JP2017198295A - One-way clutch - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a one-way clutch capable of attaining a small-sized formation in an axial line direction even if its configuration is simple.SOLUTION: This invention relates to an inscription gear type one-way clutch in which when an inner member 20 is rotated to one side in respect to an outer member 10, an engagement edge part 27 is engaged with a tooth trough part of a planetary gear 30 along with the prescribed rotation, thereby the planetary gear 30 cannot be rotated to make a drive connection between the outer member 10 and the inner member 20 and when the inner member 20 is rotated to the other side in respect to the outer member 10, the engagement between the tooth trough part of the planetary gear 30 and the engagement edge part 27 is released along with the prescribed rotation, resulting in that the planetary gear 30 becomes rotatable to allow a relative rotation between the outer member 10 and the inner member 20 to be carried out to disconnect the driving connection between the outer member 10 and the inner member 20. There is one planetary gear 30 and the gear has adsorption means in which a holding force acted between the planetary gear 30 and the inner gear is higher than a gravity force acted on the planetary gear 30.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a one-way clutch, and more particularly to an internal gear type one-way clutch.

  The following are known as internal gear type one-way clutches used in image forming apparatuses and image reading apparatuses. That is, a cylindrical outer member having an internal gear on the inner peripheral portion, an inner member having a plurality of recesses that are rotatably provided in the inner space of the internal gear and have locking edge portions formed on the outer peripheral portion, And a planetary gear that is rotatably received in each of the recesses and meshes with the internal gear. In the one-way clutch, when the inner member rotates to one side with respect to the outer member, the planetary gear rolls by engaging the engaging edge portion with the tooth root portion of the planetary gear along with the rotation. The outer member and the inner member are drivably connected by being disabled. And when an inner member rotates to the other side with respect to an outer member, engagement with the tooth | gear part of a planetary gear and a latching edge part is cancelled | released with the said rotation. As a result, the planetary gear can roll, permitting relative rotation between the outer member and the inner member, and disconnecting the drive connection between the outer member and the inner member.

  The above-mentioned internal gear type one-way clutch is such that when the planetary gear is positioned in a substantially horizontal direction with respect to the center of the inner member, the planetary gear falls by its own weight with respect to the movement of the inner member and is not locked. There is. Such a state will be described with reference to FIG. 100 is an inner member, 102 is an outer member, and an internal gear 103 is formed inside. Reference numeral 105 denotes a planetary gear.

  As shown in FIG. 14A, the planetary gear 105 is positioned substantially in the horizontal direction with respect to the center of the inner member 100. When the inner member 100 rotates counterclockwise (arrow 100A direction) at this time, the planetary gear 105 falls in the arrow 105A direction due to its own weight as shown in FIG. The lock may not be applied. Alternatively, the backlash can be very large.

  As a countermeasure, the inner member is provided with a plurality of recesses for holding the planetary gear at positions displaced around the central axis. Further, when it is difficult for the one-way clutch to have a small diameter and to arrange a plurality of recesses, the plurality of recesses are arranged to be shifted in the axial direction of the inner member (Patent Document 1).

Japanese Patent No. 5058943

  Problems to be solved by the invention will be described for each case in the prior art.

<When there are multiple planetary gears and they are shifted in the axial direction>
As an example, as shown in Patent Document 1, when two recesses for holding the planetary gear are provided in the inner member, and the plurality of recesses are provided by being shifted in the axial direction of the inner member, the axial direction becomes large.

  The first object of the present invention is to reduce the size of the one-way clutch in the axial direction.

<When there are multiple planetary gears>
As an example, it is assumed that there are two planetary gears 112 and 113, which are arranged 180 degrees from the shaft center, and the number of teeth of the internal gear 110 of the outer member 109 is 20. In this configuration, the phase relationship between the tooth tips of the planetary gears 112 and 113 and the tooth tip of the internal gear 110 is the same (see FIG. 15).

  Since the phases of the two hook portions are the same, if there is no gravity, two planetary gears 112 and 113 are engaged with the locking edge portion as shown in FIG. However, in actuality, as shown in FIG. 15B, the planetary gear 112 on one side may fall due to gravity and only the planetary gear 113 on the other side may engage. Therefore, the torque transmission capability is only one planet gear engaged with the locking edge portion.

  The second object of the present invention is to increase the torque transmission capability for a one-way clutch of the same size.

