Driven bearing

Abstract

The driven bearing (1A) of the present application has an outer ring (60), a plurality of rolling elements (70), and a cage (80) that holds the plurality of rolling elements (70). The outer ring (60) includes a first member (40) that is circular ring-shaped and is composed of steel, and a second member (50) that is circular ring-shaped, is composed of resin, and covers an outer peripheral surface of the first member (40). The first member (40) includes a cylindrical portion (42). The second member (50) includes a first portion (54A) that is disposed on one side of the cylindrical portion (42) in the axial direction and has a first opposing surface (54C) that opposes an outer peripheral surface (82A) of the cage (80) in the radial direction, and a second portion (54B) that is disposed on the other side of the cylindrical portion (42) in the axial direction and has a second opposing surface (54D) that opposes an outer peripheral surface (82B) of the cage (80) in the radial direction. In the radial direction, the first opposing surface (54C) and the second opposing surface (54C) are respectively disposed at positions that are on the outer peripheral side than the second raceway surface (41).

Description

Technical Field

[0001] This disclosure relates to driven bearings. Background Technology

[0002] A rolling bearing in which the outer ring is integrated with a resin pulley is known (see, for example, Patent Document 1). According to Patent Document 1, the outer ring has a flange at one end facing radially outward. In Patent Document 1, the end face of the flange on one axial side is exposed from the resin pulley, thereby improving the heat dissipation of the outer ring.

[0003] Existing technical documents

[0004] Patent documents

[0005] Patent document 1: Japanese Patent Application Publication No. 2009-191900. Summary of the Invention

[0006] The problem that the invention aims to solve

[0007] In driven bearings, it is sometimes necessary to suppress operating noise, and consequently, to suppress aggression towards other components in contact with the outer ring. Using a structure where the outer circumferential surface of the outer ring is covered with resin can suppress both operating noise and aggression towards other components. Furthermore, in driven bearings, a load is sometimes applied to the outer ring from the outer shaft side during operation. Since the outer circumferential surface of the outer ring is covered with resin, the bearing may sometimes deform. Even under such conditions, stable bearing operation is required.

[0008] Therefore, one objective is to provide a driven bearing that can suppress operating noise and aggression towards other components, and ensure stable operation of the bearing.

[0009] Technical means to solve the problem

[0010] The driven bearing disclosed herein comprises: an inner member having an annular first raceway surface on its outer circumferential surface; an outer ring having an annular second raceway surface on its inner circumferential surface facing the first raceway surface; a plurality of rolling elements configured to contact the first raceway surface and the second raceway surface on an annular raceway along the first raceway surface and the second raceway surface; and a cage for retaining the plurality of rolling elements. The outer ring includes: an annular first member made of steel; and an annular second member made of resin and covering the outer circumferential surface of the first member. The first member includes a cylindrical portion having a hollow cylindrical shape and containing the second raceway surface. The second member includes: a first portion axially disposed on one side of the cylindrical portion having a first opposing surface radially facing the outer circumferential surface of the cage; and a second portion axially disposed on the other side of the cylindrical portion having a second opposing surface radially facing the outer circumferential surface of the cage. Radially, the first opposing surface and the second opposing surface are respectively disposed at a position further outward than the second raceway surface.

[0011] Invention Effects

[0012] Based on the aforementioned driven bearing, it is possible to suppress operating noise and aggression towards other components, and to ensure stable bearing operation. Attached Figure Description

[0013] Figure 1 This is a schematic perspective view showing the structure of the driven bearing in one embodiment of the present disclosure.

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

[0015] Figure 3 It is a schematic three-dimensional diagram showing the structure of the first component of the outer ring.

[0016] Figure 4 It is an enlarged representation Figure 2 A schematic cross-sectional view of a portion of the driven bearing shown.

[0017] Figure 5 It is an enlarged representation Figure 2 A rough cross-sectional view of region V.

[0018] Figure 6 This is a schematic cross-sectional view showing a portion of the driven bearing under conditions where a load is applied from the outer circumferential side of the outer ring.

[0019] Figure 7 This is a schematic cross-sectional view showing a portion of the driven bearing under conditions where a load is applied from the outer circumferential side of the outer ring.

[0020] Figure 8 It is a graph showing the relationship between load and deformation when the outer circumference of the driven bearing is changed.

[0021] Figure 9 This is a schematic cross-sectional view showing a portion of the driven bearing in Embodiment 2.

[0022] Figure 10 It is an enlarged representation Figure 9 A schematic cross-sectional view of a portion of the driven bearing shown.

[0023] Figure 11 This is a schematic cross-sectional view showing a portion of the driven bearing in Embodiment 3.

[0024] Figure 12 This is a schematic cross-sectional view showing a portion of the driven bearing in embodiment 4.

[0025] Figure 13 This is a schematic cross-sectional view showing a portion of the driven bearing in embodiment 5.

[0026] Figure 14 This is a schematic perspective view of the driven bearing in Embodiment 5, where the second component is omitted.

