Flexible meshing type gear device

Abstract

To appropriately lubricate an excitation body bearing.SOLUTION: A flexible meshing type gear device 1 is provided with an excitation body bearing 15 arranged between an excitation body 10a and an external tooth gear 12. The excitation body bearing 15 includes a first rolling element row 42A in which a plurality of first rolling elements 40A are aligned in a circumferential direction, a first holder 48A for holding the first rolling element row 40A, a second rolling element row 42B arranged offset from the first rolling element row 42A in an axial direction with a plurality of second rolling elements 40B aligned in a circumferential direction, and a second holder 48B for holding the second rolling elements 40B. In the first holder 48A, a first pocket 64A for storing each first rolling element 40A opens toward the second rolling element row 42B in an axial direction. In the second holder 48B, a second pocket 64B for storing each second rolling element 40B opens toward the first rolling element row 42A. A spacer member 70 is arranged between the first rolling element row 42A and the second rolling element row 42B.SELECTED DRAWING: Figure 2

Description

[Technical Field]

[0001] The present invention relates to a flexible mesh gear device. [Background technology]

[0002] BACKGROUND ART Conventionally, a flexible mesh gear device is known that includes an external gear that is flexibly deformed by a vibrator, and a vibrator bearing that is arranged between the vibrator and the external gear (see, for example, Patent Document 1). In this type of flexible mesh gear device, when the vibrator bearing is a double-row type, a space is secured between the two rows of rolling elements, and a lubricant (grease) may be held in this space. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] International Publication No. 2017 / 006442 Summary of the Invention [Problem to be solved by the invention]

[0004] However, simply filling the spaces between the rows of rolling elements with lubricant may result in the lubricant remaining in the spaces and failing to adequately lubricate the rolling elements.

[0005] The present invention has been made in view of the above circumstances, and has an object to provide suitable lubrication for a vibrator bearing. [Means for solving the problem]

[0006] The present invention provides a flexible mesh gear device including a vibrator, a flexible gear that is flexibly deformed by the vibrator, and a vibrator bearing disposed between the vibrator and the flexible gear, The vibrator bearing comprises a first rolling element row in which a plurality of first rolling elements are arranged in a circumferential direction, a first cage that holds the plurality of first rolling elements, a second rolling element row in which a plurality of second rolling elements are arranged in a circumferential direction and are disposed at positions offset in the axial direction from the first rolling element row, and a second cage that holds the plurality of second rolling elements, the first cage includes a plurality of first pockets that accommodate the plurality of first rolling elements, respectively, and the first pockets are open toward the second rolling element row in the axial direction; the second cage includes a plurality of second pockets that accommodate the plurality of second rolling elements, respectively, and the second pockets are open toward the first rolling element row in the axial direction; A spacer member is disposed between the first row of rolling elements and the second row of rolling elements. [Effects of the Invention]

[0007] According to the present invention, the vibrator bearing can be suitably lubricated. [Brief explanation of the drawings]

[0008] [Figure 1] FIG. 1 is a cross-sectional view showing a flexible mesh gear device according to an embodiment. [Figure 2] FIG. 2 is an enlarged view of part E in FIG. [Figure 3] 3 is a diagram showing the positional relationship between a rolling element row, a cage, and a spacer member in the vibrator bearing according to the embodiment. FIG. [Figure 4] FIG. 4 is a diagram showing a modified example of the vibrator bearing according to the embodiment, and is a partial cross-sectional view showing the same part as in FIG. 3. DETAILED DESCRIPTION OF THE INVENTION

[0009] Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

[0010] [Configuration of flexible mesh gear device] FIG. 1 is a cross-sectional view showing a flexible mesh gear device 1 according to this embodiment. In the following, the direction along the rotation axis O1 in the drawing is defined as the "axial direction," the direction perpendicular to the rotation axis O1 as the "radial direction," and the direction of rotation around the rotation axis O1 as the "circumferential direction." Additionally, in the axial direction, the side that is connected to an external driven member (the left side in the drawing) is called the "load side," and the side opposite the load side (the right side in the drawing) is called the "anti-load side."

