WO2004111477A1 - 円筒ころ軸受 - Google Patents
円筒ころ軸受 Download PDFInfo
- Publication number
- WO2004111477A1 WO2004111477A1 PCT/JP2004/007044 JP2004007044W WO2004111477A1 WO 2004111477 A1 WO2004111477 A1 WO 2004111477A1 JP 2004007044 W JP2004007044 W JP 2004007044W WO 2004111477 A1 WO2004111477 A1 WO 2004111477A1
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- WO
- WIPO (PCT)
- Prior art keywords
- cylindrical roller
- roller
- flange
- face
- cylindrical
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/225—Details of the ribs supporting the end of the rollers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/22—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings
- F16C19/24—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly
- F16C19/26—Bearings with rolling contact, for exclusively rotary movement with bearing rollers essentially of the same size in one or more circular rows, e.g. needle bearings for radial load mainly with a single row of rollers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/34—Rollers; Needles
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/583—Details of specific parts of races
- F16C33/585—Details of specific parts of races of raceways, e.g. ribs to guide the rollers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/58—Raceways; Race rings
- F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
- F16C33/605—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings with a separate retaining member, e.g. flange, shoulder, guide ring, secured to a race ring, adjacent to the race surface, so as to abut the end of the rolling elements, e.g. rollers, or the cage
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2240/00—Specified values or numerical ranges of parameters; Relations between them
- F16C2240/40—Linear dimensions, e.g. length, radius, thickness, gap
- F16C2240/50—Crowning, e.g. crowning height or crowning radius
Definitions
- the present invention relates to a cylindrical roller bearing used for vehicle transmission and the like, which can tolerate an excessive axial load. Particularly, when high-speed rotation or low-viscosity oil is used, or when a lubricating device fails and a lubricating oil clears.
- the present invention relates to an improvement in a cylindrical roller bearing having improved seizure resistance so that seizure does not occur immediately even when the supply of the roller is insufficient.
- a flange is provided at an end of the race to guide a plurality of cylindrical rollers in a circumferential direction of the race, and a roller guide surface formed on an inner surface of the flange is provided.
- the end faces of the filter are configured to be in sliding contact with each other.
- cylindrical roller bearings used in transmissions of automobiles are sometimes used with an axial load in addition to a radial load.
- a local stress such as an edge load acts on the point where the end face of the cylindrical roller comes into contact with the roller guide surface of the flange, causing large friction on the contact surface. I do. If this friction becomes noticeable due to high-speed rotation, wear and seizure may occur, leading to premature failure of the bearing.
- Techniques for preventing or reducing seizure of cylindrical roller bearings include improving the surface roughness between the contact surfaces of the rollers and the flanges, and providing a crown wing on the roller end surface to contact the roller end surface at the center of the flange height. In this way, the contact point having an elliptical shape is set so as not to fall into, for example, a relief groove or to become larger than the flange height.
- roller bearings which prevent the failure (for example, see Japanese Patent Application Laid-Open No. 7-42746).
- a roller bearing is known in which a machining groove is provided in a direction substantially perpendicular to a relative movement direction in order to improve lubrication performance (for example, see Japanese Patent Application Laid-Open No. 7-91452).
- a roller bearing in which a plurality of minute concave portions are provided in a contact area of a flange portion which comes into contact with a roller end face to maintain the formation of an oil film (for example, see Japanese Patent Application Laid-Open No.
- a roller bearing in which the shape of the roller is changed so that the position where the roller contacts the flange portion is the same as the outer diameter surface of the roller (for example, see Japanese Patent Application Laid-Open No. Reference is made to Japanese Patent Application Publication No. Also, the intersection point between the chamfered portion and the flat portion of the end face of the roller is closer to the radially smaller diameter side for the outer ring flange portion and to the radially larger diameter side for the inner ring flange portion than the intersection point between the flange surface and the grinding relief portion.
- a technique has been proposed (for example, Japanese Patent Application Laid-Open No. 2002-18010). See No. 53.).
- the flange surface is crowned or the tangent to the end surface of the inner ring flange surface!
- the ⁇ part is configured to be in contact with the outer diameter surface (inner ring flange surface) of the cone with the point at the vertex and the spherical surface (roller end surface).
- this contact ellipse may be a relief groove on the inner ring flange surface, or There is a problem when edge protrusion occurs at the boundary between the contact ellipse and the relief groove or at the boundary between the contact ellipse and the outer diameter of the flange surface.
