Conical roller bearing

Abstract

To provide a conical roller bearing capable of securely guiding an inner ring and improving the durability of a retainer.SOLUTION: A conical roller bearing 1 comprises an inner ring 2 having flange parts 2b, 2c, an outward member 3, a plurality of conical rollers 4, and a retainer 5 retaining the conical rollers 4, wherein the retainer 5 has a small diameter-side annular part 6, a larger diameter-side annular part 7, and column parts 8 at a plurality of circumferential positions connecting the small diameter-side annular part 6 and the larger diameter-side annular part 7, and one or both of the small diameter-side annular part 6 and larger diameter-side annular part 7 have flange-like parts 6a, 7a extending from column parts 8 toward the inner diameter side through arcuate bent parts, the retainer being guided with the inner ring. Here, the bearing 1 revolves, and 0.50018<(d1 / d2) / 2<0.5049 and 0.50018<(d1 / d2) / 2<0.5056X(-0.002) hold for an inner diameter d1 of the flange-like parts 6a, 7a, an outer diameter d2 of the flange parts 2b, 2c of the inner ring 2, and centrifugal acceleration X of the revolving motion.SELECTED DRAWING: Figure 1

Description

[Technical field]

[0001] The present invention relates to a tapered roller bearing that can be used in locations where centrifugal force acts, such as planetary gear mechanisms that constitute reducers in construction machines and the like, and in particular in first-stage planetary gears where centrifugal force is large. [Background technology]

[0002] A typical tapered roller bearing is of the rolling element guided type, in which a cage 5 is guided by tapered rollers 4, as shown in Figure 11, for example. However, for tapered roller bearings used in an environment of revolution, such as the planetary gears of a planetary gear reducer, if the bearing is of the rolling element guided type, the centrifugal force generated by the revolution means that the behavior of the cage is less stable and wear to the columns is greater, so a raceway ring guided (inner ring guided or outer ring guided) type bearing is preferable.

[0003] In this regard, Figures 12A, 13A, 14A, and 15A show the operation of a tapered roller bearing using a standard cage with rolling element guide, and Figures 12B, 13B, 14B, and 15B show the operation of a tapered roller bearing using an inner ring guide cage capable of withstanding high centrifugal force. As shown in Figures 13A and 13B, when a tapered roller bearing is used for planetary gear 105 of a planetary reducer, the tapered roller bearing revolves as shown by arrow c, and centrifugal force F is applied to the entire tapered roller bearing. G When a tapered roller bearing with an outer ring guide and a cage capable of withstanding high centrifugal force is used in a planetary gear, the centrifugal force F acts on the entire tapered roller bearing in the same way. G comes into effect.

[0004] In this way, the centrifugal force F due to revolution is applied to the entire tapered roller bearing. G When the centrifugal force F acts on the inner ring 2, which is the fixed raceway of the tapered roller bearing, and the action between the bearing components is considered as being stationary, as shown in Figs. 14A and 14B, which are vertical cross-sectional views of the area enclosed by a square in Figs. 13A and 13B, G In the rolling element guide type shown in FIG. 14A, the clearance S between the inner ring flange, especially the small flange 2b, and the cage 5 is large, so the cage 5 is pulled by the centrifugal force F GWhen pulled in a direction away from the revolution axis center, the cage 5 moves greatly in that direction, and as shown in Fig. 15A which is an enlarged cross-sectional view of the portion enclosed by a square in Fig. 13A, the gap δ between the pocket inner surface of the column portion 8 of the cage 5 and the tapered roller 4 disappears, and the wear of the pocket inner surface of the column portion 8 increases.

[0005] However, in the inner ring guiding type shown in Fig. 14B, since the gaps S1 and S2 between the inner ring flange portions (the small flange portion 2b and the large flange portion 2c) and the cage 5 are small, even when the cage 5 is pulled in a direction away from the revolution axis center by centrifugal force, the amount of movement of the cage 5 in that direction is small. As shown in Fig. 15B which is an enlarged cross-sectional view of the portion enclosed by a square in Fig. 13B, the gap δ between the pocket inner surface of the column portion 8 and the tapered roller 4 is maintained, and the wear of the pocket inner surface of the column portion 8 does not increase either.