[0011] As shown in FIG. 1, the flexible mesh gear device 1 is a cylindrical flexible mesh gear device in which an external gear 12 is flexibly deformed to transmit rotational motion around a rotation axis O1. Specifically, the flexible mesh gear device 1 includes a vibrator shaft 10, an external gear 12 that is flexibly deformed by the vibrator shaft 10, a first internal gear 22g and a second internal gear 23g that mesh with the external gear 12, and a vibrator bearing 15. Furthermore, the flexible mesh gear device 1 includes a first casing 22, an internal gear member 23, a second casing 24, a first cover 26, a second cover 27, and a main bearing 33.

[0012] The vibrator shaft 10 is hollow and includes a vibrator 10a having an elliptical outer periphery (having a major axis and a minor axis perpendicular to each other) in cross section perpendicular to the rotation axis O1, and shaft portions 10b and 10c located on both sides of the vibrator 10a in the axial direction and having circular outer peripheries in cross section perpendicular to the rotation axis O1. Note that the elliptical shape is not limited to a strict geometric ellipse but also includes an approximate ellipse. The vibrator shaft 10 rotates around the rotation axis O1, and the center of the outer shape of the cross section perpendicular to the rotation axis O1 of the vibrator 10a coincides with the rotation axis O1. This vibrator shaft 10 is an input shaft connected to a drive source (not shown) such as a motor to input driving force. Alternatively, the vibrator shaft 10 may be a solid shaft.

[0013] The external gear 12 is a cylindrical flexible metal member having teeth on its outer periphery, and is an example of a flexure gear according to the present invention.

[0014] The first internal gear 22g and the second internal gear 23g are arranged so that their axes coincide with the rotation axis O1. The first internal gear 22g and the second internal gear 23g are arranged side by side in the axial direction and mesh with the external gear 12. Specifically, one of the first internal gear 22g and the second internal gear 23g meshes with teeth on one side of the axial center of the external gear 12, and the other meshes with teeth on the other side of the axial center of the external gear 12. The first internal gear 22g is configured by having internal teeth provided at a corresponding location on the inner periphery of the first casing 22. The second internal gear 23g is configured by having internal teeth provided at a corresponding location on the inner periphery of the internal gear member 23.

[0015] The vibrator bearing 15 is disposed between the vibrator 10 a and the external gear 12 . The specific configuration of the vibrator bearing 15 will be described later.

[0016] Spacer rings 36 and 37 are provided on both axial sides of the external gear 12 as restricting members that come into contact with the external gear 12 and restrict its movement in the axial direction.

[0017] The first casing 22 and the second casing 24 are connected to each other by bolts 57 and cover the radial outside of the first internal gear 22g, the second internal gear 23g, and the external gear 12. Of these, the first casing 22 has internal teeth on part of its inner periphery, as described above, and is configured integrally with the first internal gear 22g. Furthermore, when the flexible mesh gear device 1 is connected to an external mating device, the first casing 22 and the second casing 24 are connected to the mating device by being fastened together.

[0018] At least a portion of the internal gear member 23 is disposed radially inside the second casing 24 and radially outside the vibrator shaft 10. As described above, the internal gear member 23 has internal teeth on a portion of its inner periphery, and is configured integrally with the second internal gear 23g.

[0019] The first cover 26 is connected to the first casing 22 with bolts 51, and covers the meshing point between the external gear 12 and the first internal gear 22g from the anti-load side. An input bearing 31 (e.g., a ball bearing) is arranged between the first cover 26 and the shaft portion 10b of the vibrator shaft 10, and the first cover 26 rotatably supports the vibrator shaft 10 via the input bearing 31.