[0027] Explanation of reference numerals in the attached figures:

[0028] 1A, 1B, 1C, 1D, 1E Driven Bearings; 10 Main Body; 11 First Track Surface; 12 Flange; 13, 23, 45A, 53A First End Faces; 13A Hexagonal Hole; 14 Threaded Part; 15, 24, 45B, 53B Second End Faces; 16 Large Diameter Part; 16A Stepped Surface; 17 Shaft Part; 20 Side Plate; 21, 44A, 44B, 52, 71, 82A, 82B Outer Peripheral Surfaces; 22, 51 Inner Peripheral Surfaces; 30 Shaft Components ; 31 Rotating shaft; 40 First component; 41 Second track surface; 42 Cylindrical part; 43 Protrusion; 45C Side side; 46 End; 48 Opposing area; 49A, 49B Recess; 50, 59 Second component; 54A First part; 54B Second part; 54C First opposing surface; 54D Second opposing surface; 54E Tongue; 60 Outer ring; 70 Roller; 72 End face; 80 Cage; 81 Recess; 91A, 91B Gap; 92 Load. Detailed Implementation

[0029] [Summary of Implementation Methods]

[0030] The driven bearing disclosed herein comprises: an inner member having an annular first raceway surface on its outer circumferential surface; an outer ring having an annular second raceway surface on its inner circumferential surface facing the first raceway surface; a plurality of rolling elements configured to contact the first raceway surface and the second raceway surface on an annular raceway along the first raceway surface and the second raceway surface; and a cage for retaining the plurality of rolling elements. The outer ring includes: an annular first member made of steel; and an annular second member made of resin and covering the outer circumferential surface of the first member. The first member includes a cylindrical portion having a hollow cylindrical shape and containing the second raceway surface. The second member includes: a first portion axially disposed on one side of the cylindrical portion having a first opposing surface radially facing the outer circumferential surface of the cage; and a second portion axially disposed on the other side of the cylindrical portion having a second opposing surface radially facing the outer circumferential surface of the cage. Radially, the first opposing surface and the second opposing surface are respectively disposed at a position further outward than the second raceway surface.

[0031] In the driven bearing of this disclosure, the outer ring includes a second member made of resin. This suppresses aggression towards other members in contact with the outer ring and reduces operational noise. Furthermore, the driven bearing of this disclosure includes a cage that holds multiple rolling elements. Therefore, it is possible to ensure the stability of the rolling elements' posture during bearing operation. During bearing operation, the cage rotates together with the rolling elements. In the driven bearing, there is a possibility that a load is applied from the outer circumference of the outer ring. When a load is applied to the outer ring, it is assumed that the second member made of resin deforms towards the inner circumference. This could cause the cage holding the rolling elements to come into contact with the second member, potentially hindering the rotation of the cage.

[0032] In the driven bearing disclosed herein, the second member made of resin includes a first portion disposed axially on one side of the cylindrical portion and a second portion disposed on the other side of the cylindrical portion. Furthermore, radially, the first opposing surface included in the first portion and the second opposing surface included in the second portion are respectively disposed at positions further outward than the second raceway surface. Consequently, gaps are formed between the first opposing surface of the first portion and the outer peripheral surface of the cage, and between the second opposing surface of the second portion and the outer peripheral surface of the cage. Therefore, even when the outer ring of the driven bearing is subjected to a load from the outer peripheral side and the second member made of resin deforms inward, the likelihood of contact between the first opposing surface of the first portion and the outer peripheral surface of the cage, and between the second opposing surface of the second portion and the outer peripheral surface of the cage, is reduced. As a result, the possibility of the second member of the outer ring contacting the cage and hindering stable rotation of the cage is reduced. Thus, according to the driven bearing described above, it is possible to suppress operating noise and damage to other components, and to ensure stable bearing operation.

[0033] Furthermore, in this disclosure, "resin" includes rubber. That is, the second component may also be made of rubber. Additionally, in this disclosure, "a second component made of resin" includes a second component made of fiber-reinforced resin. That is, the resin constituting the second component may also include reinforcing fibers. For example, glass fiber, carbon fiber, etc., can be used as reinforcing fibers.

[0034] In the aforementioned driven bearing, in a cross-section cut along the plane containing the rotating shaft of the driven bearing, the outer peripheral surface of the cage can also extend straight along the axial direction. The first and second opposing surfaces can also extend straight along the axial direction. This ensures a larger contact area between the flange portion and the first and second portions in the axial direction, provided that the flange portion is axially positioned on the first and second portions and is located on the rotating shaft. Therefore, the movement of the outer ring during bearing operation is stabilized, and load distribution is achieved under thrust load conditions. As a result, stable bearing operation is further ensured. Furthermore, "extending straight" means that in a cross-section containing the rotating shaft, the hypothetical line representing the rotating shaft is parallel to the lines representing the outer peripheral surface, the first opposing surface, and the second opposing surface. Here, parallelism does not necessarily mean strictly geometrical parallelism; it also includes cases where the angle between one and the other is 3° or less.

[0035] Furthermore, in the aforementioned driven bearing, in a cross-section cut along the plane containing the rotating shaft of the driven bearing, the distance between at least one of the first and second opposing surfaces and the outer peripheral surface of the cage can be inclined relative to the axial direction, increasing from the side closer to the cylindrical portion towards the side farther from the cylindrical portion. This allows the deformed first and second opposing surfaces to be nearly parallel to the rotating shaft and, consequently, to the outer peripheral surface of the cage when a load is applied from the outer peripheral side of the outer ring. Therefore, the possibility of the second member contacting the cage can be reduced, and stable bearing operation can be further ensured.

[0036] In the aforementioned driven bearing, at least either the first portion or the second portion may include a tongue-shaped portion extending into the region between the cage and the cylindrical portion. This tongue-shaped portion significantly reduces the likelihood of contact between the cage and the cylindrical portion. Consequently, wear of the cage caused by contact with the cylindrical portion can be suppressed. Therefore, more reliable and stable bearing operation can be ensured.

