JP2001074070A - Clutch device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize a structure to certainly perform a function to transmit rotation of an input member to an output member but not to transmit rotation of the output member to the input member. SOLUTION: An input member 3a and an output member 2a are arranged on the inner diametrical side of a fixed outer ring 1a. These input member 3a and output member 2a are assembled free to slightly displace along the circumferential direction by an engagement protruded part 19 provided on the side of the input member 3a and an engagement recessed part 13 provided on the side of the output member 2a. A rotor 4 is provided between a cam surface 5a provided on an outer peripheral surface of the output member 2a and a friction surface 6a provided on an inner peripheral surface of the outer ring 1a. Each of these rotors 4 rolls at rotation of the input member 3a, and each of these rotors 4 bites in between the cam surface 5a and the friction surface 6a at rotation of the output member 2a.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION A clutch device according to the present invention enables transmission of torque from a drive source to a driven body, but prevents transmission of torque from the driven body to the drive source. For example, it is used in a state of being incorporated in various driving devices such as a window regulator (including both an electric type and a manual type) for an automobile and an electric storage mirror.

[0002]

2. Description of the Related Art In the case of a window regulator for an automobile, for example, the rotation of an electric motor or a handle, which is a driving source, is transmitted to an elevating mechanism of a window glass. However, it is necessary to prevent the electric motor or the handle from rotating (for example, for security). As a clutch device having such a function, a clutch device described in JP-A-7-103260 has been conventionally known.

As shown in FIG. 14, the clutch device described in this publication has an outer ring 1, an output member 2, and an input member 3,
And a plurality of rolling elements 4 and 4 and a plurality of cam surfaces 5 and 5. Of these, the outer ring 1 has a cylindrical friction surface 6 on the inner peripheral surface, and does not rotate while being fixed to a window regulator frame or the like in use. The output member 2 is rotatably supported inside the outer ring 1 concentrically with the outer ring 1. The input member 3 has a plurality of arms 7. These arms 7, 7 are provided intermittently in the circumferential direction, and are inserted into an annular space 8 between the inner peripheral surface of the outer ring 1 and the outer peripheral surface of the output member 2. In addition, the plurality of rolling elements 4, 4
It is provided between the arms 7 that are circumferentially adjacent to each other. Further, each of the cam surfaces 5, 5 is connected to the output member 2
Are formed at a plurality of locations on the outer peripheral surface of each of the rolling elements 4 and 4 opposite to each of the rolling elements 4 and 4. The center in the circumferential direction is located most inward in the diametric direction. It is inclined in the direction located.

[0004] In the clutch device as described above, the rotation of the input member 3 is independent of the rotation direction, and the arms 7, 7 are not rotated.
From the rolling elements 4 and 4. That is, when the input member 3 rotates, the inclined surfaces 9, 9 formed on the circumferential edges of the plurality of arms 7, 7 provided on the input member 3 cause the rolling elements 4, 4 to move to the respective rolling elements 4, 4. Press against each cam surface 5,5.
The rotation of the input member 3 is transmitted to the output member 2 by the engagement between the inclined surfaces 9 and 9 and the cam surfaces 5 and 5. On the other hand, when the output member 2 rotates, the cam surfaces 5 and 5 push the rolling elements 4 and 4 outward in the diameter direction of the output member 2, and the rolling elements 4 and 4 4 is pressed against a friction surface 6 provided on the inner peripheral surface of the outer ring 1. As a result, the rotation of the output member 2 is prevented by the frictional engagement between the rolling surfaces of the rolling elements 4 and the friction surface 6, and the rotation of the output member 2 is independent of the rotation direction. Transmission to the input member 3 is stopped.

[0005]

In the case of the conventional clutch device as described above, when the input member 3 rotates, all or some of the plurality of rolling elements 4, 4 are provided on the cam surface 5 provided on the output member 2 side. 5 and the friction surface 6 provided on the inner peripheral surface of the outer ring 1 may move to a position where they mesh with each other. For example, FIG.
Assuming that the up-down direction of the rolling element coincides with the up-down direction of the actual installation state, the lower rolling element 4 in FIG.
Actually, it does not exist at the position as shown in the figure, but is lowered to the position where it comes into contact with the friction surface 6 by gravity. When the arms 7 provided on the input member 3 rotate from this state, one of the arms 7 moves the lower rolling element 4 between the lower cam surface 5 and the friction surface 6. There is a possibility to move to the position where it meshes with. When the front and back directions in FIG. 14 match the vertical direction, more rolling elements 4 and 4
It may be pushed to a position where the cam surfaces 5, 5 and the friction surface 6 are engaged with each other.

