JP2005024029A - Tapered roller bearing - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a tapered rolling bearing capable of preventing metal touch of a flange with a roller even when the operational condition becomes severe and an oil film on a contact part of the flange with the roller is thin. <P>SOLUTION: The tapered rolling bearing A1 comprises an inner ring 30 having a conical raceway surface 30a on an outer circumferential surface, an outer ring 31 having a conical raceway surface 31a on an inner circumferential surface, a plurality of truncated conical rollers 32 disposed turnably between the inner ring 30 and the outer ring 31, and a large flange 33 which is formed on the inner ring 30 and brought into contact with a large diameter end face 32a of the roller 32 to guide the roller 32. A groove 35 is circumferentially formed in at least one surface of the large flange 33 and the roller 32 out of the surfaces on which the large flange 33 is brought into contact with the roller 32. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention belongs to the technical field of tapered roller bearings applied to power roller bearings and the like of toroidal type continuously variable transmissions.
[0002]
[Prior art]
Since the tapered roller bearing is designed so that the inner and outer ring raceway surfaces and the conical apex of the roller coincide with each other at one point on the bearing center, the roller can perform pure rolling motion with respect to the inner and outer ring raceway surfaces. However, since the angles of the inner and outer rings are different, a force is generated that pushes the roller toward the bottom of the cone. Therefore, the heel is brought into contact with the large diameter surface of the roller to support this force. Like the raceway surface, this contact portion is also in rolling contact, and an oil film is formed therebetween to prevent damage caused by direct contact between metals (see Patent Document 1).
[0003]
[Patent Document 1]
JP 2002-147461 A.
[0004]
[Problems to be solved by the invention]
However, unlike the raceway surface, the contact portion between the flange and the roller of the conventional tapered roller bearing is very slippery. Normally, the slip ratio of the raceway surface (ratio of the sliding speed to the rolling speed) is 1% or less, but the heel part is about 20%. Therefore, when the load acting on the bearing increases and the contact surface pressure increases, or when the lubricating oil temperature rises and the viscosity decreases, the oil film becomes thinner, causing direct contact and damage such as seizure. There was a problem.
[0005]
The present invention has been made paying attention to the above problem, and even if the operating condition becomes severe and the oil film at the contact portion between the heel and the roller tends to become thin, metal contact between the heel and the roller can be prevented. An object of the present invention is to provide a tapered roller bearing.
[0006]
[Means for Solving the Problems]
In order to achieve the above object, in the present invention,
An inner ring having a conical track surface on the outer peripheral surface, an outer ring having a conical track surface on the inner peripheral surface, and a plurality of truncated cone-shaped rollers disposed between the inner ring and the outer ring so as to be capable of rolling. In the tapered roller bearing provided with the flange formed on the inner ring or the outer ring and contacting the large-diameter end surface of the roller to guide the roller,
A groove is provided in a circumferential direction on at least one surface of the flange and the roller among the surfaces where the flange and the roller contact.
[0007]
【The invention's effect】
In the tapered roller bearing of the present invention, a groove is provided in the circumferential direction on at least one surface of the flange and the roller among the surfaces where the flange and the roller are in contact with each other. By ensuring the thickness of the oil film at the contact portion, even if the operating condition becomes severe and the oil film at the contact portion between the heel and the roller tends to be thin, metal contact between the heel and the roller can be prevented.
[0008]
DETAILED DESCRIPTION OF THE INVENTION
Hereinafter, embodiments for realizing the tapered roller bearing of the present invention will be described based on first to fourth examples.
[0009]
(First embodiment)
First, the configuration will be described.
FIG. 1A is a cross-sectional view showing a tapered roller bearing of the first embodiment, and FIG. 1B is an enlarged cross-sectional view of a portion B in FIG. 1A showing a contact portion between a collar and a roller of an inner ring. .
