Tapered roller bearing

Abstract

In a tapered roller bearing (1), a dimensionless number X given by the following formula (1) is defined as follows. The small-diameter side clearance S1 represents the clearance between the small-diameter side annular portion (6) of the cage (5) and the small rib portion (2b) of the inner ring (2), the large-diameter side clearance S2 represents the clearance between the large-diameter side annular portion (7) and the large rib portion (2c) of the inner ring (2), d represents the average roller diameter, l represents the roller length, and α represents the angle of the external member. Among them, this dimensionless number X is within the range of 0.69 < X < 1.12, and the formula (1) is: [Equation 1]

Description

[0001] Related applications

[0002] This application claims priority to JP Patent Application 2020-147202, filed on September 2, 2020, which is incorporated herein by reference in its entirety. Technical Field

[0003] This invention relates to parts that can be used under centrifugal force, such as planetary reducers in construction machinery, and particularly tapered roller bearings for first-stage planetary reducers where centrifugal force is high. Background Technology

[0004] For example, such as Figure 12 As shown, a typical tapered roller bearing is a roller-guided type where the cage 5 is guided by tapered rollers 4. However, for tapered roller bearings used in environments where the planetary parts of a planetary reducer are in orbital motion, the centrifugal force generated during orbital motion results in low stability of the cage operation and high wear on the column portion if the bearing is a rolling element-guided type. Therefore, a raceway-guided type bearing is preferable.

[0005] To explain this, Figure 13A , Figure 14A , Figure 15A , Figure 16A This indicates the function of tapered roller bearings using standard retainers with roller guidance. Figure 13B , Figure 14B , Figure 15B , Figure 16B This indicates the use of tapered roller bearings with retainers that act as inner ring guides to cope with high centrifugal forces. For example... Figure 14A , Figure 14B As shown, when tapered roller bearings are used in the planetary rotor 105 of the planetary reducer, the tapered roller bearings revolve as indicated by arrow c, thereby exerting centrifugal force G on the entire tapered roller bearing. The same applies to tapered roller bearings that use retainers as outer ring guides to cope with high centrifugal forces.

[0006] In this way, when the centrifugal force G generated by the revolution acts on the entire tapered roller bearing, if the inner ring 2, which is the fixed side raceway of the tapered roller bearing, is in a stationary state and the interaction between the bearing components is considered, then... Figure 15A , Figure 15B As shown in the cross-section of the bearing, centrifugal force G pulls the retainer 5 towards the inner diameter side. In this case, Figure 15A In the roller guide configuration shown, the gap d between the inner ring edge, especially the small edge 2b, and the retainer 5 is relatively large. When stretched towards the inner diameter due to centrifugal force G, the retainer 5 moves significantly radially. Figure 16AAs shown, the gap δ between the inner surface of the pocket of the retainer 5 and the tapered roller 4 disappears, and the wear of the column 8 increases.

[0007] However, in Figure 13B , Figure 14B , Figure 15B , Figure 16B In the inner ring guide configuration shown, the gaps d1 and d2 between the inner ring edge (small edge 2b, large edge 2c) and the retainer 5 are small. Even if the retainer 5 is stretched towards the inner diameter side due to centrifugal force, the radial movement of the retainer 5 is small, maintaining a gap δ between the inner surface of the pocket and the tapered roller 4, thus reducing the wear on the inner surface of the pocket of the column 8.

[0008] Documents on tapered roller bearings with inner ring guidance include the following technique: cutting edges are provided on both the minor and major diameter sides of the cage, and these cutting edges serve as sliding surfaces, with the inner ring used for guidance (e.g., Patent Document 1).

[0009] Existing technical documents

[0010] Patent documents

[0011] Patent Document 1: Specification of Chinese Patent Application CN103410853A Summary of the Invention

[0012] The problem that the invention aims to solve

[0013] The following problems exist with tapered roller bearings that use metal plates such as iron plates as retainers and are roller-guided.

