WO2006003793A1 - 円すいころ軸受 - Google Patents
円すいころ軸受 Download PDFInfo
- Publication number
- WO2006003793A1 WO2006003793A1 PCT/JP2005/011030 JP2005011030W WO2006003793A1 WO 2006003793 A1 WO2006003793 A1 WO 2006003793A1 JP 2005011030 W JP2005011030 W JP 2005011030W WO 2006003793 A1 WO2006003793 A1 WO 2006003793A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- tapered roller
- roller bearing
- cage
- rqni
- surface roughness
- Prior art date
Links
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
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/30—Parts of ball or roller bearings
- F16C33/46—Cages for rollers or needles
- F16C33/467—Details of individual pockets, e.g. shape or roller retaining means
- F16C33/4676—Details of individual pockets, e.g. shape or roller retaining means of the stays separating adjacent cage pockets, e.g. guide means for the bearing-surface 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
- F16C19/34—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 both radial and axial load
- F16C19/36—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 both radial and axial load with a single row of rollers
- F16C19/364—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 both radial and axial load with a single row of rollers with tapered rollers, i.e. rollers having essentially the shape of a truncated cone
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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
- F16C33/36—Rollers; Needles with bearing-surfaces other than cylindrical, e.g. tapered; with grooves in the bearing surfaces
-
- 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
- F16C33/46—Cages for rollers or needles
- F16C33/4605—Details of interaction of cage and race, e.g. retention or centring
-
- 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
- F16C33/46—Cages for rollers or needles
- F16C33/4617—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages
- F16C33/4623—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages
- F16C33/4635—Massive or moulded cages having cage pockets surrounding the rollers, e.g. machined window cages formed as one-piece cages, i.e. monoblock cages made from plastic, e.g. injection moulded window cages
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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
- F16C2240/30—Angles, e.g. inclinations
-
- 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
- F16C2240/54—Surface roughness
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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
- F16C2240/70—Diameters; Radii
- F16C2240/80—Pitch circle diameters [PCD]
- F16C2240/82—Degree of filling, i.e. sum of diameters of rolling elements in relation to PCD
- F16C2240/84—Degree of filling, i.e. sum of diameters of rolling elements in relation to PCD with full complement of balls or rollers, i.e. sum of clearances less than diameter of one rolling element
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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
- F16C2361/00—Apparatus or articles in engineering in general
- F16C2361/61—Toothed gear systems, e.g. support of pinion shafts
Definitions
- the present invention relates to a tapered roller, and can be applied to, for example, a tapered roller bearing used in a shaft support portion of an automobile transmission.
- low-viscosity oil tends to be used in automobile transmissions for mission AT, CVT and fuel economy.
- poor lubrication can occur when adverse conditions such as (1) high oil temperature, (2) low oil volume, and (3) preload loss occur. Due to the extremely short-lived surface-origin separation, the inner ring raceway surface with high surface pressure may occur.
- a tapered roller bearing shown in Fig. 7 (see Japanese Patent Laid-Open No. 2003-28165).
- the tapered roller bearing 61 guides the cage 62 by sliding the outer circumferential surface of the small-diameter side annular portion 62a of the cage 62 and the outer circumferential surface of the large-diameter side annular portion 62b against the inner surface of the outer ring 63.
- a recess 64 is formed to maintain a non-contact state between the outer diameter surface of the column portion 62c and the raceway surface 63a of the outer ring 63.
- the retainer 62 has a small-diameter annular portion 62a, a large-diameter-side annular portion 62b, and a small-diameter-side annular portion 62a and a large-diameter-side annular portion 62b that are axially connected to each other, and a recess 64 is formed on the outer diameter surface.
- a plurality of pockets are provided between the column portions 62c for accommodating the tapered rollers 65 in a rollable manner.
- the small-diameter annular portion 62a is provided with a collar portion 62d that extends integrally on the inner diameter side.
- the tapered roller bearing shown in FIG. 7 is intended to improve the strength of the cage 62 and is used to increase the circumferential width of the column portion 62c of the cage 62.
- the vessel 62 is brought into contact with the inner diameter surface of the outer ring 63.
- JP-A-2-168021 and JP-A-6-042536 describe rolling bearings in which minute irregularities are formed on the surface of a rolling element to improve oil film forming ability.
- These indentations with a small concave shape have a surface roughness expressed by the parameter Rqni, and the value of the ratio between the axial surface roughness Rqni (L) and the circumferential surface roughness Rqni (C) Rqni (L ) / Rqni (C) value is 1.0 or less (Rqni ⁇ 0.10), and the surface roughness parameter Sk value is 1.6 or less.
