CN100485207C - Tapered roller bearing - Google Patents
Tapered roller bearing Download PDFInfo
- Publication number
- CN100485207C CN100485207C CNB2005800153326A CN200580015332A CN100485207C CN 100485207 C CN100485207 C CN 100485207C CN B2005800153326 A CNB2005800153326 A CN B2005800153326A CN 200580015332 A CN200580015332 A CN 200580015332A CN 100485207 C CN100485207 C CN 100485207C
- Authority
- CN
- China
- Prior art keywords
- retainer
- roller bearing
- taper roller
- bearing
- outer shroud
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Landscapes
- Rolling Contact Bearings (AREA)
Abstract
A tapered roller bearing (1) used in transmissions or differentials for automobiles includes an inner ring (2), an outer ring (3), a plurality of tapered rollers (4) rollably disposed between the inner and outer rings (2 and 3), and a cage (5) for holding the tapered rollers (4) at circumferential predetermined intervals, wherein the roller coefficient Gamma exceeds 0.94, where Gamma is (the number of rollers x mean roller diameter) / (Pi x PCD).
Description
Technical field
The present invention relates to taper roller bearing, more specifically, the present invention relates to but be not limited to be used in taper roller bearing in the Support Gear of automobile gearbox or differential mechanism.
Background technique
Automobile gearbox is tending towards using light viscosity oil recently, with the AT, the CVT that obtain gearbox, low fuel consumption etc.In the environment that uses light viscosity oil, cause the very short surperficial start-up wear of bearing life to occur in inner race surface sometimes with high surface pressure, this be because take place simultaneously as (1) high oil temperature, (2) less oil mass and (3) preload lubricated relatively poor when missing the unfavorable situation of this class.
As for the solution of the short problem of this bearing life that causes owing to surperficial start-up wear, direct and effective solution is to reduce maximum surface pressure.In order to reduce maximum surface pressure, if must change that bearing size or bearing size are not changed then the quantity that increases roller in the bearing.In order under the situation that does not reduce the roller diameter, to increase the quantity of roller, the distance between the groove (pocket) in the retainer is narrowed down.Yet, must increase the pitch circle of retainer as much as possible retainer is pulled to outer shroud for this reason.
Be pulled to side, touch the example of the inside diameter surface of outer shroud as retainer, have the taper roller bearing shown in Fig. 1 (with reference to Japanese publication No.2003-28165) up to it.In this taper roller bearing 11, the external peripheral surface of the minor diameter annulus part 12a of retainer 12 and major diameter annulus part 12b is configured to the inside diameter surface of sliding contact outer shroud 13, with guiding retainer 12, the external diameter surface of each cylindrical member 12c of this retainer 12 is formed with depression 14, be used to suppress braking moment, thus the contactless state between the raceway face 13a of the external diameter surface of maintenance cylindrical member 12c and outer shroud 13.Retainer 12 has minor diameter annulus part 12a, major diameter annulus part 12b and a plurality of cylindrical member 12c, and wherein said a plurality of cylindrical member 12c connect minor diameter annulus part 12a and major diameter annulus part 12b vertically and be formed with depression 14 on its outer surface.Being provided with a plurality of grooves between the cylindrical member 12c continuously, be used for rollably receiving taper roller 15.Minor diameter annulus part 12a has the flange 12d that one is stretched over internal side diameter.Taper roller bearing among Fig. 1 is an example of attempting to improve the intensity of retainer 12, wherein for the periphery width of the cylindrical member 12c that increases retainer 12, retainer 12 is pulled to the side, touches the inside diameter surface of outer shroud 13 up to it.
Summary of the invention
In the taper roller bearing described in the Japanese publication No.2003-28165 11, retainer 12 is pulled to outside diameter, touches the inside diameter surface of outer shroud 13 up to it, thereby increases the periphery width of the cylindrical member 12c of retainer 12.In addition, because in the cylindrical member 12c of retainer 12, there is depression 14, make the plate thickness attenuation inevitably, cause the rigidity of retainer 12 to descend, be included in the bearing possibility that retainer 12 pressurizeds are deformed or retainer 12 is out of shape during the rotation of bearing 11 between 11 erecting stages.The trial that increases the rigidity of retainer 12 will make the diameter dimension of retainer 12 increase, and comprise because the sliding contact in the loop contacts part outside causes the moment of torsion increase or causes the possibility of so-called braking torque.