[0006] In this manner, with the rotation of the input member 3, all or a part of the rolling elements 4, 4 are brought into contact with the cam surfaces 5, 5 provided on the output member 2 side and the inner peripheral surface of the outer ring 1. Provided friction surface 6
The rotation of the input member 3 is not transmitted to the output member 2. The clutch device of the present invention has been invented in order to realize a structure capable of reliably transmitting the rotation of the input member to the output member without such a malfunction.

[0007]

A clutch device according to the present invention comprises an outer ring, an output member, an input member, a plurality of rolling elements, and a plurality of cam surfaces, similarly to the aforementioned conventional clutch device. Prepare. Of these, the outer ring has an inner peripheral surface as a cylindrical friction surface, and does not rotate in a fixed state in use. The output member is rotatably supported inside the outer ring concentrically with the outer ring. The input member has a plurality of arms. These arms are provided intermittently in the circumferential direction, and are inserted into an annular space between the friction surface provided on the inner peripheral surface of the outer race and the outer peripheral surface of the output member. Each rolling element is provided between arms adjacent in the circumferential direction in the annular space. Each of the cam surfaces is formed at a plurality of locations on the outer peripheral surface of the output member facing each of the rolling elements, and the center in the circumferential direction is located most inward in the diameter direction. Both ends in the circumferential direction are inclined in the direction located diametrically outward. The rotation of the input member is transmitted to the output member regardless of the rotation direction, but the rotation of the output member is not transmitted to the input member regardless of the rotation direction.

Particularly, in the clutch device of the present invention,
Provided between the output member and the input member is an engagement portion that engages with each other in a state where the two members are displaced relative to each other by a predetermined angle with respect to the rotation direction, and is capable of transmitting the rotation of the input member to the output member. ing. At the same time, an elastic member is provided between each circumferential side of each arm and each rolling element, and these rolling elements are elastically moved toward the center position of the arms adjacent in the circumferential direction. Pressing. When the input member rotates, the rotation of the input member is transmitted to the output member based on the engagement of the engagement portion, and each of the rolling elements includes the cam surface and the friction surface. It can roll freely between. On the other hand, when the output member tends to rotate with respect to the input member, the rolling elements move between the cam surfaces and the friction surfaces before the engagement portions are engaged. To prevent the output member from rotating with respect to the outer ring.

[0009]

In the clutch device of the present invention constructed as described above, when the input member rotates, the output member also rotates in the same direction based on the engagement of the engagement portion. As the input member slightly rotates with respect to the output member until the engagement portion is engaged, each rolling element rotates the input member more than the center of the cam surface in the circumferential direction. Move a little forward in the direction. When the input member and the output member rotate in the same direction in this state, the rolling elements tend to be displaced toward the central portions of the cam surfaces. Therefore, these rolling elements do not mesh with each of the cam surfaces and the friction surface of the inner peripheral surface of the outer ring. As a result, the input member and the output member are rotatable inside the outer ring, and rotation can be transmitted from the input member to the output member.

On the other hand, when the output member rotates with respect to the input member, before the engagement portion engages, that is, before the rotation of the output member is directly transmitted to the input member, Each rolling element bites between each of the cam surfaces and the friction surface. As a result, the output member does not further rotate, and the rotation of the output member is not transmitted to the input member.

[0011]

1 to 11 show an example of an embodiment of the present invention. The clutch device 10 of the present invention includes:
The vehicle includes an outer ring 1a, an output member 2a, an input member 3a, a plurality of rolling elements 4, 4, and a plurality of cam surfaces 5a, 5a.

The outer ring 1a is formed entirely of a hard metal plate such as carbonitrided steel in a cylindrical shape, and flanges 11a and 11b having inward flanges are provided at both ends in the axial direction to form the outer ring 1a. The output member 2a and the input member 3a are unitized so as not to come off from the inside, thereby facilitating the handling. A portion sandwiched between the flanges 11a and 11b on the inner peripheral surface of the outer ring 1a is a cylindrical friction surface 6a. The friction surface 6a has properties such as the outer raceway of a general cylindrical roller bearing, and has a smooth surface. When the clutch device 10 is in use, the outer ring 1a does not rotate while being fixed to a frame or the like of the window regulator.