[0020] The second cover 27 is connected to the internal gear member 23 with bolts 52, and covers the meshing point between the external gear 12 and the second internal gear 23g from the load side. An input bearing 32 (e.g., a ball bearing) is arranged between the second cover 27 and the shaft portion 10c of the vibrator shaft 10, and the second cover 27 rotatably supports the vibrator shaft 10 via this input bearing 32. When the flexible mesh gear device 1 is connected to an external mating device, the second cover 27 and the internal gear member 23 are fastened together to connect to a driven member of the mating device, and output reduced rotation to the driven member.

[0021] The main bearing 33 is, for example, a ball bearing, and is arranged between the internal gear member 23 and the second casing 24. The second casing 24 rotatably supports the internal gear member 23 via the main bearing 33. Note that the main bearing 33 is not limited to a ball bearing, and may be, for example, a cross roller bearing. Furthermore, the main bearing 33 does not have to have a dedicated inner ring or outer ring. Furthermore, the main bearing 33 may be a sealed bearing with a lubricant sealed inside.

[0022] [Operation description] In the flexible mesh gear device 1, when the vibrator shaft 10 is driven to rotate by a drive source such as a motor, the movement of the vibrator 10a is transmitted to the external gear 12 via the vibrator bearing 15. At this time, the external gear 12 is restricted to a shape that follows the outer circumferential surface of the vibrator 10a, and is bent into an elliptical shape having a major axis portion and a minor axis portion when viewed from the axial direction. Furthermore, because the external gear 12 is meshed with the fixed first internal gear 22g at the major axis position of the vibrator 10a, it does not rotate at the same speed as the vibrator 10a, and the major axis position of the vibrator 10a moves due to the flexible deformation. For example, if the number of teeth of the external gear 12 is 100 and the number of teeth of the first internal gear 22g is 102, each time the meshing position makes one revolution, the external gear 12 rotates (spins) by an amount equal to the difference in the number of teeth with the first internal gear 22g. With the above number of teeth, the rotational motion of the vibration exciter shaft 10 is transmitted to the external gear 12 after being decelerated at a reduction ratio of 100:2. On the other hand, because the external gear 12 is also meshed with the second internal gear 23g, if the number of teeth of the second internal gear 23g is the same as the number of teeth of the external gear 12, the external gear 12 and the second internal gear 23g will rotate at the same speed. As a result, the rotational motion of the vibrator shaft 10 is reduced at a reduction ratio of 100:2 and transmitted to the internal gear member 23 and the second cover 27, and this rotational motion is output to the driven member.

[0023] [Materials of each component] The materials of the members other than the vibrator bearing 15 are not particularly limited, but in this embodiment they are configured as follows. The vibrator shaft 10, external gear 12, and spacer rings 36, 37 are made of metal materials such as steel. Although not particularly limited, more specifically, the vibrator shaft 10 is made of steel materials such as chromium-molybdenum steel. The vibrator shaft 10 may also be made of an aluminum alloy. The external gear 12 is made of steel materials such as nickel-chromium-molybdenum steel. The spacer rings 36, 37 are made of steel materials such as high-carbon chromium bearing steel.

[0024] The input bearings 31, 32 and the main bearing 33 have inner and outer rings and rolling elements made of metal (for example, high carbon chromium bearing steel, etc.). Each of the bolts 51, 52, 57 is made of metal (for example, rolled steel for general structure, carbon steel wire for cold heading, carbon steel for machine structure, etc.).

[0025] On the other hand, the first casing 22, the internal gear member 23, the second casing 24, the first cover 26 and the second cover 27 are made of, but not limited to, resin (resin-based material).

