shaped annular members are used. A curved portion is formed at an inner edge portion or a radially intermediate portion of the member to form a ball raceway surface.

In addition, in the present invention, "to stack two plate-like members" means not only the case of stacking two separate plate-like members but also the bending of one eyeglass-type plate-like member at the center. In addition, a form in which two plate-shaped members are superposed is also included, such as a form in which two plate-shaped members are superposed.

A second orbit is disposed between the above first orbital ring (inner ring or outer ring) and two plate-shaped annular members forming the first orbital ring so as to be relatively rotatable. A ring (outer ring or inner ring) is used, and the second bearing ring is provided with a plurality of windows each having a surface facing the ball raceway surface as a cam surface, and the balls are arranged in the respective windows. According to the structure in which the ball is rotated with the orbital ring by the viscous fluid filled in the gap between the ball and the ball orbital surface, the portion of the first orbital ring on which the ball orbital surface is formed has the maximum width, The width dimension of this portion is substantially the total dimension of the ball diameter and the wall thickness of the two plate-shaped annular members,
The width of the one-way clutch can be made considerably smaller than that of a conventional one-way clutch using a roller or sprag which cannot be made shorter than a predetermined length due to processing restrictions. Further, by fixing the inner ring made of two or one plate-shaped member to the shaft, it is possible to easily perform axial positioning without separately providing a fixing mechanism or the like.

Further, if a viscous fluid is filled in the gap between the ball raceway surface and the ball, the viscous resistance causes the drive side (active side) race ring to rotate with respect to the driven side (passive side) race ring. In doing so, the ball always rotates along with the drive-side bearing ring due to the viscous force resulting from the viscosity of the viscous fluid. In other words, when the drive-side bearing ring rotates in a direction in which the rotation is transmitted to the driven-side bearing ring, the ball rotates along with the drive-side bearing ring and the distance between the ball raceway surface and the cam surface becomes narrow. It is urged in the direction to reliably transmit rotation. On the other hand, even when the drive-side orbital ring rotates in the opposite direction, the ball rotates along with the drive-side orbital ring and is urged to rotate in such a direction that the space between the ball raceway surface and the cam surface becomes wider. The drive-side bearing ring reliably spins without transmitting.
Therefore, according to the present invention, unlike the conventional one-way clutch, it is not necessary to use a spring for urging the power transmission member (rolling element), and it is possible to reduce the number of parts and the number of assembling steps. it can. At the same time, the durability and reliability of the one-way clutch are improved because no complicated and easily damaged parts are used.

Further, as in the invention according to claim 2, instead of each of the windows described above, a plurality of recesses which are open toward the ball bearing ring, that is, when the second bearing ring is an outer ring, the outer ring is provided. A plurality of recesses that are open toward the ball raceway surface formed on the inner ring, and are formed on the outer ring on the outer circumferential side of the inner ring when the second ring is an inner ring. Even in a configuration in which a plurality of recesses that open toward the existing ball raceway surface are provided, and a cam surface equivalent to the one described above is formed on the bottom surface of each recess, the same effect as the above can be obtained.

Further, as the viscous fluid to be filled in the gap between the ball raceway surface and the ball, as in the invention according to claim 2,
It is preferable to use grease or oil for lubricating the space between the ball raceway surface and the ball, since a kind of viscous fluid can be used for both the urging of the ball and the lubrication of its rolling portion.

[0022]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. 1 is an axially parallel sectional view of an embodiment of the present invention, and FIG. 2 is an AA sectional view thereof.
Further, FIG. 3 shows an axially parallel sectional view taken along the line BB in FIG. Further, FIGS. 4 and 5 are explanatory views of the inner ring 1 and the outer ring 2, respectively. In each of these drawings, (A) is a front view and (B) is a BB sectional view thereof.

The one-way clutch in this embodiment has an inner ring 1 in which a plurality of windows 1a are formed in a plate-shaped annular body.
An outer ring 2 in which two outer ring plates 2a, 2a are superposed in a reverse direction and integrated with each other, a plurality of balls 3 housed in each window 1a of the inner ring 1, and a basic one-way clutch thereof. It is configured by a housing 5 that accommodates members. That is, in this example, the first bearing ring is the outer ring 2. As shown in FIG. 4, the inner ring 1 which is the second bearing ring is formed by punching and pressing a plate material such as a stainless steel plate, and has a plurality of windows 1a in a plate-shaped annular member having a uniform thickness. The outer peripheral surface 1b is formed into a circular shape, and the inner peripheral surface 1c is formed into a D-cut shape so that a large torque can be applied when it is fixed to the shaft S.

