Driven bearing

Abstract

The driven bearing (1) has: an inner member (10) including a first body portion (50) and a flange portion (52); an outer ring (20); a plurality of rolling elements (40); and a first sealing member (30A), including an annular first portion disposed between the outer peripheral surface (52A) of the flange portion (52) and a first surface (22A), and at least a portion thereof forming a sealing structure with the outer ring (20). The first portion has a shape in which the outer diameter in the axial direction increases as it approaches the end face (52B) of the flange portion (52) opposite to the first rolling surface (51A).

Description

Technical Field

[0001] This disclosure relates to driven bearings.

[0002] This application claims priority based on Japanese Application No. 2020-052971, filed on March 24, 2020, the entire contents of which are incorporated herein by reference. Background Technology

[0003] A driven bearing is known in which the outer ring contacts and rotates with other components (see, for example, Patent Document 1). Patent Document 1 discloses a driven bearing comprising: an inner member having a first rolling surface; an outer ring having a second rolling surface facing the first rolling surface; a plurality of rolling elements configured to roll on both the first and second rolling surfaces; and a sealing member disposed between the inner member and the outer ring. The inner member in the driven bearing has an annular flange.

[0004] Existing technical documents

[0005] Patent documents

[0006] Patent document 1: Japanese Patent Application Publication No. 2011-33142. Summary of the Invention

[0007] The problem that the invention aims to solve

[0008] In the driven bearing disclosed in Patent Document 1, assembly is performed by inserting the inner member into the outer ring, with the sealing member disposed on the flange of the inner member. The sealing member is configured to form a sealing structure with the outer ring. This sealing structure is designed to reduce grease leakage from the interior of the driven bearing or the ingress of foreign matter, resulting in a gap between the outer ring and the sealing member, or contact between the outer ring and the sealing member. In the driven bearing of Patent Document 1, the outer ring may be hooked by the sealing member when the inner member is inserted, making it difficult to assemble the outer ring during assembly. Therefore, one object of the present invention is to provide a driven bearing that is easy to assemble.

[0009] Technical means to solve the problem

[0010] The driven bearing disclosed herein comprises: an inner member including a first body portion and a flange portion, the first body portion having a rod-like shape and an annular first rolling surface on its outer peripheral surface, the flange portion having a disc-like shape and disposed on the outer peripheral surface of one end of the first body portion and having a central axis coaxial with the first body portion, the diameter of the flange portion being larger than the diameter of the first body portion; an outer ring having an annular first surface facing the outer peripheral surface of the flange portion and an annular second rolling surface facing the first rolling surface on its inner peripheral surface; a plurality of rolling elements configured to roll on the first rolling surface and the second rolling surface; and a first sealing member including an annular first portion disposed between the outer peripheral surface of the flange portion and the first surface, and at least a portion forming a sealing structure with the outer ring. The first portion has a shape in which the outer diameter increases axially as it approaches the end face of the flange portion opposite to the first rolling surface, i.e., the first end face side.

[0011] Invention Effects

[0012] Based on the aforementioned driven bearing, the assembly of the driven bearing can be made easier. Attached Figure Description

[0013] Figure 1 This is a schematic three-dimensional diagram showing the structure of the driven bearing.

[0014] Figure 2 This is a schematic cross-sectional view showing the structure of the driven bearing.

[0015] Figure 3 This is a schematic cross-sectional view showing the structure of the driven bearing.

[0016] Figure 4 It is a schematic three-dimensional diagram showing the structure of the sealing component.

[0017] Figure 5 This is a schematic cross-sectional view used to illustrate the assembly method of the driven bearing.

[0018] Figure 6 This is a schematic cross-sectional view used to illustrate the assembly method of the driven bearing.

[0019] Figure 7 This is a schematic cross-sectional view used to illustrate the assembly method of the driven bearing.

[0020] Figure 8 This is a schematic cross-sectional view used to illustrate the assembly method of the driven bearing.

[0021] Figure 9 This is a schematic cross-sectional view showing the structure of the driven bearing in other embodiments.

[0022] Figure 10 It is an enlarged representation Figure 9A rough cross-sectional view of region α. Detailed Implementation

[0023] [Summary of Implementation Methods]

[0024] First, embodiments of the present disclosure will be described. The driven bearing of the present disclosure includes: an inner member comprising a first body portion and a flange portion, the first body portion having a rod-like shape and an annular first rolling surface on its outer peripheral surface, the flange portion having a disc-like shape and disposed on the outer peripheral surface of one end of the first body portion and having a central axis coaxial with the first body portion, the diameter of the flange portion being larger than the diameter of the first body portion; an outer ring having an annular first surface facing the outer peripheral surface of the flange portion and an annular second rolling surface facing the first rolling surface on its inner peripheral surface; a plurality of rolling elements configured to roll on the first rolling surface and the second rolling surface; and a first sealing member comprising an annular first portion disposed between the outer peripheral surface of the flange portion and the first surface, and at least a portion forming a sealing structure with the outer ring. The first portion has a shape in which the outer diameter increases axially as it approaches the end face of the flange portion opposite to the first rolling surface, i.e., the first end face side.

[0025] The driven bearing disclosed herein has a first sealing member. The first sealing member includes an annular first portion disposed between the outer peripheral surface of the flange portion and a first surface, forming a sealing structure with the outer ring. The first portion has a shape in which the outer diameter increases as it approaches the first end face. The driven bearing described above is assembled by inserting the inner member of the first sealing member disposed in the flange portion into the outer ring. By including the first portion, the first sealing member guides the outer ring when the inner member is inserted into the outer ring, reducing the possibility of the outer ring being hooked by the first sealing member. Therefore, the driven bearing according to the present disclosure facilitates the assembly of the driven bearing.

[0026] In the aforementioned driven bearing, the first portion can also be a tapered shape whose outer diameter increases as it approaches the first end face. This allows the outer ring to be more reliably guided by the first portion when the inner member is inserted, further reducing the likelihood of the outer ring being hooked by the first sealing member. Therefore, the driven bearing according to this disclosure simplifies the assembly of the driven bearing.

[0027] In the aforementioned driven bearing, the diameter of the second rolling surface may be smaller than the diameter of the first surface. The outer ring connects the second rolling surface and the first surface, and its inner circumferential surface may further have an annular second surface facing the second end face of the flange portion, which is opposite to the first end face in the axial direction. The first sealing member also includes an annular second portion connected to the first portion and disposed between the second end face and the second surface. By including the second portion in the first sealing member, contact between the second end face of the flange portion and the second surface of the outer ring can be suppressed when an axial load is applied to the driven bearing. Therefore, wear and other phenomena caused by contact between the second end face of the flange portion and the second surface of the outer ring can be suppressed.