On the other hand, except at the taper roller bearing described in the Japanese publication No.2003-28165, design has the conventional typical taper roller bearing of retainer, so that generally be not more than 0.94 by the roller coefficient gamma (roller encapsulation percentage) of following formula definition, so that guarantee the width of the cylindrical member of retainer 17, and as shown in Figure 2 avoid between outer shroud 16 and the retainer 17 after the contact the suitable cylindrical member intensity of the frame 17 that is maintained and level and smooth rotation.In addition, in Fig. 2, reference number 18 expression taper roller bearings, 19 expression cylindrical member surfaces, ring in 20 expressions, and θ represents the window angle.
The roller coefficient gamma=(Z*DA)/(π * PCD), wherein Z is the quantity of roller, and DA is the average diameter of roller, and PCD is a pitch diameter.
Increase roller encapsulation percentage simply, keep the constant trial of groove size of retainer 17 simultaneously, will cause the cylindrical member 17a of retainer 17 to become thin thin, can not guarantee enough cylindrical member intensity.On the other hand, when the direction change retainer diameter in gap between retainer and the outer shroud is reduced on the edge in order to ensure cylindrical member intensity, as introducing among the Japanese publication No.2003-28165, there are the wearing and tearing of the outer shroud contact segment of quickening retainer and cause the possibility that braking torque increases.
The purpose of this invention is to provide a kind of taper roller bearing, this taper roller bearing can increase the quantity of holding under the situation that does not reduce the retainer rigidity, and never produces braking torque.
Another object of the present invention is to prevent owing to breaking too early that the increase of load capacity on raceway face and excessive surface pressure cause, and then helps the size of gearbox to reduce and keep long working life.
According to embodiments of the invention, taper roller bearing comprise interior ring, outer shroud, rollably be arranged in a plurality of tapered roller and cages between ring and the outer shroud, this retainer is used for keeping taper roller with the predetermined circle spacing, described retainer has smaller diameter side, wherein this retainer does not contact with outer shroud when being in neutral state, but when axially moving to this smaller diameter side and radially moving, it contacts with outer shroud, make the bearing rotation, realizing the centering of described retainer, thereby described retainer and outer shroud disengage.Therefore, can reduce the maximum surface pressure of the raceway face of taper roller bearing, thus prevent from very bad lubricated environment, to take place cause the extremely short surperficial start-up wear of bearing life.
Taper roller bearing can make the roller coefficient surpass 0.94.Set roller coefficient gamma (at γ〉0.94 place) and make and to increase load capacity, also reduced the maximum surface pressure on the raceway face; Therefore, can prevent to issue the living surperficial start-up wear that causes bearing life extremely to be lacked at very bad lubricated environment.
According to another embodiment, taper roller bearing comprise interior ring, outer shroud, rollably be arranged in a plurality of tapered roller and cages between ring and the outer shroud, this retainer is used for keeping taper roller with the predetermined circle spacing, wherein the roller coefficient gamma surpasses 0.94.As top just described, the roller coefficient gamma (at γ〉0.94 place) that taper roller bearing is set makes and not only can increase load capacity, has also reduced the maximum surface pressure on the raceway face; Therefore, can prevent to issue the living surperficial start-up wear that causes bearing life extremely to be lacked at very bad lubricated environment.Therefore, use this taper roller bearing, help the size of gearbox or differential mechanism to reduce and long service life.
In taper roller bearing, the window angle of groove can be in 55 ° to 80 ° scope.Term " window angle " refers to the angle that is formed by the guide surface with the cylindrical member of the outer circumferential face adjacency of single roller.Set the window angle be in the reason that is not less than 55 ° be in order to ensure with the excellent contact state of roller, and set the window angle and be in the reason that is not more than 80 ° and be: if surpass this numerical value then radial pressure increases, even relate to the risk of using the selflubricating resin material smoothly to be rotated.In addition, common retainer has 25 °-50 ° window angle.