In the illustrated example, both the flanges 11a, 1
1b, the width W of one (right side in FIG. 1) flange 11a.
_11a is larger than the width W _11b of the other flange 11b (W
_11a > W _11b ). It also has a large width _W11a ,
When the clutch device 10 is assembled, the thickness of the flange portion 11a, which is the bottom side (the side formed in advance before the assembly operation, the right side in FIG. 1) before the assembly operation, is set to the curl side ( It is larger than the thickness of the flange 11b (left side in FIG. 1). The reason for this configuration is that the bottom side flange 1
While it is easy to increase the width W _11a of 1b, if the width W 11b of the curl-side flange _11b is increased,
This is because wrinkles are easily generated in the flange portion 11b. In other words, the width W of the flange 11b formed after the output member 2a and the input member 3a are inserted into the outer ring 1a.
This is because, when the size of the flange _11b is increased, the forming operation of the flange 11b becomes difficult in consideration of the quality of the flange 11b. Therefore, in the illustrated example, the curl-side flange portion 11b
And the outer diameter of the board portion 17 constituting the input member 3a is increased, so that the width W of the flange portion 11b is increased.
It is possible to make _11b smaller.

The output member 2a is made of, for example, JIS
As shown in FIG. 2, it is formed concentrically with and integral with the output shaft 12 by a hardened metal such as sintering hardened metal such as SMF4060, bearing steel, and the like. It is supported concentrically and rotatably. The output shaft 12 is formed in a columnar shape, and when used, its distal end (the right end in FIGS. 1 and 2) is fitted and fixed in a circular hole provided on the driven member side by interference fitting. However, the output shaft 1
The connection between the drive member 2 and the driven member may be in other known engagement states such as spline engagement and key engagement. on the other hand,
The output member 2a is formed in an outward flange shape at one end (the left end in FIG. 2) of the output shaft 12. On the outer peripheral surface of such an output member 2a, a plurality of (five in the example shown) cam surfaces 5a, 5a and engagement recesses 13, 13 are provided.
Are alternately formed at equal pitches in the circumferential direction. Each of the engaging concave portions 13 and 13 was formed through an axial end, and was integrally formed at a low cost together with the engaging convex portions 19 by injection molding of synthetic resin as described later. The input member 3a can be assembled in the axial direction.

The cam surfaces 5a and 5a are shown in FIG.
As shown, the center in the circumferential direction is circumscribed by the output member 2a.
Radius R of the circle_2aRadius of curvature R slightly smaller than₁₄Having
And the center convex curved surface portion 14 concentric with the circumscribed circle of
Is the diameter of the circumscribed circle 2R _2aA little smaller than this
Curvature radius R of central convex curved surface portion 14₁₄2R of 2 times₁₄Than
Also has a slightly larger radius of curvature R_FifteenCurved surfaces 15, 1 having both ends
5 is assumed. With such a configuration, each of the rolling elements 4,
4 is a friction surface 6 between each of the cam surfaces 5a, 5a and the outer ring 1a.
so that the wedge angle when biting between a
are doing. The width of the central convex curved surface portion 14 is very small.
You. Therefore, each of the cam surfaces 5a, 5a has a circular shape.
The center part in the circumferential direction is located most inward in the diameter direction,
Increasing in the direction located diametrically outward toward both ends in the circumferential direction
ing. In the present invention, as described later, each of the concave surfaces
15 and 15, each of the rolling elements 4, 4 is connected to the outer race 1
a cam surface for cutting into the friction surface 6a
And two cam surfaces for each rolling element 4
Is provided. The circumferential direction of each of the cam surfaces 5a, 5a
Both ends are curved in the same direction as the rolling surfaces of the rolling elements 4 and 4
The reason for the concave curved surface is that the input member 3a described below
When power is transmitted to the output member 2a, each of the cam surfaces 5a,
Secure contact area between 5a and the rolling surface of each rolling element 4, 4
Then, by suppressing an increase in surface pressure of the contact portion, each of the cam surfaces 5a,
5a and the durability (fatigue life) of the rolling surfaces of the rolling elements 4 and 4
It is for securing.

The input member 3a is formed by injection molding a synthetic resin having sufficient hardness, rigidity, strength and dimensional stability, such as a high-performance resin such as polyacetal.
It is formed integrally with the input shaft 16. The input member 3a
Are one side surfaces (FIGS. 1 and 5) of an outwardly flanged substrate portion 17 formed at one end portion (right end portion in FIGS. 1 and 5) of the input shaft 16.
On the right side), a plurality of (five in the illustrated example) arm portions 1
8, 18 are connected at the base end. Each of these arms 18,
As is clear from FIG. 6, the reference numerals 18 each have an arc-shaped cross section, and are provided intermittently in the circumferential direction on the same circle centered on the center axis of the input shaft 16. And
Between the arms 18 adjacent to each other in the circumferential direction are pockets 20 for holding the rolling elements 4. Width W ₂₀ of the pocket 20, 20 is sufficiently larger than the outer diameter D ₄ of the rolling elements 4, 4 (FIG. 12) (W
₂₀ ≫D ₄ ). At the center of the input shaft 16, an engagement hole 24 having a non-circular cross section is provided. At the time of use, the tip of the output shaft of a drive motor (not shown) capable of changing the rotation direction is inserted into the engagement hole 24 so that the input member 3a can be driven to rotate in any direction. The input member 3a
Can be manufactured by injection molding of a synthetic resin including the engagement hole 24 as described above. Therefore, the manufacturing cost of the input member 3a having a complicated shape does not increase.