[0028] In the aforementioned driven bearing, the maximum height roughness Rz of the second end face of the flange portion can also be less than 12.5 μm. By adopting such a structure, the friction between the first sealing member and the second end face of the flange portion can be reduced when an axial load is applied to the driven bearing 1.

[0029] In the aforementioned driven bearing, the first sealing member may also include a first sealing end face located axially on the first end face side. The first sealing end face may also have a shape where the outer diameter decreases as it approaches the first end face. In this way, even if dust accumulates on the first sealing end face, due to the aforementioned shape, the dust accumulated on the first sealing end face can easily slide off towards the first end face side. Therefore, dust is less likely to accumulate on the first sealing end face. Thus, the possibility of dust on the first sealing end face crossing the outer peripheral surface of the first sealing member and intruding into the bearing interior can be reduced, thereby improving the dustproof performance of the driven bearing.

[0030] In the aforementioned driven bearing, the first sealing end face can also be a tapered shape whose outer diameter decreases as it approaches the first end face side. This allows dust accumulated on the first sealing end face to slide more reliably and easily towards the first end face side. Therefore, dust is less likely to accumulate on the first sealing end face. Consequently, the possibility of dust on the first sealing end face crossing the outer circumference of the first sealing member and intruding into the bearing interior is reduced, thus improving the dustproof performance of the driven bearing.

[0031] In the aforementioned driven bearing, the first sealing end face can also extend axially to the first end face. This allows dust accumulated on the first sealing end face of the aforementioned shape to smoothly slide off to the first end face, preventing dust from easily accumulating in the area between the first sealing end face and the outer peripheral surface of the flange. Therefore, the dustproof performance of the driven bearing can be improved.

[0032] In the aforementioned driven bearing, when viewed from the first rolling surface of the first main body, the inner member further includes a ring that is embedded in contact with the outer peripheral surface opposite to the flange portion, and has a central axis coaxial with the first main body. The inner peripheral surface of the outer ring may also have: an annular third surface facing the outer peripheral surface of the ring and having a diameter larger than the diameter of the second rolling surface; and an annular fourth surface connecting the second rolling surface and the third surface, facing the end face of the ring on the first rolling surface side, i.e., the third end face, in the axial direction. The driven bearing may also have a second sealing member, which includes: an annular third portion disposed between the outer peripheral surface of the ring and the third surface, and at least a portion forming a sealing structure with the outer ring; and an annular fourth portion connected to the third portion and disposed between the third end face and the fourth surface. The third portion may also have a shape in which the outer diameter increases in the axial direction as it approaches the end face of the ring on the side opposite to the third end face, i.e., the fourth end face side.

[0033] With the first main body inserted into the outer ring, a ring equipped with a second sealing member is mounted on the first main body. Because the second sealing member includes a third portion, when the ring with the second sealing member is mounted on the first main body, the ring is guided by the outer circumferential surface of the third portion, reducing the possibility of the second sealing member being hooked by the outer ring. Therefore, the ring with the second sealing member can be easily mounted on the first main body. Furthermore, because the second sealing member includes a fourth portion, contact between the third end face and the fourth surface of the ring can be suppressed when an axial load is applied to the driven bearing. Therefore, wear and other damage caused by contact between the third end face of the ring and the fourth surface of the outer ring can be suppressed.

[0034] In the aforementioned driven bearing, the third portion can also be a tapered shape whose outer diameter increases as it approaches the fourth end face. This allows the ring to be more reliably guided by the outer circumferential surface of the third portion when it is installed on the first body portion, reducing the likelihood of the second sealing member being hooked by the outer ring. Therefore, the driven bearing according to this disclosure simplifies the assembly of the driven bearing.

[0035] In the aforementioned driven bearing, the maximum height roughness Rz of the third end face of the ring can also be less than 12.5 μm. By adopting such a structure, the friction between the second sealing member and the third end face of the ring can be reduced when an axial load is applied to the driven bearing.

[0036] In the aforementioned driven bearing, the second sealing member may also include a second sealing end face located axially on the fourth end face side. The second sealing end face may also have a shape where the outer diameter decreases as it approaches the fourth end face. In this way, even if dust accumulates on the second sealing end face, due to the aforementioned shape, the dust accumulated on the second sealing end face can easily slide off towards the fourth end face side. Therefore, dust is less likely to accumulate on the second sealing end face. Thus, the possibility of dust on the second sealing end face crossing the outer circumference of the second sealing member and intruding into the bearing interior can be reduced, thereby improving the dustproof performance of the driven bearing.

[0037] In the aforementioned driven bearing, the second sealing end face can also be a tapered shape whose outer diameter decreases as it approaches the fourth end face. This allows dust accumulated on the second sealing end face to slide more reliably and easily towards the fourth end face. Therefore, dust is less likely to accumulate on the second sealing end face. Consequently, the possibility of dust on the second sealing end face crossing the outer circumference of the second sealing member and intruding into the bearing interior is reduced, further improving the dustproof performance of the driven bearing.

[0038] In the aforementioned driven bearing, the second sealing end face can also extend axially to a fourth end face. This allows dust accumulated on the second sealing end face of the aforementioned shape to smoothly slide off towards the fourth end face, preventing dust from easily accumulating in the area between the second sealing end face and the outer circumferential surface of the ring. Therefore, the dustproof performance of the driven bearing can be improved.

[0039] In the aforementioned driven bearing, the material constituting the second sealing member can be at least one resin selected from the group consisting of polyetheretherketone, polyacetal, and polyamide. The aforementioned resins are suitable as materials constituting the second sealing member.

[0040] In the aforementioned driven bearing, the material constituting the first sealing member can be at least one resin selected from the group consisting of polyetheretherketone, polyacetal, and polyamide. The aforementioned resin is suitable as a material constituting the first sealing member.

[0041] In the aforementioned driven bearing, the rolling elements can also be rollers. This allows for the suppression of the driven bearing's cross-sectional height and facilitates sufficient load bearing capacity.

[0042] [Specific examples of implementation methods]

[0043] Next, an example of a specific embodiment of the driven bearing of this disclosure will be described with reference to the accompanying drawings. In the following drawings, the same or equivalent parts are labeled with the same reference numerals and repeated descriptions thereof are omitted.