[0014] • Because the small-diameter side of the retainer post is riveted during assembly, the inner diameter dimension is prone to deviation, sometimes resulting in a single-sided edge guide (hereinafter referred to as a single edge guide).

[0015] • In applications where high centrifugal forces are applied, such as in planetary applications, the non-guided side rotates while the outer diameter of the edge is in temporary contact with the inner diameter of the retainer due to the oscillation and deformation of the retainer, and operates with the retainer's rotation axis tilted.

[0016] • When operating with the spin axis tilted, a gyroscopic torque is generated, and an axial force acts on the cage. Through this axial force, the cage moves axially, and the roller end face makes strong contact with the axially facing face in the inner surface of the cage pocket, resulting in wear and lack of durability.

[0017] The object of the present invention is to provide a tapered roller bearing with an inner ring guide form of a retainer using a metal plate such as an iron plate, wherein even when used in an environment where the bearing revolves, the tilt of the retainer's rotation axis is suppressed and wear of the retainer is difficult to occur.

[0018] Technical solution for solving the problem

[0019] The tapered roller bearing of the present invention relates to a tapered roller bearing with an inner ring guiding form, which includes: an inner ring with two flanges; an outer member having an annular rolling surface opposite to the rolling surface of the inner ring; a plurality of tapered rollers interposed between the inner ring and the outer member; and a retainer for holding the plurality of tapered rollers. The retainer has a small-diameter side annular portion, a large-diameter side annular portion, and column portions at a plurality of circumferential positions, and the column portions at the plurality of circumferential positions connect the small-diameter side annular portion and the large-diameter side annular portion. For the dimensionless number X determined by the small-diameter side clearance S1, the large-diameter side clearance S2, the average roller diameter d, the roller length l, and the outer member angle α (where α is in the range of 20° to 40°) through the following formula, it is in the range of 0.69 < X < 1.12. Here, the small-diameter side clearance S1 refers to the clearance between the small-diameter side annular portion of the retainer and the small flange portion of the inner ring, the large-diameter side clearance S2 refers to the clearance between the large-diameter side annular portion and the large flange portion of the inner ring, and the outer member angle α refers to the conical opening angle of the rolling surface of the outer member. The formula is:

[0020] [Equation 1]

[0021]

[0022] In order to appropriately maintain the inclination of the retainer during operation, it is not sufficient to set only the retainer to the inner ring guiding form. In addition to the clearances (the small-diameter side clearance S1 and the large-diameter side clearance S2) between the outer diameters of the respective flanges of the inner ring and the retainer at rest, it is also necessary to appropriately manage the clearances (radial clearances and axial clearances) between the rollers and the retainer during operation. The clearances between the rollers and the retainer during operation are defined by the average roller diameter d and the roller length l. Considering this, it is found that for the small-diameter side clearance S1 and the large-diameter side clearance S2, by considering the above dimensionless X determined by the average roller diameter d and the roller length l, and managing the ratio of the small-diameter side clearance S1 and the large-diameter side clearance S2 in such a way that the dimensionless X is in an appropriate range (the range of 0.69 < X < 1.12), the inclination of the self-rotation axis of the retainer can be suppressed.

[0023] In this way, in the clearance between the outer diameter of the inner ring flange and the inner diameter of the retainer, by reducing the difference between the small-diameter side and the large-diameter side clearances, the bearing can be rotated in a state where the offset between the self-rotation axis of the retainer and the axis of the inner ring is small under the action of centrifugal force. As a result, the wobbling rotation of the retainer can be reduced, and the wear of the retainer can be suppressed. By reducing the wobbling rotation of the retainer, the axial movement of the retainer caused by the gyroscopic torque can be reduced, and the bearing can be operated in a stable state.

[0024] The reasons for keeping the angle α of the outer component within the range of 20° to 40° are as follows.

[0025] When the angle α of the outer component is less than 20°, the ability to apply axial load is relatively small.