[0037] In the aforementioned driven bearing, the cylindrical portion may also have a region facing the outer circumference of the cage in the radial direction. This ensures that even if the outer ring is deformed towards the inner circumference due to a load applied from the outer circumference, it still contacts the cage in the region facing the cylindrical portion. This reduces the likelihood of the cage contacting the second component. Consequently, smooth rotation of the cage is easily ensured.

[0038] In the aforementioned driven bearing, the outer circumferential surface of the cylindrical portion can also extend straight along the axial direction. This allows for a simpler shape of the cylindrical portion and good productivity.

[0039] Furthermore, in the aforementioned driven bearing, the first member may also include a protrusion extending radially outward from the cylindrical portion. This protrusion structure further reduces the possibility of axial separation between the first and second members.

[0040] The driven bearing described above may also include a rotation suppression mechanism to suppress the relative rotation of the second member with respect to the first member in the circumferential direction. This limits the relative rotation of the second member with respect to the first member, thus ensuring more reliable and stable bearing operation.

[0041] In the aforementioned driven bearing, the rotation suppression mechanism may also include a recessed portion that forms a circular hole in the outer peripheral surface of the cylindrical portion. A portion of the second member may also enter the recessed portion. In this way, the relative rotation of the second member relative to the first member can be suppressed by the recessed portion and the second member entering the recessed portion. In addition, the axial movement of the second member relative to the first member can also be restricted. Such a structure can be formed by allowing resin to flow into the recessed portion after the cylindrical portion has the recessed portion of the above structure is provided, and then by providing the second member on the outer peripheral side of the first member, thus making the above structure easy to form.

[0042] In the aforementioned driven bearings, the cage can also be a welded cage. Since welded cages (welded retainers) offer good productivity, this allows for increased productivity.

[0043] In the aforementioned driven bearing, the resin constituting the second component can also be made of an elastomer. This effectively absorbs vibrations and impacts applied to the driven bearing, thus further ensuring stable bearing operation.

[0044] In the aforementioned driven bearing, the elastomer can also be a thermoplastic elastomer. This allows for increased productivity, for example, by using injection molding. As a thermoplastic elastomer, at least one of polyurethane elastomers, polyamide elastomers, polyester elastomers, polystyrene elastomers, polyolefin elastomers, and polyvinyl chloride elastomers can be selected. Furthermore, as a thermoplastic elastomer, at least one of polyurethane elastomers, polyamide elastomers, and polyester elastomers can also be selected.

[0045] 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 achieving sufficient load-bearing capacity.

[0046] [Specific examples of implementation methods]

[0047] 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.

[0048] (Implementation Method 1)

[0049] Figure 1 This is a schematic perspective view showing the structure of the driven bearing in one embodiment of this disclosure, namely embodiment 1. Figure 2 It means Figure 1 The diagram shows a schematic cross-sectional view of the driven bearing structure. Figure 2 It is a cross-sectional view cut by a plane containing the driven bearing of the rotating shaft. Figure 3 It means Figure 1 A schematic three-dimensional view of the structure of the first component of the outer ring shown. Figure 4 It is an enlarged representation Figure 2 A schematic cross-sectional view of a portion of the driven bearing shown. Figure 5 It is an enlarged representation Figure 2 A rough cross-sectional view of region V.

[0050] Reference Figures 1-5 In this embodiment, the driven bearing 1A includes a shaft member 30 as an inner member, an outer ring 60, a plurality of rollers 70 as rolling elements, and a cage 80 for retaining the rollers 70. Furthermore, in Figure 2 In the diagram, the rotation axis 31, which serves as the central axis of the shaft member 30, is illustrated by a dashed line.

[0051] The shaft member 30 includes: a rod-shaped (solid cylindrical) main body 10; a flange 12 formed at one end of the main body 10, with a diameter larger than that of the main body 10; and a side plate 20 as a ring, coaxially disposed on the main body 10 in such a way as to surround a portion of the outer peripheral surface of the main body 10 circumferentially. The main body 10 has a first end face 13 as one end in the axial direction, and a second end face 15 as the other end opposite to the first end face 13. Both the first end face 13 and the second end face 15 have a circular planar shape.

[0052] A hexagonal hole 13A with a regular hexagonal prism shape is formed in the region of the first end face 13, which includes the area intersecting with the rotation axis 31, which is the central axis of the shaft member 30. A threaded portion 14 with a helical thread groove is disposed in the region of the main body portion 10, which includes the end (the other end) on the side of the second end face 15. With such a structure, when the driven bearing 1A is installed, for example, by passing the shaft member 30 through the housing hole and screwing the nut into the threaded portion 14, the driven bearing 1A can be fixed to the retaining member.

[0053] The main body 10 includes: a solid cylindrical shaft portion 17 containing a threaded portion 14; and a large-diameter portion 16, axially disposed between the region where the shaft portion 17 and the flange portion 12 are located, and having a diameter larger than that of the shaft portion 17. The diameter of the large-diameter portion 16 is smaller than that of the flange portion 12. A first track surface 11 with a cylindrical shape is formed on the outer peripheral surface of the large-diameter portion 16. That is, the shaft member 30 has an annular first track surface 11 on its outer peripheral surface. In this embodiment, the first protrusion has an annular shape with its central axis aligned with the first track surface 11, is disposed on one side axially relative to the first track surface 11, and protrudes radially outward from the outer periphery of the main body 10; this first protrusion is the flange portion 12. The outer periphery of the main body 10 in the region where the flange portion 12 is located is formed by... Figure 2 , Figure 4 , Figure 5 The dashed line diagram in the image.