As shown in FIG. 1, the tapered roller bearing A1 of the first embodiment includes an inner ring 30 having a conical raceway surface 30a on the outer peripheral surface, and an outer ring 31 having a conical raceway surface 31a on the inner peripheral surface. A plurality of cone-shaped trapezoidal rollers 32 disposed between the inner ring 30 and the outer ring 31 so as to be freely rollable, and a large bowl formed on the inner ring 30 to contact the large-diameter end surface 32a of the roller 32 and guide the roller 32. 33 (鍔).
[0010]
The inner ring 30 integrally includes a large collar 33 having a large collar surface 33 a and a small collar 34 having a small collar surface 34 a that contacts the small diameter end surface 32 b of the roller 32 and guides the roller 32. The track surface 30 a contacts the conical circumferential surface 32 c of the roller 32. The large collar 33 may be formed separately from the inner ring 30 and integrally coupled to the inner ring 30 by shrink fitting or the like.
[0011]
The raceway surface 31a of the outer ring 31 is in contact with only the conical circumferential surface 32c of the roller 32 because the movement of the roller 32 in the roller axis direction is restricted by the large collar surface 33a and the small collar surface 34a on the inner ring 30 side. To do.
[0012]
The roller 32 has a large-diameter end surface 32a formed by a spherical surface (curvature radius SR), a small-diameter end surface 32b formed by a flat surface, and a conical circumferential surface 32c formed by a conical surface. The plurality of rollers 32 are provided so as to roll while maintaining a distance from the adjacent rollers 32 by a retainer (not shown).
[0013]
Of the surfaces where the large flange surface 33a of the large flange 33 and the large diameter end surface 32a of the roller 32 are in contact, a groove 35 is provided on the large flange surface 33a of the large flange 33 in the circumferential direction. The width of one groove of the groove 35 is made smaller than the width of the Hertz contact ellipse formed by the contact portion between the large collar 33 and the roller 32, and the oil film formed between the large collar 33 and the roller 32 becomes thin. Two grooves 35, 35 are arranged in the portion. As shown in FIG. 1B, the two grooves 35 and 35 are arranged in the vicinity of the middle between the center position and the end position of the contact ellipse, respectively. Further, the cross-sectional shape of the grooves 35, 35 is set to a shape having an arc-shaped groove bottom.
[0014]
Next, the operation will be described.
[0015]
[Necessity of oil film at the contact part between roller and roller]
When a load is applied to the tapered roller bearing A <b> 1, a part of this load is supported by the large flange surface 33 a formed on the large flange 33. At this time, since the large-diameter end surface 32a of the roller 32 and the large collar surface 32d of the large collar 33 rotate relative to each other, slip occurs at the contact portion between them, and the frictional force due to this slip is a loss of the tapered roller bearing A1. Torque. The magnitude of this loss torque is proportional to the friction coefficient of the contact portion between the roller 32 and the large collar 33. Therefore, in order to reduce the friction coefficient of the contact portion between the roller 32 and the large flange 33, it is necessary to secure an oil film at the contact portion between the large diameter end surface 32a and the large flange surface 32d.
[0016]
[Oil film forming action]
The shape of the oil film formed at the rolling contact portion with a high surface pressure, such as a rolling bearing, is the so-called elastohydrodynamic lubrication theory (see Yamamoto / Kaneda: “Tribology” Science and Engineering Co., Ltd. (1998)) pages 113-122). Is required.
[0017]
FIG. 2 shows the numerical calculation result of the oil film thickness distribution in the conventional example without the groove 35. However, since there is a film thickness reduction part in the oil outflow part, the distribution has a horseshoe-shaped thin film part, and the thinnest The part exists on both wings of horseshoe shape. That is, if the thinnest part exists at an intermediate position between the center of the contact ellipse and the end of the contact ellipse and the surface has a uniform roughness, this part is most likely to come into contact. FIG. 3 is a view of the oil film thickness distribution as seen from the rolling direction (FIG. 4), and it is clear that the thinnest part exists at an intermediate position between the center of the contact ellipse and the end of the contact ellipse.
[0018]
On the other hand, in the first embodiment, since the grooves 35 and 35 are formed in the thinnest part of the oil film, the oil film thickness of the thinnest part is increased, and metal contact can be prevented.