[0026] In this embodiment, a resin containing reinforcing fibers in its base material is used for the second casing 24, the first cover 26, and the second cover 27. Note that a resin that does not contain reinforcing fibers may also be used. The base resin is, for example, an engineering plastic (general-purpose engineering plastic) that has a heat resistance of about 50 to 60°C. Specific examples include polyamide (PA), polycarbonate (PC), polyacetal (POM), modified polyphenylene ether (m-PPE), and polybutylene terephthalate (PBT). Heat resistance here refers to the temperature at which the gear's performance can be maintained, rather than the temperature at which the gear can statically maintain its shape. Examples of reinforcing fibers include glass fibers, aramid fibers, polyethylene fibers, Zylon fibers, and boron fibers.

[0027] In this embodiment, the resin used for the first casing 22 and the internal gear member 23 contains reinforcing fibers in the base material of the resin. The base resin is preferably a resin with heat resistance of 70°C or higher, for example, a super engineering plastic (special engineering plastic) with heat resistance of 100°C or higher. Specific examples include polyether ether ketone (PEEK), polyamide imide (PAI), polyphenylene sulfide (PPS), polytetrafluoroethylene (PTFE), aromatic polyamide (PPA), liquid crystal polymer (LCP), polysulfone (PSU), polyether sulfone (PES), polyether imide (PEI), polyarylate (PAR), thermoplastic polyimide (TPI), etc. Examples of reinforcing fibers include fibers (such as carbon fibers) that have higher thermal conductivity than the aforementioned reinforcing fibers.

[0028] In addition, the resin and reinforcing fibers used for the first casing 22 and the internal gear member 23 are preferably those with higher thermal conductivity and heat resistance than those of the second casing 24, the first cover 26, and the second cover 27, taking into consideration heat dissipation, but they may also be the same as those exemplified for the second casing 24, the first cover 26, and the second cover 27.

[0029] [Specific configuration of vibrator bearing] Fig. 2 is an enlarged view of part E in Fig. 1. Fig. 3 is an expanded cross section of the vibrator bearing 15 at a certain radial position, and shows the positional relationship of the rolling element rows, cage, and spacer members, which will be described later, in the vibrator bearing 15. As shown in FIGS. 2 and 3, the vibrator bearing 15 in this embodiment is a double-row ball bearing, and includes two rows of rolling elements and an inner ring 44 and an outer ring 46 common to these rows. Specifically, the vibrator bearing 15 comprises a first rolling element row 42A in which a plurality of first rolling elements 40A are arranged circumferentially, a first retainer 48A that holds the plurality of first rolling elements 40A, a second rolling element row 42B that is arranged axially offset from the first rolling element row 42A and in which a plurality of second rolling elements 40B are arranged circumferentially, a second retainer 48B that holds the plurality of second rolling elements 40B, an inner ring 44, and an outer ring 46.

[0030] <Rolling elements> In this embodiment, the first rolling elements 40A are spherical, but may be various types of rolling elements such as rollers, etc. The first rolling element row 42A overlaps with the first internal gear 22g in the axial direction. In this embodiment, the second rolling elements 40B are spherical, but may be various types of rolling elements such as rollers, or may be rolling elements of a different type from the first rolling elements 40A (for example, spherical rollers). The second rolling element row 42B overlaps with the second internal gear 23g in the axial direction. The first rolling element 40A and the second rolling element 40B are made of metal (for example, high carbon chromium bearing steel, etc.).

[0031] <Inner and outer rings> The inner ring 44 is fixed to the vibrator 10a by, for example, adhesive bonding or press fitting. The inner ring 44 is flexible, and when fitted onto the vibrator 10a, it is fixed in an elliptical, bent state. Restriction members 38, 39 are arranged on both axial sides of the inner ring 44 between the input bearings 31, 32 to restrict their axial movement, and are fitted onto the vibrator shaft 10. The inner ring 44 may be integrally formed with the vibrator 10a using the same member. That is, the outer peripheral surface of the vibrator 10a may form the inner ring of the vibrator bearing 15.