[0006] As a tapered roller bearing of the inner ring guiding type, there is one in which flange-like portions are provided on both the small-diameter side and the large-diameter side of the cage, and the inner peripheral edge thereof is used as a sliding surface to guide the cage with the inner ring (for example, Patent Document 1).

Prior Art Documents

Patent Documents

[0007]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0008] However, even in the case of a tapered roller bearing with an inner ring guiding type, when the inner ring 2 and the cage 5 come into contact on the sliding surface, the durability of the cage 5 may be reduced due to the stress generated by the deformation of the axial cross-section of the cage 5 into an elliptical shape with the major axis in the direction pulled from the circular shape. The degree of elliptical deformation of the cage 5 is determined by the size in the circumferential direction of the region (so-called guiding region) where the cage guiding surface of the inner ring 2 and the guided portion of the cage 5 slide. That is, the smaller the guiding region is in the circumferential direction, the more concentrated the force acting due to contact is in the circumferential direction, so the degree of elliptical deformation becomes larger. The larger the guiding region is in the circumferential direction, the more the force is dispersed in the circumferential direction, so the degree of elliptical deformation becomes smaller. The size of this guiding region is determined based on the size of the clearance (so-called guiding clearance) between the cage guiding surface of the inner ring 2 and the guided portion of the cage 5. Therefore, in order to reduce the stress generated by the elliptical deformation of the cage and improve the durability of the cage 5, it is necessary to appropriately limit the relationship between the outer diameter of the cage guiding surface of the inner ring 2 and the inner diameter of the guided portion of the cage 5. Furthermore, since the sliding between the cage guiding surface of the inner ring 2 and the guided portion of the cage 5 can be caused by the centrifugal force generated by the revolving motion of the tapered roller bearing 1, it is also necessary to consider the centrifugal acceleration of the tapered roller bearing 1.

[0009] An object of the present invention is to provide a tapered roller bearing of an inner ring guiding type that can suppress the deformation of the cage and improve the durability of the cage even in an environment where the bearing revolves and centrifugal force acts on the cage.

Means for Solving the Problems

[0010] The tapered roller bearing 1 of the present invention has an inner ring 2 having flange portions 2b and 2c, an outer member 3 having an annular rolling surface 3a facing the rolling surface 2a of the inner ring 2, a plurality of tapered rollers 4 interposed between the inner ring 2 and the outer member 3, a cage 5 that holds the plurality of tapered rollers 4, and is provided with The retainer 5 has a small-diameter side annular portion 6, a large-diameter side annular portion 7, and a plurality of column portions 8 at a plurality of circumferential positions connecting the small-diameter side annular portion 6 and the large-diameter side annular portion 7. Either one or both of the small-diameter side annular portion 6 and the large-diameter side annular portion 7 of the retainer 2 have flange-like portions 6a, 7a that bend and extend inward in diameter with respect to the column portion 8, and the retainer is a tapered roller bearing 1 guided by the inner ring. The bearing performs a revolving motion, and the inner diameters d1 of the flange-like portions 6a, 7a, the outer diameters d2 of the flange portions 2b, 2c of the inner ring 2, and the centrifugal acceleration X due to the revolving motion satisfy the following conditions expressed by the following inequalities (1) and (2). 0.50018 < (d1 / d2) / 2 < 0.5049 …(1) And, 0.50018 < (d1 / d2) / 2 < 0.5056X (-0.002) …(2) (Here, the centrifugal acceleration X is a value in units of the gravitational acceleration G.) Satisfy.