The width of each of the arms 18 in the circumferential direction is large on the outside diameter side and small on the inside diameter side.
The reason for this is that the width W20 of each of the pockets 20, ₂₀ is made equal from the inner peripheral side to the outer peripheral side, and the respective arms 1
8 and 18, which will be described later, springs 21 and 21 (FIGS. 9 to
13) is to effectively prevent outward displacement due to centrifugal force. In addition, locking projections 22, 22 are respectively provided at the center in the circumferential direction of the outer peripheral surface of the distal end portion of each of the arms 18, 18.
Is formed. The locking projections 22 engage with the edges of the base 23 of the springs 21 to prevent the springs 21 from coming out of the arms 18. Things. Such locking projections may be provided not on the outer peripheral surface of each of the arms 18, but on the circumferential side surface.

Engagement projections 19 are formed at the circumferentially intermediate portions of the inner peripheral surfaces of the arms 18, 18, respectively. As shown in FIGS.
In the assembled state, each of the engagement projections 19, 19 is provided with the engagement recess 13, which is formed on the outer peripheral surface of the output member 2a.
13 is engaged. The width W of each of the engaging projections 19, 19
₁₉ is sufficiently smaller than the width W ₁₃ of each of the engagement recesses 13, ₁₃ (W ₁₉ ≪W ₁₃ ). Therefore, the clutch device 1
In a state where the assembly 0 is assembled, the engaging projections 19, 19 and the engaging recesses 13, 13 are engaged with each other so as to be relatively displaceable in the circumferential direction. Then, the input member 3a and the output member 2a
Are combined so that they can be slightly displaced relative to each other in the rotation direction.

When the present invention is carried out, the engaging portions that engage with each other in a state where the input member 3a and the output member 2a are relatively displaced by a predetermined angle are the engaging recesses 13 and 1 as described above.
3 and not only by the engagement of the engagement projections 19, 19,
Other structures may be employed. For example, the input member 3a
A concave / convex engaging portion that engages with each other may be provided at a portion of the substrate portion 17 facing one side (the right side in FIGS. 1 and 5) and one side of the output member 2a (the left side in FIGS. 1 and 2). . In the case of such a configuration, in the illustrated example, the output member 3a is used.
No space is required for the engaging recesses 13 formed on the outer peripheral surface of the clutch device, so that more cam surfaces can be formed and more rolling elements can be incorporated, so that the clutch device The torque capacity can be increased.

A spring 21 as shown in FIGS. 9 to 11, which is an elastic material according to the second aspect, is attached to each of the arms 18 constituting the input member 2a as described above. It is formed by bending an elastic metal plate such as stainless steel spring steel.
The spring 21 includes one base 23 and a plurality (four in the illustrated example) of elastic pressing pieces 25, 25. The base portion 23 has an arc-shaped substrate portion 26 having a shape matching the outer peripheral surface of each of the arms 18, 18 so that the arms can be fitted to the arms 18 without looseness. The base 26 includes a pair of bent plates 27, 27 that are bent inward in the diametric direction from the center of both circumferential edges of the base end 26.
Also, at the tip of each of these bent plate portions 27, 27,
Locking portions 28, 28 bent in a direction approaching each other are formed, and the locking portions 28, 28 and the arms 18, 1
The inner peripheral surface of the inner peripheral surface 8 can be freely engaged with both peripheral edges.
Each of the elastic pressing pieces 25, 25 has its base end connected to both side edges of each of the bent plate portions 27, 27, and displaces its distal end portion away from the base portion 23 in a free state. It has elasticity in the direction.

The spring 21 as described above is mounted on each of the arms 18, 18, as shown in FIGS. In this mounting operation, the arms 18 are inserted into the base 23 from the front end side in the axial direction of the input shaft 16 (the left-right direction in FIG. 5 and the front and back directions in FIGS. 12 and 13). Perform in. As a result of this mounting operation, each of the arms 18, 18 is elastically displaced toward the outer diameter side in the circumferential direction of the substrate portion 26.
Pass through the locking projections 22 formed on the outer peripheral surface of the front end portion. After the passage, the engagement between the locking projection 22 and the edge of the substrate portion 26 causes the base portion 23 to move the arm portions 18,
18 is prevented from coming off in the axial direction. In addition, the respective bent plate portions 27, 27 and the respective locking portions 28, 2
8 engages with the circumferential side surfaces and the inner peripheral edge of each of the arms 18, 18, and allows the base 23 to engage with each of the arms 18, 1.
8 from being displaced toward the outer diameter side.