[0044] Figure 1This is a schematic perspective view showing the structure of the driven bearing in one embodiment of the present disclosure. From the viewpoint showing the internal structure, in... Figure 1 The image shows a portion of a component partially cut out. Figure 1 In the diagram, the shaded areas correspond to the cross-sections. Figure 2 This is a schematic cross-sectional view showing the structure of the driven bearing. Figure 2 It represents a cross-section including the rotating shaft of the driven bearing. Figure 3 It is an enlarged representation Figure 2 A rough cross-sectional view of region α.

[0045] Reference Figures 1-3 In this embodiment, the driven bearing 1 includes an inner member 10, an outer ring 20, a first sealing member 30A, a second sealing member 30B, and a plurality of rollers 40 as rolling elements. In this embodiment, the driven bearing 1 is a full roller bearing without a retainer for the rollers 40. The inner member 10 includes a first body portion 50, a flange portion 52 disposed on the outer peripheral surface of one end of the first body portion 50, and a ring 60. The inner member 10 is made of steel. The first body portion 50 has a rod-shaped (solid cylindrical) shape.

[0046] A hexagonal hole 53A with a regular hexagonal prism shape is formed at one end of the first main body 50, including a region that intersects (or is orthogonal in this embodiment) the central axis of the first main body 50. A threaded portion 54 with a helical thread groove is disposed on the outer peripheral surface of the other end of the first main body 50. With such a structure, when the driven bearing 1 is installed, for example, by screwing the threaded portion 54 into the threaded hole (not shown) formed in the retaining member that holds the driven bearing 1 and inserting the tip of a hexagonal wrench into the hexagonal hole 53A and tightening it, or by passing the inner member 10 through the outer shell hole and screwing the nut into the threaded portion 54, the driven bearing 1 can be fixed to the retaining member.

[0047] The first main body portion 50 has a large-diameter portion 51 with a diameter slightly larger than other regions. The large-diameter portion 51 is axially positioned closer to the flange portion 52 than the center. The large-diameter portion 51 is axially positioned between the flange portion 52 and the threaded portion 54 (described later). The outer peripheral surface of the large-diameter portion 51 includes a first rolling surface 51A with a cylindrical shape. That is, the first main body portion 50 has an annular first rolling surface 51A on its outer peripheral surface 50A.

[0048] The first main body portion 50 has an opening 56A at its end opposite to the flange portion 52 in the axial direction, and a first hole 56 extending axially is formed therein. The first main body portion 50 also has an opening 57A on its outer peripheral surface 50A, and a second hole 57 extending radially is formed therein. The second hole 57 communicates with the first hole 56. The first main body portion 50 has an opening 58A on the first rolling surface 51A of the large-diameter portion 51, and a third hole 58 extending radially is formed therein. The third hole 58 communicates with the first hole 56. The first main body portion 50 has an annular protrusion 501 that is axially disposed between the large-diameter portion 51 and the threaded portion 54, and has a diameter smaller than that of the large-diameter portion 51.

[0049] The flange portion 52 has a disc-shaped annular shape with a diameter larger than that of the first main body portion 50. The flange portion 52 has a central axis coaxial with the first main body portion 50. The diameter of the large-diameter portion 51 is smaller than the diameter of the flange portion 52. The flange portion 52 includes an outer peripheral surface 52A, a first end surface 52B as one axial end surface, and a second end surface 52C on the side opposite to the first end surface 52B. The first end surface 52B and the second end surface 52C are arranged parallel to each other. The first end surface 52B and the second end surface 52C have a planar shape. In this embodiment, the maximum height roughness Rz of the second end surface 52C is 12.5 μm or less. The maximum height roughness Rz of the second end surface 52C is preferably 8 μm or less, more preferably 7 μm or less, and particularly preferably 6.3 μm or less. The maximum height roughness Rz can be measured, for example, based on JIS B0601. In this embodiment, for example, by grinding the second end face 52C of the flange portion 52, a flange portion 52 having a second end face 52C that satisfies the aforementioned maximum height roughness Rz can be formed. It should be noted that the second end face 52C can also be processed by known methods other than grinding to satisfy the aforementioned maximum height roughness Rz.

[0050] When viewed axially from the large-diameter portion 51 of the first main body portion 50, the ring 60 is embedded in the outer peripheral surface of the protrusion 501 on the side opposite to the flange portion 52. The ring 60 is fixed to the outer peripheral surface of the protrusion 501 by a known method. The ring 60 has an annular shape. The ring 60 includes an outer peripheral surface 61, an inner peripheral surface 62, a third end surface 63 as one end surface in the axial direction, and a fourth end surface 64 on the side opposite to the third end surface 63. The outer peripheral surface 61 and the inner peripheral surface 62 are concentric cylindrical surfaces. The third end surface 63 and the fourth end surface 64 are arranged parallel to each other. (Refer to...) Figure 3The ring 60 is arranged such that its third end face 63 contacts the stepped portion, i.e., the stepped surface 51B, on the axial side opposite to the flange portion 52 of the large-diameter portion 51. The ring 60 is pressed into the first main body portion 50 and fixed thereto. In this embodiment, the maximum height roughness Rz of the third end face 63 of the ring 60 is 12.5 μm or less. The maximum height roughness Rz of the third end face 63 is preferably 8 μm or less, more preferably 7 μm or less, and particularly preferably 6.3 μm or less. The maximum height roughness Rz can be measured, for example, based on JIS B0601. In this embodiment, for example, by grinding the third end face 63 of the ring 60, it is possible to manufacture a ring 60 having a third end face 63 that satisfies the above-mentioned maximum height roughness Rz. By arranging the flange portion 52 and the ring 60 axially separated from the large-diameter portion 51, it is possible to prevent the outer ring 20 and the plurality of rollers 40 from axially slipping off. It should be noted that the third end face 63 can also be machined by known methods other than grinding to meet the above-mentioned maximum height roughness Rz.

[0051] The inner component 10 is made of steel such as carbon steel for mechanical construction, alloy steel for mechanical construction, or bearing steel. In this embodiment, the inner component 10 is made of high-carbon chromium bearing steel. Heat treatment may also be performed on the area of ​​the first main body 50, including the first rolling surface 51A. For example, induction hardening and tempering may be performed. Grinding may also be performed on the area of ​​the first main body 50, including the first rolling surface 51A. In this embodiment, the flange portion 52 is not heat-treated.