Retainer is by in engineering plastics manufacturing good aspect mechanical strength, oil resistance and the heat resistance.The use that is used for the resin material of retainer has following characteristics: as with compare by the retainer of iron plate manufacturing, this retainer is in light weight, selflubricating and have low coefficient of friction, and the effect of the lubricant oil that uses in these characteristics and the bearing combines and can suppress to cause owing to contacting with outer shroud the generation of wearing and tearing.Compare with steel disc, these resins are lightweight and have low coefficient of friction, so that their loss of torque and retainer wearing and tearing when being suitable for being reduced in the bearing starting.
Engineering plastics comprise general engineering plastic and senior engineering plastic.Below the typical project plastics are illustrated in, but they just as an example, and engineering plastics are not limited to following shown.
[general engineering plastic]: polycarbonate (PC) (PC), polyamide 6 (PA6), polyamide 66 (PA66), polyoxymethylene (POM), Noryl (m-PPE), polybutylene terephthalate (PBT), GF strengthen polyethylene terephthalate (GF-PBT), ultra-high molecular weight polyethylene (UHMW-PE).
[super engineering plastics]: polysulfones (PSF), polyether sulfone (PES), polyphenylene sulfide (PPS), polyacrylate (PAR), polyamidoimide (PAI), Polyetherimide (PEI), polyethers-ether ketone (PEEK), liquid-crystalline polymer (LCP), thermoplastic polyimide (TPI), polybenzimidazoles (PBI), polymethylpentene (TPX), poly terephthalic acid-1,4-hexamethylene dimethyl ester (PCT), polyamide 46 (PA46), polyamide 6 T (PA6T), polyamide 9T (PA9T), polyamide 11,12 (PA11,12), fluororesin, polyphthalamide (PPA).
When specification is set forth with reference to the accompanying drawings, these and other purposes of the present invention and feature will become clearer.
Description of drawings
Fig. 1 is the cross-sectional view of conventional taper roller bearing, and wherein retainer is pulled to outer rim side;
Fig. 2 is the part amplification sectional view of another conventional taper roller bearing;
Fig. 3 is the sectional view of the general gearbox of automobile;
Fig. 4 is the sectional view of the general differential mechanism of automobile;
Fig. 5 is the cross-sectional view of taper roller bearing of the present invention;
Fig. 6 is the longitudinal section of taper roller bearing among Fig. 1;
Fig. 7 is the sectional view of retainer before moving vertically;
Fig. 8 is the sectional view of retainer after moving vertically;
Fig. 9 is the side view of the retainer of static taper roller bearing;
Figure 10 is the side view at the retainer of the early stage taper roller bearing of rotation;
Figure 11 is the side view of the retainer of taper roller bearing during rotation;
Figure 12 is the part amplification sectional view that window angle (window angle) is in the taper roller bearing of lower limit;
Figure 13 is the part amplification sectional view that window angle (window angle) is in the taper roller bearing of CLV ceiling limit value;
Figure 14 is the result of the life test of bearing;
Figure 15 is the part amplification sectional view that changes the taper roller bearing of mode of execution according to the present invention; And
Figure 16 is the sectional view of the cylindrical member of the retainer among Figure 15.
Specific embodiment
The gearbox of automobile (main transformer speed unit) is type hand and automatic type by rough classification.In addition, they also can be classified as according to the drive system of vehicle: the transfer case (auxiliary variable speed unit) of the gearbox of the Transaxle of front-wheel drive (FWD), rear wheel drive (RWD) and four-wheel drive (4WD).They are used to make the driving power speed change from motor, and then it is passed to live axle etc.
The example of structure of Fig. 3 display automobile gearbox.This gearbox belongs to the synchromesh type, and wherein in same figure, the left side is that to start pusher side, right side be driven wheel side.Taper roller bearing 23 is inserted between main shaft 21 and the main actuation gear 22.In this example, the inner periphery of main actuation gear 22 directly is formed with the outer-race ball track surface of corresponding taper roller bearing 23.Main actuation gear 22 is supported by taper roller bearing 24, is used for the rotation with respect to housing 25.By engagement, clutch gear 26 is connected to main actuation gear 22, and near clutch gear 26 lazy-tongs 27 is set.