As shown in FIG. 5, the outer ring 2 is a plate-shaped annular member similarly formed by punching and press-forming a plate material such as a stainless steel plate, and has the same shape and size with each other.
The outer ring plates 2a, 2a are integrally formed by stacking them in opposite directions. A curved portion 2b is formed at a radially intermediate portion of each outer ring plate 2a, and a step portion 2c is formed on the outer peripheral side thereof so as to provide a gap G between the outer ring plates 2a, 2a in a superposed state. Has been done. The gap G formed between the outer ring plates 2a, 2a is also formed inside the curved portion 2b with the curved portion 2b interposed therebetween. Further, a flat portion 2d is formed on the outer peripheral side of the stepped portion 2c, and when the two outer ring plates 2a, 2a are superposed, the flat portions 2d are in close contact with each other and the curved portions 2b, 2b Raceway surface 2e of ball 3
Is formed. Then, the inner ring 1 is inserted into the gap G so as to be relatively rotatable. The inner peripheral surface 2f of each outer ring plate 2a, 2a is circular, and a plurality of recesses 2g are formed in the outer peripheral portion.

The raceway surface 2e of the outer ring 2 is set so as to almost hold the ball 3 except for the gap G formed on the outer peripheral side and the inner peripheral side thereof, and the curvature of the raceway surface 2e is the curvature of the ball 3. It is slightly larger than the above, and a proper gap is formed with the ball 3. A space between the ball 3 and the raceway surface 2e is filled with a viscous fluid VL for lubricating the space between them and for urging the ball 3 as described later. As the viscous fluid VL, grease or oil having an appropriate viscosity is used. Of the inner peripheral surface of each window 1a of the inner ring 1 described above, a portion on the outer peripheral side of the inner ring forms a cam surface 1d, which is shown in FIG.
In the assembled state shown in FIG. 3, the space between the outer race 2 and the raceway surface 2e is formed by a surface that gradually narrows in the direction indicated by the arrow R in FIG.

Each ball 3 is incorporated in each window 1a of the inner ring 1 so as to make rolling contact with the raceway surface 2e of the outer ring 2.

The housing 5 is composed of a housing main body 51 and a lid 52 which are molded products of resin such as polyacetal. 6 and 7 are cross-sectional views of the housing main body 51 and the lid 52 parallel to the axis.
In each of these drawings, (A) is a front view, and (B)
Shows a sectional view taken along line BB.

Both the housing main body 51 and the lid 52 are annular as a whole, and holes 51a and 52a for penetrating the shaft S are formed in the respective central portions. In addition, the housing body 51 and the lid 52 are
A recess 51 for accommodating the above-described assembly of the inner ring 1, the outer ring 2 and the ball 3 on the end faces on the side where they are butted against each other.
b, 52b are formed. Further, the lid 52 has a flat portion 52c formed on the outer peripheral side of the recess 52b, and the housing main body 51 has a step 51c formed on the outer peripheral side of the recess 51b. The outer peripheral surface of the lid 52 is inserted into the inner peripheral surface 51d on the outer side of 51c. Further, the stepped portion 51c has a plurality of convex portions 51e protruding in the axial direction.
The convex portions 51e are fitted into the concave portions 2g formed on the outer periphery of the outer ring 2 in the assembled state.

Then, when the lid 52 is covered in this state,
The outer ring 2 has a stepped portion 51c of the housing body 51 and a flat portion 52 of the lid 52 at the position where the flat portion 2d is formed on the outer peripheral portion of the outer ring 2.
It is sandwiched by c (see FIG. 3) and the lid 5
The two flat portions 52c are the convex portions 51e of the housing main body 51.
Is in contact with the surface (see FIG. 1). The lid 52 is fixed to the housing main body 51 by ultrasonically welding the contact surface between the flat portion 52c of the lid 52 and each convex portion 51e of the housing main body 51. With the lid 52 fixed to the housing body 51, the two outer ring plates 2a, 2a forming the outer ring 2 are sandwiched between the stepped portion 51c of the housing body 51 and the flat portion 52c of the lid 52. As a result, they are integrated with each other and also with the housing 5.