FIG. 4 shows the calculation result of the oil film shape in the first embodiment. In the case of no groove in FIG. 3, the oil film thickness of the thinnest part is 0.3 × 10 ⁻⁶ , whereas FIG. When there is a groove, the oil film thickness of the thinnest part = 0.35 × 10 ⁻⁶ , indicating that the minimum oil film thickness is increased.
[0019]
Next, the effect will be described.
In the tapered roller bearing of the first embodiment, the effects listed below can be obtained.
[0020]
(1) An inner ring 30 having a conical raceway surface 30 a on the outer peripheral surface, an outer ring 31 having a conical raceway surface 31 a on the inner peripheral surface, and an inner ring 30 and an outer ring 31 are disposed so as to be able to roll. In the tapered roller bearing A1 provided with a plurality of cone-shaped trapezoidal rollers 32 and a large flange 33 that is formed on the inner ring 30 and guides the rollers 32 in contact with the large-diameter end surface 32a of the roller 32, the large flange Since the groove 35 is provided in the circumferential direction on at least one surface of the large cage 33 and the roller 32 among the surfaces where the roller 33 and the roller 32 are in contact with each other, the operating condition becomes severe and the contact portion between the large cage 33 and the roller 32 Even if the oil film becomes thinner, the metal contact between the large cage 33 and the roller 32 can be prevented.
[0021]
(2) A circumferential groove 35 is provided on the large flange surface 33 a that contacts the roller 32 of the large flange 33, and the width of the groove 35 is a Hertzian contact ellipse formed by the contact portion between the large flange 33 and the roller 32. Since the groove 35 is disposed in a portion where the oil film formed between the large cage 33 and the roller 32 becomes thin, even if the operating condition becomes severe and the oil film becomes thin, metal contact can be made. Absent. In addition, since the grooves 35 are formed on the large flange surface 33a of the large flange 33, the processing can be completed in a shorter time than when grooves are formed on each of the plurality of rollers 32.
[0022]
(3) Since the two grooves 35 are provided and the grooves 35 and 35 are arranged near the middle between the center position and the end position of the contact ellipse, the position where the average oil film thickness is small and the grooves 35 and 35 By matching the position of 35 and effectively increasing the minimum oil film thickness, metal contact can be reliably prevented.
[0023]
(4) Since the cross-sectional shape of the groove 35 is set to a shape having an arc-shaped groove bottom, it is possible to prevent the oil film pressure from rapidly increasing due to a sharp change in shape.
[0024]
Note that the grooves 35 and 35 do not have to be completely independent, and as shown in a tapered roller bearing A1 ′ according to a modification of the first embodiment in FIG. , 35 may be formed as continuous grooves 35, 35 by a communication groove 36 having an arc convex cross section that smoothly communicates.
[0025]
(Second embodiment)
The tapered roller bearing A2 of the second embodiment is an example in which a groove is provided on the roller side of the contact surface between the roller and the flange.
[0026]
That is, as shown in FIG. 6, two grooves 35, 35 in the circumferential direction are provided on the large-diameter end surface 32 a that contacts the large flange 33 of the roller 32, and one groove width of the grooves 35, 35 is set as follows. Two grooves 35, 35 are arranged in a portion where the oil film formed between the large collar 33 and the roller 32 becomes thinner than the width of the Hertz contact ellipse formed by the contact area between the large collar 33 and the roller 32. did. Since other configurations are the same as those of the first embodiment, illustration and description thereof are omitted.
[0027]
Next, the operation will be described. The first embodiment is simple if a groove is formed on one of the large collars 33, but the large collar 33 is integrated with the inner ring 30. Depending on the angle, the shape of the inner ring 30, etc., interference of the tool may occur, making machining difficult.
[0028]
On the other hand, the tapered roller bearing A2 of the second embodiment has no hindrance in processing if the large-diameter end surface 32a of the roller 32 is used. Can be processed.
[0029]
Next, the effect will be described.
In the tapered roller bearing A2 of the second embodiment, the following effects can be obtained in addition to the effects (1), (3), and (4) of the first embodiment.