[0011] According to this configuration, the centrifugal force acting on the retainer 5 from the tapered roller bearing 1 can be dispersed in the circumferential direction to suppress the deformation of the retainer 5, so that the stress generated in the retainer 5 is reduced. As a result, the fatigue resistance of the retainer 2 is improved and the occurrence of defects can be prevented. Here, the inner ring guidance means that the retainer 5 and the inner ring 2 are in a dimensional relationship in which the inner diameter surface of the retainer 5 has a slight radial clearance with respect to the outer peripheral surface of the inner ring 2, and the retainer 5 slides and rotates its inner diameter surface on the outer peripheral surface of the inner ring 2.

[0012] In the tapered roller bearing of the present invention, the retainer may be formed by pressing or turning.

[0013] In the tapered roller bearing 1 of the present invention, the large-diameter side annular portion 7 has a flange-shaped portion 7a extending inward in diameter from the column portion 8 via an arcuate bent portion, and the bending angle formed by the flange-shaped portion 7a with respect to the column portion 8 may be in the range of 90° ± 10° based on the cage angle which is the angle at which the column portion 8 inclines with respect to the bearing axis. When the bending angle of the flange-shaped portion 7a of the large-diameter side annular portion 7 is in the range of 90° ± 10°, it becomes an appropriate shape for making the cage 2 into an inner ring guiding type.

[0014] In the tapered roller bearing 1 of the present invention, the large-diameter side annular portion 7 has a flange-shaped portion 7a extending inward in diameter from the column portion 8 via an arcuate bent portion, and the radius of curvature of the inner diameter side surface of the bent portions 6b, 7b where the flange-shaped portion 7a is continuous may be greater than 20% and less than 90% with respect to the length of the large-diameter side annular portion 7 in the direction in which the column portion 8 extends. When the radius of curvature is 20% or less with respect to the axial length of the large-diameter side annular portion 7, stress concentration during bending increases, and there is a concern that a defect may occur in the cage 5. Also, when it is 90% or more, the arc shape of the inner diameter side surface of the bent portion 7b becomes too gentle, and there is a concern that the end face of the roller 4 may hit the edge with respect to the opening edge of the pocket 9. If it is greater than 20% and less than 90%, there will be no such problem.

[0015] In the tapered roller bearing 1 of the present invention, notch-shaped or window-shaped oil passages 10, 11 that allow the passage of lubricating oil may be provided at a plurality of circumferential positions on the inner peripheral edge of the flange-shaped portions 6a, 7a in the circumferential direction with respect to the inside and outside in the bearing axis direction of the flange-shaped portions 6a, 7a. By forming the oil passages 10, 11 in this way, the lubricating oil easily passes inside and outside the flange-shaped portions 6a, 7a of the cage 5, and good lubrication can be obtained between the rolling surfaces of the tapered rollers 4 and the inner surfaces of the pockets of the cage 5.

[0016] In the tapered roller bearing 1 of the present invention, the cross-sectional area ratio of the large-diameter side annular portion 7 of the cage 5 to the small-diameter side annular portion 6 may be 1.0 to 1.2. When the cross-sectional area ratio of the large-diameter-side annular portion 7 to the small-diameter-side annular portion 6 is in the range of 1.0 to 1.2, the weight balance between the large-diameter side and the small-diameter side becomes appropriate, the running of the cage 5 is suppressed, and good inner ring guidance can be achieved.

[0017] In the tapered roller bearing 1 of the present invention, the tapered roller bearing may be used for a planetary gear of a planetary gear mechanism and revolve integrally with the planetary gear.

Advantages of the Invention

[0018] In the tapered roller bearing of the present invention, the inner diameter d1 of the flange-shaped portion of the cage, the outer diameter d2 of the collar portion of the inner ring, and the centrifugal acceleration X of the cage are the conditions represented by the following inequalities (1) and (2) 0.50018 < (d1 / d2) / 2 < 0.5049 …(1) And 0.50018 < (d1 / d2) / 2 < 0.5056X (-0.002) …(2) (Here, the centrifugal acceleration X is a value in units of the gravitational acceleration G.) By satisfying the above conditions, the clearance between the collar portion of the inner ring and the flange-shaped portion of the cage becomes sufficiently small, and the area where the collar portion of the inner ring and the flange-shaped portion of the cage come into contact becomes large in the circumferential direction. Therefore, the force acting on the cage during contact is dispersed in the circumferential direction. As a result, the elliptical deformation generated in the cage is suppressed, and the stress generated in the cage can be reduced. Thus, improvement in the durability of the cage and prevention of defects can be realized.