[0052] The outer ring 20 includes an inner peripheral surface 21A, an outer peripheral surface 21B, a first outer ring end face 21C serving as one end face in the axial direction, and a second outer ring end face 21D serving as the other end face in the axial direction. The inner peripheral surface 21A includes a second rolling surface 22C opposite to the first rolling surface 51A of the first main body portion 50. That is, the outer ring 20 has a second rolling surface 22C on the inner peripheral surface 21A. The second rolling surface 22C has a cylindrical shape. In this embodiment, the outer peripheral surface 21B has a cylindrical shape. The first outer ring end face 21C and the second outer ring end face 21D are annular planes. The first outer ring end face 21C and the second outer ring end face 21D are orthogonal to the axial direction. The first outer ring end face 21C and the second outer ring end face 21D are arranged parallel to each other. In the driven bearing 1, the first outer ring end face 21C and the second outer ring end face 21D are configured to be exposed to the outside.

[0053] The inner circumferential surface 21A includes, in the axial direction, an annular first surface 22A and an annular third surface 22D arranged to clamp the second rolling surface 22C. The first surface 22A is disposed on the inner circumferential surface 21A at one end of the outer ring 20. The third surface 22D is disposed on the inner circumferential surface 21A at the other end of the outer ring 20. The diameters of the first surface 22A and the third surface 22D are larger than the diameter of the second rolling surface 22C. The first surface 22A and the third surface 22D have a cylindrical shape with a central axis coaxial with the rotation axis. The first surface 22A faces the outer circumferential surface 52A of the flange portion 52. The third surface 22D faces the outer circumferential surface 61 of the ring 60. The inner circumferential surface 21A also includes a second surface 22B connecting the first surface 22A and the second rolling surface 22C, and a fourth surface 22E connecting the third surface 22D and the second rolling surface 22C. The second surface 22B and the fourth surface 22E are annular planes. The second surface 22B and the fourth surface 22E are orthogonal to the axial direction. The second surface 22B and the fourth surface 22E are arranged parallel to each other. The second surface 22B is opposite to the second end surface 52C of the flange portion 52. The fourth surface 22E is opposite to the third end surface 63 of the ring 60.

[0054] The outer ring 20 is made of steel such as carbon steel for mechanical construction, alloy steel for mechanical construction, or bearing steel. In this embodiment, the outer ring 20 is made of high-carbon chromium bearing steel. Heat treatment may also be performed on the region of the outer ring 20, including the second rolling surface 22C. For example, induction hardening and tempering may be performed. Grinding may also be performed on the region including the second rolling surface 22C.

[0055] Reference Figures 2-4 The first sealing member 30A and the second sealing member 30B include an annular portion 31 as a first part and a third part, and a protrusion 32 as a second part and a fourth part, respectively. The annular portion 31 has a circular shape. The annular portion 31 includes an outer peripheral surface 31A and an inner peripheral surface 31B. The outer peripheral surface 31A has a conical shape. The inner peripheral surface 31B has a cylindrical shape. The outer peripheral surface 31A and the inner peripheral surface 31B have a central axis coaxial with the axis of rotation. The outer peripheral surface 31A of the annular portion 31 has a conical shape whose diameter increases towards one end face. The outer diameter of the annular portion 31 is smaller than the inner diameter of the first surface 22A and the third surface 22D. The protrusion 32 is connected to the annular portion 31. The protrusion 32 protrudes radially inward from the other end face of the annular portion 31. The protrusion 32 has a circular shape. The protrusion 32 has a flat annular shape. The protrusion 32 is configured to be coaxial with the annular portion 31. The protrusion 32 includes an axial end face 32A and an end face 32B on the opposite side of the end face 32A.

[0056] Reference Figure 3The annular portion 31 of the first sealing member 30A is radially disposed between the outer peripheral surface 52A of the flange portion 52 and the first surface 22A. A gap is formed between the outer peripheral surface 31A of the annular portion 31 and the first surface 22A. It should be noted that a gap (not shown) is formed between the annular portion 31 and the outer peripheral surface 52A of the flange portion 52. The annular portion 31 and the flange portion 52 are fitted together with the gap. The first sealing member 30A is a so-called non-contact seal. The protrusion 32 in the first sealing member 30A is axially disposed between the second end face 52C and the second surface 22B of the flange portion 52. The end face 32A of the protrusion 32 can contact the second end face 52C of the flange portion 52. The end face 32B of the protrusion 32 is axially opposite to the second surface 22B. By forming gaps between the first sealing member 30A and the outer ring 20, and between the first sealing member 30A and the flange portion 52, the increase in sliding resistance and rotational torque of the outer ring 20 caused by the provision of the first sealing member 30A can be reduced, allowing the outer ring 20 to rotate smoothly. It should be noted that a structure can also be configured such that the outer peripheral surface 31A contacts the first surface 22A without forming a gap. Furthermore, the flange portion 52 and the first sealing member 30A can also be a structure where they are tightly fitted without any gap.

[0057] The annular portion 31 of the second sealing member 30B is radially disposed between the outer peripheral surface 61 and the third surface 22D of the ring 60. A gap is formed between the outer peripheral surface 31A and the third surface 22D of the annular portion 31 of the second sealing member 30B. It should be noted that a gap (not shown) is formed between the annular portion 31 and the outer peripheral surface 61 of the ring 60. The annular portion 31 and the ring 60 are fitted with the gap. The second sealing member 30B is a so-called non-contact seal. The protrusion 32 of the second sealing member 30B is axially disposed between the third end face 63 and the fourth surface 22E of the ring 60. The end face 32A of the protrusion 32 can contact the third end face 63 of the ring 60. The end face 32B of the protrusion 32 is axially opposed to the fourth surface 22E. By forming gaps between the second sealing member 30B and the outer ring 20, and between the second sealing member 30B and the ring 60, the increase in sliding resistance and rotational torque of the outer ring 20 caused by the provision of the second sealing member 30B can be reduced, allowing the outer ring 20 to rotate smoothly. It should be noted that a structure can also be configured such that the outer peripheral surface 61 contacts the third surface 22D without forming a gap. Alternatively, the ring 60 and the second sealing member 30B can also be configured to fit tightly without any gap.