- Rqni the value of the ratio between the axial surface roughness Rqni (L) and the circumferential surface roughness Rqni (C) Rqni (L ) / Rqni (C) value is 1.0 or less (Rqni ⁇ 0.10), and the surface roughness parameter Sk value is 1.6 or less.
- it is designed to have a long life
- a conventional typical tapered roller bearing with a cage other than the tapered roller bearing described in Patent Document 1 avoids contact between the outer ring 71 and the cage 72 as shown in FIG.
- it is usually designed with the coefficient of friction ⁇ (roller filling rate) defined by the following formula set to 0.94 or less.
- reference numeral 73 denotes a tapered roller
- 74 denotes a column surface
- 75 denotes an inner ring
- ⁇ denotes a window angle
- the present invention prevents an early breakage due to an increase in load capacity and excessive surface pressure on the raceway surface. Objective.
- the tapered roller bearing of the present invention holds an inner ring, an outer ring, a plurality of tapered rollers arranged to roll between the inner ring and the outer ring, and the tapered rollers at a predetermined circumferential interval.
- the roller coefficient ⁇ exceeds 0.94, and at least the surface of the rolling element is randomly provided with an infinite number of minute concave recesses, and the surface on which the recesses are provided
- the roughness parameter Ryni is in the range of 0.4, um ⁇ Ryni ⁇ 1. O / zm, and the Sk value is less than 1.6.
- the parameter Ryni is the average value of the maximum height for each reference length, that is, the reference length is extracted from the roughness curve in the direction of the average line, and the distance between the peak line and the valley bottom line of this extracted part. Is measured in the direction of the vertical magnification of the roughness curve (ISO 4287: 1997) o
- the metric Sk refers to the skewness of the roughness curve (ISO 4287: 1997), and is a statistic that provides a measure of the asymmetry of the uneven distribution. In a symmetric distribution such as a Gaussian distribution, Sk The value is close to 0. If the convex / concave part is deleted, the value is negative, and in the reverse case, the value is positive.
- the Sk value can be controlled by selecting the rotation speed, processing time, workpiece input, chip type and size, etc. of the barrel sander.
- the surface roughness parameter Rymax of the surface provided with the recess is 0.4 to 1.0.
- Parameter Rymax is the maximum value of the maximum height for each reference length (ISO 4287: 1997) 0
- the value of the ratio of the surface roughness Rqni (L) in the axial direction and the surface roughness Rqni (C) in the circumferential direction Rqni (L ) ZRqni (C) is preferably 1.0 or less.
- the parameter Rqni is the square root of the value obtained by integrating the square of the height deviation to the roughness center line force roughness curve over the measured length interval, and averaging it over that interval, also known as the square mean square roughness. Also say. Rqni is obtained by numerical calculation of the cross-sectional curve and roughness curve force recorded on an enlarged scale, and is measured by moving the probe of the roughness meter in the width and circumferential directions.
- the window angle of the pocket is preferably 55 ° or more and 80 ° or less.
- the window angle is the angle formed by the guide surface of the column that contacts the peripheral surface of one roller.
- the reason for setting the window angle to 55 ° or more is The reason why the angle is set to 80 ° or less is that if it is further increased, the pressing force in the radial direction increases, and even a self-lubricating grease material is smooth. This is because there is a risk that rotation cannot be obtained.
- the window angle is 25 for normal cages. It is ⁇ 50 °.
- the cage is made of an engineering plastic having excellent mechanical strength, oil resistance and heat resistance.
- a grease material for the cage the cage weight is lighter and self-lubricating, and the coefficient of friction is smaller than that of a steel plate cage. Combined with the effect, it is possible to suppress the occurrence of wear due to contact with the outer ring. Since these greases are lighter and have a smaller coefficient of friction than steel plates, they are suitable for reducing torque loss and cage wear when starting bearings.
- Engineering 'Plastics' includes general-purpose engineering' plastic and super 'engineering' plastic.
- the following are examples of engineering plastics. These are examples of engineering plastics, and engineering 'plastics are not limited to the following.