Brief Description of the Drawings

[0019]

Figure 1

Figure 2

Figure 3A

Figure 3B

Figure 4

Figure 5

Figure 6

Figure 7

Figure 8

Figure 9

Figure 10A

Figure 10B

Figure 11

Figure 12A

Figure 12B

Figure 13A

Figure 13B

Figure 14A

Figure 14B

Figure 15A

Figure 15B

Mode for Carrying Out the Invention

[0020] Hereinafter, a tapered roller bearing according to an embodiment of the present invention will be described with reference to FIGS. 1 to 7. Note that this tapered roller bearing 1 is used for a planetary gear in a planetary gear reducer or a planetary gear transmission, which will be described later with reference to FIGS. 8 and 9.

[0021] In FIG. 1, this tapered roller bearing 1 includes an inner ring 2, an outer member 3, a plurality of tapered rollers 4 interposed between the inner ring 2 and the outer member 3, and a cage 5 that holds these plurality of tapered rollers 4. The inner ring 2 has a rolling surface 2a that is a tapered surface whose diameter increases from near one end to near the other end in the axial direction of the bearing axis (the direction of the bearing axis O, simply referred to as the axial direction), and has flange portions 2b and 2c at each of the one end and the other end. The outer member 3 is an annular component having a rolling surface 3a that is a tapered surface whose diameter increases from one end to the other end and faces the rolling surface 2a of the inner ring 2. The outer member 3 is a component corresponding to the "outer ring" in the case of a component having only the function of a bearing, but is a component of a concept including, for example, a component whose outer peripheral surface is a gear portion and whose inner peripheral surface has the rolling surface 3a, and is referred to as an "outer member" in this specification. In this specification, in test and analysis examples, etc., the "outer member" may be referred to as the "outer ring". The inner ring 2 has flanges at both ends in the illustrated embodiment, but may have a flange portion only at one of the one end and the other end. Further, the outer member 3 has no flange in the illustrated embodiment, but may have a flange portion (not shown) that protrudes inward on one end or the other end.

[0022] The cage 5 has a small-diameter-side annular portion 6, a large-diameter-side annular portion 7, and a plurality of column portions 8 at a plurality of circumferential positions connecting the small-diameter-side annular portion 6 and the large-diameter-side annular portion 7. Between adjacent column portions 8, there is a pocket 9 for holding the tapered roller 4. The inner diameter surfaces of the small-diameter-side annular portion 6 and the large-diameter-side annular portion 7 of the cage 5 are sized to be guided by the two flange portions 2b and 2c of the inner ring 2 respectively. Thus, this tapered roller bearing 1 is a bearing of the inner ring guiding type. Hereinafter, the flange portion 2b that guides the small-diameter-side annular portion 6 of the cage 5 is referred to as the small flange portion, and the flange portion 2c that guides the large-diameter-side annular portion 7 is referred to as the large flange portion. Note that the cage 5 only needs to be of the inner ring guiding type, and it may be configured to be guided by only one of the small flange portion 2b and the large flange portion 2c of the inner ring 2. Basically, it is preferably of a type guided by at least the small flange portion 2b of the inner ring 2.