- An object of the present invention is to provide a cylindrical roller bearing that improves seizure performance without increasing the size of the bearing and achieves an increase in the permissible rotational speed in order to solve the above-mentioned problems.
- An inner race having an inner raceway surface, an outer race having an outer raceway surface, and a plurality of cylindrical rollers arranged between the inner raceway surface and the outer raceway surface, and at least one of the inner race and the outer race
- One is a cylindrical roller bearing having a flange provided with a roller guide surface for contacting and guiding the end face of the cylindrical roller,
- the diameter of the cylindrical roller is defined as Da, and the end face of the cylindrical roller separated from the central axis of the cylindrical roller by 0.40 Da is the first position.
- the end surface of the cylindrical roller separated by 35 Da is the second position, the end surface of the cylindrical roller contacts the roller guide surface of the flange between the first position and the second position.
- the end face of the cylindrical roller includes a convex crowning portion formed of a continuous curve passing through the first position and the second position,
- a cylindrical roller bearing wherein an angle ⁇ formed by a straight line connecting the first position and the second position and a straight line perpendicular to the central axis of the cylindrical roller is ⁇ ⁇ 0.5 °.
- an inner race having an inner raceway surface, an outer race having an outer raceway surface, and a plurality of cylindrical rollers arranged between the inner raceway surface and the outer raceway surface; At least one of the cylindrical roller bearings has a flange provided with a roller guide surface for contacting and guiding the end face of the cylindrical roller,
- the end surface of the cylindrical roller includes a convex crowning portion that comes into contact with the roller guide surface when a load equal to or more than a predetermined value is applied,
- the radial distance h between the intersection point where the end face of the cylindrical roller and the imaginary line along the roller guide surface in a state where the load is not applied, and the rolling surface of the roller are the diameter of the cylindrical roller.
- Is D a, the flange opening angle of the roller guide surface is ⁇ , and the radius of curvature of the crowning part is R '.
- a cylindrical roller bearing characterized by the following.
- the cylindrical roller bearing of (1) by configuring the shape of the end face of the roller that comes into contact with the roller guide surface of the flange portion as described above, when an axial load is applied to the cylindrical roller bearing, The contact surface pressure of the contact portion with the end surface at the roller guide surface can be reduced. As a result, the PV value (product of the contact surface pressure P and the sliding speed V) of the contact portion is reduced, and the seizure resistance can be improved. Therefore, according to the above configuration, seizure resistance can be improved without increasing the size of the bearing, and the allowable rotation speed can be improved.
- the outer diameter of the cylindrical roller is 25 mm or less, the surface roughness of 0.15 imRa or less must be satisfied by grinding the raceway surface and end surface of the cylindrical roller. Becomes possible.
- the shape of the roller end surface and the shape of the roller guide surface of the flange portion Based on the shape, the radial distance at the intersection is set in the above range. For this reason, even if a high axial load of a predetermined value or more is applied to the cylindrical roller bearing, and the contact point moves toward the peripheral surface of the flange due to the tilt, the contact point may deviate from the roller guide surface. Therefore, the contact surface pressure at the contact portion with the end surface at the roller guide surface of the flange can be reduced. As a result, the PV value (product of the contact surface pressure P and the sliding speed V) of the contact portion is reduced, and the seizure resistance can be improved. Therefore, according to the above configuration, seizure resistance can be improved without increasing the size of the bearing, and the allowable rotational speed can be improved. ⁇ Brief description of drawings>
- FIG. 1 is a partial cross-sectional view of a cylindrical roller bearing according to a first embodiment of the present invention.
- FIG. 2 shows a cylindrical roller bearing of FIG. 1 in which a roller guide surface of a flange portion comes into contact with an end surface of the cylindrical roller. It is a main part enlarged view showing a part,
- FIG. 3 is a partial cross-sectional view of a cylindrical roller bearing which is a modification of the first embodiment
- FIG. 4 is a schematic diagram showing the shape of a roller end face measured by a linear shape machine
- FIG. 4 is a diagram showing a relationship between an axial load and an allowable inner ring rotation speed in a test of the first embodiment
- FIG. 6 is a partial cross-sectional view of a cylindrical roller bearing according to a second embodiment of the present invention.
