Reverse input cutoff clutch

Abstract

The reverse input cutoff clutch (1) includes an input member (2), an output member (3), a pair of engaging elements (5, 5), a pressed surface (77) against which the engaging element (5) is pressed, a first bearing mechanism (7), and a second bearing mechanism (8). The first bearing mechanism (7) rotatably supports the input member (2). The second bearing mechanism (8) rotatably supports the output member (3). The outer ring of at least one of the first bearing mechanism (7) and the second bearing mechanism (8) is an integrated outer ring in which the pressed surface (77) and an outer ring raceway groove in which the balls of the ball bearing roll are integrally formed. The radial thickness of the integrated outer ring at the groove bottom of the outer ring raceway groove is equal to or smaller than the diameter of the balls.

Description

[Technical Field]

[0001] The present invention relates to a reverse input disconnecting clutch. This application claims priority based on Japanese Patent Application No. 2024-098095, filed June 18, 2024, the contents of which are incorporated herein by reference. [Background technology]

[0002] Conventionally, there has been known a reverse input cutoff clutch configuration that includes an input member connected to an input mechanism such as a drive source and an output member connected to an output mechanism such as a reducer, and that allows transmission of rotational force from the input member to the output member while cutting off reverse input of rotational force from the output member to the input member. Various techniques have been proposed for improving the performance of these reverse input cutoff clutches.

[0003] For example, Patent Document 1 discloses the configuration of a locking reverse input blocking clutch that blocks reverse input from the output shaft by preventing rotation of the output shaft. The reverse input blocking clutch has an input shaft and an output shaft that are coaxially arranged, a pressed member having a pressed surface, and a pair of engaging elements that are movable in the radial direction. According to the technology described in Patent Document 1, when a rotational force is reversely input to the output shaft, the engaging elements move in a direction approaching the pressed surface based on engagement between the engaging elements and the output shaft, and frictionally engage with the pressed surface, thereby blocking the rotational force reversely input to the output shaft. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Patent No. 6658965 Summary of the Invention [Problem to be solved by the invention]

[0005] In such a reverse input disconnection clutch, the hardness of the pressed member needs to be increased to suppress wear when the engaging element slides on the pressed surface and deformation of the pressed member due to stress when disconnecting the reverse input. Furthermore, for example, if the input shaft, output shaft, and pressed surface are not concentric, there is a risk of performance degradation due to issues such as play in the rotational direction and increased loss caused by sliding between the pressed surface and the engaging element.

[0006] One approach to addressing these issues is to form the outer ring of a bearing that rotatably supports an input or output shaft from a heat-treated, high-hardness steel material and to integrally form a pressed surface on the outer ring. However, with this conventional technology, the outer ring's radial thickness tends to be large, which can make assembly difficult when using ball bearings, for example. In other words, when assembling a ball bearing, the inner and outer rings are first radially shifted to create a gap, and then the outer ring is deformed to create a space where the balls are inserted, thereby filling the balls. In this case, the outer ring's thickness tends to increase when the pressed surface is integrally formed, making it difficult for the outer ring to deform, making it difficult to create a space for the balls to be inserted, or the outer ring may be damaged by stress. Therefore, in the prior art, when a ball bearing is used as a bearing for a reverse input cutoff clutch, there was room for improvement in terms of suppressing performance degradation due to a decrease in coaxiality and an increase in loss, while also improving the assembly ease of the ball bearing.

[0007] SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a reverse input cutoff clutch that can improve assembly efficiency while suppressing performance degradation due to reduced coaxiality and increased loss. [Means for solving the problem]

[0008] In order to solve the above problems, the present invention proposes the following means. A reverse input cutoff clutch according to a first aspect of the present invention comprises: an input member having an input shaft; an output member having an output shaft arranged coaxially with the input shaft and arranged axially alongside the input member; a pair of engagers provided radially outward from the input member and the output member, the engager having a pressed surface facing inward in the radial direction, a pressing surface opposing the pressed surface, an input-side engaged portion engageable with the input member, and an output-side engaged portion engageable with the output member, the engager being movable relative to each other along a first radial direction; a first bearing mechanism rotatably supporting the input shaft by a ball bearing; and a second bearing mechanism rotatably supporting the output shaft by a ball bearing, and when a rotational torque is input to the input shaft, the pair of engagers move relative to each other along a first radial direction, the first bearing mechanism rotatably supporting the input shaft by a ball bearing, and the second bearing mechanism rotatably supporting the output shaft by a ball bearing. and when rotational torque is input to the output shaft in reverse, the pair of engaging elements move away from each other radially outward in the first radial direction based on the engagement between the output member and the output-side engaged portion, causing frictional engagement between the pressed surface and the pressing surface, and the outer ring of at least one of the first bearing mechanism and the second bearing mechanism is an integral outer ring in which the pressed surface is integral with an outer ring raceway surface on which the balls of the ball bearing roll, and the radial thickness dimension of at least a portion of the integral outer ring corresponding to the groove bottom of the outer ring raceway surface is equal to or less than the diameter of the balls. [Effects of the Invention]

[0009] According to the reverse input cutoff clutch of the present invention, it is possible to provide a reverse input cutoff clutch that can improve assembly efficiency while suppressing performance degradation due to reduced coaxiality and increased loss. [Brief explanation of the drawings]

[0010] [Figure 1] FIG. 2 is a cross-sectional view of the reverse input cutoff clutch according to the first embodiment. [Figure 2] FIG. 2 is a cross-sectional view taken along line II-II in FIG. [Figure 3]FIG. 2 is a schematic diagram of a reverse input cutoff clutch according to the first embodiment. [Figure 4] FIG. 10 is a schematic diagram of a reverse input cutoff clutch according to a second embodiment. [Figure 5] FIG. 11 is a schematic configuration diagram of a reverse input cutoff clutch according to a third embodiment. [Figure 6] FIG. 10 is a schematic configuration diagram of a reverse input cutoff clutch according to a fourth embodiment. [Figure 7] FIG. 11 is a schematic configuration diagram of a reverse input cutoff clutch according to a fifth embodiment. [Figure 8] FIG. 13 is a schematic configuration diagram of a reverse input cutoff clutch according to a sixth embodiment. DETAILED DESCRIPTION OF THE INVENTION

[0011] Hereinafter, an embodiment of the present invention will be described with reference to the drawings. In the following description, the axial direction, radial direction, and circumferential direction refer to the axial direction, radial direction, and circumferential direction of the center axis C of the reverse input cutoff clutch 1, unless otherwise specified.