- PC Polycarbonate
- PA6 Polyamide 6
- PA66 Polyamide 66
- POM Polyacetanol
- m—PPE Modified Polyphenylene ether
- PBT Polybutylene terephthalate
- GF—PET GF reinforced polyethylene terephthalate
- UHM W-PE Ultra high molecular weight polyethylene
- Polysulfone PSF
- Polyethersulfone PES
- Polyphenylene sulfide PP S
- Polyarylate PAR
- Polyamideimide PAI
- Polyetherimide PEI
- Polyetheretherketone PEEK
- Liquid crystal Polymer LCP
- Thermoplastic polyimide TPI
- Polybenzimidazole PBI
- Polymethylbenten TPX
- PCT Poly 1,4-cyclohexanedimethylene terephthalate
- PCT Polyamide 46
- PA6T Polyamide 6T
- Polyamide 9T PA9T
- Polyamide 11, 12 PA11, 12
- Fluororesin Polyphthalamide
- the roller coefficient ⁇ of the tapered roller bearing to ⁇ > 0.94
- the maximum surface pressure of the raceway surface that can be reduced by force can be reduced, so that surface-origin separation can be prevented with an extremely short life under severe lubrication conditions.
- the oil film forming ability is improved, and under conditions where the oil film thickness is extremely thin under low viscosity / dilute lubrication. But it has a long life.
- the surface roughness parameter Ryni of the surface with the indentation is set within the range of 0.4 ⁇ ⁇ Ryni ⁇ l.O / zm, and is kept smaller than before, so that the oil film breaks even under lean lubrication. Compared to conventional products, it can provide a long service life even under extremely thin oil film thickness.
- the Sk value -1.6 or less is an advantageous range for forming an oil film depending on the shape and distribution of surface recesses and processing conditions.
- FIG. 1A is a cross-sectional view of a tapered roller bearing of the present invention.
- FIG. 1B is a longitudinal sectional view of the bearing of FIG. 1A.
- FIG. 2 is a partially enlarged cross-sectional view of a roller bearing with a window having a lower limit of window angle.
- FIG. 3 is a partially enlarged cross-sectional view of a roller bearing with a window having an upper limit on the window angle.
- FIG. 4 is a diagram showing the results of bearing life tests.
- FIG. 5 is a partial cross-sectional view of a tapered roller bearing according to a modification of the present invention.
- FIG. 6 is a cross-sectional view of a pillar portion of the cage in FIG.
- FIG. 7 is a cross-sectional view of a conventional tapered roller bearing in which the cage is moved to the outer ring side.
- FIG. 8 is a partially enlarged sectional view of another conventional circular roller bearing.
- FIG. 9 is an overall schematic diagram of a two-cylinder testing machine.
- FIG. 10A is a graph showing the metal contact rate of a comparative example.
- FIG. 10B is a graph showing the metal contact ratio of Examples.
- the tapered roller bearing 1 of the embodiment shown in Figs. 1A and B has a conical raceway surface 2a, and a small brim portion 2b on the small diameter side of the raceway surface 2a and a large brim portion on the large diameter side.
- Inner ring with 2c 2 The outer ring 3 having a conical raceway surface 3a, a plurality of tapered rollers 4 disposed between the raceway surface 2a of the inner ring 2 and the raceway surface 3a of the outer ring 3, and a tapered roller 4 It is composed of cages 5 that are held at regular intervals.
- the tapered roller bearing 1 has a roller coefficient ⁇ of ⁇ > 0.94.
- the cage 5 is integrally formed with a super engineering plastic such as PPS, PEEK, PA, PPA, PAI, for example, and includes a small-diameter side annular portion 5a, a large-diameter side annular portion 5b, and a small-diameter side annular portion 5a. And a plurality of column portions 5c that connect the large-diameter side annular portion 5b in the axial direction.
- a super engineering plastic such as PPS, PEEK, PA, PPA, PAI, etc., and if necessary, to increase the strength, these resin materials or other engineering 'plastic A blend of glass fiber or carbon fiber may be used.
- the window angle ⁇ of the column surface 5d has a lower limit window angle ⁇ min of 55 ° as shown in FIG. 2, and an upper limit window angle ⁇ max of 80 ° as shown in FIG.
- the window angle of a typical tapered roller bearing with a cage in which the cage is separated from the outer ring as shown in Fig. 8 is about 50 °.
- the reason why the lower limit window angle ⁇ min is set to 55 ° or more is to ensure a good contact state with the roller, and when the window angle is less than 55 °, the contact state with the roller becomes worse. In other words, when the window angle is 55 ° or more, the cage strength is secured and ⁇ > 0.94, and a good contact state can be secured.
- the upper window angle ⁇ max is set to 80 ° or less. If it is larger than this, the pressing force in the radial direction will increase, and there is a risk that smooth rotation will not be obtained even with self-lubricating grease. This is because.
- FIG. 4 shows the results of bearing life tests.