- FIG. 7 is a sectional view of the cylindrical roller bearing of FIG. 6 in which no load is applied. It is a main part enlarged view showing the end face of the cylindrical roller and
- FIG. 8 is an enlarged view of a main part of the cylindrical roller bearing of FIG. 6, showing the inner surface of the roller plan of the flange portion and the end surface of the cylindrical roller when a load is applied;
- FIG. 9 is a diagram showing the results of a rotation evaluation test in the test of the second embodiment.
- 1 and 2 1 are cylindrical roller bearings
- 2 and 2 2 are inner rings
- 3 and 23 are outer rings
- 4 and 24 are cylindrical rollers
- 5 is a cage
- 6 and 25 are flanges
- 7 and 27 are roller guide surfaces
- 10 and 26 are collar rings
- 28 is a clearance groove.
- FIG. 1 is a partial cross-sectional view of the cylindrical roller bearing according to the first embodiment.
- FIG. 2 shows a portion of the cylindrical roller bearing in FIG. 1 where a roller guide surface of a flange portion and an end surface of the cylindrical roller are in contact with each other. It is a principal part enlarged view.
- the cylindrical roller bearing 1 includes an inner ring 2, an outer ring 3, a plurality of cylindrical rollers 4, and a retainer 5.
- the inner race 2 has an inner raceway surface 2a at an intermediate portion of the outer peripheral surface
- the outer race 3 has an outer raceway surface 3a at an intermediate portion of the inner peripheral surface.
- cylindrical rollers 4 held at predetermined intervals in a circumferential direction by a retainer 5 are rotatably arranged.
- a flange 6 is provided at one end of the inner ring 2 and at both ends of the outer ring 3 to guide the cylindrical roller 4 in the circumferential direction of the inner ring 2 and the outer ring 3.
- the flange 6 has a roller guide surface 7 on its inner surface for contacting and guiding the end surface 4 a of the cylindrical roller 4.
- the roller guide surface 7 is formed to open outward by a predetermined flange opening angle 0 with respect to a surface perpendicular to the axial direction of the cylindrical roller 4. ing.
- the cylindrical roller 4 rolls on the inner ring raceway surface 2a while the end surface 4a is in sliding contact with the roller guide surface 7 of the flange portion 6.
- the end face 4a of the cylindrical roller 4 is defined as D a where the diameter of the cylindrical roller 4 is D a and the central axis of the cylindrical roller 4
- the end face 4a of the cylindrical roller 4 passes through two points of a first position A and a second position B, and has a convex crowning portion 4b formed by a continuous curve having a radius of curvature R.
- the inclination angle ⁇ between the straight line connecting the two points of the first position A and the second position B and the straight line perpendicular to the center axis CL of the cylindrical roller in the craw-jung portion 4b is expressed by the following equation. Thus, it is formed to be 0.5 ° or less.
- the crowning portion 4b of the end face 4a is provided by a smoothing process using an elastic grindstone having a Young's modulus of 10 to 50 OMPa.
- the surface roughness of at least the crowning portion 4b on the end face 4a of the cylindrical roller 4 is set to 0.02 to 0.15 mRa.
- the end face 4a of the cylindrical roller has a circular recess 4c at the center and a chamfer 4d at a portion adjacent to the rolling surface.
- the crowning 4b portion of the end face 4a of the cylindrical roller 4 is formed of a continuous curve passing through two points of the first position A and the second position B, and the inclination angle ⁇ is 0.5 ° or less. Because of the shape, the contact surface pressure in the contact area can be reduced when an axial load is applied, and the PV value can be reduced. In the present embodiment, the inclination angle ⁇ in the contact area of the end face 4 a of the cylindrical roller 4 is set smaller than the flange opening angle 0 of the roller guide surface 7, and the inclination angle of the flange opening angle ⁇ ⁇ The contact pressure is adjusted to reduce the contact surface pressure.
- a continuous curved line is formed only between the first and second positions ⁇ and ⁇ ⁇ on the end face 4 a of the cylindrical roller 4 without providing crowning on the entire end face of the roller as in the related art.
- the processing time is shortened and the cost can be reduced.
- the roughness is improved, and the seizure resistance can be improved.
- the crowning portion 4b is formed at least between the first position A and the second position B, and may be formed so as to extend on both sides from between the two points A and B.