[0058] The annular portion 31 of the first sealing member 30A includes a first sealing end face 31C located axially on the side of the first end face 52B. The annular portion 31 of the second sealing member 30B includes a second sealing end face 31D located axially on the side of the fourth end face 64. The first sealing end face 31C and the second sealing end face 31D are annular planes. The first sealing end face 31C and the second sealing end face 31D are orthogonal to the axial direction. The first sealing end face 31C and the second sealing end face 31D are arranged parallel to each other. The first sealing end face 31C is arranged axially closer to the bearing interior side than the first outer ring end face 21C. In this embodiment, the first surface 22A of the outer ring 20, the outer peripheral surface 52A of the flange portion 52, and the first sealing end face 31C of the first sealing member 30A form a space 71 with an axial opening. The second sealing end face 31D is arranged axially closer to the bearing interior side than the second outer ring end face 21D. In this embodiment, a space 72 with an axial opening is formed by the third surface 22D of the outer ring 20, the outer peripheral surface 61 of the ring 60, and the second sealing end face 31D of the second sealing member 30B.

[0059] The materials constituting the first sealing member 30A and the second sealing member 30B are at least one resin selected from the group consisting of polyetheretherketone, polyacetal, and polyamide. In this embodiment, the material constituting the first sealing member 30A and the second sealing member 30B is, for example, nylon 66. The material constituting the first sealing member 30A and the second sealing member 30B may also be nylon 66 with added molybdenum disulfide, etc. It may include molybdenum disulfide, etc., other than nylon 66. As the material constituting the first sealing member 30A and the second sealing member 30B, if nylon 66 is used, the first sealing member 30A and the second sealing member 30B are soft and easily worn. By setting the maximum height roughness Rz of the second end face 52C and the third end face 63 to 6.3 μm or less, the wear of the first sealing member 30A and the second sealing member 30B can be further reduced.

[0060] Reference Figures 2-4 Multiple rollers 40 are configured to roll on a first rolling surface 51A and a second rolling surface 22C. Each roller 40 has a solid cylindrical shape. Each roller 40 includes a cylindrical outer peripheral surface 41 and a pair of spherical end faces 42. The end faces 42 may also be flat. The roller 40 contacts the first rolling surface 51A and the second rolling surface 22C on its outer peripheral surface 41. The roller 40 is made of steel, for example, bearing steel. The roller 40 may also be hardened by quenching.

[0061] Next, the assembly method of the driven bearing 1 in this embodiment will be described. First, refer to... Figure 5 Prepare an intermediate body 2 comprising a first main body portion 50 and a flange portion 52. Next, refer to... Figure 5 and Figure 6 The first sealing member 30A is installed on the intermediate body 2. The end 55 of the first main body 50 is inserted into the first sealing member 30A, and the protrusion 32 of the first sealing member 30A is disposed in contact with the second end face 52C of the flange portion 52. Next, referring to... Figure 6 and Figure 7 The roller 40 is positioned on the intermediate body 2, which is provided with the first sealing member 30A. At this time, the roller 40 is configured to contact the first rolling surface 51A on its outer peripheral surface 41. Next, referring to... Figure 7 and Figure 8 An outer ring 20 is installed on the intermediate body 2, which is equipped with the first sealing member 30A and has rollers 40. The end 55 of the first main body 50 is inserted into the outer ring 20, and the second rolling surface 22C of the outer ring 20 contacts the outer peripheral surface 41 of the rollers 40 and is positioned opposite the first rolling surface 51A. Next, referring to… Figure 2 , Figure 3 as well as Figure 8 The ring 60, which is provided with the second sealing member 30B, is installed on the intermediate body 2, which is provided with the first sealing member 30A and the outer ring 20 and is equipped with rollers 40. The end 55 of the first main body 50 is inserted into the ring 60, and the ring 60 is embedded in such a way that it contacts the stepped surface 51B of the large diameter portion 51, thereby fixing the ring 60 to the first main body 50. Through the above steps, the driven bearing 1 of this embodiment is completed.

[0062] In this embodiment, the driven bearing 1 includes a first sealing member 30A. The first sealing member 30A includes an annular portion 31 that forms a sealing structure with the outer ring 20. The annular portion 31 has a shape in which the outer diameter increases as it approaches the first end face 52B. By including the annular portion 31 in the first sealing member 30A, the outer ring 20 is guided by the annular portion 31 when it is installed on the inner member 10, thereby reducing the possibility of the outer ring 20 being hooked by the first sealing member 30A. Therefore, according to the driven bearing 1 in this embodiment, the assembly of the driven bearing 1 becomes easier.

[0063] In this embodiment, the annular portion 31 of the first sealing member 30A is a tapered shape whose outer diameter increases as it approaches the first end face 52B. Therefore, when the inner member 10 is inserted into the outer ring 20, the outer ring 20 is more reliably guided by the annular portion 31 of the first sealing member 30A, further reducing the possibility of the outer ring 20 being hooked by the first sealing member 30A. Therefore, the driven bearing 1 according to this disclosure can be assembled more easily.

[0064] In the above embodiment, the first sealing member 30A includes a protrusion 32. By including the protrusion 32 in the first sealing member 30A, contact between the second end face 52C of the flange portion 52 and the second surface 22B of the outer ring 20 can be suppressed when an axial load, such as misalignment, is applied to the driven bearing 1. Therefore, wear and other damage caused by contact between the second end face 52C of the flange portion 52 and the second surface 22B of the outer ring 20 can be suppressed.

[0065] In the above embodiment, the maximum height roughness Rz of the second end face 52C of the flange portion 52 is 12.5 μm or less. By adopting such a structure, the friction between the first sealing member 30A and the second end face 52C of the flange portion 52 can be reduced when an axial load is applied to the driven bearing 1.

[0066] In the above embodiment, the second end face 52C of the flange portion 52 and the third end face 63 of the ring 60 are ground. In the above embodiment, the second face 22B and the fourth face 22E of the outer ring 20 may not be ground. That is, the maximum height roughness Rz of the second face 22B and the fourth face 22E is greater than 12.5 μm. In this embodiment, when an axial load is applied to the driven bearing 1, the contact area between the first sealing member 30A and the second face 22B is greater than the contact area between the first sealing member 30A and the second end face 52C. That is, the frictional force generated between the first sealing member 30A and the outer ring 20 is greater than the frictional force generated between the first sealing member 30A and the flange portion 52. Similarly, when an axial load is applied to the driven bearing 1, the contact area between the second sealing member 30B and the fourth face 22E is greater than the contact area between the second sealing member 30B and the third end face 63. That is, the frictional force generated between the second sealing member 30B and the outer ring 20 is greater than the frictional force generated between the second sealing member 30B and the ring 60. In this case, either the first sealing member 30A or the second sealing member 30B rotates together with the outer ring 20 relative to the inner member 10. When the first sealing member 30A or the second sealing member 30B rotates, sliding friction occurs between the first sealing member 30A and the second end face 52C, or between the second sealing member 30B and the third end face 63, resulting in wear on the first sealing member 30A or the second sealing member 30B. By reducing the maximum height roughness Rz of the second end face 52C and the third end face 63, the aforementioned sliding friction can be reduced, and the wear on the first sealing member 30A and the second sealing member 30B can also be reduced. It should be noted that although the case where the second surface 22B of the outer ring 20 is not ground has been described, it is not limited to this; grinding can also be performed on the second surface 22B of the outer ring 20.