[0030]
(5) Circumferential grooves 35 and 35 are provided on the large-diameter end surface 32 a that contacts the large flange 33 of the roller 32, and one groove width of the grooves 35 and 35 is set as a contact portion between the large flange 33 and the roller 32. Since the two grooves 35 and 35 are arranged in the portion where the oil film formed between the large collar 33 and the roller 32 becomes thin, the operating condition is reduced by simple processing. Even if it becomes severe, the metal contact between the large cage 33 and the roller 32 can be prevented.
[0031]
(Third embodiment)
The tapered roller bearing A3 of the third embodiment is an example in which one groove 35 is provided and the groove 35 is arranged at the center of the contact ellipse.
[0032]
That is, as shown in FIG. 7, only one groove 35 is provided on the large collar surface 33a, and the groove 35 is arranged at the center of the contact ellipse. Since other configurations are the same as those of the first embodiment, illustration and description thereof are omitted.
[0033]
Next, the operation will be described. As described in FIGS. 8 (a) and 8 (b) and elastohydrodynamic lubrication (see Yamamoto / Kaneda: Tribology Science and Engineering Co., Ltd. (1998), page 122), 32 When the rolling speed increases, the oil film thickness distribution changes, and the thinnest part at low speed exists in the middle of the center and end of the contact ellipse, whereas FIG. The thin part moves to the center part (b) in FIG. The third embodiment can prevent metal contact under such operating conditions.
[0034]
Next, the effect will be described.
In the tapered roller bearing A3 of the third embodiment, the following effects can be obtained in addition to the effects (1), (2), and (4) of the first embodiment.
[0035]
(6) Since only one groove 35 is provided on the large flange surface 33a and the groove 35 is disposed at the center of the contact ellipse, it is possible to prevent metal contact under high speed operation conditions in which the average oil film thickness is large. it can.
[0036]
(Fourth embodiment)
The tapered roller bearing A4 of the fourth embodiment is an example applied as a power roller bearing of a toroidal type continuously variable transmission.
[0037]
First, the configuration will be described.
FIG. 9 is a schematic view showing a speed change mechanism of a toroidal type continuously variable transmission to which the tapered roller bearing A4 of the fourth embodiment is applied, and the rotational driving force from the engine includes a torque converter and a forward / reverse switching mechanism which are not shown. Is input to the input shaft 1.
[0038]
A torque transmission shaft 2 is arranged coaxially with the input shaft 1, and a first input disk 3 and a second input disk 4 are spline-coupled at both end positions of the torque transmission shaft 2 so as to be axially movable. Yes.
[0039]
Between the back surface of the first input disk 3 and the input shaft 1, a loading cam mechanism 5 that generates axial thrust according to the input torque is interposed.
[0040]
Between the back surface of the second input disk 4 and the nut 6 screwed into the end of the torque transmission shaft 2, a disc spring 7 for applying preload to both the input disks 3 and 4 is interposed.
[0041]
An output disk 8 mounted on the torque transmission shaft 2 is disposed at an intermediate position between the input disks 3 and 4. The output disk 8 is formed by integrally joining the back surfaces of two output disks together, and an output gear 9 is formed on the outer periphery of the output disk 8.
[0042]
The output disk 8 facing surface of the first input disk 3, the output disk 8 facing surface of the second input disk 4, and the facing surface of the output disk 8 facing both the input disks 3 and 4, respectively, Toroidal grooves 3a, 4a, 8a and 8b are formed.
[0043]
Between the toroidal grooves 3a and 8a, two left and right first power rollers 10 and 10 are sandwiched by oil film shearing force so as to be able to deliver power. Similarly, two left and right second power rollers 11 and 11 are sandwiched between the toroidal grooves 4a and 8b so that power can be transferred by oil film shearing force.
[0044]
The first input disk 3, the output disk 8, and the first power rollers 10, 10 constitute a first toroidal transmission unit 12, and the second input disk 4, the output disk 8, and the second power rollers 11, 11 form a second A toroidal transmission unit 13 is configured.