[0054] The annular side plate 20 has a first end face 23 as one end face, a second end face 24 as the other end face, an outer peripheral surface 21, and an inner peripheral surface 22. The first end face 23 is parallel to the second end face 24. The outer peripheral surface 21 and the inner peripheral surface 22 are concentric cylindrical surfaces. The first end face 23 is parallel to the end face (stepped portion) on the axial side of the shaft portion 17 of the large diameter portion 16, i.e., the stepped surface 16A (see reference). Figure 2 and Figure 4 The side plate 20 is configured in contact with the shaft portion 17. The side plate 20 has an inner circumference (diameter of the inner circumferential surface 22) corresponding to the outer circumference of the shaft portion 17. The side plate 20 is pressed into the shaft portion 17 and fixed to the shaft portion 17. In this embodiment, the second protrusion has an annular shape with its central axis aligned with the first track surface 11, and is disposed on the opposite side of the axial direction relative to the first track surface 11, protruding radially outward from the outer circumference of the main body portion 10. This second protrusion is the side plate 20. The shaft member 30 is made of steel such as carbon steel for mechanical construction, alloy steel for mechanical construction, or bearing steel. The area of ​​the main body portion 10 in the shaft member 30 that includes at least the first track surface 11 may also be hardened by quenching. In addition, a part or the entire side plate 20 may also be hardened by quenching.

[0055] The outer ring 60 has an annular second track surface 41 on its inner circumferential surface, which is opposite to the first track surface 11. The outer ring 60 includes a first member 40 and a second member 50. The first member 40 includes a cylindrical portion 42 having a hollow cylindrical shape and containing the second track surface 41; and a protrusion 43 extending radially outward from the cylindrical portion 42. The first member 40 is made of steel. For example, mild steel, carbon steel for mechanical construction, alloy steel for mechanical construction, etc., can be used as the steel constituting the first member 40. In addition, the first member 40 can also be hardened by quenching. The first member 40 can also be formed by stamping or stretching, for example, using a steel sheet made of mild steel.

[0056] The cylindrical portion 42 has a second track surface 41 as an inner peripheral surface, an outer peripheral surface 44A, a first end surface 45A as one axial end surface, and another axial end surface 46. The first member 40 includes the second track surface 41. The first end surface 45A of the first member 40 is opposite to the flange portion 12. That is, the flange portion 12 and the first member 40 are opposite each other in the axial direction.

[0057] The thickness of the cylindrical portion 42 is the same as the thickness of the protrusion 43. In this embodiment, the outer peripheral surface 44A is a shape that extends straight along the axial direction. That is, no recess is provided on the outer peripheral surface 44A to reduce the wall thickness. In this way, the shape of the cylindrical portion 42 can be simplified, and the productivity can be improved. The first member 40 is manufactured, for example, as follows: a ring-shaped member is prepared, one end is bent outward to form a flange-shaped protrusion 43, and the rest is kept as is to form the cylindrical portion 42.

[0058] The protrusion 43 is connected to the other end 46 of the cylindrical portion 42 in the axial direction. The protrusion 43 is plate-shaped. The protrusion 43 has a continuous annular shape covering the entire circumferential region of the first member 40. The protrusion 43 has a second end face 45B as the other end face in the axial direction, an outer peripheral surface 44B, and a side surface 45C located on the opposite side of the second end face 45B in the axial direction. The boundary between the end 46 and the protrusion 43 is... Figure 2 and Figure 4 The diagram is shown in dashed lines. The second end face 45B is opposite to the first end face 23 of the side plate 20. That is, the side plate 20 and the first member 40 are opposite each other in the axial direction.

[0059] A radially inwardly recessed cut 47 is formed in the protrusion 43 (see in particular). Figure 3 Multiple cuts 47 are formed at intervals in the circumferential direction. The cuts 47 are formed in a manner that extends through the thickness direction of the plate-like protrusion 43.

[0060] The second component 50 has a ring-shaped form. The second component 50 is made of resin. Specifically, the second component 50 is made of polyurethane rubber. The resin constituting the second component 50 can be, for example, at least one resin selected from the group consisting of polyamide, polyacetal, polyphenylene sulfide, polyester, polyamide-imide, polyimide, polyetheretherketone, and polyurethane. Alternatively, the resin constituting the second component 50 can also be made of an elastomer. This allows for effective absorption of vibrations or impacts applied to the driven bearing 1A. Therefore, more stable bearing operation can be ensured. The elastomer can also be a thermoplastic elastomer. This allows for increased productivity, for example, by using injection molding. As a thermoplastic elastomer, for example, at least one of polyurethane elastomers, polyamide elastomers, polyester elastomers, polystyrene elastomers, polyolefin elastomers, and polyvinyl chloride elastomers can be selected. Furthermore, as a thermoplastic elastomer, for example, at least one of polyurethane elastomers, polyamide elastomers, and polyester elastomers can be selected. The same applies to the embodiments described below. The second member 50 is configured to be coaxial with the first member 40. The second member 50 covers the outer peripheral surfaces 44A and 44B of the first member 40 throughout the entire area. The second member 50 also covers the first end face 45A, the second end face 45B, and the side face 45C of the first member 40. That is, in the axial direction, both sides of the protrusion 43 are filled by the second member 50.

