Reverse input blocking clutch

Abstract

This reverse input blocking clutch (1) comprises: an input member (2) having an input shaft (21); an output member (3) having an output shaft (31); a pressed surface (62); a pair of engaging elements (5); a first bearing mechanism (7) that rotatably supports the input member (2); and a second bearing mechanism (8) that rotatably supports the output member (3). The outer ring of the first bearing mechanism (7) and the second bearing mechanism (8) is an integrated outer ring (61) in which a first outer ring raceway groove (73) in which a first rolling element (70) of the first bearing mechanism (7) rolls, a second outer ring raceway groove (83) in which a second rolling element (80) of the second bearing mechanism (8) rolls, and the pressed surface (62) are integrally provided.

Description

Technical Field

[0001] The present invention relates to a reverse input blocking clutch. This application claims priority based on Japanese Patent Application No. 2024-098128 filed on June 18, 2024, the content of which is incorporated herein by reference.

Background Art

[0002] Conventionally, there is known a configuration of a reverse input blocking clutch 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 speed reducer, and permits transmission of a rotational force from the input member to the output member while blocking reverse input of the rotational force from the output member to the input member. For these reverse input blocking clutches, various techniques for improving the performance of the reverse input blocking clutch have been proposed.

[0003] For example, Patent Document 1 discloses a configuration of a lock-type reverse input blocking clutch that blocks reverse input from the output member by preventing rotation of the output member. The reverse input blocking clutch has an input shaft and an output shaft provided coaxially with each other, a pressed member having a pressed surface, and a pair of engaging elements movable in the radial direction. According to the technique described in Patent Document 1, when a rotational force is reversely input to the output member, the engaging element moves in a direction approaching the pressed surface based on the engagement between the engaging element and the output member and frictionally engages with the pressed surface, thereby blocking the rotational force reversely input to the output shaft.

[0004] In such a reverse input blocking clutch, it is necessary to increase the hardness of the pressed member in order to suppress wear when the engaging element slides on the pressed surface. Further, for example, when the coaxiality of each of the input member, the output member, and the pressed surface is poor, there is a risk that the performance may deteriorate due to generation of play in the rotational direction or an increase in loss due to sliding between the pressed surface and the engaging element.

[0005] Therefore, various techniques have been proposed to suppress wear when the engaging element slides on the pressed surface and deformation of the pressed member due to stress when blocking reverse input. For example, Patent Document 2 discloses a bearing outer ring made of a heat-treated, high-hardness steel material (such as bearing steel), in which the outer ring raceway surface and the pressed surface are integrally formed. According to the technology described in Patent Document 2, since the hardness of the pressed member (i.e., the bearing outer ring) is high, wear when the engaging element slides on the pressed surface can be suppressed. [Prior art documents] [Patent Documents]

[0006] [Patent Document 1] Patent No. 6658965 [Patent Document 2] International Publication No. 2023 / 195203 [Overview of the project] [Problems that the invention aims to solve]

[0007] However, in the technology described in Patent Document 2 mentioned above, the housing is formed by joining the input member side housing and the output member side housing to each other using a spigot joint. From the standpoint of ease of assembly, this spigot joint is likely to be a gap fit. As a result, radial misalignment between the housings may occur due to the gap fit, which may make it difficult to ensure coaxiality between the input member, output member and housing.

[0008] Here, for example, if the coaxiality between the input member and the pressed member (pressed surface) is poor, the size of the gap between each engaging element and the input member will differ. As a result, when a rotational force is applied to the input member, only one engaging element will contact the input member first, and torque will be concentrated on that engaging element until the other engaging element contacts the input member. Consequently, performance may deteriorate due to wear, vibration, or contamination by foreign matter. Furthermore, if the coaxiality between the output member and the pressed member (pressed surface) is poor, the size of the gap between each engaging element and the pressed member will differ. As a result, when a rotational force is applied in reverse to the output member, only one engaging element will contact the pressed member first, and the pressing force will be weak until the other engaging element contacts the output member, preventing the locking function from working properly. Consequently, a time loss may occur before locking is achieved. Moreover, since only one engaging element contacts the output member, bending may occur in the output member, potentially degrading its performance.

[0009] Therefore, in the prior art described in Patent Document 1 and Patent Document 2, etc., there was room for improvement in terms of suppressing wear on the pressed surface when the engaging element slides on the pressed surface, while improving the coaxiality between each component such as the input member, output member, and pressed surface.

[0010] Therefore, the present invention aims to provide a reverse input blocking clutch that can suppress wear on the pressed surface and improve the coaxiality between each component compared to the conventional technology. [Means for solving the problem]

[0011] To solve the above problems, this invention proposes the following means. A reverse input blocking 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 parallel to the input member, a pair of engaging elements provided radially outward from the input member and the output member and facing radially inward, a pressing surface facing the pressing 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 relatively movable relative to each other along a first radial direction, a first bearing mechanism that rotatably supports the input member, and a second bearing mechanism that rotatably supports the output member, wherein when rotational torque is applied to the input shaft, the pair of engaging elements move relative to each other along a first radial direction. Based on engagement with the engaged portion, the two engages move toward each other radially inward in the first radial direction, and based on engagement between the output member and the output-side engaged portion, they transmit the rotational torque to the output shaft. When rotational torque is reverse-input to the output shaft, the pair of engages move toward each other radially outward in the first radial direction based on engagement between the output member and the output-side engaged portion, causing frictional engagement between the pressed surface and the pressing surface. The outer rings of the first bearing mechanism and the second bearing mechanism are integrated outer rings in which the first outer ring raceway surface on which the rolling elements of the first bearing mechanism roll, the second outer ring raceway surface on which the rolling elements of the second bearing mechanism roll, and the pressed surface are provided integrally. [Effects of the Invention]

[0012] The reverse input blocking clutch of the present invention provides a reverse input blocking clutch that suppresses wear on the pressed surface and improves the coaxiality between each component compared to the conventional technology. [Brief explanation of the drawing]

[0013] [Figure 1] A cross-sectional view of the reverse input blocking clutch according to the first embodiment. [Figure 2] A cross-sectional view along line II-II in Figure 1. [Figure 3] A schematic diagram of the reverse input blocking clutch according to the first embodiment. [Figure 4] Schematic configuration diagram of a reverse input blocking clutch according to a modified example of the first embodiment. [Figure 5] Schematic configuration diagram of a reverse input blocking clutch according to the second embodiment. [Figure 6] Schematic configuration diagram of a reverse input blocking clutch according to the third embodiment. [Figure 7] Schematic configuration diagram of a reverse input blocking clutch according to the fourth embodiment.