[0045]
In the above speed change mechanism, each of the power rollers 10, 10, 11, and 11 is tilted so as to obtain a tilt angle corresponding to the speed ratio by an operation described later, and the input rotation of both the input disks 3 and 4 is not performed. The speed is changed in stages (continuously) and transmitted to the output disk 8.
[0046]
FIG. 10 is a schematic view showing a shift control system of a toroidal type continuously variable transmission to which the tapered roller bearing A4 of the fourth embodiment is applied. The first power rollers 10, 10 are supported on one end of the trunnions 14, 14. The power roller rotation shafts 15 and 15 are rotatable about the center. Servo pistons 16 and 16 serving as hydraulic actuators that tilt the power rollers 10 and 10 by moving the trunnions 14 and 14 in the axial direction are provided at the other ends of the trunnions 14 and 14. Similarly, the second power rollers 11 and 11 are supported by one end of the trunnion, and a servo piston is provided as a hydraulic actuator that tilts each power roller 11 and 11 by moving the trunnion in the axial direction. . The four trunnions are connected by a synchronization wire (not shown) so that they move in synchronization.
[0047]
As a hydraulic control system for controlling the operation of the servo pistons 16 and 16, a high-side oil passage 17 connected to high-side oil chambers 16b and 16b defined by the pistons 16a and 16a and low-side oil chambers 16c and 16c are provided. A low-side oil passage 18 to be connected, a port 19 a for connecting the high-side oil passage 17, and a transmission control valve 19 having a port 19 b for connecting the low-side oil passage 18 are provided.
[0048]
The line pressure port 19c of the shift control valve 19 is supplied with a line pressure from a hydraulic source having an oil pump and a relief valve (not shown).
[0049]
The speed change spool 19d of the speed change control valve 19 detects the axial direction and the tilt direction of the trunnions 14 and 14, and is linked to the lever 20 and the recess cam 21 that feed back to the speed change control valve 19, and is moved in the axial direction by the step motor 22. Driven to displace.
[0050]
A CVT control unit 23 is provided as an electronic control system for driving and controlling the step motor 22, and the CVT control unit 23 includes a throttle opening sensor 24, an engine rotation sensor 25, an input disk rotation sensor 26, and an output shaft rotation sensor. Input information from (vehicle speed sensor) 27, inhibitor switch 28, oil temperature sensor 29, and the like is taken in.
[0051]
FIG. 11 is a sectional view showing a power roller 10 to which the tapered roller bearing A4 of the fourth embodiment is applied. The power roller 11 has the same structure.
[0052]
The power roller 10 includes an inner ring 30 that transmits the power of the first input disk 3 to the output disk 8 by oil film shearing force, an outer ring 31 that is swingably or slidably supported by the trunnion 14, and the outer ring 31. A tapered roller bearing A4 as a thrust bearing that rotatably supports the inner ring 30 and a radial bearing 37 that rotatably supports the inner ring 30 on the power roller shaft portion 31b of the outer ring 31 are configured. Yes.
[0053]
The tapered roller bearing A4 is formed between an inner ring 30 having a conical raceway surface 30a on an outer ring facing surface, an outer ring 31 having a conical raceway surface 31a on an inner ring facing surface, and between the inner ring 30 and the outer ring 31. A plurality of cone-shaped trapezoidal rollers 32 that are movably arranged, a large collar 33 that is formed on the outer ring 31 and that contacts the large-diameter end surface 32a of the roller 32 to guide the roller 32, and a small-diameter end surface 32b of the roller 32 And a gavel 34 for guiding the roller 32 in contact therewith. As in the second embodiment shown in FIG. 6, two grooves 35 are provided in the circumferential direction on the large-diameter end surface 32 a of the roller 32 among the surfaces where the large collar 33 and the roller 32 are in contact. .
[0054]
Next, the operation will be described.