- the flange portion on the inner ring side has been described, but the flange portion on the outer ring side is also the same. It can be configured as follows. Further, the flange portion is not limited to one formed directly in a flange shape with respect to the inner ring and the outer ring, but may be formed by a flange ring separate from the raceway ring. The flange may be a double flange or a single flange. That is, if an axial load is applied only in one direction during use, a flange may be provided only at the end on the side where the axial load acts. For example, as shown in FIG. 3, the inner ring 2 is provided with a collar ring 10 separate from the raceway ring, and the roller surface 77 of the collar ring 10 and the end face 4a of the cylindrical roller 4 have the above-described configuration. May be.
- the contact area includes a case where at least the center of the contact ellipse generated when the cylindrical roller 4 comes into contact with the flange 6 is located between the first and second positions A and B.
- the cylindrical roller bearing 1 used in Examples 1 to 3 and Comparative Examples 1 and 2 had an inner diameter of 45 mm, an outer diameter of 75 mm, and a width of 20 mm.
- the cylindrical roller 4 a roller having a diameter Da of 7.5 mm and a length of 13 mm was used, and the number of rollers was set to 18 rollers.
- An iron cage was used as the cage 5.
- the flange opening angle ⁇ of the flange 6 provided on the inner ring 2 and the outer ring 3 was 0.5 °.
- the surface roughness of the inner ring raceway surface 2a, the outer ring raceway surface 3a and the roller guide surface 7 of the flange 6 was set to 0.05 to 0.20 // mRa by grinding or superfinishing.
- the surface roughness of the rolling surface of the cylindrical roller 4 in each of Examples and Comparative Examples was set to 0.15 / mRa.
- the surface roughness of the end face 4a of the cylindrical roller 4 in each of the examples and the comparative examples is a value shown in Table 1 by swarfing using a soft grindstone having a Young's modulus of 10 to 50 OMPa. table 1
- the end face shape of the cylindrical roller 4 in each of the examples and the comparative examples is as shown in FIG. 4 by setting the vertical magnification to about 1000 times and the horizontal magnification to about 20 times using, for example, a horizontal linear machine.
- the continuity and the amount of drop are known at each position.
- the amount of roller drop at the first position A which is 0.4 OD a away from the roller center axis in the radial direction (at a position 3 mm from the roller center), is the two roller drop obtained in Fig. 4. It is given by calculating the average of the quantities dl, d1 ,.
- the roller drop amount at the second position B which is 0.35D a radially away from the roller center axis (the position at 2.625mm from the roller center), is the two positions obtained from Fig. 4. It is given by calculating the average of the drop amounts d 2 and d 2 ′.
- Table 1 shows the average roller drop amount at the first position A and the second position B in each example and the comparative example, and the inclination angle a given from the average roller drop amounts at the two points A and B.
- Comparative Example 1 is composed of cylindrical rollers whose end faces have not been subjected to the crowning treatment.
- Fig. 5 shows the results of a rotation evaluation test in each of the examples and comparative examples.
- a sufficient allowable rotation speed was given as compared with Comparative Examples 1 and 2. That is, in the contact area, there is provided a crowning portion 4b consisting of a continuous curve between the first position A and the second position B, and an inclination angle ⁇ connecting the first position A and the second position B. Is set to 0.5 ° or less, which is smaller than the flange opening angle 6, so that the permissible rotation speed can be improved.
- the surface roughness of the end face 4a including at least the crowned portion 4b is set to 0.02 to 0.15 AimRa, friction between the roller guide face 7 of the flange 6 and the end face 4a of the cylindrical roller 4 is set. , The oil film forming property was improved, and the permissible rotation speed was improved.
- the surface roughness of the end face 4a is set to 0.OS / imR a, it is possible to reduce heat generation between the end faces 4a of the flanges 6 and 4 and the allowable rotation speed. Has improved.
- the edge 4a of the cylindrical roller 4 was subjected to the crowning treatment.However, since the outer peripheral portion of the flange 6 was in contact with the edge 4a outside the substantially central portion, the sliding speed was high, and However, the contact area was small and seizure occurred due to local contact. Therefore, according to the cylindrical roller bearing of the first embodiment, the diameter of the cylindrical roller 4 is defined as Da, and the end face 4a of the cylindrical roller that is 0.4 OD a away from the center axis of the cylindrical roller is defined as the first. Position A 0.35 D a When the end face 4 a of the cylindrical roller separated from the center position is set to the second position B, the end face 4 a of the cylindrical roller is located between the first position A and the second position B.