[0023] The tapered roller bearing 1 is used for the planetary gear of a planetary gear mechanism in a device having a planetary gear mechanism such as a planetary gear reducer or a planetary gear transmission. It rotatably supports the rotational motion of this planetary gear and has a centrifugal acceleration by revolving integrally with the planetary gear. Let the value obtained by expressing the centrifugal acceleration due to the revolving motion when the tapered roller bearing 1 is incorporated into a device having a planetary gear mechanism and operates at its rated speed, as a dimensionless number with the gravitational acceleration G as the unit, be X. Regarding the dimensions of the tapered roller bearing 1, let the inner diameter of the flange-like portion in the cage 5 of the tapered roller bearing 1 be d1, and the outer diameter of the flange portion of the inner ring 2 be d2. Regarding these X, d1, and d2, the conditions expressed by the following inequalities (1) and (2) 0.50018 < (d1 / d2) / 2 < 0.5049 …(1) And, 0.50018 < (d1 / d2) / 2 < 0.5056X (-0.002) …(2) (Here, the centrifugal acceleration X is a value with the gravitational acceleration G as the unit.) are defined to be satisfied. The centrifugal acceleration X is the acceleration of the tapered roller bearing that undergoes acceleration motion along a curve such as circular motion. As in this embodiment, when the tapered roller bearing undergoes a revolving motion, as the centrifugal acceleration in circular motion, from the revolving radius r and the revolving angular velocity ω in the revolving motion, the formula (centrifugal acceleration X) = (revolving radius r) × (revolving angular velocity ω)2 It is calculated by

[0024] Here, when the cage 5 has a flange-like portion 6a on the small-diameter side annular portion 6 and the inner ring 2 has a small collar portion 2b on the small-diameter side, the inner diameter d of the flange-like portion 6a 1I and the outer diameter d of the small collar portion 2b 2I are respectively denoted as d1 and d2. When the cage 5 has a flange-like portion 7a on the large-diameter side annular portion 7 and the inner ring 2 has a large collar portion 2c on the large-diameter side, the inner diameter d of the flange-like portion 7a 1II and the outer diameter d of the large collar portion 2c 2II are respectively denoted as d1 and d2. As shown in Fig. 1, when the inner ring 2 has both collars with a small collar portion 2b and a large collar portion 2c, and the cage has flange-like portions 6a and 7a on both the small-diameter side annular portion 6 and the large-diameter side annular portion 7, the sets d of the inner diameters of the respective flange-like portions and the outer diameters of the collar portions on the small-diameter side and the large-diameter side 1I and d 2I and, d 1II and d 2II are both defined so as to satisfy the ranges represented by inequalities (1) and (2). Here, the subscript "I" means corresponding to the small-diameter side, and the subscript "II" means corresponding to the large-diameter side.

[0025] The value 0.50018 in inequalities (1) and (2) was determined so that the guiding clearance becomes 0 or more when the inner ring 2 expands. The value 0.5049 in inequality (1) was determined based on the maximum guiding clearance that can realize the inner ring guiding type in the tapered roller bearing. The term 0.5056X in inequality (2) (-0.002) was determined based on the results obtained by performing a dynamic analysis under conditions simulating the planetary gear mechanism of the planetary gear reducer, with the inner diameter d1 of the flange-like portion of the cage, the outer diameter d2 of the collar portion of the inner ring, and the centrifugal acceleration X as parameters.

[0026] A graph showing the results of the dynamic analysis is shown in FIG. 7. The horizontal axis X of the graph represents the centripetal acceleration in the revolution motion of the tapered roller bearing 1, with the gravitational acceleration G as the unit, and the vertical axis Y of the graph represents the diameter ratio (d1 / d2) / 2 between the inner diameter d1 of the cage and the outer diameter d2 of the inner ring. The points plotted in the graph are the points of the centripetal acceleration X of the tapered roller bearing at which the stress generated in the cage reaches a predetermined threshold value regarding the defects generated in the cage when the tapered roller bearing having the diameter ratio (d1 / d2) / 2 revolves in the planetary gear mechanism. These plotted points can be approximated by the formula Y = 0.5056X (-0.002) shown by the dotted line in the graph, and it was found that when the diameter ratio is below the upper limit value represented by this formula, the stress generated in the cage becomes sufficiently small, and defects generated in the cage can be prevented.