[0061] The second member 50 has an inner peripheral surface 51, an outer peripheral surface 52, a first end face 53A, and a second end face 53B. The second member 50 includes a first portion 54A, which has an annular shape with its central axis aligned with the first track surface 11, and enters between the flange portion 12 (which serves as a first protrusion) and the first member 40. The first portion 54A is axially disposed on one side of the cylindrical portion 42. The first portion 54A is formed over the entire circumference of the inner peripheral surface 51. Furthermore, the second member 50 includes a second portion 54B, which has an annular shape with its central axis aligned with the first track surface 11, and enters between the side plate 20 (which serves as a second protrusion) and the first member 40. The second portion 54B is axially disposed on the other side of the cylindrical portion 42. The second portion 54B is formed over the entire circumference of the inner peripheral surface 51. Furthermore, although not shown, the second member 50 enters the aforementioned cutout 47. Furthermore, the cut 47 and the second member 50 entering the cut 47 function as a rotation suppression mechanism to suppress the relative rotation of the second member 50 in the circumferential direction relative to the first member 40.

[0062] The outer peripheral surface 52 of the second member 50 is configured to be convex, with the most prominent convex shape at the center in the axial direction. The outer peripheral surface 52 of the second member is configured such that its diameter gradually decreases from the center in the axial direction toward both ends in the axial direction. That is, the outer peripheral surface D1 of the outer ring 60 is configured to be the largest at the center in the axial direction.

[0063] The cage 80 has an annular shape. In this embodiment, the cage 80 is a welded cage. By using a welded cage as the cage 80, productivity can be improved. The cage 80 is made of steel, but a resin cage can also be used. The cage 80 is concentrically disposed with the shaft member 30 and the outer ring 60 in the space sandwiched between the shaft member 30 and the outer ring 60. A plurality of recesses 81 are arranged at equal intervals along the circumference on the cage 80. A roller 70 is disposed in each of the plurality of recesses 81. Thus, by being held by the cage 80, the plurality of rollers 70 are configured to contact the first track surface 11 and the second track surface 41 on an annular track along the first track surface 11 and the second track surface 41. The roller 70 has a solid cylindrical shape. The roller 70 has a cylindrical outer peripheral surface 71 and a pair of spherical end faces 72. The end faces 72 of the roller 70 can also be flat. The roller 70 contacts the first track surface 11 and the second track surface 41 on its outer peripheral surface 71. The roller 70 is made of steel such as bearing steel. The roller 70 may also be hardened by quenching.

[0064] The first part 54A has a first opposing surface 54C that radially opposes the outer peripheral surface 82A of the retainer 80. Radially, the first opposing surface 54C is positioned further outward than the second track surface 41. The second part 54B has a second opposing surface 54D that radially opposes the outer peripheral surface 82B of the retainer 80. Radially, the second opposing surface 54D is positioned further outward than the second track surface 41. That is, radially, both the first opposing surface 54C and the second opposing surface 54D are positioned further outward than the second track surface 41. With this structure, a radial gap 91A can be formed between the outer peripheral surface 82A of the retainer 80 and the first opposing surface 54C. Additionally, a radial gap 91B can be formed between the outer peripheral surface 82B of the retainer 80 and the second opposing surface 54D. Furthermore, in a cross-section cut by the plane containing the rotating shaft 31 of the driven bearing 1A, the outer peripheral surfaces 82A and 82B of the cage 80 extend straight along the axial direction. The first opposing surface 54C and the second opposing surface 54D also extend straight along the axial direction. That is, the line representing the outer peripheral surface 82A of the cage 80 is parallel to the line representing the first opposing surface 54C. Additionally, the line representing the outer peripheral surface 82B of the cage 80 is parallel to the line representing the second opposing surface 54D.

[0065] In the driven bearing 1A of the above embodiment, by arranging the shaft member 30, outer ring 60, cage 80 and a plurality of rollers 70 as described above, the outer ring 60 can rotate relative to the shaft member 30 in the circumferential direction.

[0066] In the driven bearing 1A of the above embodiment, the outer ring 60 includes a second member 50 made of resin. This allows for suppression of aggression towards other members in contact with the outer ring 60 and suppression of operational noise. Furthermore, the driven bearing 1A of this disclosure includes a cage 80 that holds the rollers 70, which are multiple rolling elements. Therefore, it is possible to ensure the stable maintenance of the rollers 70's posture during bearing operation. During bearing operation, the cage 80 rotates together with the rollers 70.

[0067] In this case, in the driven bearing 1A, a load is applied from the outer circumferential side of the outer ring 60. When a load is applied to the outer ring 60, it is assumed that the second member 50, which is made of resin, deforms towards the inner circumferential side. As a result, the cage 80 that holds the roller 70 comes into contact with the second member 50, which may impede the rotation of the cage.

[0068] This needs to be explained. Figure 6 and Figure 7 This is a schematic cross-sectional view of a portion of the driven bearing 1A when a load is applied from the outer circumferential side of the outer ring. Figure 7 It is an enlarged representation Figure 2 A schematic cross-sectional view of region VII.

[0069] Reference Figure 6 and Figure 7 There exists a situation where a load 92, indicated by the arrow, is applied from the outer periphery of the outer ring 60, and in this case, from the outer periphery of the second member 50. As a result, the second member 50, being made of polyurethane rubber, deforms. Specifically, since the outer peripheral surface 52 of the second member 50 has a shape with the most prominent central projection in the axial direction, the outer peripheral surface 52 is flattened. Moreover, even the inner periphery of the second member 50 deforms due to the applied load 92. In this case, since the cylindrical portion 42 is made of steel, the amount of deformation towards the inner periphery on the side of the first opposing surface 54C closest to the cylindrical portion 42 is small, while the amount of deformation towards the inner periphery on the outer side in the axial direction, i.e., axially, increases as it moves away from the cylindrical portion 42. That is, axially, the inner periphery of the first opposing surface 54C decreases as it moves away from the cylindrical portion 42. The same tendency exists for the second opposing surface 54D.