- the end face 4a of the cylindrical roller which is in contact with the roller guide surface 7 is provided with a convex crowning portion 4b formed of a continuous curve passing through the first position A and the second position B,
- the angle ⁇ between the straight line connecting the position A and the second position B and a straight line perpendicular to the central axis of the cylindrical roller was configured to be 0.5 °.
- FIG. 6 is a partial sectional view of the cylindrical roller bearing according to the present embodiment.
- FIG. 7 is a sectional view of the cylindrical roller bearing shown in FIG.
- FIG. 8 is an enlarged view of a main part of the cylindrical roller bearing shown in FIG. 6, showing a roller guide surface of a flange portion and an end surface of the cylindrical roller when a load is applied in the cylindrical roller bearing of FIG. is there.
- the cylindrical roller bearing shown in FIG. 6 is a cylindrical roller bearing for a manual transmission for trucks in which a high axial load as well as a radial load is loaded.
- the cylindrical roller bearing 21 has an inner ring 22 and an inner ring 22.
- the inner race 22 has an inner raceway surface 22a extending from one end in the axial direction on the outer peripheral surface
- the outer race 23 has an outer raceway surface 23a at an intermediate portion of the inner peripheral surface.
- a cylindrical roller 24 is arranged between the inner raceway surface 22a and the outer raceway surface 23a so as to roll freely.
- a flange 25 for guiding the cylindrical roller 24 in the circumferential direction of the inner ring 22 and the outer ring 23 is provided at the other end of the inner ring 22 and both ends of the outer ring 23.
- an annular collar ring 26 having an outer diameter larger than that of the inner ring raceway surface 22a is in contact with one end surface of the inner ring 22.
- the ⁇ part 25 and the collar ring 26 have a flange height L from the outer ring raceway surface or the inner ring raceway surface to the peripheral surface thereof, and the inner surface of the roller surface 24 contacts the end surface 24 a of the cylindrical roller 24.
- Surface 27 is provided. As shown in Fig. 7 (in the example shown, the flange of the inner ring), the roller guide surface 27 opens outward from the surface perpendicular to the axial direction of the cylindrical roller 24 by a predetermined flange opening angle ⁇ . It is formed.
- the cylindrical roller 24 rolls on the inner ring raceway surface 22a while the end surface 24a slides against the inner surface 27 of the roller plan of the flange portion 25.
- the end surface 24a of the cylindrical roller 24 has a circular concave portion 24b at the center and a chamfered portion 24c at a portion adjacent to the rolling surface.
- the end surface 24 a of the cylindrical roller 24 is provided on the outer side in the radial direction of the chamfered portion 24 c (upper side in FIG. 7) with a convex crowning portion 24 d formed by a continuous curve having a radius of curvature R ′. Is provided.
- Da the diameter of the cylindrical roller.
- a radial gap of about 10 to 5 ⁇ generally exists. Therefore, as shown in Fig. 8, when a high axial load exceeding a predetermined value is applied, the intersection Q is displaced upward in the radial direction due to the effect of the tilt T in which the cylindrical rollers 24 tilt in the width direction. As a result, the contact point Q that actually contacts the roller guide surface 27 is obtained. Therefore, when a high axial load is applied, the load is applied so that the end surface 24 a of the cylindrical roller 24 actually contacts the roller guide surface 27 substantially at the center or below the center position.
- the position of the intersection Q in the state where the intersection Q is not set is set in advance below the flange 25, and specifically, the radial distance h of the intersection Q is set as follows. I do.
- the cylindrical roller bearing 21 for the high axial load resistance is different from the conventional relationship between the radius of curvature R ′ of the end face crowning portion 24 d and the flange portion 25 with the crowning portion 24 d
- the contact point Q can be moved to the lower side of the flange portion 25 (the inner ring raceway surface 2 2a clearance groove 2) when the axial load is small.
- the contact point Q is set near the center of the flange height L when an actual axial load (for example, 1 ton or more) is applied.
- the intersection Q when the intersection Q is set so as to satisfy the expression (2) in a state where no load is applied, the intersection Q is located radially inward of the roller guide surface 27 (the lower side in FIG. 7). Facing into the provided groove 28.
- the relief groove 28 is designed to be small and the roller guide surface 27 extends to the inside in the radial direction, the point of intersection Q is actually equal to the roller guide surface 27 when no load is applied. It may be in contact.