As described above, between the elastic pressing pieces 25, 25 of the springs 21, 21 mounted on the respective arms 18, 18, the rolling elements 4, 4 are respectively attached to the elastic pressing pieces 25, 25. 25 is held while being elastically displaced.
Each of these rolling elements 4, 4 is like a cylindrical roller constituting a general cylindrical roller bearing, and is made of a hard metal such as high carbon chromium bearing steel. Each such rolling element 4, 4
The elastic pressing pieces 25 of the springs 21 elastically press the opposite positions in the circumferential direction at both ends in the axial direction with the same force. Therefore, each of the rolling elements 4, 4, when no external force is applied thereto, has the arm portions 18, 1, 1.
8 are located in the central part. Each of the elastic pressing pieces 2
The reference numerals 5 and 25 press the rolling elements 4 and 4 almost straight in the circumferential direction. That is, the circumferential side surfaces of the arms 18, 18 are connected to the pockets 20,
The respective elastic pressing pieces 25, 25 are provided in parallel with each other and on each of the side surfaces constituting the 20. Therefore, the component force in the diametric direction of the input member 2a existing in the forces applied to the rolling elements 4, 4 from the elastic pressing pieces 25, 25 is extremely small. The springs 21 configured as described above each have one end at each end in the circumferential direction.
Since two sets of elastic pressing pieces 25 are provided for each pair,
Compared to a case where a separate spring structure is provided for each elastic pressing piece, the processing cost of the spring 21 itself can be reduced, and
1 can facilitate the mounting operation, and the cost of the entire clutch device 10 can be significantly reduced.

The input member 3 combined as described above
a, the rolling elements 4, 4 and the springs 21, 21 are assembled into the outer ring 1a as shown in FIG.
The input member 3a and the output member 2a are arranged concentrically with each other, and loosely engage the engagement protrusions 19, 19 provided on the input member 3a side with the engagement recesses 13, 13 provided on the output member 2a side. Combine them together.

The input member 3a and the output member 2a thus combined are inserted into the outer ring 1a from the side where the thin flange 11b is to be formed. Then, the output shaft 12 is inserted inside the wide flange 11a, and the input member 3a and the output member 2a are connected to the outer race 1
a is located on the inner diameter side of the friction surface 6a. Then, the thin flange portion 11b is formed, and the clutch device 10 is completed.

The clutch device 10 is constructed as described above,
Further, when incorporated in a window regulator or the like, the input member 3a and the output member 2a are relatively displaced in a direction approaching each other, but limit the relative displacement in a direction away from each other. More specifically, the distance D ₀ of the opposite side surfaces of the output member 2a and the input member 3a in combination with one another, always the pair collar portion 11
a, smaller than the interval D ₁ of the inner surfaces of the 11b (D ₀
<D ₁ ). This is because the outer surface of the input member 3a is prevented from rubbing against the inner surface of the flange 11b, or the outer surface of the output member 2a is prevented from rubbing against the inner surface of the flange 11a. That's why.

For this purpose, for example, the engagement between the input shaft 16 integrated with the input member 3a and the drive shaft (not shown) is devised (for example, the front end surface of the drive shaft is inserted into the back end surface of the engagement hole 24). 1) to prevent the input member 3a from being displaced leftward from the state shown in FIG. 1, and to engage the output shaft 12 integrated with the output member 2a with a driven member (not shown). To prevent the output shaft 2a from being displaced rightward from the state shown in FIG. Therefore, when the input member 3a and the output member 2a rotate, these two members 3
a, 2a and the flanges 11a, 11b do not rub against each other, thereby preventing power loss and heat generation due to the rubbing. Further, since no load is applied to the flanges 11a and 11b, the thickness of the outer ring 1a can be reduced, and the entire clutch device 10 can be reduced in weight and size. Since the input member 3a and the output member 2a can be displaced in a direction approaching each other, at the moment when power transmission from the input member 3a to the output member 2a is started, the two members 3a and 2a face each other. Surfaces may rub against each other. However, this rubbing is slight and is a phenomenon that occurs at the moment when the two members 3a and 2a are to be rotated in synchronization with each other, so that there is no practical problem at all.