  In order to achieve the above object, a one-way clutch according to the present invention includes a cylindrical outer member having an internal gear on an inner peripheral portion, a rotatable inner portion of the inner gear, and a locking edge portion on the outer peripheral portion. An inner member having a recess formed therein, and a planetary gear that is rotatably received in the recess and meshes with the internal gear, and the inner member rotates to one side with respect to the outer member. Sometimes, with the rotation, the engagement edge portion engages with the tooth root portion of the planetary gear, the planetary gear becomes non-rollable, and the outer member and the inner member are connected to drive, When the inner member rotates to the other side with respect to the outer member, the planetary gear is disengaged from the tooth root portion of the planetary gear and the locking edge portion with the rotation. Can roll, An internal gear type one-way clutch that allows relative rotation between the outer member and the inner member and disconnects the drive connection between the outer member and the inner member, and includes one planetary gear, and It is characterized by having adsorption means in which the holding force acting between the planetary gear and the internal gear exceeds the gravity acting on the planetary gear.

As described above, according to the present invention, the axial direction can be reduced with a simple structure.

  Alternatively, the torque transmission capability can be increased with a simple structure even if the size is the same as the conventional size.

1 is a perspective view of a one-way clutch according to Embodiment 1. FIG. 1 is an exploded perspective view of a one-way clutch according to Embodiment 1. FIG. Sectional drawing of the one-way clutch which concerns on Example 1. FIG. Sectional drawing explaining the grease application | coating state of the one-way clutch which concerns on Example 1. FIG. Sectional drawing of the one-way clutch which concerns on Example 2. FIG. Sectional drawing of the one-way clutch which concerns on Example 2. FIG. Sectional drawing of the one-way clutch which concerns on the modification of Example 2. FIG. Explanatory drawing of background art concerning Example 3 Sectional drawing of the one-way clutch which concerns on Example 3. Sectional drawing explaining the backlash of a one-way clutch Sectional drawing of the one-way clutch which concerns on Example 3. The perspective view of the one-way clutch which concerns on Example 5. FIG. Sectional drawing of the one-way clutch which concerns on Example 5. Illustration of background art Illustration of the problem

  An embodiment of a one-way clutch according to the present invention will be specifically described below with reference to the drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the components described in this embodiment are not intended to limit the scope of the present invention only to those unless otherwise specified. .

  The best mode for carrying out the present invention will be described below in detail with reference to the drawings.

  The configuration of the one-way clutch will be described with reference to FIGS.

  The one-way clutch has an outer member 10 that forms a clutch case. The outer member 10 is configured by a bottomed cylindrical body having one end in the axial direction closed by an end wall 11 and having an opening (enclosure) at the other end, and a series of internal gears 12 are provided on the inner peripheral surface. Is formed.

  A substantially columnar inner member 20 is rotatably provided in the cylindrical inner space of the outer member 10 corresponding to the inner space of the internal gear 12.

  A boss 21 around the central axis of the inner member 20 is formed at one end in the axial direction of the inner member 20 and is rotatably engaged with a groove 13 formed in the end wall 11 of the outer member 10. ing. Circular flange portions 22 and 23 are formed at the other end portion of the inner member 20 in the axial direction, and are rotatably engaged with the inner peripheral surfaces 14 and 15 of the opening end portion of the outer member 10. On the other side in the axial direction of the inner member 20 with respect to the circular flange portions 22, 23, there is an external connection portion 24 formed to project. In addition, annular guide protrusions 25 are formed on the outer peripheral surfaces of the circular flange portions 22 and 23, and the annular guide protrusions 25 are formed on the inner peripheral surfaces 14 and 15 of the opening end portion of the outer member 10. The annular groove 16 is slidably fitted. As a result, the inner member 20 assembled to the outer member 10 is not easily detached from the outer member 10.

  With this configuration, the inner member 20 is supported by the outer member 10 at both ends in the axial direction, and can rotate in the cylindrical inner space of the outer member 10 concentrically with the center of the cylindrical inner space. Here, the inner member 20 is concentric with the center of the cylindrical inner space of the outer member 10, and the center of the internal gear 12 formed on the inner peripheral surface of the cylindrical inner space and the center of rotation of the inner member 20 are the same. It means being concentric.