[0067] In the above embodiment, the first sealing end face 31C is axially positioned closer to the inside of the bearing than the first outer ring end face 21C, and has a structure in which a space 71 with an axial opening is formed by the first surface 22A of the outer ring 20, the outer peripheral surface 52A of the flange portion 52, and the first sealing end face 31C of the first sealing member 30A. This reduces the likelihood that the first sealing end face 31C will protrude further outward from the bearing than the first outer ring end face 21C in the axial direction, even if dimensional tolerances of the components constituting the driven bearing 1 accumulate. Therefore, the possibility of the outer peripheral surface 31A of the first sealing member 30A being exposed outside the bearing is reduced, making it less likely for dust to accumulate on the outer peripheral surface 31A of the first sealing member 30A. Furthermore, when resin molding the first sealing member 30A of this shape, it is easy to mold because there are fewer narrowing corner sections.

[0068] In the above embodiment, the driven bearing 1 has a second sealing member 30B. The second sealing member 30B, like the first sealing member 30A, includes an annular portion 31 and a protrusion 32. The annular portion 31 of the second sealing member 30B has a shape in which the outer diameter increases as it approaches the fourth end face 64 side of the ring 60. By including the annular portion 31 in the second sealing member 30B, when the ring 60 with the second sealing member 30B is installed on the first main body 50, the ring 60 is guided by the outer peripheral surface 31A of the annular portion 31, reducing the possibility of the second sealing member 30B being hooked by the outer ring 20. Therefore, the ring 60 with the second sealing member 30B can be easily installed on the first main body 50. Furthermore, by including the protrusion 32 in the second sealing member 30B, contact between the third end face 63 and the fourth surface 22E of the ring 60 can be suppressed when an axial load is applied to the driven bearing 1. Therefore, it is possible to suppress wear caused by the contact between the third end face 63 of the ring 60 and the fourth face 22E of the outer ring 20.

[0069] In the above embodiment, the annular portion 31 of the second sealing member 30B is a tapered shape whose outer diameter increases as it approaches the fourth end face 64. Therefore, when the ring 60 is installed on the first main body portion 50, the ring 60 is more reliably guided by the annular portion 31 of the second sealing member 30B, further reducing the possibility of the second sealing member 30B being hooked by the outer ring 20. Therefore, the driven bearing 1 according to this disclosure can be assembled more easily.

[0070] In the above embodiment, the second sealing end face 31D is axially positioned closer to the inner side of the bearing than the second outer ring end face 21D, and has a structure in which the third surface 22D of the outer ring 20, the outer peripheral surface 61 of the ring 60, and the second sealing end face 31D of the second sealing member 30B form an axially open space 72. This reduces the likelihood that the second sealing end face 31D will protrude further outward from the bearing than the second outer ring end face 21D, even if dimensional tolerances of the components constituting the driven bearing 1 accumulate. Therefore, the likelihood of the outer peripheral surface 31A of the second sealing member 30B being exposed outside the bearing is reduced, making it less likely for dust to accumulate on the outer peripheral surface 31A of the second sealing member 30B. Furthermore, when resin molding the second sealing member 30B of this shape, it is easy to mold because there are fewer narrowing corner sections.

[0071] In the above embodiment, the maximum height roughness Rz of the third end face 63 of the ring 60 is 12.5 μm or less. By adopting this structure, friction between the second sealing member 30B and the third end face 63 of the ring 60 can be reduced when an axial load is applied to the driven bearing 1. It should be noted that, depending on the application of the driven bearing 1, the maximum height roughness Rz of the third end face 63 of the ring 60 can also be greater than 12.5 μm.

[0072] In the above embodiment, although the annular portion 31 of the first sealing member 30A is a conical shape whose outer diameter increases as it approaches the first end face 52B, it is not limited to this. For example, the outer peripheral surface 31A of the annular portion 31 of the first sealing member 30A may also be... Figure 2 and Figure 3 The cross-section shown, which includes the rotating shaft of the driven bearing 1, is arc-shaped, and its outer diameter increases as it approaches the first end face 52B. Specifically, it can be an arc-shaped structure where the proportion of the increase in diameter of the outer peripheral surface 31A decreases as it approaches the first end face 52B, or it can be an arc-shaped structure where the proportion of the increase in diameter of the outer peripheral surface 31A increases as it approaches the first end face 52B. Furthermore, the outer peripheral surface 31A of the annular portion 31 of the first sealing member 30A can also be a structure including an arc-shaped region and a conical region. That is, the outer peripheral surface 31A of the annular portion 31 of the first sealing member 30A can also be formed such that the arc-shaped region and the conical region are connected axially. In addition, the outer peripheral surface 31A of the annular portion 31 of the first sealing member 30A can also be configured to include a curved surface. Similarly, although the annular portion 31 of the second sealing member 30B is a conical shape whose outer diameter increases as it approaches the fourth end face 64, it is not limited to this. For example, the outer peripheral surface 31A of the annular portion 31 of the second sealing member 30B may also be... Figure 2 and Figure 3The cross-section shown, which includes the rotating shaft of the driven bearing 1, is arc-shaped, and its outer diameter increases as it approaches the fourth end face 64. The same applies to the embodiments shown below.

[0073] Next, other implementation methods will be described. Figure 9 This is a schematic cross-sectional view showing the structure of the driven bearing in other embodiments. Figure 9 It represents a cross-section including the rotating shaft of the driven bearing. Figure 10 It is an enlarged representation Figure 9 A schematic cross-sectional view of region α. ​​Relative to... Figure 1 and Figure 2 The driven bearing shown is Figure 9 The driven bearing shown differs from the first and second sealing components in that their structures are different. Figure 1 and Figure 2 The driven bearings shown are different.