MODE FOR CARRYING OUT THE INVENTION

[0014] Hereinafter, embodiments 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 central axis C of the reverse input blocking clutch 1 unless otherwise specified.

[0015] (First Embodiment) FIG. 1 is a cross-sectional view of a reverse input blocking clutch 1 according to the first embodiment. FIG. 2 is a cross-sectional view taken along line II-II of FIG. 1. FIG. 3 is a schematic configuration diagram of the reverse input blocking 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 blocking clutch 1 in the present embodiment, and is a simplified view of FIG. 1. Also, in FIG. 3, the illustration of some components (for example, the housing 4, etc.) is omitted.

[0016] As shown in FIG. 1, the reverse input blocking clutch 1 of the present 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 blocking clutch 1 has a function of blocking the rotational force reversely input to the output shaft 31 by a lock function (reverse input blocking function). Thereby, in an electric caliper brake, a parking brake function is realized, and in a rear wheel steering device, a function of holding the steering angle of the wheel at the time of power interruption is realized.

[0017] As shown in FIGS. 1 to 3, the reverse input blocking clutch 1 includes an input member 2, an output member 3, a housing 4, a pair of engaging elements 5, and a plurality of bearing mechanisms 7, 8. The reverse input blocking clutch 1 transmits the rotational force input to the input member 2 to the output member 3. On the other hand, the reverse input blocking clutch 1 has a reverse input blocking function of blocking the rotational force reversely input to the output member 3 from being transmitted to the input member 2, or transmitting only a part of it to the input member 2 and blocking the remaining part.

[0018] 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 arm portions 23. The input shaft 21 is provided on the input mechanism side in the axial direction. The input shaft 21 is formed in a cylindrical (or tubular) shape centered on the central axis C. In the following description, the side of the input shaft 21 connected to the input mechanism may be referred to as the first side in the axial direction, and the opposite side may be referred to as the second side in the axial direction.

[0019] The pair of arm portions 23 extend from the input shaft 21 toward the second side in the axial direction. The arm portions 23 are integrally formed with the input shaft 21. The arm portions 23 are provided in a pair at both ends in the first radial direction D1 with respect to the input shaft 21. As shown in FIG. 2, the arm portions 23 are formed in a trapezoidal shape with one side curved when viewed from the axial direction. Specifically, the arm portion 23 has a planar input-side engaging portion 25 facing the inner side in the radial direction, a curved surface portion 26 facing the outer side in the radial direction, and two side surface portions 27 connecting the ends of the input-side engaging portion 25 and the curved surface portion 26. The curved surface portion 26 is formed in an arc shape centered on the central axis C. Note that the shape of the arm portion 23 is not limited to the shape described above. The shape of the arm portion 23 may be, for example, a semi-circular shape, a polygonal shape, an oval shape, etc., having an arc-shaped curved surface portion and a planar portion.

[0020] A plurality of arm portions 23 are provided according to the number of the engaging elements 5 described later. In the present embodiment, a pair of arm portions 23 are provided according to the provision of a pair of engaging elements 5. Note that the number of the arm portions 23 is not limited to two, and according to the number of the engaging elements 5, the number of the arm portions 23 may be one or three or more.

[0021] As shown in Figures 1 to 3, the output member 3 is connected to an output mechanism such as a reduction gear (not shown) and outputs rotational force (rotational torque). The output member 3 has an output shaft 31 and an insertion part 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 cylindrical shape (or cylindrical shape) with the central axis C as its center.

[0022] The insertion portion 32 extends from the first end of the output shaft 31 in the axial direction toward the first side in the axial direction. The insertion portion 32 is integrally formed with the output shaft 31. The insertion portion 32 is the part inserted between the pair of engaging elements 5, which will be described later, and is positioned radially inward from the pair of arm portions 23 of the input member 2. The base end of the insertion portion 32 that is inserted between the pair of engaging elements 5 (for example, the part located second axially from the retaining ring 39 in Figure 1) is formed in a plate shape (see also Figure 2). The tip of the insertion portion 32 (for example, the part located first axially from the retaining ring 39) is formed in a cylindrical shape. Note that the shape of the base end of the insertion portion 32 is not limited to a plate shape. The tip of the insertion portion 32 may also be rotatably supported on the input shaft 21 via a bearing (not shown).

[0023] As shown in Figure 2, the outer circumferential 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 portions 36 connecting the ends of the pair of output-side engaging portions 35. Each output-side engaging portion 35 is composed of 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 portions 35 are located inward in the first radial direction D1 compared to the input-side engaging portion 25 of the input member 2. The pair of side portions 36 connect the ends of the output-side engaging portions 35, respectively.

[0024] The output-side engaging portion 35 and side portion 36 of the insertion portion 32 are provided in multiple quantities depending on the number of engaging elements 5, which will be described later. In this embodiment, a pair of output-side engaging portions 35 and side portions 36 are provided in accordance with the provision of a pair of engaging elements 5. Note that the number of output-side engaging portions 35 is not limited to two; depending on the number of engaging elements 5, the number of output-side engaging portions 35 may be one or three or more.

[0025] As shown in Figure 1, the housing 4 is positioned radially outward from the input member 2 and output member 3 described above. The housing 4 is a housing component with a cylindrical inner circumference. The housing 4 is fixed to other members (not shown) and its rotation is constrained. The input member 2, the output member 3, and a pair of engaging elements 5 are housed inside the inner circumference of the housing 4. The housing 4 rotatably houses the input member 2 and output member 3 via a plurality of bearing mechanisms 7 and 8, which will be described in more detail later.