  One recess 26 is formed in the inner member 20. The concave portion 26 is formed by cutting out a part of the outer peripheral portion of the inner member 20 into a pocket shape. In the recess 26, the planetary gear 30 having a series of external gears 31 formed on the outer peripheral surface thereof is rotatable around its own central axis, that is, can be rotated, and in the circumferential direction of the inner member 20 by a predetermined amount. Displaceable. The planetary gear 30 is thus received in the recess 26, and the external gear 31 of the planetary gear 30 meshes with the internal gear 12.

  Next, the operation of the one-way clutch will be described with reference to FIG.

The rotation direction of the inner member 20 at the time of clutch engagement in which the inner member 20 rotates to one side with respect to the outer member 10 is a counterclockwise direction as viewed in FIG. Then, the rotation direction of the inner member 20 when the inner member 20 rotates to the other side with respect to the outer member 10 when the clutch is not engaged (released) is the clockwise direction as viewed in FIG.

  When viewed in the above-described counterclockwise direction of the inner member 20, a locking edge portion that selectively engages with a tooth root portion 30 </ b> A by the external gear 31 of the planetary gear 30 is provided at the edge portion of the concave portion 26 on the rotation direction delay side. 27 is formed.

  When the inner member 20 rotates on one side with respect to the outer member 10, that is, in the counterclockwise direction as viewed in FIG. 3, the inner member moves with respect to the planetary gear 30 received in the recess 26 with the rotation. 20 is displaced counterclockwise. Due to the displacement of the inner member 20 with respect to the planetary gear 30, the locking edge portion 27 is changed from the state of FIG. 3A through FIG. 3B to the tooth root portion 30 A of the planetary gear 30 as shown in FIG. Engage. As a result, the planetary gear 30 becomes non-rollable, and the outer member 10 and the inner member 20 are drivingly connected under the meshing of the outer gear 31 of the planetary gear 30 and the inner gear 12 of the outer member 10.

  On the other hand, when the inner member 20 rotates with respect to the outer member 10 on the other side, that is, in the clockwise direction as viewed in FIG. 3, the rotation of the inner member 20 with respect to the planetary gear 30 received in the concave portion 26 occurs. The inner member 20 is displaced in the clockwise direction. Due to the displacement of the inner member 20 relative to the planetary gear 30, the locking edge portion 27 is disengaged (disengaged) from the engagement with the tooth root portion 30 </ b> A of the planetary gear 30. As a result, the planetary gear 30 can roll, the outer member 10 and the inner member 20 can rotate relative to each other, and the drive connection between the outer member 10 and the inner member 20 is disconnected.

  As shown in FIG. 4, grease G is used as an adsorbing means for holding the planetary gear 30 on the inner gear 12 of the outer member 10 at the meshing portion of the outer gear 31 of the planetary gear 30 and the inner gear 12 of the outer member 10. Is applied. In this example, Moricoat (trademark) EM50-L (trade name) manufactured by Toray Dow Corning Co., Ltd. was used, but other greases may be used. Although illustration of grease is omitted in the drawings other than FIG. 4, it is applied in the same manner. Further, by holding the planetary gear 30 by the viscosity of the grease, when the inner member 20 rotates counterclockwise, the planetary gear 30 does not fall by its own weight. Therefore, the engaging edge portion 27 engages with the tooth root portion 30 </ b> A of the planetary gear 30 without the inner member 20 rotating excessively. That is, no matter where the planetary gear 30 is located, the backlash does not become larger than expected.

At this time, the condition for the engagement edge portion 27 to engage with the tooth root portion 30A of the planetary gear 30 may satisfy the following expression (1). Here, the holding force by the grease on the contact surface 30B of the internal gear 12 and the planetary gear 30 is A. The gravity acting on the planetary gear 30 is B, and the direction in which the planetary gear 30 is attracted to the inner member 20 when the inner member 20 is rotated by the grease on the planetary gear 30, the inner member 20, and the contact surface 30C. The component is C.
A ≧ B + C (1)

At this time, since the contact surface 30B of the internal gear 12 and the planetary gear 30 is significantly larger than the contact surface 30C of the planetary gear 30 and the inner member 20, the holding force A is significantly greater than the attractive force C in the direction of gravity. Therefore, the suction force C can be ignored. Therefore, the condition that the locking edge portion 27 engages with the tooth root portion 30 </ b> A of the planetary gear 30 is that the holding force by the grease on the contact surface 30 </ b> B of the internal gear 12 and the planetary gear 30 exceeds the gravity acting on the planetary gear 30. Therefore, the following equation (2) is obtained.
A ≧ B (2)