[0074] Reference Figure 9 and Figure 10 In other embodiments, the driven bearing 1 includes a first sealing member 30C and a second sealing member 30D. The first sealing member 30C, like the first sealing member 30A, includes an annular portion 31 and a protrusion 32. The outer peripheral surface 31A of the annular portion 31 of the first sealing member 30C has a tapered shape whose outer diameter increases as it approaches the first end face 52B side of the flange portion 52. The first sealing member 30C includes a first sealing end face 31E located axially on the side of the first end face 52B. The first sealing end face 31E has a shape whose outer diameter decreases as it approaches the first end face 52B. Specifically, the first sealing end face 31E is a tapered shape whose outer diameter decreases as it approaches the first end face 52B side. Furthermore, the first sealing end face 31E extends axially to the first end face 52B. In this embodiment, a so-called C-bevel is applied to the first end face 52B, but the first sealing end face 31E extends to the first end face 52B where the C-bevel is applied. In this embodiment, no C-bevel is provided. Figure 2 and Figure 3 The structure of space 71 shown.

[0075] Furthermore, the second sealing member 30D, like the second sealing member 30B, includes an annular portion 31 and a protrusion 32. The outer peripheral surface 31A of the annular portion 31 of the second sealing member 30D has a conical shape whose outer diameter increases as it approaches the fourth end face 64 of the ring 60. The second sealing member 30D includes a second sealing end face 31F located axially on the side of the fourth end face 64. The second sealing end face 31F has a shape whose outer diameter decreases as it approaches the fourth end face 64. Specifically, the second sealing end face 31F is a conical shape whose outer diameter decreases as it approaches the fourth end face 64. It should be noted that the second sealing end face 31F is a structure that does not reach the fourth end face 64 of the ring 60 axially. In this embodiment, it is not provided. Figure 2 and Figure 3 The structure of space 72 shown.

[0076] In the above embodiment, even if dust accumulates on the first sealing end face 31E, the shape of the first sealing end face 31E allows the dust accumulated on the first sealing end face 31E to easily slide off towards the first end face 52B. Therefore, dust is less likely to accumulate on the first sealing end face 31E. This reduces the possibility of dust on the first sealing end face 31E crossing the outer peripheral surface 31A of the first sealing member 30C and intruding into the bearing, thereby improving the dustproof performance of the driven bearing 1.

[0077] In the above embodiment, the first sealing end face 31E is a tapered shape whose outer diameter decreases as it approaches the first end face 52B. Therefore, it becomes easier for dust accumulated on the first sealing end face 31E to reliably slide off towards the first end face 52B. Consequently, dust is less likely to accumulate on the first sealing end face 31E. Therefore, the possibility of dust on the first sealing end face 31E crossing the outer peripheral surface 31A of the first sealing member 30C and intruding into the bearing interior can be significantly reduced, thereby improving the dustproof performance of the driven bearing 1.

[0078] In the above embodiment, the first sealing end face 31E extends axially to the first end face 52B. Therefore, dust accumulated on the first sealing end face 31E of the above-described shape can smoothly slide off to the first end face 52B, preventing dust from easily accumulating in the area between the first sealing end face 31E and the outer peripheral surface 52A of the flange portion 52. Thus, the dustproof performance of the driven bearing 1 can be improved.

[0079] In the above embodiment, the second sealing member 30D includes a second sealing end face 31F located axially on the side of the fourth end face 64. The second sealing end face 31F has a shape in which the outer diameter decreases as it approaches the fourth end face 64. Therefore, even if dust accumulates on the second sealing end face 31F, due to the aforementioned shape, the dust accumulated on the second sealing end face 31F can easily slide off towards the fourth end face 64. Therefore, dust is less likely to accumulate on the second sealing end face 31F. Therefore, the possibility of dust on the second sealing end face 31F crossing the outer peripheral surface 31A of the second sealing member 30D and intruding into the bearing interior can be reduced, thereby improving the dustproof performance of the driven bearing 1.

[0080] In the above embodiment, the second sealing end face 31F is a tapered shape whose outer diameter decreases as it approaches the fourth end face 64. Therefore, it becomes easier for dust accumulated on the second sealing end face 31F to reliably slide off towards the fourth end face 64. Consequently, dust is less likely to accumulate on the second sealing end face 31F. Therefore, the possibility of dust on the second sealing end face 31F crossing the outer peripheral surface 31A of the second sealing member 30D and intruding into the bearing interior is reduced, thereby improving the dustproof performance of the driven bearing 1.

[0081] It should be noted that in the above embodiment, the second sealing end face 31F may also extend axially to the fourth end face 64. This allows dust accumulated on the second sealing end face 31F of the aforementioned shape to smoothly slide off towards the fourth end face 64, preventing dust from easily accumulating in the area between the second sealing end face 31F and the outer peripheral surface 61 of the ring 60. Therefore, the dustproof performance of the driven bearing 1 can be improved. Alternatively, a structure in which the first end face 52B of the flange portion 52 is not chamfered may also be used.

[0082] In the above embodiment, a first hole 56 extending axially is formed in the first main body portion 50. A second hole 57 communicating with the first hole 56 and having an opening 57A on the outer peripheral surface 50A is formed in the first main body portion 50. A third hole 58 having an opening 58A on the first rolling surface 51A and communicating with the first hole 56 is formed in the first main body portion 50. By injecting lubricant through the opening 56A of the first hole 56, oil can be supplied to the outer peripheral surface 41 of the roller 40 through the first hole 56 and the third hole 58. An oil nozzle or a stopcock valve may also be installed to close the opening 56A of the first hole 56.

[0083] In the above embodiments, although the outer peripheral surface 21B of the outer ring 20 has a cylindrical shape, it is not limited to this; the shape of the outer peripheral surface 21B can also be spherical. In the above embodiments, although the case where rollers 40 are used as the rolling elements of the driven bearing 1 is described, balls can also be used as rolling elements. Furthermore, in the above embodiments, although the case where the rolling elements are arranged in a single row is described, they can also be arranged in multiple rows. Furthermore, in the above embodiments, although the case where the inner member 10 includes a first main body portion 50 having a first rolling surface 51A on the outer peripheral surface 50A is described, it is not limited to this; the inner member 10 can also include the first main body portion 50 and an inner ring having the first rolling surface 51A on the outer peripheral surface and embedded in the first main body portion 50. It should be noted that gaps are formed between the first sealing member 30A and the outer ring 20, and between the first sealing member 30A and the flange portion 52. Furthermore, gaps are formed between the second sealing member 30B and the outer ring 20, and between the second sealing member 30B and the flange portion 52. By creating such a gap, the increase in rotational torque of the outer ring 20 caused by the provision of the first sealing member 30A and the second sealing member 30B can be reduced, allowing the outer ring 20 to rotate smoothly. Furthermore, although the above embodiment describes a full roller bearing 1 without a cage, it is not limited to this; the driven bearing 1 may also have a cage.