[0026] As shown in Figures 1 to 3, the pair of engaging elements 5 are configured in a semicircular shape and are positioned 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 move toward and toward 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.

[0027] As shown in Figure 2, the pressing surface 51 is the radially outer surface that presses against the pressed surface 62 provided on the outer ring 61 (integrated outer ring 61 of the claim) of the first bearing mechanism 7 and the second bearing mechanism 8, which will be described later, and is an arc-shaped convex surface. Note that a part of the outer circumferential surface of the engaging element 5 facing the pressed surface 62 may also be the pressing surface 51. The pressing surface 51 presses against the pressed surface 62 when the reverse input blocking clutch 1 is locked (when reverse input from the output member 3 is blocked). The radius of curvature of the pressing surface 51 is less than or equal to the radius of curvature of the pressed surface 62. Two pressing surfaces 51 are provided for each engaging element 5, and they are formed so that the frictional engagement force between the engaging element 5 and the pressed surface 62 is increased by 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 a part of the outer surface of the engaging element 5, or it may be formed to have a surface texture with a higher coefficient of friction compared to 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 adhesion or bonding.

[0028] The bottom surface 52 of the engaging element 5 is located inward from the pressing surface 51 in the first radial direction D1. The bottom surface 52, together with the output-side engaged portion 56 of the engaging element 5 (described in more detail later), forms the straight portion of the semicircular engaging element 5. In this embodiment, the bottom surface 52 is formed in a substantially flat shape except for a pair of protrusions 53 (described later). The bottom surfaces 52 of the pair of engaging elements 5 face each other in the first radial direction D1. With the pair of engaging elements 5 positioned inside the pressed surface 62, the inner diameter of the pressed surface 62 and the outer dimensions of the engaging elements 5 are set such that there is a gap between the pressed surface 62 and the pressing surface 51, and between the pair of bottom surfaces 52 and the output member 3.

[0029] The input-side engaged portion 55 is a hole that penetrates the central part of the engaging element 5 in the axial direction when viewed from the axial direction. The input-side engaged portion 55 is formed as an elongated hole extending in the second radial direction D2. The arms 23 of the input member 2 are inserted into the input-side engaged portion 55. The input-side engaged portion 55 engages with the arms 23. The input-side engaged portion 55 is sized to allow the arms 23 of the input member 2 to be loosely inserted. Specifically, when the arms 23 of the input member 2 are inserted inside the input-side engaged portion 55, a gap exists between the arms 23 and the inner circumferential surface of the input-side engaged portion 55.

[0030] The output-side engaged portion 56 is located near the center in the second radial direction D2 of the straight portion (bottom surface 52) of the semicircularly formed engaging element 5. The output-side engaged portion 56 is located inward in the first radial direction D1 compared to the input-side engaged portion 55. The insertion portion 32 of the output member 3 engages with the output-side engaged portion 56. The output-side engaged portion 56 is formed as a flat surface continuous with the bottom surface 52.

[0031] As shown in Figures 1 and 2, in the assembled state of the reverse input blocking clutch 1, the arm portion 23 of the input member 2 is inserted axially into the respective 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 their respective output-side engaged portions 56 sandwich the insertion portion 32 of the output member 3 from the radially outer side.

[0032] As shown in Figure 1, a leaf spring 38 is provided between a 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 62. On the first axial side of the engaging element 5, a retaining ring 39 is provided for positioning each member. Furthermore, end plates or the like (not shown) may be provided on both axial sides of the engaging element 5 for positioning each member. In addition to the positioning function, parts 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. Note that the leaf spring 38 is optional.

[0033] As shown in Figures 1 and 3, the reverse input blocking clutch 1 has a first bearing mechanism 7 and a second bearing mechanism 8 as multiple bearing mechanisms. In this embodiment, both the first bearing mechanism 7 and the second bearing mechanism 8 are deep groove ball bearings.

[0034] The first bearing mechanism 7 rotatably supports the input member 2 with respect to the housing 4. The first bearing mechanism 7 includes a first rolling element 70 (rolling element of the first bearing mechanism in the claim) that rolls around the input shaft 21, an integrated outer ring 61 common to the second bearing mechanism 8 which will be described in more detail later, a first outer ring raceway groove 73 (outer ring raceway surface in the claim) and a pressed surface 62 formed on the integrated outer ring 61, and a first inner ring raceway groove 75 (inner ring raceway surface in the claim) formed on the input shaft 21. The integrated outer ring 61 is formed in a cylindrical shape with a central axis C as the center. The outer circumferential surface of the integrated outer ring 61 is attached to the inner circumference of the housing 4 (see Figure 1). The integrated outer ring 61 is provided extending axially from the part where the input shaft 21 is located to the part where the output shaft 31 is located. On the inner circumferential surface of the integrated outer ring 61, a first outer ring raceway groove 73 for the first rolling element 70 to roll on, a pressed surface 62 that contacts the engaging element 5, and a second outer ring raceway groove 83 for the second rolling element 80 of the second bearing mechanism 8 are formed in order from the first side in the axial direction. That is, the pressed surface 62 is positioned between the first outer ring raceway groove 73 and the second outer ring raceway groove 83 in the axial direction. Furthermore, the outer ring of the first bearing mechanism 7 is an integrated outer ring 61 in which the first outer ring raceway groove 73 for the first rolling element 70 of the first bearing mechanism 7 to roll on, the second outer ring raceway groove 83 for the second rolling element 80 of the second bearing mechanism 8 to roll on, and the pressed surface 62 are integrally formed on a single component.

[0035] The integrated outer ring 61 is formed from a high-hardness steel material, such as bearing steel. Examples of high-hardness steel materials include heat-treated high-carbon steels such as SUJ3 and SUJ2. However, the steel material can be any material with high hardness, and is not limited to the materials mentioned above.