  The material of the suction means applied to the meshing portion of the outer gear 31 of the planetary gear 30 and the inner gear 12 of the outer member 10 is not limited to grease, but may be any material as long as the above equation (2) is satisfied. The suitability of the coating material is determined by assembling the outer member 10, the inner member 20, and the planetary gear 30 in a state where the coating material is applied, placing the planetary gear 30 at the position of FIG. 3A, and rotating the inner member 20 counterclockwise. It can be determined by whether or not the planetary gear 30 falls when it is rotated. At that time, if the planetary gear 30 does not fall or the dropping speed of the planetary gear 30 is slower than the rotational speed of the inner member 20, the coating material can be used.

  Further, when the planetary gear is urged by a spring or the like in the rotation lock direction, as in the needle type one-way clutch, when the drive connection is disconnected, the engaging edge portion of the planetary gear and the inner member is The sound hits and hits. In this embodiment, since the spring is not urged in the rotation lock direction, the above-described problems do not occur.

  In this embodiment, the backlash is stable even if there is one planetary gear. Therefore, even if the one-way clutch has a small diameter, it is not necessary to displace the two planetary gears in the axial direction, so that the size in the axial direction can be reduced.

  Further, by applying grease as an adsorbing means for holding the planetary gear, it is possible to prevent wear of sliding portions and locking edge portions of the internal gear and the planetary gear and to prevent noise.

  Example 2 will be described with reference to FIG.

  In this embodiment, two planetary gears are used. The two recesses 45 and 46 formed in the inner member 44 are in positions that are rotated and displaced by 180 degrees around the central axis. The planetary gears 51 and 54 are respectively received in the recesses 45 and 46, and the external gears 52 and 55 of the planetary gears 51 and 54 mesh with the internal gear 41 of the outer member 40, respectively. The number of teeth of the internal gear 41 of the outer member 40 is 20 teeth. Further, grease is applied to the meshing portions of the external gears 52 and 55 of the planetary gears 51 and 54 and the internal gear 41, and the formula (2) described in the first embodiment is satisfied (see FIG. 4).

  When the inner member 44 rotates counterclockwise with respect to the outer member 40, the locking edge portions 47 and 48 of the inner member 44 engage with the tooth roots of the planetary gears 51 and 54, and the outer member 40 and the inner member 44 are connected in a drive connection relationship. At that time, the number of teeth of the internal gear 41 is an even number (20 teeth), the two concave portions 45 and 46 of the inner member 44 are point-symmetric with respect to the central axis of the inner member 44, and the effect of the grease The planetary gears 51 and 54 do not fall due to their own weight. For this reason, the tooth root portions of the two planetary gears 51 and 54 simultaneously engage with the locking edge portions 47 and 48 of the inner member 44. That is, the phase relationship between the planetary gear 51 and the locking edge portion 47 corresponding thereto and the phase relationship between the planetary gear 54 and the locking edge 48 corresponding thereto are substantially the same.

  When the grease is not applied, the planetary gear 51 falls due to its own weight and does not engage with the locking edge portion 47 of the inner member 44, and there is a case where only one planetary gear 54 is engaged. In the embodiment, since the grease is applied, the two planetary gears 51 and 54 are always engaged. That is, the torque transmission capability of this embodiment is twice that when no grease is applied.

  In this embodiment, the number of teeth of the internal gear is an even number, and the two planetary gears are arranged at positions that are rotationally displaced from each other by 180 degrees around the central axis, thereby providing an arrangement configuration with good rotation balance.

  In this embodiment, the number of teeth of the inner gear of the outer member is an even number, but it may be an odd number.

  In this embodiment, as shown in FIG. 6, the number of teeth of the inner gear of the outer member 40 is an odd number (21 teeth), and the two planetary gears 51 and 54 are simultaneously engaged with the locking edge portions 47 and 48 of the inner member 44. It is comprised so that it may engage with. In FIG. 6, by adjusting the rotational direction positions of the locking edges 47 and 48 of the inner member 44, the tooth root portions of the two planetary gears 51 and 54 are simultaneously changed to the locking edge portions 47 and 48 of the inner member 44. Engaged.

  Further, in the present embodiment, an example in which there are two planetary gears is shown, but three or more planetary gears may be arranged. At this time, the number of teeth of the internal gear and the position of the locking edge portion of the inner member may be adjusted so that the tooth valley portions of two or more planetary gears simultaneously engage with the locking edge portion of the inner member.