Further, the outer diameter of the substrate portion 17 constituting the input member 3a is made smaller than the inner diameter of the outer ring 1a (diameter of the friction surface 6a), and, of course, the respective arm portions 18, 18 are formed.
The diameter of the circumscribed circle of each of the springs 21 mounted on the outer ring 1a is also smaller than the inner diameter of the outer ring 1a. Therefore, even when the input member 3a rotates, the outer peripheral surfaces of the substrate portion 17 and the springs 21 and 21 do not rub against the friction surface 6a. For this reason, it is possible to prevent power loss and heat generation due to friction. The diameter of the circumscribed circle of each of the springs 21 is the same as that of the outer ring even when the displacement of each of the arms 18, 18 and each of the springs 21, 21 based on the centrifugal force caused by the rotation of the input member 3a is taken into account. It is made smaller than the inner diameter of 1a. Each of the arms 18, 18 based on the centrifugal force
For example, in the case of the clutch device 10 used for a window regulator, the displacement between the springs 21 and 21 and the friction surface 6a between the outer peripheral surfaces of the springs 21 and the friction surface 6a is small. If a gap of about 3 to 0.5 mm is interposed, the friction between the springs 21 and the friction surface 6a can be sufficiently prevented.

The axial movement of each of the rolling elements 4 and 4 is prevented by the inner surface of the flange 11a formed on the outer ring 1a, thereby reducing the axial dimension (width) of the outer ring 1a. are doing. A flange is provided on the outer peripheral surface of the output shaft 12 so that each of the rolling elements 4, 4
Although it is possible to prevent the rightward movement of
The width of the outer ring 1a is increased by the thickness of the flange. In the illustrated example, the tip surfaces of the arms 18, 18 provided on the input member 3a are connected to the flanges 1 of the outer race 1a.
In order to prevent a large bending moment from being applied to the substrate 17 to which the base ends of the arms 18 and 18 are connected by rubbing against the inner surface of the arm 1a, the distal ends of the arms 18 and 18 should be The rollers 4, 4 do not protrude from the end faces.

Next, the operation of the clutch device 10 according to the present invention configured as described above will be described. First, a case where the rotation of the input member 3a is transmitted to the output member 2a, for example, when the window glass is moved up and down by an electric motor will be described with reference to FIG. In this case, the input member 3a rotates, for example, in the counterclockwise direction in FIG. 12, and the engaging protrusions 19 provided on the input member 3a side are provided on the output member 2a side. Each of the engagement recesses 13, 13
To the end in the circumferential direction. Then, the inner surface of each of the engaging recesses 13, 13 and the outer surface of each of the engaging protrusions 19, 19 abut (the engaging portions engage), and the input member 3 is engaged.
The rotation of a is transmitted to the output member 2a as it is, and the output member 2a rotates in the same direction and at the same speed as the input member 3a. The outer surfaces of the engaging projections 19, 19 and the inner surfaces of the engaging recesses 13, 13 correspond to the base ends of the engaging projections 19, 19 (the arms 18, 18). (The end near the inner peripheral surface). The reason for this is
When transmitting the rotational force from the input member 3a to the output member 2a, the bending moment applied to each of the engagement projections 19 is minimized to minimize the bending moment. This is to prevent the projections 19, 19 from being damaged.

As described above, the input member 3a is slightly moved relative to the output member 2a until the outer surface of each of the engagement projections 19, 19 and the inner surface of each of the engagement recesses 13, 13 abut. As it rotates, the rolling elements 4, 4
As shown in FIG. 2, the rotational direction of the input member 3a is slightly forward (leftward in FIG. 12) of the input member 3a relative to the circumferential center of the cam surfaces 5a and 5a provided on the outer peripheral surface of the output member 2a. Moving. As a result, the rolling elements 4, 4 are guided by the curved surfaces 15, 15 at both ends of the cam surfaces 5a, 5a,
The output member 2a is displaced outward in the diameter direction. And
The rolling surfaces of the rolling elements 4 and 4 and the friction surface 6 of the outer race 1a
a contacts.