[0036] A first inner ring raceway groove 75 is formed on the outer circumferential surface of the input shaft 21, which contacts the first rolling element 70 and allows the first rolling element 70 to roll. In other words, the first bearing mechanism 7 of this embodiment is formed without having separate components that constitute the inner ring. Therefore, the first rolling element 70 rolls within the rolling element raceway path formed between the first inner ring raceway groove 75 formed on the input shaft 21 and the first outer ring raceway groove 73 formed on the integrated outer ring 61.

[0037] The second bearing mechanism 8 is located second axially to the first bearing mechanism 7. The second bearing mechanism 8 rotatably supports the output member 3 with respect to the housing 4. The second bearing mechanism 8 includes a second rolling element 80 (rolling element of the second bearing mechanism in the claim) that rolls around the output shaft 31, an integrated outer ring 61 common to the first bearing mechanism 7 described above, a second outer ring raceway groove 83 (outer ring raceway surface in the claim) formed on the integrated outer ring 61, and a second inner ring raceway groove 85 (inner ring raceway surface in the claim) formed on the output shaft 31.

[0038] In this embodiment, the first bearing mechanism 7 and the second bearing mechanism 8 use the same type of bearing (deep groove ball bearing), but their parameters, such as bearing size, differ from each other. In this embodiment, the bearing of the first bearing mechanism 7 has a larger PCD (Pitch Circle Diameter) and bearing diameter compared to the bearing of the second bearing mechanism 8. In addition to PCD, other bearing parameters such as the diameter of the rolling elements, the diameters of the inner and outer rings, and the rated load may also differ from each other.

[0039] Furthermore, in this embodiment, in accordance with the difference in bearing sizes between the first bearing mechanism 7 and the second bearing mechanism 8, the inner diameter of the integrated outer ring 61 is formed to differ between the input member 2 side and the output member 3 side. Specifically, the inner diameter R1 of the integrated outer ring 61 on the first axial side where the first outer ring raceway groove 73 and the pressed surface 62 are formed is greater than the inner diameter R2 of the integrated outer ring 61 on the second axial side where the second outer ring raceway groove 83 is formed (R1 > R2). On the inner circumference of the integrated outer ring 61, a stepped portion 63 is provided between the axial pressed surface 62 and the second outer ring raceway groove 83.

[0040] A second inner ring raceway groove 85 is formed on the outer circumferential surface of the output shaft 31, which contacts the second rolling element 80 and allows the second rolling element 80 to roll. In other words, the second bearing mechanism 8 of this embodiment, like the first bearing mechanism 7, is formed without having separate components that constitute the inner ring. Therefore, the second rolling element 80 rolls within the rolling element raceway path formed between the second inner ring raceway groove 85 formed on the output shaft 31 and the second outer ring raceway groove 83 formed on the integrated outer ring 61.

[0041] In this embodiment, the bearings in the first bearing mechanism 7 and the second bearing mechanism 8 are of the same type, but this is not limited to this. The bearings in the first bearing mechanism 7 and the second bearing mechanism 8 may be of different types. Furthermore, the bearing type is not limited to deep groove ball bearings. For example, the bearing type may be any of angular contact ball bearings, deep groove ball bearings, four-point contact ball bearings, tapered roller bearings, and cylindrical roller bearings. These may also be used in combination.

[0042] (Operation of the reverse input blocking clutch) Next, the operation of the reverse input blocking clutch 1 of this embodiment will be described. First, let's explain the case where a rotational force is applied to the input shaft 21 from the input mechanism. When a rotational force is applied to the input shaft 21, as shown in Figure 2, the arm portion 23 of the input member 2 rotates inside the input-side engaging portion 25 in the direction of rotation of the input shaft 21 (counterclockwise CCW in the example shown in Figure 2) around the central axis C. Then, the corner portion between the input-side engaging portion 25 and the side portion 27 on the counterclockwise CCW side of the arm portion 23 (point P1 in Figure 2) presses the inner surface of the input-side engaged portion 55 radially inward, causing the pair of engaging elements 5 to move away from the pressed surface 62 (inward in the first radial direction D1). In other words, the pair of engaging elements 5 move radially inward so as to approach 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 toward 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.

[0043] This causes the output member 3 to rotate so that the long axis of the insertion portion 32 is parallel to the bottom surface 52 of the engaging element 5, while simultaneously engaging the insertion portion 32 with the pair of output-side engaged portions 56 without any wobbling. As a result, the rotational force input to the input shaft 21 is transmitted to the output member 3 via the pair of engaging elements 5 and output from the output shaft 31. In this embodiment, when a rotational force is applied to the input shaft 21, the reverse input blocking clutch 1 moves a pair of engaging elements 5 away from the pressed surface 62, regardless of the rotational direction of the input shaft 21. Then, regardless of the rotational direction of the input shaft 21, the rotational force applied to the input shaft 21 is transmitted to the output shaft 31 via the pair of engaging elements 5.

[0044] Next, we will explain the case where a rotational force is input in reverse from the output mechanism to the output shaft 31. When a rotational force is input in reverse to the output shaft 31, as shown in Figure 2, the insertion portion 32 of the output member 3 rotates in the direction of rotation of the output shaft 31 (clockwise CW in the example shown in Figure 2) inside the pair of output-side engaged portions 56. Then, the corner between the side portion 36 of the insertion portion 32 and the output-side engaged portion 35 (point P2 in Figure 2) presses the output-side engaged portion 56 radially outward, causing the pair of engaging elements 5 to move toward the pressed surface 62. In other words, the pair of engaging elements 5 move apart from each other toward the outside in the first radial direction D1 based on the engagement between the output member 3 and the output-side engaged portion 56. As a result, each of the pressing surfaces 51 of the pair of engaging elements 5 is pressed against the pressed surface 62. At this time, the pressing surface 51 and the pressed surface 62 are frictionally engaged over the entire range or at least a portion of the circumferential direction of the pressing surface 51.