[0070] In the driven bearing 1A of this disclosure, the first opposing surface 54C and the second opposing surface 54D are respectively arranged radially at positions further outward than the second track surface 41. Furthermore, a radial gap 91A is formed between the outer peripheral surface 82A of the cage 80 and the first opposing surface 54C. Additionally, a radial gap 91B is formed between the outer peripheral surface 82B of the cage 80 and the second opposing surface 54D. Therefore, even when the outer ring 60 of the driven bearing 1A is subjected to a load 92 from the outer peripheral side and the second resin member 50 is deformed towards the inner peripheral side, the possibility of contact between the first opposing surface 54C of the first portion 54A and the outer peripheral surface 82A of the cage 80, and the possibility of contact between the second member 50 of the outer ring 60 and the cage 80 and the outer peripheral surface 82B of the second portion 54B, is reduced. As a result, the possibility of contact between the second member 50 of the outer ring 60 and the cage 80, thus hindering the stable rotation of the cage 80, is reduced. Thus, based on the aforementioned driven bearing 1A, it is possible to suppress operating noise and aggression towards other components, and to ensure stable operation of the bearing.

[0071] In the driven bearing 1A of the above embodiment, in a cross-section cut by the plane containing the rotating shaft 31 of the driven bearing 1A, the outer peripheral surfaces 82A and 82B of the cage 80 extend straight along the axial direction. Furthermore, the first opposing surface 54C and the second opposing surface 54D extend straight along the axial direction. Therefore, in the axial direction, the contact area between the flange portion 12 and the first portion 54A, and between the side plate 20 and the second portion 54B, can be maximized. Thus, it is possible to suppress the outer ring 60 from overshooting the flange portion 12 and the side plate 20 during bearing operation, thereby stabilizing the operation, and to distribute the load in cases where thrust loads are generated due to misalignment, etc. As a result, the driven bearing 1A with this structure becomes a driven bearing that can more effectively ensure stable bearing operation. Furthermore, for example, the choice between the structure of Embodiment 1 and Embodiment 2 is determined based on factors such as the radial dimensions of the flange portion 12 and the side plate 20, and the operating environment of the driven bearing.

[0072] In the driven bearing 1A of the above embodiment, the first member 40 includes: a cylindrical portion 42 having a hollow cylindrical shape and including a second track surface 41; and a protrusion 43 extending radially outward from the cylindrical portion 42. Axially, the two sides of the protrusion 43 are filled by the second member 50. Therefore, the possibility of axial separation between the first member 40 and the second member 50 can be reduced. Thus, such a driven bearing 1A becomes a driven bearing capable of achieving improved reliability.

[0073] In the driven bearing 1A of the above embodiment, the protrusion 43 is connected to the axial end 46 of the cylindrical portion 42. Therefore, the first member 40 with such a structure of protrusion 43 can be easily manufactured using stamping, drawing, or other methods. Furthermore, the shape of the protrusion 43 is not limited to the above embodiment; for example, a shape in which the protrusion 43 is bent radially outward and then folded back toward the outer peripheral surface 44A of the cylindrical portion 42 can be appropriately selected. In addition, the protrusion 43 may also be formed at both axial ends of the cylindrical portion 42.

[0074] In the driven bearing 1A of the above embodiment, the protrusion 43 has a continuous annular shape covering the entire circumferential region of the first member 40. The driven bearing 1A with such a structure in the first member 40 becomes a driven bearing that can further reduce the possibility of axial separation between the first member 40 and the second member 50.

[0075] In the driven bearing 1A of the above embodiment, a recessed cut 47 is formed in the protrusion 43. Therefore, the second member 50 can enter the interior of the cut 47. Thus, such a driven bearing 1A becomes a driven bearing capable of limiting the relative rotation of the first member 40 with respect to the second member 50.

[0076] In the driven bearing 1A of the above embodiment, multiple cutouts 47 are formed at intervals in the circumferential direction. Therefore, such a driven bearing 1A becomes a driven bearing capable of further limiting the relative rotation of the first member 40 with respect to the second member 50.

[0077] In the driven bearing 1A of the above embodiment, the shaft member 30 includes: a main body portion 10 including a first track surface 11; and a flange portion 12 as a first protrusion, the flange portion 12 having an annular shape with its central axis aligned with the first track surface 11, disposed on one side axially relative to the first track surface 11, and protruding radially outward from the outer periphery of the main body portion 10. Furthermore, the second member 50 includes a first portion 54A, the first portion 54A having an annular shape with its central axis aligned with the first track surface 11, and entering between the flange portion 12 and the first member 40. Therefore, such a driven bearing 1A becomes a driven bearing capable of preventing the flange portion 12 from contacting the first member 40 axially.

[0078] In the driven bearing 1A of the above embodiment, the shaft member 30 includes a side plate 20 as a second protrusion. The side plate 20 has an annular shape with its central axis aligned with the first track surface 11, and is disposed on the opposite side of the axial direction relative to the first track surface 11, protruding radially outward from the outer periphery of the main body 10. The second member 50 includes a second portion 54B, which has an annular shape with its central axis aligned with the first track surface 11, and enters between the side plate 20 and the first member 40. Therefore, such a driven bearing 1A becomes a driven bearing that can prevent the side plate 20 and the first member 40 from contacting each other in the axial direction.