[0027] Thus, for the inner diameter d1 of the cage and the outer diameter d2 of the inner ring, by determining the diameter ratio (d1 / d2) / 2 to be in the range of 0.50018 < (d1 / d2) / 2 < 0.5049 and 0.50018 < (d1 / d2) / 2 < 0.5056X (-0.002) the inner diameter d1 of the flange-shaped portion of the cage and the outer diameter d2 of the collar portion of the inner ring are appropriately defined in consideration of the deformation of the cage, the expansion of the inner ring, etc. due to the centripetal acceleration X of the tapered roller bearing. As a result, the elliptical deformation generated in the cage can be suppressed, and the stress generated in the cage can be reduced, so that the durability of the cage can be improved and defects can be prevented.

[0028] Further, in this tapered roller bearing, as shown in FIG. 4, the small-diameter side annular portion 6 and the large-diameter side annular portion 7 of the cage 5 have flange-shaped portions 6a and 7a that extend inward in diameter via arcuate bent portions 6b and 7b from the column portion 8. The cage 5 may be a molded product of resin, but in this embodiment, it is formed by pressing from a metal plate such as an iron plate. The small-diameter side annular portion 6 and the large-diameter side annular portion 7 are formed by bending, and the column 8 is formed by punching out the pocket 9 by pressing. In addition to this, the cage 5 may be formed by turning from metal or may be a molded product of resin.

[0029] In addition, in this tapered roller bearing 1, the large-diameter side annular portion 7 has a flange-shaped portion 7a, and the bending angle β formed with respect to the column portion 8 of the flange-shaped portion 7a is in the range of 90° ± 10° (80° or more and 100° or less) based on the cage angle which is the angle at which the column portion 8 inclines with respect to the bearing axis O. When the bending angle β of the flange-shaped portion 7a is in the range of 90° ± 10°, it becomes an appropriate shape for adopting the inner ring guiding type for the cage 5. The inner diameter surfaces of the small-diameter side annular portion 6 and the large-diameter side annular portion 7 are preferably parallel to the outer peripheral surfaces of the small collar portion 2b and the large collar portion 2c of the inner ring 2, but they may be inclined.

[0030] Furthermore, in this tapered roller bearing 1, as shown in FIG. 4, the large-diameter side annular portion 7 has a flange-shaped portion 7a, and the curvature radius b1 of the inner diameter side surface of the bending portion 7b where the flange-shaped portion 7a is continuous is more than 20% and less than 90% with respect to the length a of the large-diameter side annular portion 7 in the direction in which the column portion 8 extends. If the curvature radius b1 of the inner diameter side surface of the bending portion 7b of the large-diameter side annular portion 7 is 20% or less with respect to the length a of the large-diameter side annular portion 7b in the direction in which the column portion 8 extends, there is a concern that the stress concentration during the bending process of the cage 5 will increase and problems will occur. If it is 90% or more, as shown by the thin line in FIG. 5, the arc shape of the inner diameter side surface of the bending portion 7b becomes too gentle, and there is a concern that the end face of the tapered roller 4 will hit the edge with respect to the opening edge of the pocket 9. If it is more than 20% and less than 90%, there will be no such problems.

[0031] Furthermore, in this tapered roller bearing 1, as shown in FIGS. 3A and 3B, at a plurality of locations on the inner peripheral edges of the flange-like portions 6a and 7a, there are notch-shaped oil passages 10 and 11 that allow the passage of lubricating oil in the axial direction inside and outside the bearing shaft of the flange-like portions 6a and 7a. The notch shape of the oil passages 10 and 11 is an arc in this embodiment, but it may be an elliptical arc or other shapes. Also, the flange-like portion may be provided only on either one of the small-diameter side annular portion 6 and the large-diameter side annular portion 7. By providing such oil passages 10 and 11, it becomes easier for the lubricating oil to pass inside and outside the flange-like portions 6a and 7a of the cage 5, and good lubrication can be obtained between the tapered roller 4 and the rolling surfaces 2a and 3a and the inner surface of the cage pocket. However, the oil passages 10 and 11 do not necessarily have to be provided.

[0032] Furthermore, in this tapered roller bearing 1, as shown in the upper part of FIG. 1, the cross-sectional area ratio, which is the cross-sectional area of the vertical section that does not pass through the oil passage 11 in the large-diameter side annular portion 7 to the cross-sectional area of the vertical section that does not pass through the oil passage 10 in the small-diameter side annular portion 6, is greater than 1.0 and less than 1.2. When this cross-sectional area ratio is greater than 1.0 and less than 1.2, the weight balance between the large-diameter side and the small-diameter side becomes appropriate, the wobbling of the cage 5 is suppressed, and good inner ring guidance can be achieved. Note that the cross-sectional area of the vertical section that does not pass through the oil passage 10 in the small-diameter side annular portion 6 is the maximum value of the cross-sectional area of the vertical section of the small-diameter side annular portion 6, and the cross-sectional area of the vertical section that does not pass through the oil passage 11 in the large-diameter side annular portion 7 is the maximum value of the cross-sectional area of the vertical section of the large-diameter side annular portion 7.

[0033] Figs. 8 and 9 show an example of a planetary gear speed reducer in which the tapered roller bearing 1 of this embodiment is used. This planetary gear speed reducer has a planetary gear mechanism, that is, a plurality of planetary gears 105 meshing with both gears 102 and 104 are arranged between a sun gear 102 attached to an input shaft 101 and an internal gear 104 fixed to a housing 103. Each planetary gear 105 is rotatably supported with respect to a carrier 107 connected to an output shaft 106, and the revolving motion of the planetary gear 105 revolving while rotating between the sun gear 102 and the internal gear 104 is output to the output shaft 106 via the carrier 107. This planetary gear speed reducer performs the first-stage deceleration of a final reduction gear provided inside a wheel rim of a construction machine, for example.

[0034] A pair of tapered roller bearings 1 are arranged between the planetary gear 105 and the carrier 107 of the planetary gear speed reducer. The outer member 3 (Fig. 1) of each tapered roller bearing 1 is attached to the planetary gear 105 and rotates integrally with the planetary gear 105. The inner ring 2 of each tapered roller bearing 1 is fixedly attached to a support shaft 108 provided on the carrier 107.

[0035] Note that the small-diameter side gap S1 in Fig. 14B, which is the gap between the small-diameter side annular portion 6 in Fig. 1 and the small flange portion 2b of the inner ring 2, and the large-diameter side gap S2, which is the gap between the large-diameter side annular portion 7 and the large flange portion 2c of the inner ring 2, change due to insufficient caulking of the small-diameter side annular portion 6 of the cage 5 during assembly or the like. Therefore, it is desirable to appropriately measure and confirm whether they are within an appropriate range. For example, to appropriately measure the small-diameter side gap S1, first, the tip spherical portion of the reference gap gauge 51 shown in Fig. 10A (for example, having a design value of S1 as a predetermined diameter) is inserted between the small-diameter side annular portion 6 of the cage 5 and the small flange portion 2b of the inner ring 2 at an arbitrary circumferential position (set as the 0° phase position), and at the 180° phase position facing the 0° phase position in the radial direction, the small-diameter side gap S1 is measured using the measuring gap gauges 52 shown in Fig. 10B (a plurality of them, with the diameters of the tip cylindrical portions slightly different from each other). The same is done by reversing the phase position where the reference gap gauge 51 is inserted and the phase position where the measuring gap gauge 52 is used, and the average value of the small-diameter side gaps S1 obtained by both is set as the reference gap.

[0036] Then, during measurement as appropriate, the tip sphere of the reference clearance gauge 51 is inserted between the small-diameter side annular portion 6 of the cage 5 and the small collar portion 2b of the inner ring 2 at an arbitrary circumferential position (set as the 0° phase position). By setting the 180° phase position to the state of the reference clearance, the small-diameter side clearance S1 at the 180° phase position is measured using the measurement clearance gauge 52, and it is confirmed whether the small-diameter side clearance S1 is within a predetermined appropriate range compared to the reference clearance. The large-diameter side clearance S2 can also be measured as appropriate in the same way to confirm whether it is within the appropriate range.