[0045] As a result, the rotational force reversed on the output shaft 31 is either blocked and not transmitted to the input member 2, or only a portion of the rotational force reversed on the output shaft 31 is transmitted to the input member 2 and the rest is blocked. In order to completely block the rotational force reversed on the output shaft 31 and prevent it from being transmitted to the input member 2, the pair of engaging elements 5 are braced between the insertion part 32 and the pressed surface 62 so that the pressing surface 51 does not slide (rotate relative to) the pressed surface 62, thereby locking the output member 3. On the other hand, in order to transmit only a portion of the rotational force reversed on the output shaft 31 to the input member 2 and the rest is blocked, the pair of engaging elements 5 are braced between the insertion part 32 and the pressed surface 62 so that the pressing surface 51 slides against the pressed surface 62, thereby semi-locking the output member 3. When the output member 3 is semi-locked and a rotational force is applied in reverse to the output shaft 31, the pair of engaging elements 5 rotate around the central axis C, sliding their pressing surface 51 against the pressed surface 62, based on the engagement between the insertion portion 32 of the output member 3 and the output-side engaged portion 56. As 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), thereby transmitting a portion of the rotational force to the input member 2.

[0046] (Effect, Action) According to the reverse input blocking clutch 1 of this embodiment, the outer rings of the first bearing mechanism 7 and the second bearing mechanism 8 are integrated outer rings 61 in which the first outer ring raceway groove 73 (first outer ring raceway surface in the claim) on which the first rolling element 70 of the first bearing mechanism 7 rolls, the second outer ring raceway groove 83 (second outer ring raceway surface in the claim) on which the second rolling element 80 of the second bearing mechanism 8 rolls, and the pressed surface 62 are integrally provided on a single component. Since the pressed surface 62 is integrally formed on the outer ring of the bearing (integrated outer ring 61 in this embodiment), which is generally formed from a material with high hardness, the hardness of the pressed surface 62 can be increased. As a result, wear caused by the pressing surface 51 of the engaging element 5 sliding on the pressed surface 62 can be suppressed. Furthermore, since the integrated outer ring 61 is integrally provided with a first outer ring raceway groove 73 on which the first rolling element 70 on the input member 2 side rolls, a second outer ring raceway groove 83 on which the second rolling element 80 on the output member 3 side rolls, and a pressed surface 62, it becomes easier to ensure coaxiality between the input member 2, the output member 3, and the pressed surface 62. Therefore, compared to conventional technology, it is possible to provide a reverse input blocking clutch 1 that suppresses wear on the pressed surface 62 while improving the coaxiality between each component. By improving the coaxiality between the input member 2 and the pressed surface 62, the pair of arms 23 can press against the engaging element 5 at the same time, suppressing wear, vibration, and foreign matter contamination of parts caused by one arm 23 pressing against the engaging element 5 first. Similarly, by improving the coaxiality between the output member 3 and the pressed surface 62, it becomes easier to equalize the gap between the pair of engaging elements 5 and the pressed surface 62. Therefore, a decrease in the locking function and bending of the output member 3 can be suppressed, and the performance of the reverse input blocking clutch 1 can be improved.

[0047] The first bearing mechanism 7 and the second bearing mechanism 8 have bearings of different sizes. This allows each bearing mechanism to be configured in various combinations. Thus, the versatility of the reverse input blocking clutch 1 can be increased.

[0048] The first bearing mechanism 7 and the second bearing mechanism 8 may have bearings of different types. In this case, each bearing mechanism can be configured in various combinations. Therefore, the versatility of the reverse input blocking clutch 1 can be further enhanced.

[0049] The input member 2 has the first inner ring raceway groove 75 (the inner ring raceway surface in the claim) of the first bearing mechanism 7 integrally formed on it. This eliminates the need to provide a separate inner ring component, thus reducing the number of parts. Furthermore, since the machining of the first inner ring raceway groove 75 and the machining of the arm portion 23 of the input member 2 can be performed in the same process, such as a single chuck, the coaxiality between the input member 2 and other components can be improved. In addition, compared to the case where a separate inner ring is provided, the number of mating surfaces in the first bearing mechanism 7 is reduced, thus improving the coaxiality between components connected via the first bearing mechanism 7.

[0050] The output member 3 has the second inner ring raceway groove 85 (the inner ring raceway surface in the claim) of the second bearing mechanism 8 integrally formed on it. This eliminates the need to provide a separate inner ring component, thus reducing the number of parts. Furthermore, since the machining of the second inner ring raceway groove 85 and the machining of the insertion portion 32 of the output member 3 can be performed in the same process, such as a single chuck, the coaxiality between the output member 3 and other components can be improved. In addition, compared to the case where a separate inner ring is provided, the number of mating surfaces in the second bearing mechanism 8 is reduced, thus improving the coaxiality between components connected via the second bearing mechanism 8.

[0051] The first bearing mechanism 7 and the second bearing mechanism 8 may be any of the following: deep groove ball bearings, angular contact ball bearings, four-point contact ball bearings, tapered roller bearings, and cylindrical roller bearings. This allows various types of bearings to be applied to the present invention. Thus, the versatility of the reverse input blocking clutch 1 can be increased.

[0052] (Modification of the first embodiment) Next, a modified example of the first embodiment of the present invention will be described. In the following description, components similar to those in the first embodiment described above will be denoted by the same reference numerals and their descriptions 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 spirit of the present invention. Figure 4 is a schematic diagram of the reverse input blocking clutch 1A according to a modified example of the first embodiment. The modified example of the first embodiment differs from the first embodiment described above in that the rated load of the bearing in the second bearing mechanism 8 is formed to be greater than the rated load of the bearing in the first bearing mechanism 7.