[0079] Here, the radial lengths of gaps 91A and 91B can be adjusted based on the displacement and the assumed load. Figure 8 This is a graph showing the relationship between load and deformation after changing the outer circumferential dimensions of the driven bearing 1A. Figure 8 In the diagram, the vertical axis represents the deformation (mm), and the horizontal axis represents the load (N). The diagram shows cases where the outer perimeter D1 is set to 16mm, 19mm, 22mm, and 30mm. (Refer to...) Figure 8 For example, with an outer perimeter D1 dimension of 16 mm and an assumed load of 100 N, the deformation amount is expressed as a value slightly smaller than 0.3 mm. Conversely, with an outer perimeter D1 dimension of 30 mm and an assumed load of 100 N, the deformation amount is expressed as a value slightly larger than 0.1 mm. These values ​​can be taken into account when defining the radial dimensions of the gaps 91A and 91B, i.e., the radial positions of the first opposing surface 54C and the second opposing surface 54D.

[0080] (Implementation Method 2)

[0081] Next, another implementation method, namely implementation method 2, will be described. Figure 9 This is a schematic cross-sectional view showing a portion of the driven bearing in Embodiment 2. Figure 10 It is an enlarged representation Figure 9 A schematic cross-sectional view of a portion of the driven bearing shown. The driven bearing in Embodiment 2 differs from that in Embodiment 1 in that the shapes of the first opposing surface and the second opposing surface are different.

[0082] Reference Figure 9 and Figure 10In the cross-section of Embodiment 2, cut along the plane containing the rotating shaft of the driven bearing 1B, the distance between the first opposing surface 54C and the outer peripheral surface 82A of the cage 80 is inclined relative to the axial direction, increasing from the side closer to the cylindrical portion 42 towards the side farther from the cylindrical portion 42. Furthermore, in the driven bearing 1B described above, the first portion 54A includes a tongue-shaped portion 54E extending into the region between the cage 80 and the cylindrical portion 42. The tongue-shaped portion 54E is formed to extend radially inward. Additionally, the tongue-shaped portions 54E are connected in a ring shape.

[0083] Here, when a load is applied from the outer periphery of the outer ring 60, specifically in the first portion 54A of the second member 50, the area near the outer side of the bearing, closer to the flange 12, experiences greater deformation towards the inner periphery than the area away from the flange 12. In this embodiment, as described above, the first opposing surface 54C is inclined axially in a manner that increases from the side closer to the cylindrical portion 42 towards the side farther from the cylindrical portion 42. Therefore, when a load is applied from the outer periphery of the outer ring 60, the deformed first opposing surface 54C can be nearly parallel to the arrangement of the rotation shaft 31 and, consequently, the outer periphery surface 82A of the cage 80. This reduces the likelihood of the second member 50 contacting the cage 80 and further ensures stable bearing operation.

[0084] Furthermore, according to this embodiment, the tongue-shaped portion 54E significantly reduces the likelihood of the cage 80 contacting the cylindrical portion 42. This suppresses wear on the cage 80 caused by contact with the cylindrical portion 42. Consequently, more reliable and stable bearing operation can be ensured.

[0085] Furthermore, in the above-described embodiment, the distance between the first opposing surface 54C and the outer peripheral surface 82A of the retainer 80 is configured such that it increases from the side closer to the cylindrical portion 42 to the side farther away from the cylindrical portion 42. However, it is not limited to this. Alternatively, the distance between at least one of the first opposing surface 54C and the second opposing surface 54D and the outer peripheral surfaces 82A and 82B of the retainer 80 may be inclined relative to the axial direction such that it increases from the side closer to the cylindrical portion 42 to the side farther away from the cylindrical portion 42.

[0086] Furthermore, in the above embodiment, the first portion 54A includes a tongue-shaped portion 54E extending into the region between the retainer 80 and the cylindrical portion 42. However, it is not limited to this; at least either the first portion 54A or the second portion 54B may include a tongue-shaped portion extending into the region between the retainer 80 and the cylindrical portion 42. Multiple tongue-shaped portions may be provided at intervals in the circumferential direction, or only one tongue-shaped portion may be provided in the circumferential direction.

[0087] (Implementation Method 3)

[0088] Next, another implementation method, namely implementation method 3, will be described. Figure 11 This is a schematic cross-sectional view showing a portion of the driven bearing in Embodiment 3. The driven bearing in Embodiment 3 differs from that in Embodiment 1 in that the cylindrical portion has an opposing region that faces the outer circumference of the cage in the radial direction.

[0089] Reference Figure 11 In Embodiment 3, in a cross-section cut along the plane containing the rotating shaft of the driven bearing 1C, the axial length of the cylindrical portion 42 is configured to be longer than the axial length of the cylindrical portion 42 in Embodiment 1. Furthermore, the cylindrical portion 42 has a counter region 48 that radially opposes the outer peripheral surface 82A of the retainer 80. The counter region 48 is formed in connection with the second track surface 41.

[0090] According to this embodiment, even if the outer ring 60 deforms towards the inner circumference due to loads applied from the outer periphery, it will still contact the cage 80 in the opposing region 48 of the cylindrical portion 42. This reduces the likelihood of the cage 80 contacting the second member 50. Therefore, smooth rotation of the cage 80 is easily ensured.