As described above, when the input member 3a and the output member 2a rotate in the same direction with the rolling surfaces of the rolling elements 4 and 4 and the friction surface 6a of the outer ring 1a in contact with each other, Each of the rolling elements 4 has a tendency to be displaced toward the respective central convex curved surface portions 14, which are central portions of the cam surfaces 5a, 5a. That is, when the input member 3a and the output member 2a rotate in the same direction in a state where the rolling surfaces of the rolling elements 4, 4 and the friction surface 6a of the outer race 1a are in contact with each other, the rolling elements 4, 4 No. 4 tries to stay at the same position based on the frictional engagement between the respective rolling surfaces and the friction surface 6a.
On the other hand, the output member 2a formed with the cam surfaces 5a, 5a rotates counterclockwise in FIG. 12, so that the rolling elements 4, 4 are formed on both side surfaces of the arms 18, 18, respectively. Of the elastic pressing pieces 25, 25 arranged on the front side, the elastic pressing pieces 25, 25 on the front side in the rotational direction are increased in the amount of compression and displaced rearward in the rotational direction with respect to the output member 2a. Therefore, each of the rolling elements 4, 4 is connected to each of the cam surfaces 5.
a, 5a and the friction surface 6a do not mesh with each other.
As a result, each of the rolling elements 4, 4
It moves to a portion where the distance between 5a and the friction surface 6a is large, and rolls at this portion. In this state, the outer ring 1a
The input member 3a and the output member 2a are in a rotatable state inside, and rotation can be transmitted from the input member 3a to the output member 2a.

When the frictional force acting on the contact portion between the rolling surfaces of the rolling elements 4 and 4 and the friction surface 6a is large, the rolling elements 4 and 4 are indicated by chain lines in FIG. As described above, each elastic pressing piece 2 on the front side in the rotation direction of each of the arms 18, 18.
5, 25 may be completely crushed. When implementing the clutch device 10 of the present invention, even in such a state,
The engaging projections 1 are arranged so that the rolling elements 4 and 4 do not bite between the cam surfaces 5a and 5a and the friction surface 6a.
9 and ₁₉ and the width W _{13 of} each of the engagement recesses 13 and _13.
These engagement recesses 1 correspond to the difference (W ₁₃ −W ₁₉ )
The size δ of the displaceable gap of each of the engaging projections 19 within the third and third portions 13 is regulated. In the above description, the case where the input member 3a rotates in the counterclockwise direction is described. However, when the input member 3a rotates in the clockwise direction, the same operation is performed except that the rotation direction is reversed.

The input member 3a and the output member 2a
Centering in the radial direction with respect to the diameter of the inscribed circle of each of the engagement projections 19, 19 and the engagement recesses 13, 1
The diameter of a circle connecting the bottoms of the engagement protrusions 3 is regulated, and the inner peripheral side surfaces of the engagement protrusions 19 are brought close to the bottoms of the engagement recesses 13. The input member 3a
When the engagement portion between the output member 2a and the engagement portion between the one side of the substrate portion 17 and the one side of the output member 2a on the input member 3a side is provided, By regulating the gap in the radial direction of the joint portion, it is possible to align the input member 3a and the output member 2a in the radial direction.

Next, although the electric motor is stationary and the input member 3a is stationary, a force is applied in the direction of raising and lowering the window glass, and a rotational force is applied to the output member 2a. FIG. 13 will be used to explain this case. In this case, as the output member 2a rotates counterclockwise in FIG.
Before the inner surface of the rolling element 3 comes into contact with the outer surface of each of the engaging projections 19, that is, before the rotation of the output member 2a is transmitted to the input member 3a as it is, each of the rolling elements 4, 4 are the cam surfaces 5a, 5a and the friction surface 6
bite between a. Moreover, in this case, the cam surfaces 5a, 5a are connected to the rolling elements 4, 4, respectively, and the rolling elements 4, 4 are connected to the cam surfaces 5a, 5a and the friction surface 6, respectively.
Only a force in the direction of digging is applied between them.
In other words, each rolling element 4, 4 is connected to each cam surface 5.
No force acts in the direction of displacement at the center in the circumferential direction of a and 5a. The force of the spring 21 is extremely small compared to the force required to rotate the input member 3a, and can be ignored in this case. Therefore, each of the rolling elements 4, 4
It bites between each of the cam surfaces 5a, 5a and the friction surface 6a to prevent the rotation of the output member 2a. As a result, the output member 2a does not rotate any more, and the rotation of the output member 2a does not transmit to the input member 3a. In the above description, the case where the output member 2a rotates in the counterclockwise direction has been described. However, when the output member 2a rotates in the clockwise direction, the same operation is performed except that the rotation direction is reversed.

In the case of the clutch device 10 of the present invention,
Regardless of the direction in which the output member 2a rotates, the rolling elements 4, 4 bite between the cam surfaces 5a, 5a and the friction surface 6a without fail because the spring 21 This is because the rolling elements 4 and 4 are pressed from both sides in the circumferential direction to regulate the positions of the rolling elements 4 and 4 in the circumferential direction. On the other hand, in the case of a structure in which the spring presses the rolling element in only one direction, the rolling element can be reliably engaged only when the output member rotates in a direction opposite to the pressing direction of the spring. Can not. In other words, in the present invention, since the rolling elements 4 are pressed from both sides in the circumferential direction,
Regardless of the direction in which the output member 2a rotates, all the rolling elements 4, 4 can be reliably engaged between the cam surfaces 5a, 5a and the friction surface 6a.