- the intersection Q in consideration of the influence of tilt when a high axial load equal to or more than a predetermined value is applied, the intersection Q is set so that the intersection Q does not exceed the flange height L so that no load is applied.
- the ratio between the radial distance h of the intersection Q and the flange height L is set as follows.
- the inner ring-side flange has been described.
- the outer ring-side flange may be configured in the same manner.
- the configuration may be such that the roller guide surface and the end surface of the cylindrical roller are formed on a wheel separate from the bearing ring.
- the flange may be a double flange or a single flange. That is, if an axial load is applied in only one direction during use, a flange may be provided only at the end on the side where the axial load acts.
- the raceway surface and the end surface of the cylindrical roller are reduced to 0.15 mRa or less by polishing.
- the seizure performance can be further improved.
- the surface roughness of the inner ring raceway surface 22a, the outer ring raceway surface 23a, and the roller guide surface 28 of the flange 27 was set to 0.05 to 0. SO / mRa by grinding or superfinishing. Furthermore, the surface roughness of the rolling surface of the cylindrical roller 24 in each of Examples and Comparative Examples was set to the same 0.15 / xmRa.
- Table 2 shows the flange opening angle 6 of the roller guide surface 27 and the cylindrical roller. The radius of curvature R 'at the crowned portion 24d of the end face 24a of the filter 24 is shown. Table 2
- Number of rotations N 500 to 600 rpm (Tested for 10 minutes, increased every 500 rpm)
- FIG. 9 shows the results of a rotation evaluation test in each example and comparative example. As can be seen from the test results, in Examples 4 to 6, a sufficient increase in the allowable number of revolutions was observed as compared with Comparative Examples 3 and 4.
- the radius of curvature R 'of the craw-jung portion 24d is set to 1810 mm
- the flange opening angle ⁇ of the roller guide surface 27 is set to 0.3 °
- the intersection point where no load is applied is set.
- the results of the rotation evaluation test shown in Fig. 9 show that seizure does not occur until the rotation speed reaches 5000 rpm (seizure occurs after 10 minutes at 5000 rpm).
- the radius of curvature R of the crowned portion 24d was set to 114 Omm
- the flange opening angle ⁇ of the roller guide surface 27 was set to 0.5 °
- the intersection Q in the state where no load was applied was set.
- the intersection Q is located at a height of 1.2 mm from the inner ring raceway surface due to the influence of the tilt T. It was confirmed that a contact ellipse had actually occurred, and that the end face 24a of the cylindrical roller 24 was in contact below the center of the flange height L.
- the results of the rotation evaluation test shown in Fig. 9 show that seizure and abrasion do not occur until the rotation speed reaches 6000 rpm (seizure occurs after 10 minutes at 6000 rpm). ).
- Example 6 the radius of curvature R 'of the crown dung portion 24 d was set to 80 Omm, the flange opening angle 0 of the roller guide surface 27 was 0.7 °, and the guide surface 27 was further inclined, so that the load was reduced.
- the end face 24a has almost no crowning, and the end face 24a of the cylindrical roller 24 has an edge contact with the clearance groove 28.
- the intersection Q is located in the clearance groove even if the tilt T is affected, and the end face 24a generates an edge contact with the clearance groove. I do. For this reason, seizure and abrasion occurred in a short time of 4 minutes at a rotation speed of 500 rpm.
- the end face 24a of the roller 24 includes the convex crowning portion 24d that comes into contact with the roller guide surface 27 when a load equal to or more than a predetermined value is applied,
- the radial distance h between the intersection point where the imaginary line C along the guide surface 27 contacts the end face 24 a of the roller 24 when no load is applied and the rolling surface of the roller 24 is the cylindrical roller 24.
- the standard heat treatment of SUJ 2 was performed, but by performing carburizing and carbonitriding on the cylindrical rollers and the inner and outer rings, seizure resistance can be improved. Furthermore, by using case-hardened steel as the material, the amount of retained austenite is set to 20 to 45%, and the surface hardness is set to Hv 700 to 850 to further improve seizure resistance. Can be.
- the retainer of the present embodiment may be any of an iron press retainer, a plastic retainer, and a keystone type having no retainer.
- a steel iron press retainer was tested using a keystone type cylindrical roller bearing without a retainer, or a plastic retainer was used for high-speed rotation.
- the friction coefficient between the cylindrical roller and the cage is reduced, the seizure performance can be further improved.