[0084] In this disclosure, the driven bearing 1 refers to a bearing in which the outer ring 20 rotates relative to the first main body 50 in the circumferential direction while in contact with other components, with the first main body 50 fixed. The other components are not particularly limited and may include, for example, a cam, a guide rail, or a belt. According to the driven bearing 1 in the above embodiment, linear motion can be smoothly guided in machine tools, industrial robots, and the like.

[0085] The embodiments disclosed herein are illustrative in all respects and should be understood as not being limited in any way. The scope of the invention is not limited by the foregoing description, but is defined by the claims, and is intended to include all modifications within the meaning and scope equivalent to the claims.

[0086] Explanation of reference numerals in the attached figures

[0087] 1 Driven bearing; 2 Intermediate body; 10 Inner component; 20 Outer ring; 21A, 31B, 62 Inner circumferential surfaces; 21B, 31A, 41, 50A, 52A, 61 Outer circumferential surfaces; 21C First outer ring end face; 21D Second outer ring end face; 22A First surface; 22B Second surface; 22C Second rolling surface; 22D Third surface; 22E Fourth surface; 30A, 30C First sealing components; 30B, 30D Second sealing components; 31 Annular portion; 31C, 31E First sealing end faces; 31D, 31F Second sealing end faces. End face; 32 protrusion; 32A, 32B, 42 end faces; 40 roller; 50 first main body; 501 protrusion; 51 large diameter part; 51A first rolling surface; 51B stepped surface; 52 flange; 52B first end face; 52C second end face; 53A hexagonal hole; 54 threaded part; 55 end; 56 first hole; 56A, 57A, 58A opening; 57 second hole; 58 third hole; 60 ring; 63 third end face; 64 fourth end face; 71, 72 space; Rz maximum height roughness; α region.

Claims

1. A driven bearing, wherein, have: The inner component includes a first main body and a flange. The first main body has a rod-shaped shape and an annular first rolling surface on its outer peripheral surface. The flange has a disc-shaped annular shape and is disposed on the outer peripheral surface of one end of the first main body and has a central axis coaxial with the first main body. The diameter of the flange is larger than the diameter of the first main body. The outer ring has an annular first surface facing the outer circumferential surface of the flange portion, an annular second rolling surface with a diameter smaller than the diameter of the first surface and facing the first rolling surface, and an annular second surface connecting the second rolling surface and the first surface; and the first surface has a cylindrical shape having a central axis coaxial with the rotation axis of the driven bearing. Multiple rolling elements, configured to roll on both the first rolling surface and the second rolling surface; and The first sealing member includes an annular first portion disposed between the outer peripheral surface of the flange and the first surface, and at least a portion thereof forming a sealing structure with the outer ring, and an annular second portion connected to the first portion; The flange portion has a first end face and a second end face, wherein the first end face is the end face opposite to the first rolling surface in the axial direction, and the second end face is the end face opposite to the first end face in the axial direction. The second surface is axially opposite to the second end surface. The second portion is disposed between the second end face and the second surface, and protrudes radially inward. The first portion has a shape in which the outer diameter increases in the axial direction as it approaches the first end face in the region from the connection portion with the second portion to the first sealing end face located on the first end face side. When the inner member is inserted into the outer ring, the outer ring is guided by the first portion, which can reduce the possibility of the outer ring being hooked by the first sealing member.

2. The driven bearing as claimed in claim 1, wherein, The first part is a conical shape whose outer diameter increases as it approaches the first end face side.

3. The driven bearing as described in claim 1 or 2, wherein, The maximum height roughness Rz of the second end face of the flange is less than 12.5 μm.

4. The driven bearing as described in claim 1 or 2, wherein, The first sealing end face has a shape in which the outer diameter decreases as it approaches the first end face.

5. The driven bearing as claimed in claim 4, wherein, The first sealing end face is a conical shape whose outer diameter decreases as it approaches the first end face side.

6. The driven bearing as claimed in claim 4, wherein, The first sealing end face extends axially to the first end face.

7. The driven bearing as claimed in claim 1 or 2, wherein, The inner component further includes a ring that, when viewed from the first rolling surface of the first body portion, is embedded in such a manner that it contacts the outer peripheral surface on the side opposite to the flange portion, and the ring has a central axis coaxial with the first body portion. The inner circumferential surface of the outer ring further comprises: a third annular surface facing the outer circumferential surface of the ring and having a diameter larger than that of the second rolling surface; and a fourth annular surface connecting the second rolling surface to the third surface, and axially facing the end face of the ring on the first rolling surface side, i.e., the third end face. The driven bearing further comprises a second sealing member, the second sealing member including: an annular third portion disposed between the outer peripheral surface of the ring and the third surface, and at least a portion thereof forming a sealing structure with the outer ring; and an annular fourth portion connected to the third portion and disposed between the third end face and the fourth surface. The fourth part protrudes along the radially inward side. The third part, in the region from the connection portion with the fourth part to the second sealing end face located axially on the side opposite to the third end face of the ring, i.e., the fourth end face side, has a shape in which the outer diameter increases axially as it approaches the fourth end face side.

8. The driven bearing as claimed in claim 7, wherein, The third part is a conical shape whose outer diameter increases as it approaches the fourth end face.

9. The driven bearing as claimed in claim 7, wherein, The maximum height roughness Rz of the third end face of the ring is less than 12.5 μm.

10. The driven bearing as claimed in claim 7, wherein, The second sealing end face has a shape in which the outer diameter decreases as it approaches the fourth end face.

11. The driven bearing as claimed in claim 10, wherein, The second sealing end face is a conical shape whose outer diameter decreases as it approaches the fourth end face side.

12. The driven bearing as claimed in claim 10, wherein, The second sealing end face extends axially to the fourth end face.

13. The driven bearing as claimed in claim 7, wherein, The material constituting the second sealing member is at least one resin selected from the group consisting of polyetheretherketone, polyacetal, and polyamide.

14. The driven bearing as claimed in claim 1 or 2, wherein, The material constituting the first sealing member is at least one resin selected from the group consisting of polyetheretherketone, polyacetal, and polyamide.

15. The driven bearing as claimed in claim 1 or 2, wherein, The rolling element is a roller.

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