  Further, a plurality of planetary gears may be arranged shifted in the axial direction. FIG. 7 shows an example in which the two planetary gears 71 and 74 are arranged shifted in the axial direction. That is, the inner member 64 is provided with recesses 65 and 66 at two positions shifted in the axial direction. A planet gear 71 is received in the recess 65, and a planet gear 74 is received in the recess 66. In this modification, when viewed from the central axis direction, the two planetary gears 71 and 74 are arranged so as to be shifted from each other in the axial direction so that they are positioned 180 degrees away from each other around the central axis. Each of the outer gear 72 of the planetary gear 71 and the outer gear 75 of the planetary gear 74, the engaging edge portion (not shown) of the inner member 64, and the outer member 60 when the inner member 64 rotates in one direction or the other direction. The interrelationship with the internal gear 61 is the same as in the above embodiment. Also in this modified example, grease is applied to the meshing portions of the external gear 72 of the planetary gear 71 and the external gear 75 of the planetary gear 74 and the internal gear 61 of the outer member 60. The planetary gears 71 and 74 and the outer member 60 satisfy Expression (2) described in the first embodiment. According to such a configuration, since the recesses 65 and 66 can be formed without interfering with each other, the outer diameter of the one-way clutch can be reduced.

  Example 3 described below is intended to reduce backlash. First, the prior art will be described with reference to FIG. Here, there are two planetary gears 127 and 128, which are arranged at a phase of 180 ° from the shaft center, and the number of teeth of the internal gear 126 of the outer member 125 is 21 teeth. In this configuration, the phase relationship between the tooth tips of the planetary gears 127 and 128 and the tooth tip of the internal gear 126 of the outer member 125 is reversed. Since the phases of the tooth tips at the two hook portions are just reversed, if there is no gravity, one planetary gear 127 or the other planet as shown in FIG. 8 (a) or FIG. 8 (b). Since the gear 128 is hooked first, the backlash is smaller than the example of FIG. However, actually, as shown in FIG. 8C, the planetary gear 127 on one side may fall due to gravity and only the other planetary gear 128 may be caught. The backlash in that case is the same size as the example of FIG.

  Next, Example 3 will be described with reference to FIGS.

  In this embodiment, two planetary gears are used. The two recesses 85 and 86 formed in the inner member 84 are at positions that are rotated and displaced by 180 degrees around the central axis. The planetary gears 91 and 94 are received in the recesses 85 and 86, respectively, and the external gears 92 and 95 of the planetary gears 91 and 94 mesh with the internal gear 81 of the outer member 80, respectively. The number of teeth of the internal gear 81 of the outer member 80 is 21. Further, grease is applied to the meshing portions of the external gears 92 and 95 of the planetary gears 91 and 94 and the internal gear 81, and the formula (2) described in the first embodiment is satisfied (see FIG. 4).

  FIG. 10 is an enlarged view for explaining the operation in which the engaging edge portion of the inner member engages with the tooth root portion of the planetary gear when the inner member 84 rotates counterclockwise. The magnitude of the backlash of the planetary gear will be described with reference to FIG.

  First, the magnitude of the backlash when there is one planetary gear described in the first embodiment will be described. The backlash is a total of an angle e (set to 5 degrees) from the free state where the engaging edge portion 27 of the inner member intersects the tooth tip circle of the planetary gear 30 and an angle f until the locking is performed. The angle f is at most close to the angle interval of the internal gear 12 due to the structure of the internal gear type one-way clutch. Therefore, if the number of teeth of the internal gear 12 is 21, f = 360 ÷ 21≈17 degrees. That is, the maximum backlash is e + f = 5 + 17 = 22 degrees.

  The case of the second embodiment is the same as that of the first embodiment because the planetary gear 51 (planetary gear 54) simultaneously engages with the locking edge portion 47 (locking edge portion 48) of the inner member 44.

  Next, the size of the backlash of the present embodiment will be described. In the present embodiment, the two planetary gears 91 and 94 are not simultaneously engaged with the locking edge portions 87 and 88 of the inner member 84. 9A or 9B, one of the planetary gears 91 and 94 is engaged with the locking edge portion 87 or 88 of the inner member 84, as shown in FIG. Thus, the outer member 80 and the inner member 84 are drivingly connected. Therefore, the angle f is halved compared to the case of the first and second embodiments, so that f = 17 ÷ 2 = 8.5 degrees. Therefore, the maximum backlash is e + f = 5 + 8.5 = 13.5 degrees.