The rolling elements 4 and 4 have the same size, and the cam surfaces 5a and 5a have the same shape and size. Therefore, when the output member 2a tends to rotate, the rolling elements 4, 4 all bite between the cam surfaces 5a, 5a and the friction surface 6a at the same time. Therefore, the torque applied to the output member 2a can be supported by all the rolling elements 4 and 4, and damage due to an excessive load applied to some of the rolling elements can be prevented. With respect to such a structure of this example, the same function can be exerted even if a plurality of sets (for example, three sets) of one-way clutch mechanisms having different rotation allowable directions are provided between the outer ring and the output member. . However, in this case, when the output shaft tends to rotate, only a part of the rolling elements will support the torque, which causes a problem in securing durability.

[0037]

Since the clutch device of the present invention is constructed and operates as described above, it is possible to realize a structure capable of reliably transmitting the rotation of the input member to the output member without malfunction.
Therefore, it is possible to reduce malfunctions and failures of various mechanical devices including the clutch device such as a window regulator.

[Brief description of the drawings]

FIG. 1 is a sectional view showing an example of an embodiment of the present invention in an assembled state.

FIG. 2 is a cross-sectional view showing the output member.

FIG. 3 is a view seen from the left side of FIG. 2;

FIG. 4 is an enlarged view of a portion A in FIG. 3;

FIG. 5 is a sectional view showing the input member taken out therefrom.

FIG. 6 is a view seen from the right side of FIG. 5;

FIG. 7 is an enlarged view of a portion B in FIG. 5;

FIG. 8 is a view seen from the left side of FIG. 5;

FIG. 9 is a perspective view of a spring for pressing a rolling element.

FIG. 10 is a view taken in the direction of the arrow C in FIG. 9;

FIG. 11 is a view as seen from the direction of arrow D in FIG.

FIG. 12 is an enlarged cross-sectional view taken along the line EE of FIG. 1, showing a state where power is transmitted from the input member to the output member.

FIG. 13 is a view similar to FIG. 12, showing a state in which the output member tends to rotate and is locked.

FIG. 14 is a sectional view showing an example of a conventional structure.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1, 1a Outer ring 2, 2a Output member 3, 3a Input member 4 Rolling element 5, 5a Cam surface 6, 6a Friction surface 7 Arm portion 8 Annular space 9 Inclined surface 10 Clutch device 11a, 11b Collar portion 12 Output shaft 13 Engagement Concave part 14 Center convex curved part 15 Both ends concave curved part 16 Input shaft 17 Substrate part 18 Arm part 19 Engagement convex part 20 Pocket 21 Spring 22 Locking projection 23 Base part 24 Engagement hole 25 Elastic pressing piece 26 Substrate part 27 Bending plate Part 28 Locking part

Claims (2)

[Claims] 1. A fixed outer ring having an inner peripheral surface having a cylindrical friction surface, an output member rotatably supported inside the outer ring and concentrically with the outer ring, intermittently in a circumferential direction. And an input member having a plurality of arms inserted into an annular space between the inner peripheral surface of the outer ring and the outer peripheral surface of the output member, and arms circumferentially adjacent to each other in the annular space. A plurality of rolling elements provided between the portions, and a plurality of cam surfaces formed at a plurality of locations facing the respective rolling elements on the outer peripheral surface of the output member, and the rotation of the input member is The clutch device transmits the rotation to the output member regardless of the rotation direction, but the rotation of the output member is not transmitted to the input member regardless of the rotation direction. When the members are displaced relative to each other by a predetermined angle An engagement portion for engaging and transmitting the rotation of the input member to the output member. When the input member rotates, the input member is provided based on the engagement of the engagement portion. Is transmitted to the output member, and the rolling elements are allowed to roll freely between the cam surfaces and the friction surfaces, and the output member tends to rotate with respect to the input member. In this case, each rolling element bites between each of the cam surfaces and the friction surface before the engagement portion is engaged to prevent the output member from rotating with respect to the outer ring. Characteristic clutch device. 2. Each of the cam surfaces has a shape in which the center portion in the circumferential direction is located most inward in the diametrical direction, and each of the cam surfaces is inclined in such a direction as to be located diametrically outward toward both ends in the circumferential direction. Elastic members are respectively provided between the circumferential side surfaces of each arm and each rolling element, and these rolling elements elastically move toward the central position between the arms adjacent in the circumferential direction. The clutch device according to claim 1, wherein the clutch device is pressed.