[0091] (Implementation Method 4)

[0092] Next, another implementation method, namely implementation method 4, will be described. Figure 12 This is a schematic cross-sectional view showing a portion of the driven bearing in Embodiment 4. The driven bearing in Embodiment 4 differs from that in Embodiment 1 in that the cage is a stamped steel cage.

[0093] Reference Figure 12 In embodiment 4, the driven bearing 1D includes a cage 80 made of steel and stamped. Even with such a structure, stable operation of the bearing can be ensured.

[0094] (Implementation Method 5)

[0095] Next, another implementation method, namely implementation method 5, will be described. Figure 13 This is a schematic cross-sectional view showing a portion of the driven bearing in embodiment 5. Figure 14 This is a schematic perspective view of the driven bearing in Embodiment 5, in which the second member is omitted. The driven bearing in Embodiment 5 differs from that in Embodiment 1 in that the first member is provided with a recess, which serves as a rotation suppression mechanism to suppress circumferential rotation of the second member relative to the first member.

[0096] Reference Figure 13 and Figure 14The driven bearing 1E in embodiment 4 includes recesses 49A and 49B as rotation suppression mechanisms for suppressing relative rotation of the second member 50 with respect to the first member 40 in the circumferential direction, and a second member 59 that penetrates into the recesses 49B and 49B. The recesses 49A and 49B are recessed in a circular hole shape from the outer peripheral surface 44A of the cylindrical portion 42. A plurality of recesses 49A and 49B are provided at intervals in the circumferential direction.

[0097] According to this embodiment, the relative rotation of the second member 50 with respect to the first member 40 can be suppressed by the recesses 49A and 49B and the second member 59 entering the recesses 49A and 49B. Furthermore, the axial movement of the second member 50 relative to the first member 40 can also be restricted. This structure can be easily formed by providing the recesses 49A and 49B of the above structure in the cylindrical portion 42, and then providing the second member 50 on the outer periphery of the first member 40, allowing resin to flow into the recesses 49A and 49B.

[0098] (Other implementation methods)

[0099] In the aforementioned driven bearing, the resin constituting the second component 50 may also include reinforcing fibers. Examples of reinforcing fibers include glass fiber and carbon fiber.

[0100] Furthermore, while the above embodiment describes the use of rollers 70 as the rolling elements of the driven bearing, balls can also be used as rolling elements. Additionally, while the above embodiment describes the rolling elements arranged in a single row, multiple rows are also possible. Furthermore, while the above embodiment describes the use of a solid shaft member 30 as the inner member, a raceway ring (inner ring) can also be used as the inner member. Moreover, the second member 50 can be appropriately selected to be a hollow cylindrical member, a member with a spherical outer surface, or the like.

[0101] In this disclosure, a driven bearing refers to a bearing in which the outer ring contacts other components while rotating relative to the shaft component in the circumferential direction with respect to the shaft component, while the shaft component is fixed. The other components are not particularly limited and may be, for example, a cam, a guide rail, or a belt.

[0102] 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.

[0103] Industrial applicability

[0104] The driven bearing of the present invention is particularly effective in situations where it is required to ensure stable operation of the bearing.

Claims

1. A driven bearing, wherein, have: The inner component has a first track surface in the shape of an annulus on its outer circumferential surface; The outer ring has a second track surface in the shape of an annulus on its inner circumferential surface that faces the first track surface; Multiple rolling elements are configured to contact the first and second track surfaces on an annular track along the first and second track surfaces; as well as A cage holds the plurality of rolling elements; The outer ring includes: The first ring-shaped component is made of steel; and The second ring-shaped component is made of resin and covers the outer peripheral surface of the first component. The first component includes a cylindrical portion having a hollow cylindrical shape and containing the second track surface. The second component includes: The first part, axially disposed on one side of the cylindrical portion, has a first opposing surface radially facing the outer peripheral surface of the retainer; and The second part, axially disposed on the other side of the cylindrical portion, has a second opposing surface that radially faces the outer periphery of the retainer. In the radial direction, the first opposing surface and the second opposing surface are respectively positioned on the outer periphery side of the second track surface. In a cross-section cut by the plane containing the rotating shaft of the driven bearing, The distance between at least one of the first opposing surface and the second opposing surface and the outer peripheral surface of the cage is inclined relative to the axial direction in a manner that increases from the side closer to the cylindrical portion to the side farther away from the cylindrical portion.

2. The driven bearing as claimed in claim 1, wherein, At least one of the first portion and the second portion includes a tongue-shaped portion that extends into the region between the retainer and the cylindrical portion.

3. The driven bearing as described in claim 1, wherein, The cylindrical portion has an opposing region that faces the outer periphery of the cage in the radial direction.

4. The driven bearing as claimed in claim 1, wherein, The outer peripheral surface of the cylindrical portion extends straight along the axial direction.

5. The driven bearing as claimed in claim 1, wherein, The first component includes a protrusion extending radially outward from the cylindrical portion.

6. The driven bearing as claimed in claim 1, wherein, It also has a rotation suppression mechanism. The rotation suppression mechanism suppresses the relative circumferential rotation of the first member with respect to the second member.

7. The driven bearing as claimed in claim 6, wherein, The rotation suppression mechanism further includes a recessed portion that forms a circular hole in the outer peripheral surface of the cylindrical portion. A portion of the second component enters the recess.

8. The driven bearing as claimed in claim 1, wherein, The cage is a welded cage.

9. The driven bearing as claimed in claim 1, wherein, The resin constituting the second component is composed of an elastomer.

10. The driven bearing as claimed in claim 9, wherein, The elastomer is a thermoplastic elastomer.

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

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