[0053] In a modified version of the first embodiment, the bearing of the second bearing mechanism 8 has a larger PCD value, bearing diameter, and ball diameter compared to the bearing of the first bearing mechanism 7. As a result, the rated load of the bearing in the second bearing mechanism 8 is formed to be greater than the rated load of the bearing in the first bearing mechanism 7. More specifically, the rated load of the bearing in the second bearing mechanism 8 is formed to be greater than at least one of the dynamic rated load and static rated load of the bearing in the first bearing mechanism 7. In addition, in accordance with the difference in bearing sizes between the first bearing mechanism 7 and the second bearing mechanism 8, the inner diameter dimensions of the integrated outer ring 61 are formed to be different on the input member 2 side and the output member 3 side. Specifically, the inner diameter dimension R4 of the integrated outer ring 61 on the axial second side where the second outer ring raceway groove 83 and the pressed surface 62 are formed is greater than the inner diameter dimension R3 of the integrated outer ring 61 on the axial first side where the first outer ring raceway groove 73 is formed (R4 > R3). In the inner circumference of the integrated outer ring 61, a stepped portion 63 is provided between the axially pressed surface 62 and the first outer ring raceway groove 73.

[0054] In the modified reverse input blocking clutch 1A of the first embodiment, the rated load of the second bearing mechanism 8 located on the output mechanism side of the reverse input blocking clutch 1A is formed to be greater than the rated load of the first bearing mechanism 7 located on the input mechanism side. Here, a motor shaft or the like is connected to the input shaft 21 of the reverse input blocking clutch 1A, and a gear or the like is connected to the output shaft 31. For this reason, the load on the output member 3 tends to be larger than that on the input member 2. In this modified example, since the rated load of the second bearing mechanism 8 located on the output member 3 side is greater than the rated load of the first bearing mechanism 7, the second bearing mechanism 8 can support relatively large loads such as gear loads. Therefore, a reverse input blocking clutch 1A is made that is particularly suitable when the load on the output mechanism is greater than that on the input mechanism.

[0055] In the modified version of the first embodiment, the parameters such as PCD in the first bearing mechanism 7 and the second bearing mechanism 8 are not limited to the embodiments described above. For example, the second bearing mechanism 8 may be formed to have a smaller PCD value and a larger ball diameter compared to the first bearing mechanism 7. In other words, it is sufficient that the rated load of the bearing in the second bearing mechanism 8 is greater than the rated load of the bearing in the first bearing mechanism 7, and the magnitude of each parameter is not limited to the configuration of the embodiments described above.

[0056] (Second Embodiment) Next, a second embodiment of the present invention will be described. In the following description, components similar to those in the first embodiment described above will be denoted by the same reference numerals and their descriptions 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 spirit of the present invention. Figure 5 is a schematic diagram of the reverse input blocking clutch 201 according to the second embodiment. The second embodiment differs from the first embodiment described above in that the inner rings of the first bearing mechanism 7 and the second bearing mechanism 8 are formed separately from the input member 2 and the output member 3.

[0057] In the second embodiment, a first inner ring 245 is attached to the outer circumference of the input shaft 21 in the input member 2. A first inner ring raceway groove 275 for the first rolling element 70 to roll is formed on the outer circumference of the first inner ring 245. In other words, in this embodiment, the first bearing mechanism 207 includes a first rolling element 70, an integrated outer ring 61, a first outer ring raceway groove 73 and a pressed surface 62 formed on the integrated outer ring 61, a first inner ring 245 attached to the input member 2, and a first inner ring raceway groove 275 formed on the first inner ring 245.

[0058] A second inner ring 246 is attached to the outer circumference of the output shaft 31 in the output member 3. A second inner ring raceway groove 285 for the second rolling element 80 to roll is formed on the outer circumference of the second inner ring 246. In other words, in this embodiment, the second bearing mechanism 208 includes a second rolling element 80, an integrated outer ring 61, a second outer ring raceway groove 83 and a pressed surface 62 formed on the integrated outer ring 61, a second inner ring 246 attached to the output member 3, and a second inner ring raceway groove 285 formed on the second inner ring 246.

[0059] The reverse input blocking clutch 201 of the second embodiment can achieve the same effects as the first embodiment. Specifically, since the pressed surface 62 is integrally formed on the outer ring (integrated outer ring 61) of the bearing, which is generally made of a material with high hardness, the hardness of the pressed surface 62 can be increased. This suppresses wear caused by the pressing surface 51 of the engaging element 5 sliding on the pressed surface 62. Furthermore, since the first outer ring raceway groove 73, the second outer ring raceway groove 83, and the pressed surface 62 are integrally provided on the integrated outer ring 61, the coaxiality between the input member 2, the output member 3, and the pressed surface 62 can be increased. Therefore, compared to conventional technology, it is possible to provide a reverse input blocking clutch 201 that suppresses wear on the pressed surface 62 while improving the coaxiality between each component.

[0060] (Third embodiment) Next, a third embodiment of the present invention will be described. In the following description, components similar to those in the first embodiment described above will be denoted by the same reference numerals and their descriptions will be omitted as appropriate. Figure 6 is a schematic diagram of the reverse input blocking clutch 301 according to the third embodiment. The third embodiment differs from the first embodiment described above in that the type and size of the bearings in the first bearing mechanism 7 and the second bearing mechanism 8 are the same.

[0061] In the third embodiment, the bearings of the first bearing mechanism 307 and the bearings of the second bearing mechanism 308 are the same in type and size (diameter of rolling elements, PCD, etc.). Therefore, the inner circumference of the integrated outer ring 361 is formed without the stepped portion 63 (see Figure 3) as in the first embodiment, and is formed to have a substantially uniform inner diameter R3 in the axial direction. In other words, the first outer ring raceway groove 373, the pressed surface 62, and the second outer ring raceway groove 383 formed on the inner circumference of the integrated outer ring 361 are located at substantially the same position in the radial direction.

[0062] Similar to the first embodiment, a first inner ring raceway groove 375 is formed on the outer circumferential surface of the input shaft 21, which contacts the first rolling element 370 and allows the first rolling element 370 to roll. Similar to the first embodiment, a second inner ring raceway groove 385 is formed on the outer circumferential surface of the output shaft 31, which contacts the second rolling element 380 and allows the second rolling element 380 to roll.