Lazy-tongs 27 comprise effect (with the left and right directions among the same figure) motion vertically that is suitable for by the selector (not shown) axle sleeve 28, be installed in the inner periphery of axle sleeve 28 axially slidably synchronizer key 29, be connected to the wheel hub 30 of the outer periphery of main shaft 21, be installed in the synchronizer ring 31 on the outer periphery (conical section) of clutch gear 26 and synchronizer key 29 elasticity are pressed against pin 32 and spring 33 on the inner periphery of axle sleeve 28 slidably.
In the situation shown in the same figure, sleeve pipe 28 and synchronizer key 29 are remained on neutral position by pad 32.At this moment, main actuation gear 22 is with respect to main shaft 21 idle running.On the other hand, when the excitation selector so that sleeve pipe 28 for example moves to when left side vertically from state shown in the same figure, synchronizer key 29 is followed sleeve pipe 28 and is moved to the left side vertically, on the inclined surface with the tapering part that synchronizer ring 31 is pressed against clutch gear 26.The rotational velocity that this has reduced clutch gear 26 has relatively increased the rotational speed of lazy-tongs 27.And big when both rotational speeies are synchronous, sleeve pipe 28 further moves to the left side vertically, be meshed with clutch gear 26, and main shaft 21 and main actuation gear 22 is connected to each other by lazy-tongs 27 each other.This allows main shaft 21 and main actuation gear 22 to rotate synchronously.
Fig. 4 shows the general differential mechanism that is used for automobile.In same figure, upper and lower side is respectively towards the forward and backward side of vehicle.Driving pinion axle 35 is accommodated in the front of the case of differential 34, and is rotatably supported by a pair of taper roller bearing 37 and 38.Driving pinion axle 35 have the cardan shaft (not shown) that is connected to its front end and be fixed to the driving pinion axle (reduction pinion teeth) 36 of its rear end or whole position thereon, it is meshed with linkage gear (deceleration gearwheel) 39.
The driving torque of cardan shaft is transmitted with following route: driving pinion 36-linkage gear 39-differential gear case 40-small gear 43-side gear 44-live axle.On the other hand, the driving resistance of tire is transmitted with following route: live axle-side gear 44-small gear 43.
Taper roller bearing 1 shown in Fig. 5 and 6 is used to above gearbox or differential mechanism in conjunction with Fig. 3 or 4 described automobiles.It comprises the interior ring 2 with tapered raceway surface 2a, outer shroud 3, a plurality of taper roller 4 and the retainer 5 with tapered raceway surface 3a, wherein said tapered raceway surface 2a has at the tapered front surface rib 2b of its smaller diameter side with at the taper rear surface of its larger diameter side rib 2c, described a plurality of taper roller 4 is by between the raceway face 2a and 3a of ring 2 in rollably inserting and outer shroud 3, and described retainer 5 is used for keeping taper roller 4 with the interval that equates along circumference.This taper roller bearing 1 has the roller coefficient gamma〉0.94.
The outer diameter of retainer 5 is set in size like this: when retainer 5 when state shown in Fig. 7 moves to smaller diameter side (Fig. 8) vertically, as indicated by arrow among the same figure, radially move downward as shown in Figure 9 then, outer shroud 3 and retainer 5 contact with each other the centering that influences retainer 5 to cause the bearing rotation, as shown in Figure 11, thereby retainer 5 and outer shroud 3 disengage, the remaining predetermined gap that runs through circumference.In other words, this size is such size, this size guarantee retainer 5 as shown in Figure 8 be provided with and be pulled under the situation of smaller diameter side vertically between two parties, between retainer 5 and outer shroud 3, there is the gap, and at retainer 5 radially when axial centre moves, outer shroud 3 contacts with retainer 5.Thereby, contact with retainer 5 at early stage (Figure 10) outer shroud 3 of running, and they disengage (Figure 11) between on-stream period; Therefore, the braking torque that causes owing to contact, moment of torsion increase or wear and tear and can be suppressed.