- the present invention is useful as a cylindrical roller bearing capable of improving seizure resistance without increasing the size of the bearing and improving the allowable rotation speed.
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP04733675.5A EP1632685B1 (en) | 2003-06-12 | 2004-05-18 | Cylindrical roller bearing |
US10/560,283 US7416346B2 (en) | 2003-06-12 | 2004-05-18 | Cylindrical roller bearing |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2003168107A JP2005003121A (ja) | 2003-06-12 | 2003-06-12 | 円筒ころ軸受 |
JP2003-168107 | 2003-06-12 | ||
JP2003291258A JP2005061495A (ja) | 2003-08-11 | 2003-08-11 | 円筒ころ軸受 |
JP2003-291258 | 2003-08-11 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2004111477A1 true WO2004111477A1 (ja) | 2004-12-23 |
Family
ID=33554398
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2004/007044 WO2004111477A1 (ja) | 2003-06-12 | 2004-05-18 | 円筒ころ軸受 |
Country Status (3)
Country | Link |
---|---|
US (1) | US7416346B2 (ja) |
EP (1) | EP1632685B1 (ja) |
WO (1) | WO2004111477A1 (ja) |
Cited By (2)
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DE102005061102A1 (de) * | 2005-12-21 | 2007-07-05 | Schaeffler Kg | Wälzlager |
DE112006000523B4 (de) * | 2005-03-03 | 2017-03-02 | Nsk Ltd. | Axial-Zylinderrollenlager |
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US7178004B2 (en) | 2003-01-31 | 2007-02-13 | Yan Polansky | Memory array programming circuit and a method for using the circuit |
WO2005028887A1 (ja) * | 2003-09-16 | 2005-03-31 | Ntn Corporation | シェル型針状ころ軸受、コンプレッサ主軸の支持構造およびピストンポンプ駆動部の支持構造 |
US7638850B2 (en) | 2004-10-14 | 2009-12-29 | Saifun Semiconductors Ltd. | Non-volatile memory structure and method of fabrication |
DE102005061103A1 (de) * | 2005-12-21 | 2007-07-05 | Schaeffler Kg | Wälzlager mit verbesserter Bordgeometrie |
US7760554B2 (en) | 2006-02-21 | 2010-07-20 | Saifun Semiconductors Ltd. | NROM non-volatile memory and mode of operation |
DE102008028164B4 (de) * | 2008-06-12 | 2021-07-01 | Ab Skf | Rolle und Rollenlager mit der Rolle |
JP5455329B2 (ja) * | 2008-06-24 | 2014-03-26 | Ntn株式会社 | 円筒ころ軸受 |
DE102008025595A1 (de) * | 2008-06-27 | 2009-12-31 | Schaeffler Kg | Lager, insbesondere Radsatzlager, speziell Radsatzlager für Bahnräder |
JP5182068B2 (ja) * | 2008-12-24 | 2013-04-10 | 株式会社ジェイテクト | 転がり軸受 |
DE102010018553A1 (de) * | 2010-04-28 | 2012-01-19 | Aktiebolaget Skf | Rolle und Rollenlager |
US9702407B2 (en) * | 2010-11-16 | 2017-07-11 | Harnischfeger Technologies, Inc. | Roller circle assembly for heavy machinery |
DE102011076328B4 (de) * | 2011-05-24 | 2013-11-07 | Aktiebolaget Skf | Geometriekonzept für einen Bord eines Rollenlagers |
JP2013117249A (ja) * | 2011-12-02 | 2013-06-13 | Ntn Corp | ころ軸受 |
US9447821B2 (en) * | 2011-12-13 | 2016-09-20 | Koyo Bearings North America, LLC | Bearing outer race |
FR2998630B1 (fr) * | 2012-11-28 | 2015-02-20 | Ntn Snr Roulements | Palier a roulement |
CN105992882A (zh) * | 2013-11-21 | 2016-10-05 | 日本精工株式会社 | 圆筒滚子轴承和变速器用轴承装置 |
JP6323136B2 (ja) * | 2014-04-16 | 2018-05-16 | 株式会社ジェイテクト | ころ軸受用軌道輪、ころ軸受及び動力伝達装置 |
US20170210166A1 (en) | 2014-09-11 | 2017-07-27 | Koyo Bearings North America Llc | Axle wheel end axial thrust assembly |