[0063] The reverse input blocking clutch 301 of the third embodiment is particularly suitable when the same bearing is used in the first bearing mechanism 307 and the second bearing mechanism 308. Therefore, the versatility of the reverse input blocking clutch 301 can be increased. In addition, since the integrated outer ring 361 is formed without having a stepped portion 63, the integrated outer ring 361 can be formed more easily compared to the case where there is a stepped portion 63. Furthermore, the thickness of the integrated outer ring 361 along the radial direction can be kept small. In the third embodiment, the inner rings (first inner ring 245 and second inner ring 246) may be provided separately, similar to the second embodiment described above.

[0064] (Fourth Embodiment) Next, a fourth embodiment of the present invention will be described. In the following description, components similar to those in the first embodiment described above will be denoted by the same reference numerals and their descriptions will be omitted as appropriate. Figure 7 is a schematic diagram of the reverse input blocking clutch 401 according to the fourth embodiment. The fourth embodiment differs from the first embodiment described above in that tapered roller bearings are used as bearings for the first bearing mechanism 7 and the second bearing mechanism 8.

[0065] In the fourth embodiment, both the first bearing mechanism 407 and the second bearing mechanism 408 are tapered roller bearings. The first bearing mechanism 407 rotatably supports the input shaft 21 and has a pair of third tapered roller bearings 493 and fourth tapered roller bearings 494. The third tapered roller bearing 493 is provided at the first axial end of the integrated outer ring 461. The third tapered roller bearing 493 has a tapered roller as the third rolling element 470, an integrated outer ring 461, a third outer ring raceway groove 473 formed in the integrated outer ring 461, and a third inner ring raceway groove 475 formed in the input shaft 21. The third tapered roller bearing 493 is provided such that the apex of the conical surface of the third rolling element 470 is located on the second axial side. The third outer ring raceway groove 473 formed on the inner circumference of the integrated outer ring 461 is formed so that its inner diameter gradually increases from the second axial side to the first axial side.

[0066] The fourth tapered roller bearing 494 is positioned at a greater distance from the third tapered roller bearing 493, towards the first axial direction. Since the fourth tapered roller bearing 494 has a symmetrical configuration with the third tapered roller bearing 493, a detailed explanation of the parts that overlap with the configuration of the third tapered roller bearing 493 will be omitted. The fourth tapered roller bearing 494 is provided such that the apex of the conical surface of the fourth rolling element 471, a cone-shaped roller, is located on the first axial direction. In this embodiment, the outer ring 463 of the fourth tapered roller bearing 494 is formed from a separate part from the integrated outer ring 461. An input mechanism 491 is connected to the input shaft 21 between the third tapered roller bearing 493 and the fourth tapered roller bearing 494. As a result, rotational force from the input mechanism 491 is input to the input member 2.

[0067] The second bearing mechanism 408 rotatably supports the output shaft 31 and has a pair of fifth tapered roller bearings 495 and sixth tapered roller bearings 496. The fifth tapered roller bearing 495 is provided at the second axial end of the integrated outer ring 461. The fifth tapered roller bearing 495 has a tapered roller as the fifth rolling element 480, an integrated outer ring 461, a fifth outer ring raceway groove 483 formed in the integrated outer ring 461, and a fifth inner ring raceway groove 485 formed in the output shaft 31. The fifth tapered roller bearing 495 is provided such that the apex of the conical surface of the fifth rolling element 480 is located on the first axial side. The fifth outer ring raceway groove 483 formed on the inner circumference of the integrated outer ring 461 is formed so that its inner diameter gradually increases from the first axial side to the second axial side.

[0068] The sixth tapered roller bearing 496 is positioned at a distance of two axial sides from the fifth tapered roller bearing 495. Since the sixth tapered roller bearing 496 has a symmetrical configuration with the fifth tapered roller bearing 495, a detailed explanation of the parts that overlap with the configuration of the fifth tapered roller bearing 495 will be omitted. The sixth tapered roller bearing 496 is provided such that the apex of the conical surface of the sixth rolling element 481, which is a cone-shaped roller, is located on the second axial side. In this embodiment, the outer ring 464 of the sixth tapered roller bearing 496 is formed from a separate part from the integrated outer ring 461. An output mechanism 492 is connected to the output shaft 31 between the fifth tapered roller bearing 495 and the sixth tapered roller bearing 496. As a result, the rotational force (rotational torque) transmitted from the input member 2 to the output member 3 is output to the output mechanism 492.

[0069] According to the reverse input blocking clutch 401 of the fourth embodiment, tapered roller bearings can be used as bearings for the first bearing mechanism 407 and the second bearing mechanism 408. Furthermore, the same effects as in the first embodiment can be achieved in a configuration using tapered roller bearings. Therefore, the versatility of the reverse input blocking clutch 401 can be increased.

[0070] It should be noted that the technical scope of the present invention is not limited to the embodiments described above, and various modifications can be made without departing from the spirit of the invention. For example, in the first embodiment described above, the pressure-bearing surface 62 and the first outer ring raceway groove 73 are formed at the same radial position in the integrated outer ring 61, but this is not limited to this. In the integrated outer ring 61, the radial positions of the pressure-bearing surface 62 and the first outer ring raceway groove 73 may be different from each other. In this case, a second stepped portion (not shown) or the like may be provided between the pressure-bearing surface 62 and the first outer ring raceway groove 73 in the axial direction to create a difference in the inner diameter dimension. The same applies to the third and fourth embodiments.

[0071] In the embodiments described above, a configuration was described in which the pressure-bearing surface 62 is positioned between the first outer ring raceway grooves 73,373,473 and the second outer ring raceway grooves 83,383,483 in the axial direction of the integrated outer ring 61,361,461, but the configuration is not limited to this. For example, the first outer ring raceway grooves 73,373,473, the second outer ring raceway grooves 83,383,483, and the pressure-bearing surface 62 may be arranged in that order from the first side in the axial direction. The order is not limited to this.