[0032] The outer ring 46 is fitted onto the inner periphery of the external gear 12. The outer ring 46 is flexible, and is flexibly deformed via the inner ring 44 and rolling element rows 42A and 42B as the vibrator 10a rotates. The outer ring 46 may be integrally formed from the same material as the external gear 12. In other words, the inner peripheral surface of the external gear 12 may form the outer ring of the vibrator bearing 15.

[0033] The inner ring 44 is formed with a first rolling surface 54A on which the first rolling element 40A rolls, and a second rolling surface 54B on which the second rolling element 40B rolls. The outer ring 46 is formed with a first rolling surface 54A on which the first rolling element 40A rolls, and a second rolling surface 54B on which the second rolling element 40B rolls. The first rolling surface 54A and the second rolling element 40B are groove-shaped, into which portions of the rolling elements 40A, 40B fit. However, the shape of the rolling surfaces 54A, 54B is not particularly limited, and may be, for example, a rectangular groove-shaped surface that matches the rolling elements 40A, 40B, which serve as rollers, or may not be groove-shaped. The first rolling surface 54A restricts the axial movement of the first rolling element 40A, and the second rolling element 40B restricts the axial movement of the second rolling element 40B. The inner ring 44 and the outer ring 46 are made of metal (for example, high carbon chromium bearing steel, etc.).

[0034] <Cage> The first retainer 48A rotatably holds the plurality of first rolling elements 40A around the rotation axis O1 (see FIG. 1), and is rotatable together with the first rolling element row 42A around the rotation axis O1. The first retainer 48A is made of, but is not particularly limited to, resin (a resin-based material). The first retainer 48A comprises a first ring portion 60A positioned on the anti-load side of the first rolling element row 42A, a plurality of first column portions 62A protruding axially from the first ring portion 60A toward the load side, and a plurality of first pockets 64A formed between adjacent first column portions 62A in the circumferential direction and accommodating each of the plurality of first rolling elements 40A.

[0035] The first cage 48A is formed in a comb shape by a first ring portion 60A and a plurality of first column portions 62A. The comb-shaped first cage 48A does not include a ring portion disposed on the load side of the first rolling element row 42A.

[0036] The first pillar portions 62A are arranged at intervals in the circumferential direction. The first pillar portions 62A are cantilevered by the first ring portion 60A, with the load side being the free end. The first pocket 64A opens toward the load side (the second rolling element row 42B side) in the axial direction, and a first opening 66A is formed at the opening of the first pocket 64A.

[0037] The first retainer 48A includes a first drop-out prevention portion 68A that prevents the first rolling element 40A from dropping out of the first pocket 64A via the first opening 66A. The first drop-out prevention portions 68A are formed by protrusions (claw portions) that protrude circumferentially inward of the first pocket 64A at the tip ends of the first pillar portions 62A that are adjacent in the circumferential direction. The first drop-out prevention portions 68A in this embodiment are integrally formed from the same material as the first pillar portions 62A, but may also be formed separately from the first pillar portions 62A.

[0038] The second retainer 48B rotatably holds the plurality of second rolling elements 40B around the rotation axis O1 (see FIG. 1), and is rotatable together with the second rolling element row 42B around the rotation axis O1. The second retainer 48B is made of, but is not particularly limited to, resin (a resin-based material). The second retainer 48B includes a second ring portion 60B disposed on the load side of the second rolling element row 42B, a plurality of second pillar portions 62B protruding from the second ring portion 60B toward the anti-load side in the axial direction, and a plurality of second pockets 64B formed between adjacent second pillar portions 62B in the circumferential direction to accommodate each of the plurality of second rolling elements 40B. In this embodiment, the positional relationship between the components of the second retainer 48B (the second ring portion 60B, the second pillar portions 62B, the second pockets 64B) when viewed from the axial direction is the same as the positional relationship between the components of the first retainer 48A (the first ring portion 60A, the first pillar portions 62A, the first pockets 64A).