- "Comparative Example” in the "Bearing” column is a typical conventional tapered roller bearing with the cage and outer ring separated
- “Example 1” is a conventional tapered roller bearing of the present invention.
- “Example 2” is a book in which the roller coefficient ⁇ is set to ⁇ > 0.94 and the window angle is in the range of 55 ° to 80 °.
- the tapered roller bearing of the invention was conducted under severe lubrication and overload conditions.
- “Example 1” has a lifetime that is at least twice that of “Comparative Example”.
- Example 2 has a roller coefficient of 0.96, the same as that of “Example 1”, but the life time is about five times that of “Example 1”.
- the circular V and roller bearing 1 shown in the figure has a protruding portion 5f that is convex toward the outer ring raceway surface side on the outer diameter surface of the column portion 5c of the cage 5 integrally molded with engineering plastic. Is. The rest is the same as the cage 5 described above.
- the projecting portion 5f has a circular cross-sectional contour shape of the column portion 5c. This arc-shaped radius of curvature R is the outer ring raceway
- the surface radius is smaller than R. This is a good wedge between the protrusion 5f and the outer ring raceway surface.
- the opening angle becomes too large and the dynamic pressure decreases. If it exceeds 90%, the inlet angle of the wedge-shaped oil film becomes too small, and the dynamic pressure decreases in the same manner.
- the width W of the protrusion 5f is
- the column part 5c Preferably, it is formed so that it is 50% or more of the lateral width W of the column part 5c (W ⁇ 0.5 X W). 50%
- the tapered roller bearing 1 of FIGS. 5 and 6 is configured as described above, when the bearing 1 rotates and the cage 5 starts to rotate, the outer ring raceway surface and the protrusion of the cage 5 A wedge-shaped oil film is formed between 5f.
- This wedge-shaped oil film generates a dynamic pressure that is almost proportional to the rotational speed of the bearing 1. Therefore, even if the pitch circle diameter (PCD) of the cage 5 is made larger than before and close to the outer ring raceway surface, the bearing 1 becomes larger. It can be rotated without causing wear or torque loss, and the number of rollers can be increased without difficulty.
- PCD pitch circle diameter
- At least one of the rolling surface and end surface of the tapered roller and the raceway surface of the inner and outer rings has a minute recess.
- An infinite number of shape indentations are randomly formed to give a fine rough surface.
- This micro-rough surface has a surface roughness parameter Rq of the indented surface in the range of 0.4 i um ⁇ Rqni ⁇ l. ⁇ ⁇ m and a Sk value of 1.6 or less, preferably 4 9 to 1 in the range of 1. 6 is there.
- the surface roughness parameter Rymax of the surface provided with the indentation is 0.4 to 1.0.
- the ratio of the axial surface roughness Rqni (L) to the circumferential surface roughness Rqni (C) is less than 1.0.
- a desired finished surface can be obtained by special barrel polishing, but a shot or the like may be used.
- the rolling surface of the tapered roller 4 is in rolling contact with the races of the inner ring 2 and the outer ring 3, and the large end surface of the tapered roller 4 is the inner ring 2.
- the tapered roller 4 In sliding contact with the inner surface of the large brim 2c. Therefore, in the case of the tapered roller 4, an infinite number of minute concave recesses may be randomly formed on the large end surface in addition to the rolling surface.
- an infinite number of minute concave recesses may be formed on the inner surface of the large brim 2c in addition to the raceway surface.
- the measurement method and conditions of the parameters Ryni, Rymax, Sk, and Rqni are exemplified as follows.
- the measured value at one location can be relied on as a representative value. It is good to measure two places.
- Measuring device Surface roughness measuring instrument Surfcom 1400A (Tokyo Seimitsu Co., Ltd.)
- the conventional tapered roller bearings A and B (comparative example) in which the rolling surface of the tapered roller is finished to a smooth surface, and a random number of minute concave recesses on the rolling surface of the tapered roller
- the bearings AG used are tapered roller bearings with an outer ring outer diameter of 81 mm and an inner ring inner diameter of 45 mm. Note that the rolling surfaces of the rollers in the bearings A and B of the comparative example are processed by superfinishing (superfinishing) after grinding, and are not recessed. Bearings of comparative examples CE and bearings of examples The rolling surfaces of the FG rollers have innumerable numbers of micro-concave recesses formed by special barrel polishing.
- roller bearing C G is 1.0 or less, and the roller bearings A and B are around 1.0.
- a peeling test was performed using a two-cylinder testing machine shown in Fig. 9, and the metal contact rate was evaluated.