[0055]
During the gear ratio control of the toroidal-type continuously variable transmission, a large thrust load is applied from the inner ring 30 to the tapered roller bearing A4 due to contact with the input / output disks 3 and 8. Due to this thrust load, a radial component force is generated in the roller 32, and this radial load is supported by the large flange surface 33 a of the large flange 33. At this time, since the large-diameter end surface 32a of the roller 32 and the large collar surface 32d of the large collar 33 rotate relative to each other, slip occurs at the contact portion between them, and the frictional force due to this slip is a loss of the tapered roller bearing A4. Torque M, and the magnitude of the loss torque M is given by the following equation (1).
M = eμFcosβ (1)
e: Height per hook μ: Friction coefficient F: Thrust load β: Conical half apex angle of the roller As apparent from the equation (1), the loss torque M decreases as the friction coefficient μ decreases. In order to reduce the coefficient of friction μ, it is necessary to form an oil film at the contact portion between the large diameter end surface 32a and the large collar surface 32d. In particular, in the toroidal type continuously variable transmission, since the thrust load F becomes large when a large torque is transmitted, it is an important issue to reduce the loss torque M.
[0056]
Therefore, in the case of the power roller 10 that receives a large radial component force, in order to reduce the loss torque M, an oil film is secured at the contact portion between the large diameter end surface 32a of the roller 32 and the large collar surface 32d of the large collar 33, and the friction is reduced. It is necessary to reduce the coefficient μ.
[0057]
On the other hand, in the tapered roller bearing A4 of the fourth embodiment, since the grooves 35 and 35 are formed in the portion where the oil film becomes the thinnest, the oil film thickness of the thinnest portion is the same as in the first embodiment. It becomes thick and can prevent the metal contact in the contact part of the large collar 33 and the roller 32, As a result, the loss torque M falls.
[0058]
Next, the effect will be described.
In the tapered roller bearing A4 of the fourth embodiment, in addition to the effects of (1), (3), (4) of the first embodiment and (5) of the second embodiment, the following effects can be obtained. Can do.
[0059]
(7) The input disk 3, the output disk 8, a plurality of power rollers 10 sandwiched between toroidal grooves 3a and 8a formed on the opposing surfaces of the input / output disks 3 and 8, respectively, and the power roller 10 A trunnion 14 that is supported so as to be tiltable, and the power roller 10 is capable of swinging or sliding relative to the trunnion 14 and an inner ring 30 that transmits the power of the first input disk 3 to the output disk 8 by an oil film shearing force. In a toroidal-type continuously variable transmission that includes an outer ring 31 that is supported and a power roller bearing that rotatably supports the inner ring 30 with respect to the outer ring 31, a tapered roller is used as the power roller bearing. Since the bearing A4 is applied, an oil film is secured at the contact portion between the large-diameter end surface 32a of the roller 32 and the large flange surface 32d of the large flange 33, and the friction coefficient μ is reduced. Te, it is possible to reduce the loss torque M.
[0060]
Although the tapered roller bearing of the present invention has been described based on the first to fourth embodiments, the specific configuration is not limited to these embodiments, and each claim in the claims Design changes and additions are permitted without departing from the spirit of the invention according to the paragraph.
[0061]
For example, in the fourth embodiment, an example in which a tapered roller bearing is applied as a power roller bearing of a toroidal-type continuously variable transmission is shown. However, various rotating devices in which a tapered roller bearing other than the toroidal-type continuously variable transmission is adopted. Can be applied to
[0062]
In the first to fourth embodiments, the example in which the groove is provided only on one surface of the large corrugated surface of the large coral and the large-diameter end surface of the roller is illustrated. For example, two grooves are provided on one surface. If it is effective for securing an oil film, such as providing a groove on the other surface and ensuring that the roller rolling speed can be secured from low to high, You may make it provide a groove | channel on both radial end surfaces.
[0063]
In the first to fourth embodiments, the number of grooves is one and two. However, three or more fine grooves may be provided.
[Brief description of the drawings]
FIG. 1 is a cross-sectional view showing a tapered roller bearing of a first embodiment and an enlarged cross-sectional view of a contact portion between a collar and a roller.
FIG. 2 is a film thickness distribution diagram at a contact portion between a collar and a roller of a tapered roller bearing without a groove.