The above-described embodiment of the present invention is used in a state where the inner peripheral surface 1c of the inner ring 1 is fitted and fixed to the shaft S. When the outer ring 2 and the housing 5 rotate in the direction shown by the arrow F in FIG. 2 with respect to the shaft S and the inner ring 1 in a state where the inner ring 1 is fixed to the shaft S, the raceway surface 2e of the outer ring 2 makes rolling contact. Each of the balls 3 in the same direction as the outer ring 2, that is, the arrow F, by viscous force resulting from the viscosity of the viscous fluid VL made of grease or oil filled between the balls 3 and the raceway surface 2e. Move in the direction indicated by. The direction indicated by the arrow F is a direction in which the distance between the raceway surface 2e of the outer ring 2 and the cam surface 1d becomes wide, and therefore, each ball 3 has the raceway surface 2
There is no bite between e and the cam surface 1d, and the rotation of the outer ring 2 is not transmitted to the inner ring 1 and the shaft. Therefore, the outer ring 2 and the housing 5 idle with respect to the inner ring 1 and the shaft S.

On the other hand, when the outer ring 2 and the housing 5 rotate with respect to the shaft S and the inner ring 1 in the direction shown by the arrow R in FIG. 2, the balls 3 in rolling contact with the raceway surface 2e of the outer ring 2 are Fluid VL consisting of grease or oil filled between the bearing 3 and the raceway surface 2e
Due to the viscous force due to the viscosity of, the outer ring 2 moves in the same direction as the outer ring 2 in the same manner as described above, that is, in the direction indicated by the arrow R. The direction indicated by the arrow R is a direction in which the distance between the raceway surface 2e of the outer ring 2 and the cam surface 1d is narrowed, so that each ball 3 bites between the raceway surface 2e and the cam surface 1d. Therefore, in this case, the rotation of the outer ring 2 is transmitted to the inner ring 1 and the shaft S to rotate the inner ring 1 and the shaft S. At this time, the ball 3 comes into contact with the raceway surface 2e on both sides thereof with a gap G in between, and comes into contact with the inner and outer rings 1 and 2 at a total of three points including the contact point of the inner ring 1 with the cam surface 1d. Power can be transmitted stably in this state.

The point to be noted in the above embodiment is that the maximum width dimension as a one-way clutch excluding the housing 5 is the portion where the raceway surface 2e of the outer ring 2 is formed. In addition, the diameter of the ball 3 and the thickness of the two outer ring plates 2a, 2a are the total dimensions, and the maximum width dimension can be significantly reduced as compared with the conventional one-way clutch using rollers and sprags. . Moreover, 1
The one-way clutch can be easily positioned in the axial direction only by fixing the inner ring 1 made of a single plate-shaped annular member to the shaft S.

Further, a point to be further noted in the above embodiment is that the ball 3 which is a power transmission member is attached to the raceway surface 2
By using the viscous resistance of the viscous fluid VL to rotate the ball 3 around the drive-side bearing ring (outer ring 2) without providing a spring that biases the gap between the e and the cam surface 1d in a narrowing direction. The one-way clutch operates reliably, which eliminates the need to provide a spring having a complicated shape and can significantly reduce the cost including the assembly cost.

In the above embodiment, an example is shown in which a plurality of windows are provided in the inner ring and a cam surface is formed on the inner peripheral surface of each window on the inner peripheral side of the inner ring, but as shown in FIG. Alternatively, a plurality of recesses 1a 'may be formed instead of the windows, and the cam surface 1d may be formed on the bottom surface of each recess 1a'.

In the above description, the outer ring 2 is the driving-side bearing ring and the inner ring 1 is the driven-side bearing ring. However, even if they are reversed, the same effect can be obtained. Of course you can get it.

In the above embodiment, an example in which the two outer ring plates 2a, 2a are integrated by being sandwiched between the housing body 51 and the lid 52 welded or adhered thereto has been shown. Outer ring plate 2
It is possible to adopt a structure in which a and 2a are integrated by caulking each other.

Further, in the above embodiment, the bearing ring (first ring-shaped member formed by stacking two plate-shaped annular members on top of each other)
In the above example, the outer ring 2 is used as the outer ring 2 and the inner ring 1 is used as the bearing ring (second bearing ring) composed of one plate-shaped member. The plate-shaped annular members may be stacked to form the inner ring, and one plate-shaped member may form the outer ring. An example is shown below.