  Thus, in this embodiment, the backlash of the one-way clutch can be reduced.

  In this embodiment, the number of teeth of the internal gear is an odd number, and the two planetary gears are arranged at positions that are rotationally displaced from each other by 180 degrees around the central axis, thereby providing an arrangement configuration with good rotation balance.

  In this embodiment, the number of teeth of the inner gear of the outer member is odd, but the number of teeth of the internal gear 61 may be even as shown in FIG. In FIG. 11, by adjusting the rotational direction positions of the locking edge portions 87 and 88 of the inner member 84, the tooth root portions of the two planetary gears 91 and 94 are simultaneously locked to the locking edge portions 87 and 88 of the inner member 84. Is not engaged.

  In the present embodiment, an example in which there are two planetary gears is shown, but three or more planetary gears may be arranged. At this time, the number of teeth of the internal gear and the position of the locking edge portion of the inner member may be adjusted so that the tooth valley portions of two or more planetary gears do not simultaneously engage with the locking edge portion of the inner member.

  Further, similarly to the modified example of the second embodiment, a plurality of planetary gears may be arranged shifted in the axial direction. According to such a configuration, the outer diameter of the one-way clutch can be reduced.

  Since Example 4 has exactly the same cross-sectional configuration as Example 1, it will be described with reference to FIGS.

  In the fourth embodiment, a magnetic attractive force is used as a suction means between the planetary gear and the inner gear of the outer member.

  The outer member 10 is made of a plastic magnet material. The planetary gear 30 is injection molded by mixing magnetic powder with a general plastic material. The plastic magnet material and the magnetic powder are materials on which a magnetic attractive force acts, but are not limited thereto. The inner member 20 is a general plastic.

As a result, the planetary gear 30 is attracted to the inner gear 12 of the outer member by a magnetic attractive force. By holding the planetary gear 30 by the magnetic attractive force, the planetary gear 30 does not fall by its own weight when the inner member 20 rotates counterclockwise. Therefore, the engaging edge portion 27 engages with the tooth root portion 30 </ b> A of the planetary gear 30 without the inner member 20 rotating excessively. That is, no matter where the planetary gear 30 is located, the backlash does not become larger than expected.

  In this embodiment, the function as a one-way can be satisfied without applying grease, but grease may be applied to improve wear resistance.

  Moreover, you may utilize electrostatic attraction force as an attraction | suction means between the planetary gear and the inner gear of an outer member. For this reason, the planetary gear and the inner gear of the outer member can be formed including materials that act on each other by electrostatic attraction force.

  Example 5 will be described with reference to FIG. Since the fifth embodiment has substantially the same configuration as that of the first embodiment, the same reference numerals as those in FIG.

  The present embodiment differs from the first embodiment only in the shape of the inner member 20 in the vicinity of the sliding portion of the opening end (end portion on the sealing port side) portion of the outer member 10. Specifically, the sliding portion 23 outside the annular guide protrusion 25 of the inner member 20 existing in the first embodiment is not present in the fifth embodiment, and the inner peripheral surface 15 of the opening end portion of the outer member 10 is the inner surface. The member 20 extends outward from the annular guide protrusion 25. That is, along the axial direction of the inner member 20, on the side opposite to the side where the planetary gear (not shown) is enclosed with respect to the sliding portion composed of the inner circumferential surface 14 of the outer member 20 and the annular groove 16. An inner peripheral surface (extension portion) 15 extends. 13A and 13B are cross-sectional views along the central axis direction showing the open end portion of the outer member 10 of the one-way clutch of the present embodiment and the first embodiment. With the configuration of this embodiment shown in FIG. 13A, even if the grease G protrudes from the inside, the grease G is caught on the inner peripheral surface 15 of the opening end portion of the outer member 10. Even if the centrifugal force is applied to the grease G due to the rotation, the grease G can be prevented from scattering to the outside of the one-way clutch.