[0026] When the outer ring component angle α is 40° or greater, the bearing capacity for axial loads is greater, but the bearing capacity for radial loads is smaller. Tapered roller bearings used in environments with centrifugal forces, such as planetary gear reducers, primarily bear radial loads; therefore, bearings with large outer ring component angles α are less common. Furthermore, considering the axial loads generated by gear meshing in planetary gear reducers, the bearing capacity for axial loads may be insufficient when the outer ring component angle is 20° or less.

[0027] In this invention, the large-diameter annular portion of the retainer may have a flange-like portion that bends and extends towards the inner diameter relative to the column portion. The bending angle of the flange-like portion relative to the column portion is within the range of 90°±10°, based on the retainer angle, which is the angle at which the column portion is tilted relative to the bearing axis. By having the bending angle of the flange-like portion within the range of 90°±10°, a suitable shape is formed for configuring the retainer as an inner ring guide.

[0028] In the tapered roller bearing of the present invention, the large-diameter annular portion of the retainer may have a flange-like portion that bends towards the inner diameter side relative to the cylindrical portion via an arc-shaped curved portion. The radius of curvature (R-dimensional) of the curved portion's arc length relative to the axial length of the direction in which the cylindrical portion extends from the large-diameter annular portion is located within the range of 20% to 90%. When the arc length of the curved portion relative to the axial length of the large-diameter annular portion is less than 20%, stress concentration during bending increases, potentially damaging the retainer. Furthermore, if it is 90% or more, the arc shape of the inner diameter side surface of the curved portion becomes too gentle, potentially causing edge contact between the roller end face and the opening edge of the pocket.

[0029] In the tapered roller bearing of the present invention, the small-diameter annular portion and the large-diameter annular portion of the retainer may have flange-like portions that extend inwardly relative to the column portion. Multiple circumferential locations of the flange-like portions have notched or window-like oil passages that allow lubricating oil to pass through the bearing axially relative to the flange-like portions. By forming oil passages as described above, lubricating oil can easily pass through the flange-like portions of the retainer, achieving good lubrication between the rolling surfaces of the tapered rollers and the inner surface of the retainer pocket.

[0030] In the tapered roller bearing of the present invention, the cross-sectional area ratio of the large-diameter annular portion to the small-diameter annular portion of the cage may be 1.0 to 1.2. If the cross-sectional area ratio of the large-diameter annular portion to the small-diameter annular portion is in the range of 1.0 to 1.2, the weight balance between the large-diameter and small-diameter sides becomes appropriate, the vibration of the cage is suppressed, and good inner ring guidance is possible.

[0031] Any combination of at least two structures disclosed in the claims and / or description and / or drawings is also included in this invention. In particular, any combination of two or more of the claims is also included in this invention. Attached Figure Description

[0032] The invention can be more clearly understood from the following description of preferred embodiments with reference to the accompanying drawings. However, the embodiments and drawings are for illustration and description only and should not be used to limit the scope of the invention. The scope of the invention is defined by the claims. In the drawings, the same reference numerals in the plurality of figures denote the same or equivalent parts.

[0033] Figure 1 This is a cross-sectional view of the tapered roller bearing according to the first embodiment of the present invention;

[0034] Figure 2 This is a cross-sectional view of the cage of the tapered roller bearing;

[0035] Figure 3A This is an end view of the small-diameter side of the retainer;

[0036] Figure 3B This is an end view of the large-diameter side of the retainer;

[0037] Figure 4 This is a partially enlarged cross-sectional view of the retainer;

[0038] Figure 5 A partially enlarged sectional view showing the large-diameter side annular portion and tapered rollers of the retainer;

[0039] Figure 6 A diagram illustrating the centrifugal force acting on the tapered roller bearing in a planetary gearbox using this tapered roller bearing;

[0040] Figure 7 A cross-sectional view showing a modified example of the retainer used for this tapered roller bearing;

[0041] Figure 8A This is an end view of the small-diameter side of the retainer;

[0042] Figure 8B This is an end view of the large-diameter side of the retainer;

[0043] Figure 9 A cross-sectional view showing an example of a planetary reducer using tapered roller bearings;

[0044] Figure 10 For along Figure 9 A cross-sectional view of the X-X line in the image;

[0045] Figure 11A An illustrative diagram of an example of a gauge used for clearance management in tapered roller bearings;

[0046] Figure 11B An illustrative diagram of another example of a gauge used for clearance management in tapered roller bearings;

[0047] Figure 12 A cross-sectional view of a traditional rolling element guided tapered roller bearing;

[0048] Figure 13A An explanatory diagram illustrating the effect of centrifugal force acting on a rolling element guided tapered roller bearing;

[0049] Figure 13B An explanatory diagram illustrating the effect of centrifugal force acting on an inner ring guided tapered roller bearing;

[0050] Figure 14A An explanatory diagram illustrating the effect of centrifugal force acting on a rolling element guided tapered roller bearing;

[0051] Figure 14B An explanatory diagram illustrating the effect of centrifugal force acting on an inner ring guided tapered roller bearing;

[0052] Figure 15A An explanatory diagram illustrating the effect of centrifugal force acting on a rolling element guided tapered roller bearing;

[0053] Figure 15B An explanatory diagram illustrating the effect of centrifugal force acting on an inner ring guided tapered roller bearing;

[0054] Figure 16A An explanatory diagram illustrating the effect of centrifugal force acting on a rolling element guided tapered roller bearing;

[0055] Figure 16B This diagram illustrates the effect of centrifugal force acting on an inner ring guided tapered roller bearing. Detailed Implementation

[0056] Combination Figures 1-6The tapered roller bearing according to the first embodiment of the present invention will be described. Furthermore, this tapered roller bearing 1 will be described later in conjunction with... Figure 9 , Figure 10 Used in the planetary section of a planetary reducer or planetary transmission as described in this specification.

[0057] exist Figure 1 The tapered roller bearing 1 includes: an inner ring 2; an outer square component 3; a plurality of tapered rollers 4 between the inner ring 2 and the outer square component 3; and a retainer 5 for holding the plurality of tapered rollers 4. The inner ring 2 has a rolling surface 2a of a tapered surface that expands in diameter from near one end of its outer circumferential surface to near the other end, and has a structure with two edges, one small edge 2b and the other large edge 2c. The outer square component 3 is an annular component that faces the rolling surface 2a of the inner ring 2 and has a rolling surface 3a of a tapered surface that expands in diameter from one end to the other. The outer square component 3 is a component equivalent to the "outer ring" when it only functions as a bearing component, for example, a component conceptually including a component whose outer circumferential surface is a gear portion and has the aforementioned rolling surface 3a on its inner circumferential surface, and is referred to as the "outer square component" in this specification. Furthermore, in this specification, in experimental and analytical examples, the "outer square component" is sometimes referred to as the "outer ring". In the illustrated embodiment, the outer component 3 does not have a shank, but it may also have a shank protruding towards the inner diameter side at one or the other end (not shown in the figure).

[0058] The retainer 5 has a small-diameter annular portion 6; a large-diameter annular portion 7; and column portions 8 at multiple circumferential locations connecting these small-diameter annular portions 6 and large-diameter annular portions 7. Adjacent column portions 8 form pockets 9 for retaining the tapered rollers 4. The inner diameter surfaces of the small-diameter annular portion 6 and the large-diameter annular portion 7 of the retainer 5 have diameters guided by the small edge 2b and the large edge 2c of the inner ring 2, respectively. Thus, this tapered roller bearing 1 is an inner-ring guided bearing. Furthermore, the retainer 5 can be any type of inner-ring guided bearing, or it can be a structure guided only by either the small edge 2b or the large edge 2c of the inner ring 2. Essentially, it is best to have a type where at least the small edge 2b of the inner ring 2 provides guidance.

[0059] In this embodiment, the retainer 5 is a stamped retainer made of a metal sheet such as iron plate, and the small-diameter annular portion 6 and the large-diameter annular portion 7 are formed by bending. The column 8 is formed by punching the pocket 9 using a stamping process. In addition, the retainer 5 can also be made of resin.

[0060] The dimensional relationships of each part of the tapered roller bearing 1 will be described. The small-diameter side clearance S1, which is the clearance between the small-diameter side annular portion 6 of the cage 5 and the small collar portion 2b of the inner ring 2, the large-diameter side clearance S2, which is the clearance between the large-diameter side annular portion 7 and the large collar portion 2c of the inner ring 2, the average roller diameter d of the rollers 4, the roller length l of the rollers 4, and the outer member angle α (where α is in the range of 20° to 40°) define a dimensionless number X determined by the following formula. The outer member angle α refers to the conical opening angle at which the rolling surface 3a of the outer member 3 is inclined (the angle formed by two straight lines representing the rolling surfaces 3a on both sides obtained by剖切 with a plane containing the bearing axis O of the outer ring 3), and the formula is:

[0061] [Equation 2]

[0062]

[0063] The dimensionless number X determined in this way satisfies the range of 0.69 < X < 1.12. The dimensionless number X particularly preferably satisfies 0.73 < X < 1.046. However, in the tapered roller bearing 1 of the present embodiment, the outer member angle α is in the range of 20° to 40°.

[0064] The small-diameter side annular portion 6 and the large-diameter side annular portion 7 of the cage 5 have flange-like portions 6a and 7a that extend bent toward the inner diameter side with respect to the column portion 8. The bending angle β of the flange-like portion 7a of the large-diameter side annular portion 7 with respect to the column portion 8 is in the range of 90° ± 10° based on the angle at which the column portion 8 is inclined with respect to the bearing axis O, that is, the cage angle (in other words, the direction in which the column portion 8 extends). 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 also be inclined.

[0065] As Figure 4 enlarged and shown, the large-diameter side annular portion 7 of the cage 5, more specifically, has an arcuate bending portion 7b interposed with respect to the column portion 8 (refer to Figure 4 ), and the above-mentioned flange-like portion 7a is bent toward the inner diameter side. The radius of curvature of the inner diameter side surface of the bending portion 7b, that is, the arcuate dimension b1 of the bending portion, is in the range of 20% to 90% with respect to the length in the direction in which the column portion 8 of the large-diameter side annular portion 7 extends, that is, the axial length a. There is no particular specification for the arcuate dimension b2 of the outer diameter side surface of the bending portion 7b.

[0066] The flange-like portions 6a and 7a of the above-mentioned small-diameter side annular portion 6 and large-diameter side annular portion 7 of the cage 5 have oil passageways 10 and 11 at multiple positions in the circumferential direction, and these oil passageways 10 and 11 allow lubricating oil to pass through axially inside and outside with respect to these flange-like portions 6a and 7a. In this embodiment, as Figure 3A 、 Figure 3B As shown, the oil passages 10 and 11 are formed as notch-like shapes formed on the inner peripheral edges of the flange-like portions 6a and 7a. Specifically, the oil passages 10 and 11 are formed as arc-shaped notch-like shapes.

[0067] As Figure 7 , Figure 8A , Figure 8B shown, the oil passages 10 and 11 may also be window-like. In Figure 8A , Figure 8B , the oil passage 10 of the flange-like portion 6a of the small-diameter side annular portion 6 is circular, and the oil passage 11 of the flange-like portion 7a of the large-diameter side annular portion 7 is elliptical. In addition, the above-mentioned oil passages 10 and 11 may not be provided.

[0068] In these Figure 1 to the embodiments shown in FIG. 8, 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 is in the range of 1.0 to 1.2. The cross-sectional ratio mentioned here is the cross-sectional ratio of the circumferential portion where the above-mentioned oil passages 10 and 11 are not provided.

[0069] The operation of the above structure will be described.

[0070] As Figure 6 shown, when the tapered roller bearing 1 is used in an environment with公转(arrow c) of the planetary part of a planetary reducer, etc., a centrifugal force G acts, and a force that causes the [[ID=2*]] Figure 1 cage 5 to tilt acts through this centrifugal force. In order to appropriately maintain the tilt angle of the cage 5 during operation, it is not sufficient to set only the cage 5 to the inner ring guiding form. In addition to the clearances (the above-mentioned small-diameter side clearance S1 and large-diameter side clearance S2) between the outer diameters of the respective flange portions 2b and 2c of the inner ring 2 and the cage 5 at rest, it is also necessary to appropriately manage the clearances (radial clearances and axial clearances) between the rollers 4 and the cage 5 during operation. The clearances between the rollers 4 and the cage 5 during operation are defined by the average roller diameter d and the roller length l.

[0071] Taking this into account, in the above-mentioned small-diameter side clearance S1 and large-diameter side clearance S2, considering the above-mentioned dimensionless X determined by the average roller diameter d and the roller length l, it was found that if this dimensionless X is within an appropriate range, the tilt angle of the self-rotation axis of the cage can be suppressed, and this was confirmed through experiments and analysis. As a result, it was found that by managing the ratio of the small-diameter side clearance S1 and the large-diameter side clearance S2 such that the above-mentioned dimensionless X is within the range of 0.69 < X < 1.12, the tilt angle of the self-rotation axis of the cage 5 can be suppressed.

[0072] It should be noted that there seems to be a formatting or content issue in the original text where "公转(arrow c)" is not a standard or clear expression. It might need further clarification in the original context. Also, there is an unclear "the " in line 28 which might be a typo. This translation is based on the best understanding of the provided text.The above tests and analyses simulate the planetary section of the planetary gear reducer under the condition of durability with a centrifugal force of 30G or more. The dimensions of the tapered roller bearings 1 used in the tests and analyses are all inner diameter φ76 × outer diameter φ136.5 × width 46.0 (unit: mm), and the outer ring angle (outer component angle α) is 35°. In addition, the dimensions of each part of the tapered roller bearing 1 used in the tests and analyses (roller average diameter, roller length, small diameter side clearance S1, large diameter side clearance S2) omit their respective values, and the above dimensionless X is the dimension of the value shown in Table 1.

[0073] [Table 1]

[0074]

[0075] ○: No wear, slight wear (can be used continuously), ×: Severe wear (cannot be used continuously)

[0076] As shown in Table 1, the results of the tests and analyses obtained good results (the cage 5 has no wear or slight wear) within the range including samples (2) to (6), that is, within the range of 0.69 < X < 1.12. In particular, samples (3) and (4) have no wear, and the range of 0.73 < X < 1.04 is more preferable.

[0077] In this way, in the clearance between the outer diameters of the inner ring flanges 2b and 2c and the inner diameter of the cage 5, by reducing the difference between the small diameter side and the large diameter side clearances S1 and S2, the tapered bearing 1 can be rotated in a state where the offset between the self-rotation axis of the cage 5 and the axis of the inner ring 2 is small under the action of centrifugal force, the wobbling rotation of the cage 5 can be reduced, and the wear of the cage 5 can be suppressed. By reducing the wobbling rotation of the cage 5, the axial movement of the cage 5 caused by the gyroscopic torque can be reduced, and the tapered roller bearing 1 can be operated in a stable state.

[0078] The reason why the outer component angle α is within the range of 20° to 40° is as follows.

[0079] When the outer component angle α is 20° or less, the ability to apply an axial load is small. When the outer component angle α is 40° or more, the ability to apply an axial load is large, but the ability to apply a radial load is small. Tapered roller bearings used in environments where centrifugal force acts, such as in the planetary reduction section, mainly bear radial loads, so there are few cases of applying bearing products with a large outer component angle α. In addition, considering the axial load generated due to the meshing of gears in the planetary gear reducer, when the outer ring component angle is 20° or less, the ability to apply an axial load may be insufficient.

[0080] The retainer 5 is based on the retainer angle, and the bending angle β (the bending angle of the flange-shaped portion 7a relative to the column portion 8) of the large-diameter side annular portion 7 is set to a range of 90°±10°. Therefore, an appropriate shape is formed in terms of making the retainer 5 an inner ring guide.

[0081] The arc dimension b1 of the curved portion 7b on the inner diameter side surface of the curved portion in the large diameter side annular portion 7 of the retainer 5. Figure 4 The range of 20% to 90% relative to the axial length a of the large-diameter side annular portion 7 prevents the following problem. Specifically, when the arc dimension b1 of the bent portion is less than 20% relative to the axial length a of the large-diameter side annular portion 7, stress concentration during bending increases, potentially damaging the retainer 5. Conversely, if it is 90% or more, then... Figure 5 As indicated by the thin line, the arc shape of the inner diameter side surface of the curved portion 7b becomes too gentle, creating a possibility that the end face of the roller 4 may come into contact with the opening edge of the pocket 9. This problem is eliminated by setting it to a range of 20% to 90%.

[0082] In this embodiment, multiple circumferential locations of the flange-shaped portions 6a and 7a of the small-diameter annular portion 6 and the large-diameter annular portion 7 of the retainer 5 are provided with slit-shaped or window-shaped oil passages 10 and 11 as described above. Therefore, the following effect can be obtained: By forming the oil passages 10 and 11, lubricating oil can easily pass through both the inside and outside of the flange-shaped portions 6a and 7a of the retainer 5. Therefore, good lubrication can be obtained between the rolling surface of the tapered roller 4 and the inner surface of the pocket of the retainer 5.

[0083] Furthermore, the cross-sectional area ratio of the large-diameter annular portion 7 to the small-diameter annular portion 6 of the retainer 5 is 1.0 to 1.2, thus providing the following advantages. That is, if the cross-sectional area ratio 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 oscillation and rotation of the retainer 5 are suppressed, and good inner ring guidance is possible.

[0084] Figure 9 , Figure 10This section describes an example of a planetary reducer using the tapered roller bearing 1 described in the above embodiment. The planetary reducer has a plurality of planetary rotating bodies 105, which mesh with the two gears 102 and 104, arranged between a sun gear 102 mounted on an input shaft 101 and an internal gear 104 fixed to a housing 103. Each planetary rotating body 105 is rotatably supported on a planet carrier 107 connected to an output shaft 106. The revolution of the planetary rotating body 105, which rotates on its own axis and revolves around the sun gear 102 and the internal gear 104, is output to the output shaft 106 via the planet carrier 107. This planetary reducer is used, for example, as the first stage of a final reduction device installed inside the rim of a construction machine.

[0085] A pair of tapered roller bearings 1 are disposed between the planetary rotor 105 and the planet carrier 107 of the planetary reducer. The outer components 3 of each tapered roller bearing 1... Figure 1 The inner rings 2 of each tapered roller bearing 1 are mounted on the planetary rotor 105 and rotate integrally with the planetary rotor 105. The inner rings 2 of each tapered roller bearing 1 are mounted in a fixed state on the support shaft 108 provided on the wheel frame 107.

[0086] Furthermore, the aforementioned small-diameter side clearance S1 and large-diameter side clearance S2 vary due to insufficient seam closing of the small-diameter side annular portion 6 of the retainer 5 during assembly. Therefore, in order to measure the small-diameter side clearance S1, for example, by... Figure 11A , Figure 11B The reference clearance gauge 51 is inserted between the inner diameter of the cage and the outer diameter of the inner ring flange at a 180° phase. The small diameter side clearance S1 at 0° and 180° phases is confirmed, and the averaged clearance is used as the reference clearance. Then, the reference clearance gauge 51 is inserted into the aforementioned small diameter side clearance S1, so that one side becomes the reference clearance (the aforementioned average value). In this state, the small diameter side clearance S1 when the measuring clearance gauge 52 is inserted at the 180° phase position is measured to confirm whether it is within the appropriate range.

[0087] The foregoing has described the methods for implementing the present invention based on various embodiments. However, the embodiments disclosed herein are illustrative in all respects and are not restrictive. The scope of the present invention is not defined by the foregoing description, but by the claims, and is intended to include all modifications equivalent to and within the scope of the claims.

[0088] Explanation of symbols:

[0089] The designation 1 indicates a tapered roller bearing;

[0090] The number 2 indicates the inner circle;

[0091] The designation 2a indicates the rolling surface;

[0092] The designation 2b indicates the small shank;

[0093] The designation 2c indicates the large shank;

[0094] The number 3 indicates the outer component;

[0095] The designation 4 indicates a tapered roller;

[0096] The number 5 indicates a retainer;

[0097] The designation 3a indicates the rolling surface;

[0098] The number 6 indicates the annular portion on the small diameter side;

[0099] The designation 6a indicates a flange-like portion;

[0100] The number 7 indicates the large-diameter side annular portion;

[0101] The designation 7a indicates a flange-like portion;

[0102] The designation 7b indicates the curved section;

[0103] The number 8 indicates the column section;

[0104] The number 9 indicates a pocket;

[0105] Numbers 10 and 11 indicate oil passages;

[0106] The symbol S1 indicates the small-diameter side clearance;

[0107] The symbol S2 indicates the large-diameter side clearance;

[0108] The symbol d represents the average roller diameter;

[0109] The symbol 'l' indicates the length of the roller;

[0110] The symbol α represents the angle of the outer component;

[0111] The symbol X represents a dimensionless number.

Claims

1. A tapered roller bearing, wherein the tapered roller bearing is an inner ring guided tapered roller bearing, comprising: An inner ring with two serrations; An outer component having an annular rolling surface opposite to the rolling surface of the inner ring; A plurality of tapered rollers, the plurality of tapered rollers being positioned between the inner ring and the outer component; and A retainer that holds the aforementioned plurality of tapered rollers; The aforementioned retainer has a small-diameter side annular portion, a large-diameter side annular portion, and a column portion in a circumferential direction, which connects the small-diameter side annular portion to the large-diameter side annular portion. For the dimensionless number X determined by the small-diameter side clearance S1, the large-diameter side clearance S2, the average roller diameter d, the roller length l and the angle α of the outer member being within the range of 0.69 < X < 1.12, where the small-diameter side clearance S1 refers to the clearance between the small-diameter side annular portion of the retainer and the small rib portion of the inner ring, the large-diameter side clearance S2 refers to the clearance between the large-diameter side annular portion and the large rib portion of the inner ring, and the angle α of the outer member refers to the conical opening angle at which the rolling surface of the outer member is inclined, and α is from 20° to 40°, and the formula is: 。 2. Tapered roller bearing according to claim 1, wherein The aforementioned retainer has a large-diameter side annular portion that bends and extends towards the inner diameter relative to the aforementioned column portion. The bending angle of the aforementioned flange portion relative to the aforementioned column portion is within the range of 90°±10° based on the retainer angle, which is the angle at which the aforementioned column portion is tilted relative to the bearing axis.

3. Tapered roller bearing according to claim 1 or 2, wherein The aforementioned retainer has a flange-like portion that bends toward the inner diameter side relative to the aforementioned column portion via an arc-shaped curved portion. The arc dimension of the curved portion, which is the radius of curvature of the inner diameter side surface of the curved portion, is in the range of 20% to 90% relative to the axial length of the direction in which the aforementioned column portion extends, which is the aforementioned large-diameter side annular portion.

4. Tapered roller bearing according to claim 1 or 2, wherein The aforementioned retainer has a flange-shaped portion extending inwardly relative to the aforementioned column portion, with multiple notch-shaped or window-shaped oil passages in the circumferential direction, which allow lubricating oil to pass through the bearing axially relative to the aforementioned flange-shaped portion.

5. Tapered roller bearing according to claim 1 or 2, wherein The ratio of the cross-sectional area of ​​the large-diameter annular portion to the small-diameter annular portion of the aforementioned retainer is 1.0 to 1.2.

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