[0039] The second retainer 48B is formed in a comb shape by a second ring portion 60B and a plurality of second pillar portions 62B. The comb-shaped second retainer 48B does not include a ring portion disposed on the anti-load side with respect to the second rolling element row 42B.

[0040] The second pillar portions 62B are arranged at intervals in the circumferential direction. The second pillar portions 62B are cantilevered by the second ring portion 60B, with the anti-load side being the free end. The second pocket 64B opens toward the anti-load side (the first rolling element row 42A side) in the axial direction, and a second opening 66B is formed at the opening of the second pocket 64B.

[0041] The second retainer 48B includes a second drop-out prevention portion 68B that prevents the second rolling element 40B from dropping out of the second pocket 64B via the second opening 66B. The second drop-out prevention portions 68B are formed by protrusions (claw portions) that protrude circumferentially inward of the second pocket 64B at the tip ends of the second pillar portions 62B that are adjacent in the circumferential direction. In this embodiment, the second drop-out prevention portions 68B are integrally formed from the same material as the second pillar portions 62B, but may be formed separately from the second pillar portions 62B.

[0042] <Spacer member> Inside the vibrator bearing 15, a spacer member 70 is arranged in a bearing space S between the first rolling element row 42A and the second rolling element row 42B. The spacer member 70 is formed in a substantially cylindrical shape and is disposed in the bearing internal space S so as to be movable in the radial and axial directions. Specifically, the spacer member 70 is disposed between the outer periphery of the inner ring 44 and the inner periphery of the outer ring 46 so as to be movable in the radial direction. In other words, the inner diameter of the spacer member 70 has a predetermined clearance relative to the outer diameter of the inner ring 44, and the outer diameter of the spacer member 70 has a predetermined clearance relative to the inner diameter of the outer ring 46. Here, the terms "inner ring" and "outer ring" are interchangeable with the vibrator 10a or the external gear 12 when they are provided integrally as the same member. Furthermore, the spacer member 70 is disposed between the first rolling element 40A and the second rolling element 40B so as to be movable in the axial direction. The ends of the first rolling element 40A and the second rolling element 40B protrude further inward in the axial direction of the vibrator bearing 15 than the retainers 48A and 48B that retain them, respectively. Therefore, the spacer member 70 is positioned in a different axial direction from both the first retainer 48A and the second retainer 48B. In other words, the spacer member 70 does not come into contact with either the first retainer 48A or the second retainer 48B. The material of the spacer member 70 is not particularly limited, and may be, for example, metal or resin. However, it is preferable that the spacer member 70 be made of resin (a resin-based material) because contact with the metallic rolling elements 40A, 40B may occur, the spacer member 70 is lightweight, and the spacer member 70 has self-lubricating properties.

[0043] A lubricant (not shown) is accommodated (placed) inside the vibrator bearing 15. From the viewpoint of retaining the lubricant inside the bearing internal space S, it is preferable to use grease with a certain degree of hardness. From this viewpoint, the consistency number of the grease is preferably No. 1 or higher, and more preferably No. 1 to No. 2. The consistency number here refers to the number that classifies greases according to the range of worked consistency as specified in JIS K2220. However, the lubricant is not limited to grease, and may be lubricating oil or the like.

[0044] [Technical effect of this embodiment] As described above, according to this embodiment, the spacer member 70 is disposed in the bearing space S between the first rolling element row 42A and the second rolling element row 42B in the vibrator bearing 15. This narrows the bearing space S, making it easier for the lubricant filled in the bearing space S to be supplied to the raceway surfaces (rolling surfaces 54A, 54B) of the rolling elements 40A, 40B. Therefore, even if the lubricant is a relatively hard grease, for example, the vibrator bearing 15 can be suitably lubricated.