DESCRIPTION OF SYMBOLS 10 ... Outer member, 12 ... Internal gear, 20 ... Inner member, 26 ... Recess, 27 ... Locking edge part, 30 ... Planetary gear, 30A ... Root area, 31 ... External gear, Grease ... G

Claims (11)

A cylindrical outer member having an internal gear on the inner peripheral portion, an inner member having a concave portion that is rotatably provided in the inner space of the internal gear and has a locking edge portion formed on the outer peripheral portion, and a roller that is turned into the concave portion. A planetary gear that is movably received and meshes with the internal gear, and when the inner member rotates to one side with respect to the outer member, a tooth root portion of the planetary gear accompanies the rotation. Engagement of the locking edge portion makes the planetary gear incapable of rolling and drivingly connects the outer member and the inner member, and the inner member rotates to the other side with respect to the outer member. When the rotation, the engagement between the root of the planetary gear and the locking edge portion is released along with the rotation, so that the planetary gear can roll, and the outer member and the inner member Relative rotation of the Disconnecting motor member and a driving connection between said inner member, an internal gear one-way clutch,
The one-way clutch is characterized in that the number of planetary gears is one, and there is an adsorption means in which the holding force acting between the planetary gear and the internal gear exceeds the gravity acting on the planetary gear. A cylindrical outer member having an internal gear on an inner peripheral portion; an inner member having a plurality of recesses provided rotatably in an inner space of the internal gear and having locking edge portions formed on the outer peripheral portion; A plurality of planetary gears that are rotatably received in each of the recesses and mesh with the inner gear, and when the inner member rotates to one side with respect to the outer member, When the engaging edge portion engages with the tooth root portion of the planetary gear, the planetary gear becomes non-rollable, and the outer member and the inner member are driven and connected, and the inner member is the outer member. When rotating to the other side, the planetary gear is allowed to roll by releasing the engagement between the tooth root portion of the planetary gear and the locking edge portion with the rotation. The outer member and the inner member; Allow relative rotation, disconnecting the driving connection between the inner member and the outer member, an internal gear one-way clutch,
The phase relationship between the plurality of planetary gears and the plurality of locking edge portions corresponding to the planetary gears is substantially the same, and the gravity between the planetary gears and the internal gears rather than the gravity acting on the planetary gears. A one-way clutch characterized by having an adsorbing means having a higher acting holding force.   The one-way clutch according to claim 2, wherein the number of teeth of the internal gear is an even number.   4. The one-way clutch according to claim 2, wherein the plurality of planetary gears and the plurality of concave portions that respectively receive the planetary gears are shifted in the axial direction of the inner member. 5. A cylindrical outer member having an internal gear on an inner peripheral portion; an inner member having a plurality of recesses provided rotatably in an inner space of the internal gear and having locking edge portions formed on the outer peripheral portion; A plurality of planetary gears that are rotatably received in each of the recesses and mesh with the inner gear, and when the inner member rotates to one side with respect to the outer member, When the engaging edge portion engages with the tooth root portion of the planetary gear, the planetary gear becomes non-rollable, and the outer member and the inner member are driven and connected, and the inner member is the outer member. When rotating to the other side, the planetary gear is allowed to roll by releasing the engagement between the tooth root portion of the planetary gear and the locking edge portion with the rotation. The outer member and the inner member; Allow relative rotation, disconnecting the driving connection between the inner member and the outer member, an internal gear one-way clutch,
The phase relationship between the plurality of planetary gears and the plurality of locking edge portions corresponding to the planetary gears is different, and gravity acting on the planetary gear acts between the planetary gear and the internal gear. A one-way clutch characterized by having an adsorbing means having a higher holding force.   The one-way clutch according to claim 5, wherein the number of teeth of the internal gear is an odd number.   7. The one-way clutch according to claim 5, wherein the plurality of planetary gears and the plurality of concave portions that respectively receive the planetary gears are shifted in the axial direction of the inner member.   The one-way clutch according to any one of claims 1 to 7, wherein the adsorption means is grease applied between the planetary gear and the internal gear.   The one-way clutch according to any one of claims 1 to 7, wherein the attracting means is based on a magnetic attractive force between the planetary gear and the internal gear.   10. The one-way clutch according to claim 9, wherein the planetary gear and the internal gear are formed to include a material on which a magnetic attractive force acts.   The outer member includes an enclosure port that encloses the planetary gear with the inner member, a sliding portion on which the inner member slides at an end on the enclosure port side, and an axial direction of the inner member The one-way clutch according to claim 8, further comprising an extending portion extending to a side opposite to the side on which the planetary gear is enclosed with respect to the sliding portion.

Images