[0037] As described above, the embodiments for implementing the present invention based on the embodiments have been described. However, the embodiments disclosed this time are illustrative in all respects and not restrictive. The scope of the present invention is indicated by the claims rather than the above description, and it is intended that all modifications within the meaning and scope equivalent to the claims are included.

Explanation of Reference Numerals

[0038] 1... Tapered roller bearing 2... Inner ring 2a... Raceway surface 2b, 2c... Collar portions 3... Outer member 3a... Raceway surface 4... Tapered roller 5... Cage 6... Small-diameter side annular portion 6a... Flange-shaped portion 7... Large-diameter side annular portion 7a... Flange-shaped portion 7b... Bent portion 8... Column portion 9... Pocket 10, 11... Oil passage b1... Curvature radius of the inner diameter side surface of the bent portion d 1I ... Inner diameter of the flange-shaped portion of the small-diameter side annular portion d 1II ... Inner diameter of the flange-shaped portion of the large-diameter side annular portion d 2I ... Outer diameter of the small-diameter side collar portion of the inner ring d 2II ... Outer diameter of the large-diameter side collar portion of the inner ring O... Bearing axis β... buckling angle

Claims

1. An inner ring having a flange portion, An outer member having an annular rolling surface facing the rolling surface of the inner ring, A plurality of tapered rollers interposed between the inner ring and the outer member, A cage for holding the plurality of tapered rollers, Comprising, The cage has a small-diameter side annular portion, a large-diameter side annular portion, and a plurality of column portions in the circumferential direction connecting the small-diameter side annular portion and the large-diameter side annular portion, Either one or both of the small-diameter side annular portion and the large-diameter side annular portion have a flange-shaped portion extending inward in diameter via an arcuate bent portion from the column portion, and the cage is a tapered roller bearing guided by the inner ring, The bearing performs a revolving motion, and the inner diameter d of the flange-shaped portion １ , the outer diameter d of the flange portion ２ , and the centrifugal acceleration X due to the revolving motion satisfy the conditions expressed by the following inequalities (1) and (2), a tapered roller bearing. 0.50018 < (d １ / d ２ ) / 2 < 0.5049...(1) And, 0.50018 < (d １ / d ２ ) / 2 < 0.5056X （－０．００２） …(2) (Here, the centrifugal acceleration X is a value in units of the gravitational acceleration G.)

2. The tapered roller bearing according to claim 1, wherein the cage is formed by pressing or turning.

3. In the tapered roller bearing according to claim 1 or 2, the large-diameter side annular portion has a flange-shaped portion extending inward in diameter via an arcuate bent portion from the column portion, and the bending angle formed by the flange-shaped portion with respect to the column portion is in the range of 90° ± 10° based on the cage angle which is the angle at which the column portion inclines with respect to the bearing axis.

4. In the tapered roller bearing according to claim 1 or claim 2, the large-diameter side annular portion has a flange-shaped portion extending inward in diameter via an arcuate bent portion from the column portion, and the radius of curvature of the inner diameter side surface of the bent portion where the flange-shaped portion is continuous is greater than 20% and less than 90% with respect to the length of the large-diameter side annular portion in the direction in which the column portion extends.

5. In the tapered roller bearing according to claim 1 or claim 2, notch-shaped oil passages for allowing the passage of lubricating oil are provided at a plurality of locations on the inner peripheral edge of the flange-shaped portion, both inside and outside in the bearing axis direction of the flange-shaped portion.

6. In the tapered roller bearing according to claim 1 or claim 2, the cross-sectional area ratio, which is the ratio of the cross-sectional area of the large-diameter side annular portion to the cross-sectional area of the small-diameter side annular portion, is greater than 1.0 and less than 1.

2.

7. In the tapered roller bearing according to claim 1 or claim 2, the tapered roller bearing is used for a planetary gear of a planetary gear mechanism and revolves integrally with the planetary gear.

Images