FIG. 3 is a film thickness distribution diagram viewed from the rolling direction at the contact portion between the flange and the roller of the tapered roller bearing without a groove.
FIG. 4 is a film thickness distribution diagram viewed from the rolling direction at the contact portion between the flange and the roller of the tapered roller bearing of the first embodiment.
FIG. 5 is an enlarged cross-sectional view of a contact portion between a flange and a roller in a tapered roller bearing according to a modification of the first embodiment.
FIG. 6 is an enlarged cross-sectional view of a contact portion between a collar and a roller in a tapered roller bearing according to a second embodiment.
FIG. 7 is an enlarged cross-sectional view of a contact portion between a collar and a roller in a tapered roller bearing according to a third embodiment.
FIG. 8 is a film thickness distribution chart when the rolling speed is low and a film thickness distribution chart when the rolling speed is high in the contact portion between the flange and the roller of the tapered roller bearing of the third embodiment.
FIG. 9 is a schematic view showing a transmission mechanism of a toroidal continuously variable transmission to which a tapered roller bearing according to a fourth embodiment is applied.
FIG. 10 is a schematic diagram showing a shift control system of a toroidal type continuously variable transmission to which a tapered roller bearing according to a fourth embodiment is applied.
FIG. 11 is a sectional view showing a power roller to which a tapered roller bearing according to a fourth embodiment is applied.
[Explanation of symbols]
A1, A2, A3, A4 Tapered roller bearing 30 Inner ring 30a Raceway surface 31 Outer ring 31a Raceway surface 32 Roller 32a Large diameter end surface 32b Small diameter end surface 32c Conical peripheral surface 33
33a Large surface 34 Small surface 34a Small surface 35 Groove

Claims (7)

An inner ring having a conical track surface on the outer peripheral surface, an outer ring having a conical track surface on the inner peripheral surface, and a plurality of truncated cone-shaped rollers disposed between the inner ring and the outer ring so as to roll freely. In the tapered roller bearing provided with the flange formed on the inner ring or the outer ring and contacting the large-diameter end surface of the roller to guide the roller,
A tapered roller bearing, wherein a groove is provided in a circumferential direction on at least one surface of the flange and the roller among the surfaces where the flange and the roller are in contact with each other. The tapered roller bearing according to claim 1,
A groove in the circumferential direction is provided on the surface that contacts the roller of the heel, and the width of the groove is made smaller than the width of the Hertzian contact ellipse formed by the contact portion of the heel and roller, and formed between the roller and the roller. A tapered roller bearing in which a groove is arranged in a portion where the formed oil film becomes thin. The tapered roller bearing according to claim 1,
A groove in the circumferential direction is provided on the surface of the roller that contacts the collar, and the width of the groove is smaller than the width of the Hertzian contact ellipse formed by the contact portion between the collar and the roller, and is formed between the collar and the roller. A tapered roller bearing in which a groove is arranged in a portion where the formed oil film becomes thin. In the tapered roller bearing according to any one of claims 1 to 3,
A tapered roller bearing characterized in that two grooves are provided, and each groove is arranged in the vicinity of the middle between the center position and the end position of the contact ellipse. In the tapered roller bearing according to any one of claims 1 to 3,
A tapered roller bearing, wherein one groove is provided, and the groove is arranged at the center of the contact ellipse. In the tapered roller bearing according to any one of claims 1 to 5,
A tapered roller bearing characterized in that the cross-sectional shape of the groove is set to a shape having an arc-shaped groove bottom. The tapered roller bearing according to any one of claims 1 to 6,
An input disk, an output disk, a plurality of power rollers sandwiched between toroidal grooves formed on the opposing surfaces of these input / output disks, and a trunnion that supports the power rollers in a tiltable manner,
The power roller has an inner ring that transmits the power of the input disk to the output disk by an oil film shearing force, an outer ring supported by a trunnion, and a power roller bearing that rotatably supports the inner ring with respect to the outer ring. A tapered roller bearing characterized by being applied as the power roller bearing in a toroidal-type continuously variable transmission configured as described above.

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