US11028880B2 (en) | 2016-01-21 | 2021-06-08 | Ntn Corporation | Rolling bearing, rolling device, and method of manufacturing rolling device |
CN113864327A (zh) * | 2017-04-26 | 2021-12-31 | 铁姆肯公司 | 用于滚子轴承的非椭圆形接触轮廓 |
US10883542B2 (en) * | 2019-05-21 | 2021-01-05 | Raytheon Technologies Corporation | Cylindrical roller bearing containing a crowned inner ring shoulder |
DE102020211036B4 (de) * | 2020-09-02 | 2022-04-14 | Aktiebolaget Skf | Anordnung mit einem Schleifwerkzeug und einer Rolle für ein Rollenlager sowie Verfahren zum Herstellen einer Rolle für ein Rollenlager |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS51156346U (ja) * | 1975-06-09 | 1976-12-13 | ||
JPS59106719A (ja) * | 1982-12-08 | 1984-06-20 | Koyo Seiko Co Ltd | 円筒ころ軸受 |
JPH09229057A (ja) * | 1996-02-27 | 1997-09-02 | Nippon Seiko Kk | 転がり軸受 |
JPH10196660A (ja) * | 1996-11-13 | 1998-07-31 | Nippon Seiko Kk | ころ軸受 |
Family Cites Families (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4027930A (en) * | 1975-12-19 | 1977-06-07 | The Garrett Corporation | Bearing assembly and method |
JPS5843609A (ja) * | 1981-09-09 | 1983-03-14 | Toshiba Corp | 弾性表面波装置 |
JPH06241235A (ja) | 1993-02-17 | 1994-08-30 | Koyo Seiko Co Ltd | ころ軸受 |
JPH0712119A (ja) * | 1993-06-28 | 1995-01-17 | Nippon Seiko Kk | 円筒ころ軸受 |
JPH0742746A (ja) | 1993-07-30 | 1995-02-10 | Ntn Corp | ころ軸受 |
JPH0791452A (ja) | 1993-07-30 | 1995-04-04 | Ntn Corp | 転がり軸受 |
JPH09236131A (ja) | 1996-02-29 | 1997-09-09 | Ntn Corp | ころ軸受 |
US6086261A (en) * | 1998-01-14 | 2000-07-11 | Ntn Corporation | Tapered roller bearing |
JPH11236920A (ja) * | 1998-02-24 | 1999-08-31 | Nippon Seiko Kk | 転がり軸受 |
JP2000065066A (ja) * | 1998-08-19 | 2000-03-03 | Nippon Seiko Kk | 円筒ころ軸受 |
JP2002181053A (ja) * | 2000-12-13 | 2002-06-26 | Nsk Ltd | ころ軸受 |
JP2003021145A (ja) * | 2001-07-05 | 2003-01-24 | Nsk Ltd | ころ軸受 |
US6702471B2 (en) * | 2001-11-06 | 2004-03-09 | Nsk Ltd. | Radial roller bearing |
TWI285243B (en) * | 2002-03-20 | 2007-08-11 | Ntn Toyo Bearing Co Ltd | Cylindrical roller bearing |
-
2004
- 2004-05-18 US US10/560,283 patent/US7416346B2/en active Active
- 2004-05-18 WO PCT/JP2004/007044 patent/WO2004111477A1/ja active Application Filing
- 2004-05-18 EP EP04733675.5A patent/EP1632685B1/en not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS51156346U (ja) * | 1975-06-09 | 1976-12-13 | ||
JPS59106719A (ja) * | 1982-12-08 | 1984-06-20 | Koyo Seiko Co Ltd | 円筒ころ軸受 |
JPH09229057A (ja) * | 1996-02-27 | 1997-09-02 | Nippon Seiko Kk | 転がり軸受 |
JPH10196660A (ja) * | 1996-11-13 | 1998-07-31 | Nippon Seiko Kk | ころ軸受 |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE112006000523B4 (de) * | 2005-03-03 | 2017-03-02 | Nsk Ltd. | Axial-Zylinderrollenlager |
DE102005061102A1 (de) * | 2005-12-21 | 2007-07-05 | Schaeffler Kg | Wälzlager |
Also Published As
Publication number | Publication date |
---|---|
US20060126983A1 (en) | 2006-06-15 |
EP1632685A1 (en) | 2006-03-08 |
EP1632685A4 (en) | 2012-03-07 |
US7416346B2 (en) | 2008-08-26 |
EP1632685B1 (en) | 2013-07-10 |
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