[0012] (First embodiment) FIG. 1 is a cross-sectional view of the reverse input cutoff clutch 1 according to the first embodiment. FIG. 2 is a cross-sectional view taken along line II-II in FIG. 1. FIG. 3 is a schematic diagram of the reverse input cutoff clutch 1 according to the first embodiment. Note that FIG. 3 is a schematic diagram for easily explaining the characteristic configuration of the reverse input cutoff clutch 1 according to this embodiment, and is a simplified version of FIG. 1. Also, some components (such as the housing 4) are not shown in FIG. 3.

[0013] As shown in Fig. 1, the reverse input cutoff clutch 1 of this embodiment is used in, for example, an electric caliper brake or a rear wheel steering device of an automobile or the like. The reverse input cutoff clutch 1 has a locking function (reverse input cutoff function) that cuts off rotational force that is reversely input to the output shaft 31. This allows the electric caliper brake to achieve a parking function, and the rear wheel steering device to achieve a function of maintaining the steering of the wheels when power is cut off.

[0014] 1 to 3, the reverse input cutoff clutch 1 includes an input member 2, an output member 3, a housing 4, a pair of engagers 5, and a plurality of bearing mechanisms 7 and 8. The reverse input cutoff clutch 1 transmits the rotational force input to the input member 2 to the output member 3. On the other hand, the reverse input cutoff clutch 1 has a reverse input cutoff function that cuts off the rotational force that is reversely input to the output member 3 and does not transmit it to the input member 2, or that transmits only a portion of the rotational force to the input member 2 and cuts off the remainder.

[0015] The input member 2 is connected to an input mechanism such as an electric motor (not shown). A rotational force from the input mechanism is input to the input member 2. The input member 2 has an input shaft 21 and a pair of arms 23. The input shaft 21 is provided on the input mechanism side in the axial direction. The input shaft 21 is formed in a columnar (or cylindrical) shape centered on a central axis C. In the following description, the side of the input shaft 21 connected to the input mechanism may be referred to as a first axial side, and the opposite side may be referred to as a second axial side.

[0016] The pair of arms 23 extend from the input shaft 21 toward the second side in the axial direction. The arms 23 are integrally formed with the input shaft 21. A pair of the arms 23 is provided at both ends of the input shaft 21 in the first radial direction D1. As shown in FIG. 2 , the arms 23 are trapezoidal in shape with one curved side when viewed in the axial direction. Specifically, the arms 23 have a flat input-side engagement portion 25 facing radially inward, a curved portion 26 facing radially outward, and two side portions 27 connecting the ends of the input-side engagement portion 25 and the curved portion 26. The curved portion 26 is formed in an arc shape centered on the central axis C. Note that the shape of the arms 23 is not limited to the above-described shape. The shape of the arms 23 may be, for example, a semicircular shape, a polygonal shape, an elliptical shape, or the like having an arc-shaped curved portion and a flat portion.

[0017] A plurality of arm portions 23 are provided in accordance with the number of engaging elements 5 described below. In this embodiment, a pair of arm portions 23 is provided in accordance with the number of engaging elements 5. The number of arm portions 23 is not limited to two, and the number of arm portions 23 may be one, or three or more, in accordance with the number of engaging elements 5.

[0018] As shown in FIGS. 1 to 3, the output member 3 is connected to an output mechanism such as a reducer (not shown), and outputs a rotational force (rotational torque). The output member 3 has an output shaft 31 and an insertion portion 32. The output shaft 31 is arranged coaxially with the input shaft 21. The output shaft 31 is provided on the output mechanism side in the axial direction (second side in the axial direction). The output shaft 31 is formed in a columnar (or cylindrical) shape centered on a central axis C.

[0019] The insertion portion 32 extends from a first axial end of the output shaft 31 toward the first axial side. The insertion portion 32 is integrally formed with the output shaft 31. The insertion portion 32 is inserted between a pair of engaging elements 5 (described later) and is disposed radially inward of a pair of arm portions 23 of the input member 2. A base end of the insertion portion 32 inserted between the pair of engaging elements 5 (e.g., a portion located on the second axial side of the retaining ring 39 in FIG. 1 ) is formed in a plate shape (see also FIG. 2 ). A tip end of the insertion portion 32 (e.g., a portion located on the first axial side of the retaining ring 39) is formed in a cylindrical shape. The shape of the base end of the insertion portion 32 is not limited to a plate shape. The tip end of the insertion portion 32 may be rotatably supported on the input shaft 21 via a bearing (not shown).

[0020] As shown in FIG. 2, the outer peripheral surface of the base end of the insertion portion 32 has a pair of output-side engaging portions 35 facing both sides in the thickness direction (first radial direction D1) of the insertion portion 32, and a pair of side surfaces 36 connecting the ends of the pair of output-side engaging portions 35. Each output-side engaging portion 35 is formed by a flat surface along the second radial direction D2. Each output-side engaging portion 35 faces a pair of engaging elements 5. The output-side engaging portion 35 is provided more inward in the first radial direction D1 than the input-side engaging portion 25 of the input member 2. The pair of side surfaces 36 connect both ends of the output-side engaging portion 35.

[0021] The insertion portion 32 is provided with a plurality of output side engaging portions 35 and side surface portions 36 in accordance with the number of engaging elements 5 described below. In this embodiment, a pair of output side engaging portions 35 and side surface portions 36 is provided in accordance with the provision of a pair of engaging elements 5. The number of output side engaging portions 35 is not limited to two, and the number of output side engaging portions 35 may be one, or three or more, in accordance with the number of engaging elements 5.

[0022] As shown in FIG. 1, the housing 4 is disposed radially outward of the input member 2 and output member 3 described above. The housing 4 is a housing component with an inner periphery formed into a cylindrical shape. The housing 4 is fixed to another member (not shown) and its rotation is restricted. The input member 2, output member 3, and a pair of engaging elements 5 are housed inside the inner periphery of the housing 4. The housing 4 houses the input member 2 and output member 3 in a rotatable state via a plurality of bearing mechanisms 7 and 8, which will be described in detail later.

[0023] 1 to 3, the pair of engaging elements 5 are semicircular and disposed radially inward of the housing 4. The pair of engaging elements 5 face each other in the first radial direction D1 and are configured to be movable toward and away from each other in the first radial direction D1. Each of the pair of engaging elements 5 has a pressing surface 51, a bottom surface 52, an input-side engaged portion 55, and an output-side engaged portion 56.