[0045] Furthermore, according to this embodiment, the spacer member 70 is disposed between the outer periphery of the inner ring 44 and the inner periphery of the outer ring 46 so as to be movable in the radial direction. As a result, the spacer member 70 moves in the bearing space S in accordance with the movement or posture change of the flexible mesh gear device 1 itself. As a result, the grease in the bearing space S is more easily supplied to the raceway surfaces (rolling surfaces 54A, 54B) of the rolling elements 40A, 40B.

[0046] [others] Although the embodiments of the present invention have been described above, the present invention is not limited to the above-described embodiments. For example, in the above embodiment, the vibrator bearing 15 is a double-row bearing. However, as long as the vibrator bearing 15 has at least two rows of rolling elements, the inner ring and outer ring do not have to be common to these rows of rolling elements. Specifically, as shown in Fig. 4, the vibrator bearing 15 may be configured with two rows of single-row bearings. In other words, the vibrator bearing 15 may be configured such that the first inner ring 44A and first outer ring 46A that support the first rolling element 40A are separate from the second inner ring 44B and second outer ring 46B that support the second rolling element 40B.

[0047] The vibrator bearing may also include three or more rows of rolling elements. In this case, a spacer member may be disposed between each of the rows of rolling elements adjacent to each other in the axial direction.

[0048] In the above embodiment, a so-called cylindrical type was exemplified as the flexible mesh gear device 1. However, the present invention is not limited to this and can also be applied to, for example, a so-called cup type or top hat type flexible mesh gear device. In addition, the details shown in the above embodiment can be modified as appropriate without departing from the spirit of the invention. [Explanation of symbols]

[0049] 1. Flexible mesh gear device 10 Vibrator axis 10a Vibrator 12 External gear (flexure gear) 15 Vibrator bearing 40A First rolling element 40B 2nd rolling element 42A First rolling element row 42B Second rolling element row 44 Inner Circle 44A First inner ring 44B Second inner ring 46 Outer ring 46A First outer ring 46B Second outer ring 48A 1st retainer 48B 2nd retainer 54A 1st raceway 54B 2nd raceway 60A 1st ring part 60B Second Ring Section 62A 1st pillar section 62B 2nd pillar section 64A First pocket 64B Second pocket 66A 1st opening 66B 2nd opening 68A 1st fall prevention part 68B Second fall prevention part 70 Spacer member S Bearing internal space

Claims

1. A flexible mesh gear device comprising: a vibration exciter; a flexible gear that is flexibly deformed by the vibration exciter; and a vibration exciter bearing that is disposed between the vibration exciter and the flexible gear, The vibrator bearing comprises a first rolling element row in which a plurality of first rolling elements are arranged in a circumferential direction, a first cage that holds the plurality of first rolling elements, a second rolling element row in which a plurality of second rolling elements are arranged in a circumferential direction and are disposed at positions offset in the axial direction from the first rolling element row, and a second cage that holds the plurality of second rolling elements, the first cage includes a plurality of first pockets that accommodate the plurality of first rolling elements, each of the first pockets being open toward the second rolling element row in the axial direction; the second cage includes a plurality of second pockets that accommodate the plurality of second rolling elements, and the second pockets are open toward the first rolling element row in the axial direction; a spacer member is disposed between the first row of rolling elements and the second row of rolling elements; Flexible mesh gearing.

2. the vibrator bearing has an outer ring common to the first rolling element row and the second rolling element row, 2. The flexible mesh gear device according to claim 1.

3. the vibrator bearing has an inner ring common to the first rolling element row and the second rolling element row, 2. The flexible mesh gear device according to claim 1.

4. The spacer member is disposed between the outer periphery of the inner ring and the inner periphery of the outer ring so as to be movable in the radial direction.

2. The flexible mesh gear device according to claim 1.

5. the spacer member does not contact either the first retainer or the second retainer; 2. The flexible mesh gear device according to claim 1.

6. Grease having a consistency number of 1 or more is disposed between the first row of rolling elements and the second row of rolling elements.

2. The flexible mesh gear device according to claim 1.

Images