[0072] In the embodiments described above, a configuration in which the input shaft 21 and arm portion 23 of the input member 2 are integrally formed has been described, but the invention is not limited to this. The input member 2 may be formed by combining multiple parts. Similarly, the output shaft 31 and insertion portion 32 of the output member 3 may be formed by combining separate parts. In this case, a part of the output shaft 31 may be inserted between the bottom surfaces 52 of a pair of engaging elements 5, and the insertion portion 32, which is formed separately from the output shaft 31, may be externally fitted to the outer circumference of the portion inserted between the pair of engaging elements 5. Alternatively, the output shaft 31 and the insertion portion 32 may be connected to each other in the axial direction.

[0073] In the fourth embodiment described above, the types and sizes of the bearings in the first bearing mechanism 407 and the second bearing mechanism 408 were the same, but this is not limited to this. For example, the sizes of the third tapered roller bearing 493 and the fourth tapered roller bearing 494, and the fifth tapered roller bearing 495 and the sixth tapered roller bearing 496 may differ from each other. In the fourth embodiment, the integrated outer ring 461 and the outer ring 463 of the fourth tapered roller bearing 494 may be the same part. Similarly, the integrated outer ring 461 and the outer ring 464 of the sixth tapered roller bearing 496 may be the same part.

[0074] The reverse input blocking clutches 1,201,301,401 of each embodiment described above may be applied, for example, to a system in which the direction in which the reverse input torque is generated is not constant. Similarly, they may be applied to a system in which the direction in which the input torque is generated is not constant.

[0075] In the embodiments described above, linkless reverse input blocking clutches 1,201, 301, and 401, which do not use a link structure as the reverse input blocking mechanism, were explained as examples, but the invention is not limited to these. A link-type reverse input blocking clutch using a known link mechanism may also be employed as the reverse input blocking mechanism.

[0076] Furthermore, this disclosure may also be a combination of the following configurations. (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 member, A second bearing mechanism that rotatably supports the output member, 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. The outer rings of the first bearing mechanism and the second bearing mechanism are integrated outer rings in which the first outer ring raceway surface on which the rolling elements of the first bearing mechanism roll, the second outer ring raceway surface on which the rolling elements of the second bearing mechanism roll, and the pressed surface are provided as a single unit. Reverse input blocking clutch. (2) The first bearing mechanism and the second bearing mechanism have bearings of different sizes. (1) The reverse input blocking clutch described above. (3) The first bearing mechanism and the second bearing mechanism are of different types of bearings, and the reverse input blocking clutch is as described in (1) or (2). (4) The inner ring raceway surface of the first bearing mechanism is integrally formed on the input member. A reverse input blocking clutch as described in any one of (1) to (3). (5) The inner ring raceway surface of the second bearing mechanism is integrally formed on the output member. A reverse input blocking clutch as described in any one of (1) to (4). (6) The rated load of the bearing in the second bearing mechanism is formed to be greater than at least one of the dynamic rated load and static rated load of the bearing in the first bearing mechanism. A reverse input blocking clutch as described in any one of (1) to (5). (7) The first bearing mechanism and the second bearing mechanism are one of the following: deep groove ball bearings, angular contact ball bearings, four-point contact ball bearings, tapered roller bearings, and cylindrical roller bearings. A reverse input blocking clutch as described in any one of (1) to (6). [Explanation of Symbols]

[0077] 1,201,301,401 Reverse input cutoff clutch 2 Input Members 3 Output component 5 Engagement element 7,207,307,407 First bearing mechanism 8,208,308,408 Second bearing mechanism 21 Input axis 31 Output shaft 51 Pressing surface 55 Input side engaged portion 56 Output side engaged part 61,361,461 Integrated outer ring (outer ring of the first bearing mechanism and outer ring of the second bearing mechanism) 62 Pressed surface 70,370 First rolling element (rolling element of the first bearing mechanism) 73,373 First outer ring raceway groove (first outer ring raceway surface) 75,275,375 First inner ring raceway groove (inner ring raceway surface) 80,380 Second rolling element (rolling element of the second bearing mechanism) 83,383 Second outer ring raceway groove (second outer ring raceway surface) 85,285,385 Second inner ring raceway groove (inner ring raceway surface) 470 Third rolling element (rolling element of the first bearing mechanism) 473 Third outer ring raceway groove (first outer ring raceway surface) 475 Third inner ring raceway groove (inner ring raceway surface) 480 Fifth rolling element (rolling element of the second bearing mechanism) 483 Fifth outer ring raceway groove (second outer ring raceway surface) 485 Fifth inner ring raceway groove (inner ring raceway surface) D1 First radial direction

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 member, A second bearing mechanism that rotatably supports the output member, 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. The outer rings of the first bearing mechanism and the second bearing mechanism are integrated outer rings in which the first outer ring raceway surface on which the rolling elements of the first bearing mechanism roll, the second outer ring raceway surface on which the rolling elements of the second bearing mechanism roll, and the pressed surface are provided as a single unit. The inner diameter of at least one of the first outer ring raceway surface and the second outer ring raceway surface is larger than the inner diameter of the surface to be pressed. Reverse input blocking clutch.

2. The first bearing mechanism and the second bearing mechanism have bearings of different sizes. The reverse input interruption clutch according to claim 1.

3. The first bearing mechanism and the second bearing mechanism have bearings of different types. The reverse input interruption clutch according to claim 1 or claim 2.

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

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

6. The rated load of the bearing in the second bearing mechanism is formed to be greater than at least one of the dynamic rated load and static rated load of the bearing in the first bearing mechanism. The reverse input interruption clutch according to claim 1 or claim 2.

7. The first bearing mechanism and the second bearing mechanism are one of the following: deep groove ball bearings, angular contact ball bearings, four-point contact ball bearings, tapered roller bearings, and cylindrical roller bearings. The reverse input interruption clutch according to claim 1 or claim 2.

Images