- the driving side cylinder 32 (D cylinder: Driver) and the driven side cylinder 34 (F cylinder: Follower) are attached to one end of each rotating shaft, and the two rotating shafts 36, 38 are pulleys 40, 42, respectively. Can be driven by a separate motor.
- the shaft 36 on the D cylinder 2 side was driven by a motor, and the F cylinder 34 was driven to freely follow the D cylinder 32.
- Two types of F cylinders 34 were prepared for surface treatment: a comparative example and an example. Details of test conditions are shown in Table 2.
- FIG. 10 shows comparison data of the metal contact ratio.
- the horizontal axis represents the elapsed time
- the vertical axis represents the metal contact rate
- FIG. 10B shows the metal contact rate of the rolling surface of the roller in the bearing of the example
- FIG. 10A shows the rolling of the roller in the bearing of the comparative example.
- the metal contact ratio of the surface is shown respectively.
- the tapered roller bearing according to the present invention is incorporated into an automobile transmission and is It can also be used for applications other than vehicle differentials and automobile gears.
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Rolling Contact Bearings (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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US11/629,166 US8118493B2 (en) | 2004-07-05 | 2005-06-16 | Tapered roller bearing |
EP05751508A EP1770294B1 (en) | 2004-07-05 | 2005-06-16 | Tapered roller bearing |
DE602005018061T DE602005018061D1 (de) | 2004-07-05 | 2005-06-16 | Verjüngtes Rollenlager |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004-227330 | 2004-07-05 | ||
JP2004227330A JP2006022935A (ja) | 2004-07-05 | 2004-07-05 | 円すいころ軸受 |
Publications (1)
Publication Number | Publication Date |
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WO2006003793A1 true WO2006003793A1 (ja) | 2006-01-12 |
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ID=35782605
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/JP2005/011030 WO2006003793A1 (ja) | 2004-07-05 | 2005-06-16 | 円すいころ軸受 |
Country Status (5)
Country | Link |
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US (1) | US8118493B2 (ja) |
EP (1) | EP1770294B1 (ja) |
JP (1) | JP2006022935A (ja) |
DE (1) | DE602005018061D1 (ja) |
WO (1) | WO2006003793A1 (ja) |
Families Citing this family (18)
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WO2007077804A1 (ja) * | 2005-12-27 | 2007-07-12 | Ntn Corporation | アーム式動弁装置のロッカーアーム、ロッカーシャフト、バルブキャップ、アジャストスクリュー、ピボット受け部材、及びバルブ |
JP2008038927A (ja) * | 2006-08-01 | 2008-02-21 | Ntn Corp | 円すいころ軸受 |
JP2008164105A (ja) * | 2006-12-28 | 2008-07-17 | Ntn Corp | 円すいころ軸受 |
JP2008196594A (ja) * | 2007-02-13 | 2008-08-28 | Ntn Corp | 円すいころ軸受 |
JP5183998B2 (ja) * | 2007-08-02 | 2013-04-17 | Ntn株式会社 | 円すいころ軸受 |
DE102007048655A1 (de) * | 2007-10-10 | 2008-02-07 | Schaeffler Kg | Käfigsegment eines Kunststoffkäfigs sowie Wälzlager mit dem Kunststoffkäfig |
WO2009063802A1 (ja) | 2007-11-12 | 2009-05-22 | Ntn Corporation | 円錐ころ軸受 |
US20130170780A1 (en) * | 2010-02-23 | 2013-07-04 | Nsk Ltd. | Roller Bearing and Method for Manufacturing the Same |
JP5466100B2 (ja) * | 2010-06-30 | 2014-04-09 | Ntn株式会社 | 円すいころ軸受 |
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JP7071801B2 (ja) * | 2017-03-03 | 2022-05-19 | Ntn株式会社 | 転がり軸受及びそれを備えた軸受構造 |
IT201900000238A1 (it) * | 2019-01-09 | 2020-07-09 | Skf Ab | Rolling contact bearing with improved performances |
WO2023283085A1 (en) * | 2021-07-08 | 2023-01-12 | The Timken Company | High-capacity cylindrical roller bearing and cage |
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Also Published As
Publication number | Publication date |
---|---|
DE602005018061D1 (de) | 2010-01-14 |
EP1770294A1 (en) | 2007-04-04 |
EP1770294B1 (en) | 2009-12-02 |
EP1770294A4 (en) | 2007-08-01 |
US20090016664A1 (en) | 2009-01-15 |
JP2006022935A (ja) | 2006-01-26 |
US8118493B2 (en) | 2012-02-21 |
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