[0024] As shown in FIG. 2 , the pressing surface 51 is a radially outer surface that presses a pressed surface 77 provided on an outer ring 71 (an integrated outer ring 71 in the claims) described later, and is an arc-shaped convex surface. Note that a portion of the outer peripheral surface of the engaging element 5 that faces the pressed surface 77 may be used as the pressing surface 51. The pressing surface 51 presses the pressed surface 77 when the reverse input cutoff clutch 1 is in a locked state (a state in which the reverse input from the output member 3 is cut off). The radius of curvature of the pressing surface 51 is equal to or smaller than the radius of curvature of the pressed surface 77. Two pressing surfaces 51 are provided for each engaging element 5, and are formed so as to increase the frictional engagement force between the engaging element 5 and the pressed surface 77 due to a wedge effect. The two pressing surfaces 51 are provided at positions spaced apart from each other in the circumferential direction of the engaging element 5. The pressing surface 51 may be directly formed by the entire or part of the outer circumferential surface of the engaging element 5, or may be formed to have a surface property with a higher friction coefficient than other parts of the engaging element 5. For example, the pressing surface 51 may be formed by a friction material fixed to the engaging element 5 by sticking or bonding.

[0025] The bottom surface 52 of the engaging element 5 is located more inward in the first radial direction D1 than the pressing surface 51. The bottom surface 52, together with an output-side engaged portion 56 of the engaging element 5, which will be described in detail later, forms a linear portion of the semicircular engaging element 5. In this embodiment, the bottom surface 52 is formed as a substantially flat surface except for a pair of protrusions 53, which will be described later. The bottom surfaces 52 of the pair of engaging elements 5 face each other in the first radial direction D1. The inner diameter dimension of the pressed surface 77 and the outer dimensions of the engaging elements 5 are set so that when the pair of engaging elements 5 are positioned inside the pressed surface 77, a gap exists between the pressed surface 77 and the pressing surface 51, and between the pair of bottom surfaces 52 and the output member 3.

[0026] The input side engaged portion 55 is a hole that penetrates the center of the engaging element 5 in the axial direction when viewed from the axial direction. The input side engaged portion 55 is formed in the shape of an elongated hole extending in the second radial direction D2. The arm portions 23 of the input member 2 are inserted into the input side engaged portions 55, respectively. The input side engaged portions 55 engage with the arm portions 23. The input side engaged portions 55 have a size that allows the arm portions 23 of the input member 2 to be loosely inserted therein. Specifically, the input side engaged portion 55 is formed so that when the arm portions 23 of the input member 2 are inserted inside the input side engaged portion 55, a gap exists between the arm portions 23 and the inner peripheral surface of the input side engaged portion 55.

[0027] The output-side engaged portion 56 is provided near the center in the second radial direction D2 of the straight portion (bottom surface 52) of the engaging element 5 formed in a semicircular shape. The output-side engaged portion 56 is provided more inward in the first radial direction D1 than the input-side engaged portion 55. The output-side engaged portion 56 engages with the insertion portion 32 of the output member 3. The output-side engaged portion 56 is formed in the shape of a flat surface that is continuous with the bottom surface 52.

[0028] 1 and 2, in the assembled state of the reverse input cutoff clutch 1, the arm portion 23 of the input member 2 is inserted axially into each of the input-side engaged portions 55 of the pair of engaging elements 5, and the insertion portion 32 of the output member 3 is inserted axially between the output-side engaged portions 56 of the pair of engaging elements 5. In other words, the pair of engaging elements 5 are arranged so that the output-side engaged portions 56 sandwich the insertion portion 32 of the output member 3 from the radially outer side.

[0029] As shown in FIG. 1 , a leaf spring 38 is provided between the pair of engaging elements 5. The leaf spring 38 is elastically sandwiched between the engaging element 5 and the output member 3. The leaf spring 38 biases the engaging element 5 radially outward, i.e., toward the pressed surface 77. A retaining ring 39 for positioning each component is provided on a first axial side of the engaging element 5. Furthermore, end plates (not shown) or the like for positioning each component may be provided on both axial sides of the engaging element 5. In addition to the positioning function, components such as end plates may be provided to prevent contact between the engaging element 5 and the output member 3 and input member 2, thereby suppressing wear, for example. The leaf spring 38 may be omitted. Alternatively, an elastic member other than the leaf spring 38 may be provided.

[0030] 1 and 3, the reverse input disconnecting clutch 1 has a plurality of bearing mechanisms, namely, a first bearing mechanism 7 and a second bearing mechanism 8. In this embodiment, the first bearing mechanism 7 and the second bearing mechanism 8 are both ball bearings. Specifically, the first bearing mechanism 7 and the second bearing mechanism 8 are deep groove ball bearings or four-point contact ball bearings.

[0031] The first bearing mechanism 7 rotatably supports the input member 2 relative to the housing 4. The first bearing mechanism 7 has balls 70 that roll around an axis, an outer ring 71, an outer ring raceway groove 76 (outer ring raceway surface in the claims) and a pressed surface 77 formed on the outer ring 71, and an inner ring raceway groove 72 (inner ring raceway surface in the claims) formed on the input shaft 21. The outer peripheral surface of the outer ring 71 is attached to the first accommodating portion 41 of the housing 4. The outer ring 71 is provided axially from the input shaft 21 to a position where the pressing surface 51 of the engaging element 5 is located. The outer ring raceway groove 76, in which the balls 70 roll, and the pressed surface 77 that comes into contact with the engaging element 5 are formed on the inner peripheral surface of the outer ring 71, and are aligned in the axial direction. In other words, the outer ring 71 of the first bearing mechanism 7 is an integrated outer ring (hereinafter sometimes referred to as the integrated outer ring 71) in which both the outer ring raceway groove 76 and the pressed surface 77 are formed in a single component.

[0032] The outer ring (integral outer ring 71) of the first bearing mechanism 7 is formed of a high-hardness steel material such as bearing steel. An example of a high-hardness steel material is a heat-treated high-carbon steel such as SUJ3 or SUJ2. Note that the steel material is not limited to the above-mentioned materials as long as it has high hardness.

[0033] Furthermore, the radial thickness dimension W1 of the portion of the one-piece outer ring 71 that corresponds to the balls 70 is equal to or less than the diameter D of the balls 70 (W1≦D). In this embodiment, "the thickness dimension W1 of the portion of the one-piece outer ring 71 that corresponds to the balls 70" refers to the radial thickness dimension of the portion that corresponds to the groove bottom of the outer ring raceway groove 76 formed in the one-piece outer ring 71. Even more preferably, the radial thickness dimension W1 of the portion of the one-piece outer ring 71 that corresponds to the balls 70 (the thickness dimension at the groove bottom) is equal to or less than 1 / 2 the diameter D of the balls 70 (W1≦D / 2).