The window angle θ of the cylindrical member surface 5d of retainer 5 has lower limit window angle θ min, and θ min is 55 ° as shown in Figure 12, and has upper limit window angle θ max, and θ max is 80 ° as shown in Figure 13.For the taper roller bearing of its retainer and the isolated Type Equipment retainer of outer shroud, window angle θ is at most about 50 °, as shown in Figure 2.The reason that lower limit window angle θ min is set in 55 ° is in order to ensure the excellent contact state; Less than 55 ° window angles contact condition will be degenerated.Just, with the window angle be set in 55 ° or abovely can guarantee γ after retainer intensity is guaranteed 0.94, and make up the excellent contact state.Further, the reason that upper limit window angle θ max is set in 80 ° is that if surpass this numerical value, then radial pressure increases, even relate to the risk of using the selflubricating resin material also can not smoothly be rotated.
Figure 14 shows the result of bearing life test.In Figure 14, [comparative example 1] relates to typical conventional taper roller bearing in [bearing] row, retainer and outer shroud are spaced apart in this routine taper roller bearing, [embodiment 1] relates to one of taper roller bearing according to the embodiment of the invention, only the roller coefficient gamma is set at γ with respect to conventional object therein〉0.94 place, and [embodiment 2] relate to the taper roller bearing according to the embodiment of the invention, and the roller coefficient gamma is set at γ therein〉0.94 place and window angle be set in 55 °-80 ° the scope.Under very bad lubricating condition and excessive loads condition, implement this test.As from can being clear that the same figure, [embodiment 1] has the life-span of twice or more times [comparative example].In addition, the bearing in [embodiment 2] has 0.96 roller coefficient, its with [embodiment 1] in identical, but its life-span be [embodiment 1] about 5 times or longer.In addition, in [comparative example 1], [embodiment 1] and [embodiment 2], this size is φ 45 * φ 81 * 16 (is the unit with mm), and the quantity of roller is 24 ([comparative example]), 27 ([embodiments 1 and 2]), and oil film parameter Λ=0.2.
Next, with reference to Figure 15 and 16 modification of the present invention will be described.At the taper roller bearing 1 shown in the same figure is such: the external diameter surface by the cylindrical member 5c of the Unitarily molded retainer 5 of engineering plastics has been formed protruding 5f, and it is to outer shroud raceway face side projection.The remaining part of this structure is identical with above-described retainer 5 (Fig. 6).In protruding 5f, the cross-sectional profiles transversely of cylindrical member 5c is an arch, as shown in Figure 16.The radius of curvature R 2 of this arcuate in shape is less than outer-race ball track surface radius R
1This be in order to ensure, good wedge-shaped oil film can be formed between protruding 5f and the outer-race ball track surface, ideally, the radius of curvature R of projection
2Be outer-race ball track surface radius R
1About 70-90%.If it is less than 70%, the inlet angular aperture of wedge-shaped oil film becomes excessive, has just reduced hydrodynamic pressure.In addition, if it surpasses 90%, then the inlet angular aperture of wedge-shaped oil film becomes too small, has similarly reduced hydrodynamic pressure.
In addition, the width W of protruding 5f
2Be desirably cylindrical member 5c width W
150% or bigger (W
2〉=0.5 * W
1).This is because if it less than 50%, then can not guarantee to form enough height of good wedge-shaped oil film for protruding 5f.In addition, because outer-race ball track surface radius R
1Change to smaller diameter side from larger diameter side continuously, the radius of curvature R of protruding 5f
2Change continuously, in order to coordinate, then from the larger radius of curvature R of larger diameter side annulus part 5b with this situation
2Small radii of curvature R to smaller diameter side annulus part 5a
2(see figure 6).
Taper roller bearing 1 among Figure 15 and 16 is configured in above-mentioned mode; Therefore, when bearing 1 begins rotation and retainer 5 rotation, between the outer-race ball track surface of retainer 5 and protruding 5f, form wedge-shaped oil film.This wedge-shaped oil film produces roughly and the proportional hydrodynamic pressure of the rotational speed of bearing 1; Therefore, even the pitch diameter of retainer 5 (PCD) is done than big and close outer-race ball track surface of the prior art, it also can rotate under the situation that does not cause galling or loss of torque for bearing 1, thereby does not have the quantity that increases roller difficultly.
So far, a plurality of embodiment of the present invention has been described; Yet the present invention is not restricted to this, and various change is possible.For example, although senior engineering plastic for example PPS, PEEK, PA, PPA and PAI has been used as the retainer material, but in the time of if needed, can use these resin materials or the Other Engineering plastics that wherein are added with glass fibre or carbon fiber, to be used to strengthen intensity.