FIG. 9 is an axially parallel sectional view showing the structure of the main part of another embodiment of the present invention, and FIG. 10 is an axially orthogonal sectional view.
In this example, two inner ring plates 81a, 81a formed by punching and press-forming a plate material such as a stainless steel plate are overlapped with each other and integrated by caulking each other to form the inner ring 81. Plates 81a, 81a
The raceway surface 81c by the curved portion 81b formed on the outer edge of the
Is formed.

The outer ring 82 is formed by punching and pressing a plate material such as a stainless steel plate, and a plurality of windows 82a are formed in one plate-shaped member.
It is relatively rotatably inserted into a gap G formed between the inner ring plates 81a, 81a. Also, this outer ring 8
Of the inner peripheral surface of each window 82a of No. 2, the outer portion is the inner ring 8
A cam surface 82b that gradually narrows in the direction indicated by the arrow R in FIG. 10 is formed with respect to the first raceway surface 81c.
A plurality of recesses 82d are formed on the outer peripheral surface 82c of the outer ring 82.

Each ball 83, which is housed in each window 82a, is incorporated so as to make rolling contact with the raceway surface 81c of the inner ring 81. In the gap between each ball 83 and raceway surface 81c, Similarly, the viscous fluid VL such as grease or oil is filled.

A basic assembly as a one-way clutch composed of the inner ring 81, the outer ring 82 and the balls 83 is a housing main body 851 and a lid 852 similar to the previous example.
In this state, the plurality of concave portions 82d formed on the outer peripheral surface 82c of the outer ring 82 and the convex portion 851a formed on the inner peripheral surface of the housing main body 851 are engaged with each other. As a result, the outer ring 82 cannot rotate relative to the housing 85.

Also in this embodiment, the inner ring 8 is attached to the shaft S.
It is used with the inner peripheral surface of No. 1 fitted and fixed. In this state, when the shaft S and the inner ring 81 rotate in the direction indicated by the arrow F in FIG.
The balls 83 in rolling contact with the first raceway surface 81c are
The viscous force resulting from the viscosity of the viscous fluid VL filled between the balls 83 and the raceway surface 81c causes the inner ring 8 to move.
1 is rotated in the same direction as the direction 1 (the direction indicated by arrow F), and this direction is the raceway surface 81c of the inner ring 81 and the cam surface 8
2b, the distance between the ball 83 and the cam surface 82b is wide, and the balls 83 do not bite between the raceway surface 81c and the cam surface 82b.
The rotation of the inner ring 81 is not transmitted to the outer ring 82, so that the inner ring 8
1 and the shaft S rotate idly with respect to the outer ring 82 and the housing 85.

On the other hand, when the shaft S and the inner ring 81 rotate with respect to the outer ring 82 in the direction indicated by the arrow R in FIG. 10, the balls 8 rollingly contacting the raceway surface 81c of the inner ring 81.
3 is rotated in the same direction as the inner ring 81 (the direction indicated by the arrow R) in the same manner as above due to the viscous resistance of the viscous fluid VL filled between the balls 83 and the raceway surface 81c. Moving. This direction is the raceway surface 81 of the inner ring 81.
The direction in which the distance between c and the cam surface 81b becomes narrower, and each ball 83 bites between the raceway surface 81c and the cam surface 82b. Therefore, in this case, the rotation of the inner ring 81 is transmitted to the outer ring 82, and the outer ring 82 and the housing 85 are rotated.

In the above embodiment, an example in which a plurality of windows are provided in the outer ring and the cam surface is formed on the outer ring outer peripheral side surface of each window is shown. However, as shown in FIG. A plurality of recesses 82a 'are formed instead of the windows, and each recess 82a' is formed.
The cam surface 82b may be formed on a '.

[0045]

As described above, according to the present invention, a ball is used as a power transmission member, and at least one of the inner ring and the outer ring has two plate-shaped members (first bearing ring).
Since the other is composed of a single plate-shaped member (second bearing ring), its maximum width dimension is significantly smaller than that of a conventional one-way clutch that uses rollers or sprags as power transmission members. can do. Further, by fixing the inner ring made of one or two plate-shaped members to the shaft, the positioning in the axial direction can be easily performed without separately receiving a fixing mechanism or the like.

Further, by filling a viscous fluid between each ball and the ball raceway formed on the first bearing ring, each ball is rotated by the viscous resistance of the viscous fluid. At the same time, it rotates in the same direction as that of rotation, so there is no need for a spring that biases each power transmission member in a certain direction, unlike the conventional one-way clutch, and the number of parts and assembly man-hours are reduced. It is possible to obtain an inexpensive and compact one-way clutch.

[Brief description of drawings]

FIG. 1 is an axially parallel sectional view of an embodiment of the present invention.

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

FIG. 3 is a sectional view taken along line BB of FIG.

FIG. 4 is an explanatory view of the inner ring 1 according to the embodiment of the present invention, (A) is a front view, and (B) is a BB sectional view thereof.

5A and 5B are explanatory views of the outer ring 2 according to the embodiment of the present invention, in which FIG. 5A is a front view and FIG.

6A and 6B are explanatory views of the housing main body 51 according to the present invention, where FIG. 6A is a front view and FIG. 6B is a BB cross-sectional view thereof.

7A and 7B are explanatory views of a lid body 52 according to the present invention, in which FIG. 7A is a front view and FIG. 7B is a sectional view taken along line BB.

FIG. 8 is a front view showing another configuration example of the inner ring in the embodiment of FIGS.

FIG. 9 is an axially parallel sectional view of another embodiment of the present invention.

FIG. 10 is a front view shown by an arrow A in FIG. 8, showing a state in which a lid body 852 is removed.

FIG. 11 is a front view showing another configuration example of the outer ring in the embodiment of FIGS. 9 and 10.

FIG. 12 is an axially parallel sectional view showing a configuration example of a roller clutch, which is a type of conventional one-way clutch.

13 is a cross-sectional view of the roller clutch of FIG. 8 orthogonal to the axis.

FIG. 14 is an axially parallel sectional view showing a practical structure example of a spring used in a conventional roller clutch.

FIG. 15 is an axially parallel sectional view showing another example of the practical structure of the spring used in the conventional roller clutch.

[Explanation of symbols]

1,81 inner ring 81a Inner ring plate 1a, 82a windows 1b outer peripheral surface 1c Inner surface 1d cam surface 2,82 outer ring 2a Outer ring plate 2b curved part 2c step 2d flat part 2e, 81c Orbital surface 2f inner surface 2g recess 3,83 balls 5,85 housing 51,851 housing body 51c step 51e convex part 52,852 lid 52c flat part VL Viscous fluid

Claims (3)

[Claims] 1. A one-way clutch comprising two orbital rings arranged concentrically, transmitting the relative rotation of each orbital ring in only one direction, and idling to the other, comprising two plate-shaped clutches. And a first race ring in which the ball raceway surfaces are formed by the curved portions formed on the outer edge side or the inner edge side of each of the annular members or on the radially intermediate portion of the respective annular members. A plate-shaped member that is disposed between the two annular members to be rotatable relative to the first bearing ring, and has a plurality of windows in the circumferential direction.
The inner peripheral surface of each window is formed with a cam surface whose gap is gradually narrowed in a certain direction with respect to the ball raceway surface, and the clearance between the ball raceway surface and the ball is formed. A one-way clutch, characterized in that a viscous fluid that causes the balls to rotate together when the first bearing ring and the second bearing ring rotate relative to each other is filled. 2. A one-way clutch that includes two concentrically arranged bearing rings, transmits the relative rotation of each bearing ring in only one direction, and idles the other in two directions. And a first race ring in which the ball raceway surfaces are formed by the curved portions formed on the outer edge side or the inner edge side of each of the annular members or on the radially intermediate portion of the respective annular members. Between the two annular members, the plate-shaped member being rotatably arranged relative to the first bearing ring, and having a plurality of recesses opening toward the ball raceway surface along the circumferential direction. A second race formed by the above-mentioned method, and a cam surface having a narrower interval in a fixed direction with respect to the ball raceway surface is formed on the bottom surface of each recess. In the gap between the ball, the first bearing ring and the second bearing ring Way clutch fluid to rotate with the respective ball during relative rotation, characterized in that it is filled. 3. The one-way clutch according to claim 1, wherein the viscous fluid is grease or oil for lubricating the space between the ball raceway surface and the ball.