[0034] An inner ring raceway groove 72 that contacts the balls 70 and allows the balls 70 to roll is formed on the outer peripheral surface of the input shaft 21. In other words, the first bearing mechanism 7 of this embodiment is formed without having a separate component that constitutes an inner ring. Therefore, the balls 70 roll in the rolling element raceway that is formed between the inner ring raceway groove 72 formed on the input shaft 21 and the outer ring raceway groove 76 formed on the one-piece outer ring 71.

[0035] The second bearing mechanism 8 is provided on a second axial side of the first bearing mechanism 7. The second bearing mechanism 8 rotatably supports the output member 3 relative to the housing 4. The second bearing mechanism 8 has balls 80 that roll around the axis, an outer ring 81, an outer ring raceway groove 86 (outer ring raceway surface in the claims) formed in the outer ring 81, and an inner ring raceway groove 82 (inner ring raceway surface in the claims) formed in the output shaft 31. The outer peripheral surface of the outer ring 81 is attached to the second accommodating portion 42 of the housing 4. The second accommodating portion 42 and the first accommodating portion 41 have different inner diameters. The outer ring 81 is provided at a position corresponding to the output shaft 31 in the axial direction. The outer ring 81 has an outer ring raceway groove 86 formed on its inner peripheral surface in which the balls 80 roll.

[0036] An inner ring raceway groove 82 that contacts the balls 80 and allows the balls 80 to roll is formed on the outer peripheral surface of the output shaft 31. In other words, the second bearing mechanism 8 of this embodiment is formed without having a separate component that constitutes an inner ring, similar to the first bearing mechanism 7. Therefore, the balls 80 roll in a rolling element raceway that is formed between the inner ring raceway groove 82 formed on the output shaft 31 and the outer ring raceway groove 86 formed on the outer ring 81.

[0037] (Reverse input cutoff clutch operation) Next, the operation of the reverse input cutoff clutch 1 of this embodiment will be described. First, a case will be described where a rotational force is input from the input mechanism to the input shaft 21. When a rotational force is input to the input shaft 21, as shown in Fig. 2, the arm portion 23 of the input member 2 rotates around the central axis C inside the input-side engaging portion 25 in the rotational direction of the input shaft 21 (counterclockwise CCW in the example shown in Fig. 2). Then, a corner portion (point P1 in Fig. 2) between the input-side engaging portion 25 and the side surface portion 27 on the counterclockwise CCW side of the arm portion 23 presses the inner surface of the input-side engaged portion 55 radially inward, causing the pair of engaging elements 5 to move in a direction away from the pressed surface 77 (inward in the first radial direction D1). In other words, the pair of engaging elements 5 move radially inward and closer to each other due to the rotational force from the input shaft 21 acting on them via the input-side engaged portion 55. As a result, the bottom surfaces 52 of the pair of engaging elements 5 move in directions approaching each other, and the pair of output-side engaged portions 56 clamp the insertion portion 32 of the output shaft 31 from both radial sides.

[0038] As a result, the output member 3 is rotated so that the longitudinal axis direction of the insertion portion 32 is parallel to the bottom surface 52 of the engagement element 5, and the insertion portion 32 and the pair of output-side engaged portions 56 are engaged without rattle. Therefore, the rotational force input to the input shaft 21 is transmitted to the output member 3 via the pair of engagement elements 5 and output from the output shaft 31. When a rotational force is input to the input shaft 21, the reverse input cutoff clutch 1 of this embodiment moves the pair of engaging elements 5 in a direction away from the pressed surface 77, regardless of the rotational direction of the input shaft 21. Then, regardless of the rotational direction of the input shaft 21, the rotational force input to the input shaft 21 is transmitted to the output shaft 31 via the pair of engaging elements 5.

[0039] Next, a case where a rotational force is input from the output mechanism to the output shaft 31 will be described. When a rotational force is input to the output shaft 31 in reverse, as shown in FIG. 2, the insertion portion 32 of the output member 3 rotates in the rotational direction of the output shaft 31 (clockwise CW in the example shown in FIG. 2) inside the pair of output-side engaged portions 56. Then, a corner portion (point P2 in FIG. 2) between the side surface portion 36 of the insertion portion 32 and the output-side engaging portion 35 presses the output-side engaged portion 56 radially outward, causing the pair of engaging elements 5 to move in directions approaching the pressed surfaces 77. In other words, based on the engagement between the output member 3 and the output-side engaged portions 56, the pair of engaging elements 5 move away from each other radially outward in the first radial direction D1. As a result, the pressing surfaces 51 of the pair of engaging elements 5 are pressed against the pressed surfaces 77. At this time, the pressing surfaces 51 and the pressed surfaces 77 are frictionally engaged over the entire range or at least a portion of the circumferential range of the pressing surfaces 51.

[0040] As a result, the rotational force reversely input to the output shaft 31 is blocked and not transmitted to the input member 2, or only a portion of the rotational force reversely input to the output shaft 31 is transmitted to the input member 2 and the remainder is blocked. To completely block the rotational force reversely input to the output shaft 31 and prevent it from being transmitted to the input member 2, the pair of engaging elements 5 are tensioned between the insertion portion 32 and the pressed surface 77 so that the pressing surface 51 does not slide (rotate relative to) the pressed surface 77, thereby locking the output member 3. On the other hand, to transmit only a portion of the rotational force reversely input to the output shaft 31 to the input member 2 and block the remainder, the pair of engaging elements 5 are tensioned between the insertion portion 32 and the pressed surface 77 so that the pressing surface 51 slides against the pressed surface 77, thereby semi-locking the output member 3. When a rotational force is further input in reverse to the output shaft 31 while the output member 3 is in a semi-locked state, the pair of engaging elements 5 rotate about the central axis C while sliding the pressing surface 51 against the pressed surface 77 based on the engagement between the insertion portion 32 of the output member 3 and the output-side engaged portion 56. When the pair of engaging elements 5 rotate, the inner surface of the input-side engaged portion 55 presses the radially inner surface of the arm portion 23 of the input member 2 in the circumferential direction (rotational direction), and part of the rotational force is transmitted to the input member 2.

[0041] (Action, effect) According to the reverse input cutoff clutch 1 of this embodiment, the outer ring of at least one of the first bearing mechanism 7 and the second bearing mechanism 8 (the outer ring 71 of the first bearing mechanism 7 in this embodiment) is an integral outer ring 71 in which the outer ring raceway surface (the outer ring raceway groove 76) and the pressed surface 77 are integrally formed. The pressed surface 77 is integrally formed with the outer ring 71 of the bearing, which is generally made of a hard material, so that the hardness of the pressed surface 77 can be increased. This can suppress wear caused by the pressing surface 51 of the engaging element 5 sliding on the pressed surface 77, as well as deformation of the pressed member (the integral outer ring 71 in this embodiment) due to stress when cutting off the reverse input. Furthermore, the pressed surface 77 is provided on the outer ring 71 of the bearing that rotatably supports the input shaft 21 or the output shaft 31 (the input shaft 21 in this embodiment). This makes it easier to ensure concentricity between the input shaft 21 or the output shaft 31 and the pressed surface 77. This makes it possible to suppress the occurrence of rattle and an increase in loss due to sliding between the pressed surface 77 and the engaging element 5. Therefore, the performance of the reverse input cutoff clutch 1 can be improved. Furthermore, the radial thickness W1 of the portion of the one-piece outer ring 71 that corresponds to the balls 70 (thickness at the groove bottom) is equal to or smaller than the diameter D of the balls 70. This makes it easier to elastically deform the one-piece outer ring 71 compared to prior art in which the thickness of the one-piece outer ring 71 is formed larger than the diameter of the balls 70. Therefore, even when using an outer ring 71 that is integrally formed with the pressed surface 77, the assembly of the ball bearing can be improved. In other words, the one-piece outer ring 71 can be deformed to insert the balls 70 into the gap. Furthermore, damage to the outer ring 71 due to stress during assembly can be suppressed. Therefore, it is possible to provide a reverse input cutoff clutch 1 that can improve assembly ease while suppressing performance degradation due to reduced coaxiality and increased loss, particularly when ball bearings are used as bearings for the reverse input cutoff clutch. Furthermore, in this embodiment, ball bearings are used as the first bearing mechanism 7 and the second bearing mechanism 8, so torque loss during rotation can be reduced compared to when other types of bearings, such as tapered roller bearings, are used. This allows for a higher transmission efficiency and higher performance reverse input cutoff clutch 1.

[0042] The radial thickness W1 of the portion of the one-piece outer ring 71 that corresponds to the balls 70 (thickness at the groove bottom) is set to be equal to or less than half the diameter D of the balls 70. This makes it even easier for the one-piece outer ring 71 to elastically deform. Therefore, even when using an outer ring 71 that is integrally formed with the pressed surface 77, the assembly of the ball bearing can be improved. Furthermore, damage to the outer ring 71 due to stress during assembly can be suppressed.

[0043] The one-piece outer ring 71 is formed from a high-hardness material. This increases the hardness of the pressed surface 77 formed on the one-piece outer ring 71. This reduces wear caused by the pressing surface 51 of the engagement element 5 sliding on the pressed surface 77. This reduces the occurrence of rattles caused by wear and increases in loss due to sliding between the pressed surface 77 and the engagement element 5. This further improves the performance of the reverse input cutoff clutch 1.

[0044] The outer ring (integral outer ring 71) of the first bearing mechanism 7 is fixed to the housing 4. As a result, when the pressing surface 51 of the engaging element 5 and the pressed surface 77 of the integrated outer ring 71 come into contact with each other, the rotational force reversely input to the output shaft 31 is transmitted to the housing 4 and blocked. Therefore, the reverse input can be blocked effectively.

[0045] The input shaft 21 is integrally formed with an inner ring raceway groove 72 (inner ring raceway surface in the claims) of the first bearing mechanism 7. This eliminates the need to provide a separate component as an inner ring, thereby reducing the number of components. Furthermore, since the inner ring raceway groove 72 and the arm portion 23 of the input member 2 can be machined in the same process using a single chuck, for example, the coaxiality between the input shaft 21 and other components can be improved. Furthermore, since the mating surfaces in the first bearing mechanism 7 are smaller than when a separate inner ring is provided, the coaxiality between the components connected via the first bearing mechanism 7 can be improved.

[0046] The ball bearing is either a deep groove ball bearing or a four-point contact ball bearing. This reduces torque loss during rotation, resulting in a high-performance reverse input cutoff clutch 1 with higher transmission efficiency.

[0047] (Second embodiment) Next, a second embodiment of the present invention will be described. In the following description, the same components as those in the first embodiment described above will be denoted by the same reference numerals, and the description thereof will be omitted as appropriate. Note that the specific configuration is not limited to these embodiments, and can be modified as appropriate without departing from the gist of the present invention. FIG. 4 is a schematic diagram of a reverse input cutoff clutch 201 according to the second embodiment. The second embodiment differs from the first embodiment described above in that the input member 2 and the inner ring of the first bearing mechanism 7 are formed as separate bodies.

[0048] In the second embodiment, an inner ring 245 is attached to the outer periphery of the input shaft 21 of the input member 2. An inner ring raceway groove 72 in which the balls 70 roll is formed on the outer periphery of this inner ring 245. In other words, in this embodiment, the first bearing mechanism 207 has the balls 70, the one-piece outer ring 71, the outer ring raceway groove 76 and the pressed surface 77 formed on the one-piece outer ring 71, the inner ring 245 attached to the input member 2, and the inner ring raceway groove 72 formed on the inner ring 245.

[0049] The reverse input cutoff clutch 201 of the second embodiment can achieve the same effects as those of the first embodiment. That is, the thickness dimension W1 along the radial direction of the portion of the integral outer ring 71 that corresponds to the balls 70 (thickness dimension at the groove bottom) is equal to or less than the diameter D of the balls 70, which makes it easier to elastically deform the integral outer ring 71 and improves the ease of assembly of the ball bearing. Therefore, it is possible to provide a reverse input cutoff clutch 201 that can improve assembly efficiency while suppressing performance degradation due to reduced coaxiality and increased loss, particularly when using ball bearings.

[0050] (Third embodiment) Next, a third embodiment of the present invention will be described. In the following description, the same components as those in the first embodiment described above will be denoted by the same reference numerals, and the description thereof will be omitted as appropriate. Fig. 5 is a schematic diagram of a reverse input cutoff clutch 301 according to the third embodiment. The third embodiment differs from the first embodiment described above in that the outer ring of the second bearing mechanism 8 provided on the output member 3 side is an integrated outer ring.

[0051] In the third embodiment, the second bearing mechanism 308 includes balls 380 that roll around the shaft, an outer ring 391, an outer ring raceway groove 392 (referred to as an outer ring raceway surface in the claims) and a pressed surface 77 formed on the outer ring 391, and an inner ring raceway groove 393 (referred to as an inner ring raceway surface in the claims) formed on the output shaft 31. The outer ring 391 is provided axially from the output shaft 31 to a position where the pressing surface 51 of the engaging element 5 is located. The outer ring raceway groove 392, in which the balls 380 roll, and the pressed surface 77 that comes into contact with the engaging element 5 are formed side by side in the axial direction on the inner peripheral surface of the outer ring 391. In other words, the outer ring 391 of the second bearing mechanism 308 is an integrated outer ring 391 in which both the outer ring raceway groove 392 and the pressed surface 77 are formed in a single component. The outer ring 391 is fixed to the housing 4 (see FIG. 1).

[0052] The radial thickness dimension W3 (thickness dimension at the groove bottom) of the portion of the one-piece outer ring 391 that corresponds to the ball 380 is equal to or less than the diameter D of the ball 380 (W3≦D). More preferably, the radial thickness dimension W3 of the portion of the one-piece outer ring 391 that corresponds to the ball 380 is equal to or less than 1 / 2 of the diameter D of the ball 380 (W3≦D / 2).

[0053] An inner ring raceway groove 393 that contacts the balls 380 and allows the balls 380 to roll is formed on the outer peripheral surface of the output shaft 31. In other words, the second bearing mechanism 308 of this embodiment is formed without having a separate component that constitutes an inner ring. Therefore, the balls 380 roll in the rolling element raceway that is formed between the inner ring raceway groove 393 formed on the output shaft 31 and the outer ring raceway groove 392 formed on the one-piece outer ring 391.

[0054] Although not shown in the drawings, the first bearing mechanism 7 in this embodiment has the same configuration as the second bearing mechanism 8 (see FIG. 1) in the first embodiment. That is, the first bearing mechanism 7 has balls that roll around the axis, an outer ring, an outer ring raceway groove formed in the outer ring, and an inner ring raceway groove formed in the input shaft 21. The outer peripheral surface of the outer ring is attached to the housing 4 (see FIG. 1).

[0055] According to the reverse input blocking clutch 301 of the third embodiment, the outer ring 391 of the second bearing mechanism 308 is an integral outer ring 391, and the integral outer ring 391 is fixed to the housing 4. As a result, when the pressing surface 51 of the engaging element 5 and the pressed surface 77 of the integral outer ring 391 come into contact with each other, the rotational force reversely input to the output shaft 31 is transmitted to the housing 4 and blocked. This effectively blocks the reverse input. Furthermore, the thickness W3 of the integral outer ring 391 along the radial direction of the portion corresponding to the ball 380 (thickness at the groove bottom) is equal to or smaller than the diameter D of the ball 380. This facilitates elastic deformation of the integral outer ring 391, improving the assembly of the ball bearing. Therefore, a reverse input blocking clutch 301 can be provided that can suppress performance degradation due to reduced coaxiality and increased loss, and improves assembly, particularly when using a ball bearing.

[0056] Furthermore, an inner ring raceway groove 393 (inner ring raceway surface in the claims) of the second bearing mechanism 308 is integrally formed with the output shaft 31. This eliminates the need to provide a separate component as an inner ring, thereby reducing the number of components. Furthermore, since the inner ring raceway groove 393 and the insertion portion 32 of the output member 3 can be machined in the same process using a single chuck or the like, the coaxiality between the output shaft 31 and other components can be improved. Furthermore, since the mating surfaces in the second bearing mechanism 308 are smaller than when a separate inner ring is provided, the coaxiality between the components connected via the second bearing mechanism 308 can be improved.

[0057] (Fourth embodiment) Next, a fourth embodiment of the present invention will be described. In the following description, the same components as those in the third embodiment described above will be denoted by the same reference numerals, and the description thereof will be omitted as appropriate. FIG. 6 is a schematic diagram of a reverse input cutoff clutch 401 according to the fourth embodiment. The fourth embodiment differs from the third embodiment described above in that the output member 3 and the inner ring of the second bearing mechanism 308 are formed separately.

[0058] In the fourth embodiment, an inner ring 446 is attached to the outer periphery of the output shaft 31 of the output member 3. An inner ring raceway groove 493 in which the balls 480 roll is formed on the outer periphery of this inner ring 446. In other words, in this embodiment, the second bearing mechanism 408 has the balls 480, the one-piece outer ring 491, the outer ring raceway groove 492 and the pressed surface 77 formed on the one-piece outer ring 491, the inner ring 446 attached to the output member 3, and the inner ring raceway groove 493 formed on the inner ring 446.

[0059] The reverse input cutoff clutch 401 of the fourth embodiment can achieve the same effects as those of the third embodiment. That is, when a ball bearing is used in the reverse input cutoff clutch 401, it is possible to provide a reverse input cutoff clutch 401 that can improve assembly efficiency while suppressing performance degradation due to a decrease in coaxiality and an increase in loss.

[0060] (Fifth embodiment) Next, a fifth embodiment of the present invention will be described. In the following description, the same components as those in the first embodiment described above will be denoted by the same reference numerals, and the description thereof will be omitted as appropriate. FIG. 7 is a schematic diagram of a reverse input cutoff clutch 501 according to the fifth embodiment. The fifth embodiment differs from the first embodiment described above in that the outer rings of both the first bearing mechanism 7 and the second bearing mechanism 8 are integral outer rings.

[0061] In the fifth embodiment, the outer rings 595 of the first bearing mechanism 507 and the second bearing mechanism 508 are an integrated outer ring 595 configured from a common component. In other words, the integrated outer ring 595, which is a single component, is formed with an outer ring raceway groove 596 of the first bearing mechanism 507, an outer ring raceway groove 597 of the second bearing mechanism 508, and a pressed surface 77. The integrated outer ring 595 is provided axially from a position where the balls 580 on the output shaft 31 side are located to a position where the balls 570 on the input shaft 21 side are located. The integrated outer ring 595 is fixed to the housing 4 (see FIG. 1).

[0062] The radial thickness dimension W5 (thickness dimension at the groove bottom) of the portion of the integral outer ring 595 that corresponds to the balls 570 on the input shaft 21 side is equal to or less than the diameter DX of the balls 570 on the input shaft 21 side (W5≦DX). More preferably, the radial thickness dimension W5 of the portion of the integral outer ring 595 that corresponds to the balls 570 on the input shaft 21 side is equal to or less than 1 / 2 the diameter DX of the balls 570 on the input shaft 21 side (W5≦DX / 2). Similarly, the radial thickness dimension W6 (thickness dimension at the groove bottom) of the portion of the integral outer ring 595 that corresponds to the balls 580 on the output shaft 31 side is equal to or less than the diameter DY of the balls 580 on the output shaft 31 side (W6≦DY). More preferably, the radial thickness dimension W6 of the portion of the integral outer ring 595 that corresponds to the balls 580 on the output shaft 31 side is equal to or less than 1 / 2 the diameter DY of the balls 580 on the output shaft 31 side (W6≦DY / 2). The first bearing mechanism 507 and the second bearing mechanism 508 may have different parameters such as ball diameter and bearing size.

[0063] An inner ring raceway groove 546 that comes into contact with balls 570 on the input shaft 21 side and in which balls 570 roll is formed on the outer peripheral surface of input shaft 21. In other words, first bearing mechanism 507 of this embodiment is formed without having a separate component that constitutes an inner ring. Therefore, balls 570 on the input shaft 21 side roll in a rolling element raceway that is formed between inner ring raceway groove 546 formed on input shaft 21 and outer ring raceway groove 596 formed on one-piece outer ring 595. Similarly, an inner ring raceway groove 547 that comes into contact with the balls 580 on the output shaft 31 side and in which the balls 580 roll is formed on the outer peripheral surface of the output shaft 31. In other words, the second bearing mechanism 508 of this embodiment is formed without having a separate component that constitutes an inner ring. Therefore, the balls 580 on the output shaft 31 side roll in the rolling element raceway that is formed between the inner ring raceway groove 547 formed on the output shaft 31 and the outer ring raceway groove 597 formed on the one-piece outer ring 595.

[0064] According to the reverse input disconnect clutch 501 of the fifth embodiment, the outer rings 595 of both the first bearing mechanism 507 and the second bearing mechanism 508 are integral outer rings 595. In other words, the outer ring raceway groove 596 of the first bearing mechanism 507, the outer ring raceway groove 597 of the second bearing mechanism 508, and the pressed surface 77 are formed on the integral outer ring 595, which is a single component. This allows for a reduction in the number of components compared to a case where the first bearing mechanism 507 and the second bearing mechanism 508 each have an outer ring. Furthermore, because the bearing of the input shaft 21, the bearing of the output shaft 31, and the pressed surface 77 are formed from the same component (integral outer ring 595), it is possible to improve the coaxiality between the input shaft 21, the output shaft 31, and the pressed surface 77. This allows for a high-performance reverse input disconnect clutch 501.

[0065] An inner ring raceway groove 546 (inner ring raceway surface in the claims) of the first bearing mechanism 507 is integrally formed with the input shaft 21. This eliminates the need to provide a separate component as an inner ring, thereby reducing the number of components. Furthermore, since the inner ring raceway groove 546 and the arm portion 23 of the input member 2 can be machined in the same process using a single chuck or the like, coaxiality between the input shaft 21 and other components can be improved. Furthermore, since the mating surfaces in the first bearing mechanism 507 are smaller than when a separate inner ring is provided, coaxiality between the components connected via the first bearing mechanism 507 can be improved.

[0066] An inner ring raceway groove 547 (inner ring raceway surface in the claims) of the second bearing mechanism 508 is integrally formed with the output shaft 31. This eliminates the need to provide a separate component as an inner ring, thereby reducing the number of components. Furthermore, since the inner ring raceway groove 547 and the insertion portion 32 of the output member 3 can be machined in the same process using a single chuck or the like, coaxiality between the output shaft 31 and other components can be improved. Furthermore, since the number of mating surfaces in the second bearing mechanism 508 is smaller than when a separate inner ring is provided, coaxiality between the components connected via the second bearing mechanism 508 can be improved.

[0067] (Sixth embodiment) Next, a sixth embodiment of the present invention will be described. In the following description, the same components as those in the fifth embodiment described above will be assigned the same reference numerals and description thereof will be omitted where appropriate. FIG. 8 is a schematic diagram of a reverse input cutoff clutch 601 according to the sixth embodiment. The sixth embodiment differs from the fifth embodiment described above in that the inner rings on which the balls on the input member 2 side and the balls on the output member 3 side roll are formed separately from the input member 2 and the output member 3, respectively.

[0068] In the sixth embodiment, an inner ring 648 is attached to the outer periphery of the input shaft 21 of the input member 2. An inner ring raceway groove 646 in which balls 670 on the input member 2 side roll is formed on the outer periphery of this inner ring 648. In other words, in this embodiment, the first bearing mechanism 607 has balls 670, a one-piece outer ring 695, an outer ring raceway groove 696 and a pressed surface 77 formed on the one-piece outer ring 695, an inner ring 648 attached to the input member 2, and an inner ring raceway groove 646 formed on the inner ring 648. Similarly, an inner ring 649 is attached to the outer periphery of the output shaft 31 of the output member 3. An inner ring raceway groove 647 in which the balls 680 on the output member 3 side roll is formed on the outer periphery of this inner ring 649. In other words, in this embodiment, the second bearing mechanism 608 has the balls 680, the one-piece outer ring 695, the outer ring raceway groove 697 and the pressed surface 77 (which is the same as the pressed surface 77 of the first bearing mechanism 607) formed on the one-piece outer ring 695, the inner ring 649 attached to the output member 3, and the inner ring raceway groove 647 formed on the inner ring 649.

[0069] The reverse input cutoff clutch 601 of the sixth embodiment can achieve the same effects as those of the fifth embodiment. That is, when a ball bearing is used in the reverse input cutoff clutch 601, it is possible to provide a reverse input cutoff clutch 601 that can improve assembly efficiency while suppressing performance degradation due to a decrease in coaxiality and an increase in loss.

[0070] According to the second to sixth embodiments described above, bearing mechanisms of various configurations can be applied to the present invention, thereby improving the versatility of the reverse input cutoff clutches 1, 201, 301, 401, 501, and 601.

[0071] The technical scope of the present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the spirit of the present invention. For example, in the first embodiment described above, the pressed surface 77 and the outer ring raceway groove 76 are formed at the same radial position in the one-piece outer ring 71, but this is not limited to this. The pressed surface 77 and the outer ring raceway groove 76 may be positioned at different radial positions in the one-piece outer ring 71. In this case, a step or the like may be provided between the pressed surface 77 and the outer ring raceway groove 76 in the axial direction to make the inner diameter dimension different.

[0072] In the above-described embodiments, the radial thickness dimensions W1, W3, W5, and W6 of the portions of the one-piece outer ring 71, 391, 491, 595, and 695 that correspond to the groove bottoms of the outer ring raceway surface are equal to or smaller than the diameter of the balls in the bearing mechanism. However, this is not limited to this. For example, the thickness dimension of the entire portion of the one-piece outer ring 71, 391, 491, 595, and 695 that corresponds to the balls (the entire portion where the outer ring raceway surface is formed) may be formed to be equal to or smaller than the diameter of the balls.

[0073] In the first embodiment described above, the input shaft 21 and the arm portion 23 of the input member 2 are integrally formed, but this is not limiting. The input member 2 may be formed by combining multiple parts. Similarly, the output shaft 31 and the insertion portion 32 of the output member 3 may be formed by combining separate parts.

[0074] The reverse input cutoff clutch 1 of each of the above-described embodiments may be applied to a system in which the direction in which the reverse input torque is generated is not constant, for example. Similarly, it may be applied to a system in which the direction in which the input torque is generated is not constant.

[0075] In the above-described embodiments, the reverse input cutoff clutch 1 is a linkless type that does not use a link structure as a reverse input cutoff mechanism, but the present invention is not limited to this. A link type reverse input cutoff clutch that uses a link mechanism, which is a known technology, may also be used as the reverse input cutoff mechanism. [Explanation of symbols]

[0076] 1,201,301,401,501,601 Reverse input cutoff clutch 2 Input member 3 Output member 4. Housing 5 Engagement element 7 First bearing mechanism 8 Second bearing mechanism 21 Input shaft 31 Output shaft 51 Pressing surface 55 Input side engaged portion 56 Output side engaged part 70,570,670 (first bearing mechanism) ball 71,391,491,595,695 Outer ring (integrated outer ring) 72,82,393,493,546,547,646,647 Inner ring raceway groove (inner ring raceway surface) 76,392,492,596,597,696,697 Outer ring raceway groove (outer ring raceway surface) 77 Pressed surface 80,380,480,580,680 (second bearing mechanism) balls 81 outer ring D1 First radial direction W1, W3, W5, W6 thickness dimensions D, DX, DY (ball) diameter

Claims

1. An input member having an input shaft, The output shaft is arranged coaxially with the input shaft, and the output member is arranged parallel to the input member in the axial direction, A surface to be pressed is provided radially outward from the input member and the output member, and facing radially inward, A pair of engaging elements having a pressing surface facing the pressed surface, an input-side engaging portion that can engage with the input member, and an output-side engaging portion that can engage with the output member, and which are movable relative to each other along the first radial direction, A first bearing mechanism that rotatably supports the input shaft with a ball bearing, A second bearing mechanism that rotatably supports the output shaft with a ball bearing, Equipped with, When rotational torque is applied to the input shaft, the pair of engaging elements move toward each other radially inward in the first radial direction based on the engagement between the input member and the input-side engaged portion, and transmit the rotational torque to the output shaft based on the engagement between the output member and the output-side engaged portion. When rotational torque is applied in reverse to the output shaft, the pair of engaging elements move apart from each other radially outward in the first radial direction based on the engagement between the output member and the output-side engaged portion, causing frictional engagement between the pressed surface and the pressing surface. At least one of the outer rings of the first bearing mechanism and the second bearing mechanism is an integrated outer ring in which the outer ring raceway surface on which the ball bearings roll and the pressed surface are provided integrally. The thickness dimension along the radial direction of at least the portion of the integrated outer ring corresponding to the groove bottom of the outer ring raceway surface is less than or equal to the diameter of the ball. The outer ring of the first bearing mechanism is the integrated outer ring. The housing further comprises the aforementioned integrated outer ring to which the housing is fixed. The outer ring of the second bearing mechanism is provided in the housing. Reverse input blocking clutch.

2. An input member having an input shaft, The output shaft is arranged coaxially with the input shaft, and the output member is arranged parallel to the input member in the axial direction, A surface to be pressed is provided radially outward from the input member and the output member, and facing radially inward, A pair of engaging elements having a pressing surface facing the pressed surface, an input-side engaging portion that can engage with the input member, and an output-side engaging portion that can engage with the output member, and which are movable relative to each other along the first radial direction, A first bearing mechanism that rotatably supports the input shaft with a ball bearing, A second bearing mechanism that rotatably supports the output shaft with a ball bearing, Equipped with, When rotational torque is applied to the input shaft, the pair of engaging elements move toward each other radially inward in the first radial direction based on the engagement between the input member and the input-side engaged portion, and transmit the rotational torque to the output shaft based on the engagement between the output member and the output-side engaged portion. When rotational torque is applied in reverse to the output shaft, the pair of engaging elements move apart from each other radially outward in the first radial direction based on the engagement between the output member and the output-side engaged portion, causing frictional engagement between the pressed surface and the pressing surface. At least one of the outer rings of the first bearing mechanism and the second bearing mechanism is an integrated outer ring in which the outer ring raceway surface on which the ball bearings roll and the pressed surface are provided integrally. The thickness dimension along the radial direction of at least the portion of the integrated outer ring corresponding to the groove bottom of the outer ring raceway surface is less than or equal to the diameter of the ball. The outer ring of the second bearing mechanism is the integrated outer ring. The housing further comprises the aforementioned integrated outer ring to which the housing is fixed. The outer ring of the first bearing mechanism is provided in the housing. Reverse input blocking clutch.

3. The thickness dimension along the radial direction of at least the portion of the integrated outer ring corresponding to the bottom of the groove on the outer ring raceway surface is 1 / 2 or less of the diameter of the ball. The reverse input interruption clutch according to claim 1 or claim 2.

4. The aforementioned integrated outer ring is formed from a high-hardness material. The reverse input interruption clutch according to claim 1 or claim 2.

5. The inner ring raceway surface of the first bearing mechanism is integrally formed on the input shaft. The reverse input interruption clutch according to claim 1 or claim 2.

6. The inner ring raceway surface of the second bearing mechanism is integrally formed on the output shaft. The reverse input interruption clutch according to claim 1 or claim 2.

7. The outer rings of the first bearing mechanism and the second bearing mechanism are the integrated outer rings. The single-piece integrated outer ring has the outer ring raceway surface of the first bearing mechanism, the outer ring raceway surface of the second bearing mechanism, and the pressed surface formed thereon. The reverse input interruption clutch according to claim 1 or claim 2.

8. The inner ring raceway surface of the first bearing mechanism is integrally formed on the input shaft. The reverse input interruption clutch according to claim 7.

9. The inner ring raceway surface of the second bearing mechanism is integrally formed on the output shaft. The reverse input interruption clutch according to claim 7.

10. The aforementioned ball bearing is either a deep groove ball bearing or a four-point contact ball bearing. The reverse input interruption clutch according to claim 1 or claim 2.

Images