Claims (6)
1. taper roller bearing, it comprise interior ring, outer shroud, rollably be arranged on described in a plurality of tapered roller and cages between ring and the outer shroud, described retainer is used for keeping taper roller with the predetermined interval along circumference, described retainer has smaller diameter side, wherein said retainer does not contact with outer shroud when being in neutral state, but when axially moving to this smaller diameter side and radially moving, it contacts with outer shroud, make the bearing rotation, realizing the centering of described retainer, thereby described retainer and outer shroud disengage.
2. taper roller bearing as claimed in claim 1, wherein the roller coefficient surpasses 0.94.
3. taper roller bearing as claimed in claim 1 or 2, the window angle of the groove of wherein said retainer changes in 55 ° to 80 ° scope.
4. as each the described taper roller bearing in claim 1 or 2, wherein said retainer is by in engineering plastics manufacturing good aspect mechanical strength, oil resistance and the heat resistance.
5. as each the described taper roller bearing in claim 1 or 2, wherein said bearing is used to gearbox.
6. as each the described taper roller bearing in claim 1 or 2, wherein said bearing is used to differential mechanism.
Applications Claiming Priority (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004143882 | 2004-05-13 | ||
| JP143882/2004 | 2004-05-13 | ||
| JP198704/2004 | 2004-07-05 | ||
| JP198703/2004 | 2004-07-05 | ||
| JP257108/2004 | 2004-09-03 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1957186A CN1957186A (en) | 2007-05-02 |
| CN100485207C true CN100485207C (en) | 2009-05-06 |
Family
ID=38063719
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005800153326A Active CN100485207C (en) | 2004-05-13 | 2005-04-18 | Tapered roller bearing |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100485207C (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102011007495A1 (en) * | 2011-04-15 | 2012-10-18 | Aktiebolaget Skf | Rolling bearing cage and method for producing a rolling bearing cage |
| WO2017159467A1 (en) * | 2016-03-18 | 2017-09-21 | Ntn株式会社 | Tapered roller bearing |
| JP6790517B2 (en) * | 2016-07-06 | 2020-11-25 | 株式会社ジェイテクト | Tapered roller bearing |
| CN110131306B (en) * | 2018-02-09 | 2023-05-02 | 舍弗勒技术股份两合公司 | Rolling bearing and static ring thereof |
-
2005
- 2005-04-18 CN CNB2005800153326A patent/CN100485207C/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN1957186A (en) | 2007-05-02 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US7789570B2 (en) | Tapered roller bearing | |
| EP1746298B1 (en) | Tapered roller bearing | |
| US8939044B2 (en) | Retainer made of synthetic resin for use in a deep groove ball bearing; deep groove ball bearing; and gear support device | |
| US20070242914A1 (en) | Double-Row Antifriction Bearing | |
| EP1614914B1 (en) | Tapered roller bearing | |
| JP5005209B2 (en) | Tapered roller bearing | |
| CN100485207C (en) | Tapered roller bearing | |
| US8123414B2 (en) | Tapered roller bearing | |
| EP2175151A1 (en) | Taper roller bearing | |
| JP2005003198A (en) | Rolling bearing and transmission for hybrid car or fuel cell car using the same | |
| JP2005098316A (en) | Conical roller bearing | |
| JP2008051274A (en) | Wheel bearing device | |
| JP4994643B2 (en) | Tapered roller bearing | |
| JP2006022821A (en) | Tapered roller bearing | |
| JP2006022824A (en) | Tapered roller bearing for differential | |
| JP4994630B2 (en) | Tapered roller bearings | |
| JP4987278B2 (en) | Tapered roller bearing for transmission | |
| JP2007127220A (en) | Tapered roller bearing for transmission | |
| JP5031220B2 (en) | Tapered roller bearing | |
| JP2007120575A (en) | Tapered roller bearing | |
| JP2005351472A (en) | Tapered roller bearing | |
| JP2006022823A (en) | Tapered roller bearing for transmission | |
| JP2007113656A (en) | Conical roller bearing | |
| JP2006022822A (en) | Tapered roller bearing | |
| JP2007120650A (en) | Roller bearing |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant |