JP2007198399A - Power transmission shaft - Google Patents
Power transmission shaft Download PDFInfo
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- JP2007198399A JP2007198399A JP2006013968A JP2006013968A JP2007198399A JP 2007198399 A JP2007198399 A JP 2007198399A JP 2006013968 A JP2006013968 A JP 2006013968A JP 2006013968 A JP2006013968 A JP 2006013968A JP 2007198399 A JP2007198399 A JP 2007198399A
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- Prior art keywords
- bearing
- shaft
- dust cover
- power transmission
- cylindrical
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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
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/164—Sealings between relatively-moving surfaces the sealing action depending on movements; pressure difference, temperature or presence of leaking fluid
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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
- F16C33/72—Sealings
- F16C33/76—Sealings of ball or roller bearings
- F16C33/80—Labyrinth sealings
- F16C33/805—Labyrinth sealings in addition to other sealings, e.g. dirt guards to protect sealings with sealing lips
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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
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/063—Fixing them on the shaft
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/202—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints
- F16D3/205—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially outwardly from the coupling part
- F16D3/2055—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members one coupling part having radially projecting pins, e.g. tripod joints the pins extending radially outwardly from the coupling part having three pins, i.e. true tripod joints
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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
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
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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
- F16C2326/00—Articles relating to transporting
- F16C2326/01—Parts of vehicles in general
- F16C2326/06—Drive shafts
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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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
- F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
- F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
- F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
- F16D2003/22326—Attachments to the outer joint member, i.e. attachments to the exterior of the outer joint member or to the shaft of the outer joint member
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mounting Of Bearings Or Others (AREA)
- Sealing Of Bearings (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Abstract
Description
本発明は、自動車のドライブシャフト等として使用される動力伝達シャフトに関するものである。 The present invention relates to a power transmission shaft used as a drive shaft of an automobile.
例えば、自動車のフロント用ドライブシャフトにおいて、変速機の差動装置（デファレンシャル）が左右の車輪の片側に偏在して配置される場合、発進時や加速時にハンドルが取られたり車両が偏向したりする、いわゆるトルクステア現象が発生するおそれがある。この問題を解決するため、例えば特許文献１のドライブシャフトでは、左右いずれか一方の等速ジョイントに延長軸部を設け、車体中心線に対する左右等速ジョイントの配設位置を均等位置に近づけている。 For example, in a front drive shaft of an automobile, when a transmission differential (differential) is arranged unevenly on one side of the left and right wheels, the steering wheel is taken or the vehicle is deflected when starting or accelerating. A so-called torque steer phenomenon may occur. In order to solve this problem, for example, in the drive shaft of Patent Document 1, an extension shaft portion is provided in one of the left and right constant velocity joints, and the arrangement positions of the left and right constant velocity joints with respect to the vehicle body center line are brought closer to the uniform position. .
このようなドライブシャフトにおいて、等速ジョイントと差動装置との間の軸部が長大化することにより、車両振動に伴い軸部の振れが生じるおそれがある。軸部と差動装置とはスプライン結合されているが、このスプラインの嵌合長は軸部の長さに対して短いため、軸部の振れを抑えるほどの固定力は有さない。この点に鑑み、例えば特許文献２では、中間軸の等速自在継手側端部を、ブラケットおよびベアリングを介してエンジンに回転自在に固定することで、中間軸の振れを抑えている。ベアリング１’は、図７に示すように、サークリップ５１によって中間軸５０に対して軸方向一方に位置決めされている。 In such a drive shaft, if the shaft portion between the constant velocity joint and the differential device is lengthened, the shaft portion may be shaken due to vehicle vibration. The shaft portion and the differential device are spline-coupled. However, since the fitting length of the spline is shorter than the length of the shaft portion, the shaft portion and the differential device do not have a fixing force enough to suppress the shake of the shaft portion. In view of this point, for example, in Patent Document 2, a constant velocity universal joint side end portion of the intermediate shaft is rotatably fixed to the engine via a bracket and a bearing, thereby suppressing the shake of the intermediate shaft. As shown in FIG. 7, the bearing 1 ′ is positioned in one axial direction with respect to the intermediate shaft 50 by the circlip 51.
また、このような自動車のドライブシャフトでは、走行時に路上の粉塵などが軸受１’の内部に混入するおそれが高い。軸受１’内への異物の混入を防ぐために、上記の特許文献２のドライブシャフトでは、ダストカバー５２が装着されている（図７を参照）。なお、図７では、他の図面と整合させるため、特許文献２とは異なる符合を付している。
上記のように、従来のドライブシャフトでは、軸受をシャフトに固定する目的と、軸受内への異物の混入を防ぐ目的とを達成するために、それぞれサークリップおよびダストカバーといった別部材およびこれらを組付ける工程が必要であった。 As described above, in the conventional drive shaft, in order to achieve the purpose of fixing the bearing to the shaft and the purpose of preventing the foreign matter from entering the bearing, separate members such as a circlip and a dust cover are assembled. The attaching process was necessary.
本発明の課題は、低コストに、かつ効率よく製造できる動力伝達シャフトを提供することである。 An object of the present invention is to provide a power transmission shaft that can be efficiently manufactured at low cost.
前記課題を解決するため、本発明の動力伝達シャフトは、等速自在継手の外側継手部材と、外側継手部材との間でトルク伝達を行うシャフト部と、シャフト部に固定された軸受とを有し、シャフト部に固定したダストカバーで、軸受をシャフト部に対して軸方向で位置決めしたことを特徴とする。 In order to solve the above problems, the power transmission shaft of the present invention has an outer joint member of a constant velocity universal joint, a shaft portion that transmits torque between the outer joint member, and a bearing fixed to the shaft portion. The bearing is positioned in the axial direction with respect to the shaft portion with a dust cover fixed to the shaft portion.
このように、本発明では、軸受内部への異物の混入を防ぐダストカバーにより、軸受の位置決めを行う。よって、従来品に使用されていたサークリップ等の固定具が不要となるため、部材数および工程数を減らすことができ、コストの低減および生産性の向上を図ることができる。 Thus, in the present invention, the bearing is positioned by the dust cover that prevents foreign matters from entering the bearing. Therefore, a fixing tool such as a circlip, which has been used in the conventional product, is not necessary, so that the number of members and the number of processes can be reduced, and the cost can be reduced and the productivity can be improved.
このダストカバーに、シャフト部の外周面に嵌合する筒部を設け、この筒部の軸受から離隔する側の端部をシャフト部と係合させると、ダストカバーの抜けを確実に防止することができ、軸受の位置決めをより一層確実に行うことが可能となる。 This dust cover is provided with a cylindrical portion that fits to the outer peripheral surface of the shaft portion, and when the end portion on the side away from the bearing of the cylindrical portion is engaged with the shaft portion, the dust cover is reliably prevented from coming off. Therefore, the bearing can be positioned more reliably.
また、このダストカバーの筒部のうち、前記端部を含む一部領域を、軸受から離隔する方向へ向けて縮径するテーパ形状としておくと、前記端部をシャフト部に容易に係合させることが可能となる。すなわち、ダストカバーの筒部をシャフト部へ嵌合させると、筒部のテーパ部が拡径方向に弾性変形する。この場合、例えばシャフト部に溝等の凹部を予め形成しておけば、シャフト部に嵌合したダストカバーを推し進めるだけで、テーパ部が凹部と対向すると同時に縮径方向に弾性的に復元し、筒部の前記端部が凹部の内壁と係合するので、ワンタッチでダストカバーの取り付けが可能となる。 In addition, if a part of the cylindrical portion of the dust cover including the end portion is tapered so as to reduce the diameter in a direction away from the bearing, the end portion is easily engaged with the shaft portion. It becomes possible. That is, when the cylindrical portion of the dust cover is fitted to the shaft portion, the tapered portion of the cylindrical portion is elastically deformed in the diameter increasing direction. In this case, for example, if a concave portion such as a groove is formed in the shaft portion in advance, only by pushing forward the dust cover fitted to the shaft portion, the taper portion is opposed to the concave portion and at the same time elastically restored in the reduced diameter direction, Since the end of the cylindrical portion engages with the inner wall of the recess, the dust cover can be attached with a single touch.
また、このダストカバーに、筒部の外径側に延びる鍔部を設け、鍔部の軸受と対向する端面に軸受側に突出して設けた当接部を、軸受内輪と軸方向で当接させれば、鍔部と軸受外輪との間に適度の軸方向隙間を確保することができ、鍔部と軸受外輪との干渉を確実に防止できる。また、筒部の端部をシャフト部と係合させた状態で当接部が軸受内輪と当接するため、当接部、さらには筒部にテーパ部を設けた場合はテーパ部が僅かに弾性変形する。これにより、ダストカバーが軸方向かつ伸張方向の弾性力を生じるので、ダストカバーをガタなくシャフト部に固定することができ、軸受の位置決め効果を高めることができる。 Also, the dust cover is provided with a flange extending toward the outer diameter side of the cylindrical portion, and an abutting portion that protrudes toward the bearing side on the end surface facing the bearing of the flange is brought into contact with the bearing inner ring in the axial direction. As a result, an appropriate axial clearance can be secured between the flange and the bearing outer ring, and interference between the flange and the bearing outer ring can be reliably prevented. In addition, since the abutting part abuts on the bearing inner ring with the end of the cylindrical part engaged with the shaft part, the tapered part is slightly elastic when a tapered part is provided on the abutting part or the cylindrical part. Deform. Thereby, since the dust cover generates an elastic force in the axial direction and in the extending direction, the dust cover can be fixed to the shaft portion without play and the positioning effect of the bearing can be enhanced.
以上のように、本発明によれば、低コストに、かつ効率よく製造できる動力伝達シャフトが得られる。 As described above, according to the present invention, a power transmission shaft that can be efficiently manufactured at low cost can be obtained.
以下、本発明を自動車のフロント用ドライブシャフトに適用した場合を例にとって、実施形態を説明する。なお、上述のように、自動車のフロント用ドライブシャフトは、トルクステア現象を回避するため、左右いずれか一方の摺動式等速ジョイントの外側継手部材に取り付けられたシャフト部を延長し、左右の等速ジョイントを車体中心線に対して均等に配設する必要がある。本実施形態では、延長されたシャフト部が取り付けられた摺動式等速ジョイントＪ１を備えたドライブシャフトを示している。 Hereinafter, embodiments will be described by taking the case where the present invention is applied to a front drive shaft of an automobile as an example. As described above, in order to avoid the torque steer phenomenon, the front drive shaft of the automobile extends the shaft portion attached to the outer joint member of either the left or right sliding constant velocity joint, It is necessary to arrange the constant velocity joints evenly with respect to the vehicle center line. In the present embodiment, showing a drive shaft shaft portion extended is provided with a sliding type constant velocity joint J 1 attached.
図１は、デファレンシャル側（以下、デフ側）の摺動式等速自在継手Ｊ1と、ホイール側の固定式等速自在継手Ｊ2（本実施形態ではツェッパ型を例示）と、各等速自在継手の内側継手部材同士を接続する中間シャフトＳとからなる自動車のドライブシャフトを例示している。図示する実施の形態では中間シャフトＳを中空とすることにより軽量化を図ってある。中空シャフトは中間部分のパイプの両端に連結要素を溶接や圧接にて接合したものでもよいが、より軽量化を図るために、中間部分と連結要素を一体的に加工することが好ましい。その加工方法としては、鋼材から形成されたパイプの端部を加工して連結要素と成してもよいし、電縫管やシームレス管などの鋼製素管を塑性加工によって全体を加工して成してもよい。なお、左右のドライブシャフトで、各中間シャフトＳの長さは等しくする。 FIG. 1 shows a differential constant velocity universal joint J 1 on the differential side (hereinafter, differential side), a fixed constant velocity universal joint J 2 on the wheel side (in this embodiment, a Zepper type is illustrated), and each constant velocity. The drive shaft of the motor vehicle which consists of the intermediate shaft S which connects the inner joint members of a universal joint is illustrated. In the illustrated embodiment, the intermediate shaft S is made hollow to reduce the weight. The hollow shaft may be formed by joining connection elements to both ends of the pipe of the intermediate part by welding or pressure welding, but it is preferable to integrally process the intermediate part and the connection element in order to further reduce the weight. As the processing method, the end portion of the pipe formed from steel material may be processed to form a connecting element, or the whole steel raw pipe such as an electric-welded pipe or seamless pipe is processed by plastic working. You may make it. In addition, the length of each intermediate shaft S is made equal in the left and right drive shafts.
デフ側の摺動式等速自在継手Ｊ1は、図２および図３に示すように、外側継手部材２と、内側継手部材としてのトリポード部材４と、トルク伝達要素としてのローラ・アセンブリ３と、ブーツ５とを主要な構成要素としている。外側継手部材２には、これとトルク伝達を行うシャフト部が設けられる。本実施形態では、シャフト部が外側継手部材２に一体形成されたステム部２６で構成される場合を例示しているが、シャフト部を外側継手部材２と別体に形成することもできる。 As shown in FIGS. 2 and 3, the differential sliding constant velocity universal joint J 1 includes an outer joint member 2, a tripod member 4 as an inner joint member, and a roller assembly 3 as a torque transmission element. The boot 5 is a main component. The outer joint member 2 is provided with a shaft portion that performs torque transmission therewith. In this embodiment, the case where the shaft portion is configured by the stem portion 26 integrally formed with the outer joint member 2 is illustrated, but the shaft portion can be formed separately from the outer joint member 2.
図示した実施の形態では、外側継手部材２は一体に形成されたマウス部２２とステム部２６とからなる。ステム部２６は端部に形成したスプライン軸２８（またはセレーション軸、以下同じ）にてデファレンシャル（図示せず）とトルク伝達可能に結合する。マウス部２２は一端にて開口したカップ状で、内周の円周方向三等分位置に軸方向に延びるトラック溝２４が形成してある。マウス部２２の外周面は、横断面（図３（Ａ））で見ると、大径部２２ａと小径部２２ｂが交互に現れる非円筒形状である。この実施の形態の場合、大径部２２ａはトラック溝２４に対応する凸円弧形状の部分で、小径部は隣り合うトラック溝２４間の部分に対応する凹円弧形状の部分である。 In the illustrated embodiment, the outer joint member 2 includes a mouth portion 22 and a stem portion 26 that are integrally formed. The stem portion 26 is coupled to a differential (not shown) by a spline shaft 28 (or a serration shaft, which is the same hereinafter) formed at an end portion so that torque can be transmitted. The mouse portion 22 has a cup shape opened at one end, and a track groove 24 extending in the axial direction is formed at a position of the inner circumference in three equal parts. The outer peripheral surface of the mouse part 22 has a non-cylindrical shape in which the large diameter part 22a and the small diameter part 22b appear alternately when viewed in a cross section (FIG. 3A). In this embodiment, the large-diameter portion 22 a is a convex arc-shaped portion corresponding to the track groove 24, and the small-diameter portion is a concave arc-shaped portion corresponding to a portion between the adjacent track grooves 24.
トリポード部材４はボス４２と脚軸４６とからなる。ボス４２には中間シャフトＳとトルク伝達可能に結合するスプラインまたはセレーション穴４４が形成してある。脚軸４６はボス４２の円周方向三等分位置から半径方向に突出している。本実施形態では、図３（Ｂ）に示すように、各脚軸４６の横断面は、長軸が継手の軸線方向に対して直行する略楕円形状である場合を例示しているが、脚軸４６の横断面形状はこれに限定されず、例えば真円形状とすることもできる。 The tripod member 4 includes a boss 42 and a leg shaft 46. The boss 42 is formed with a spline or serration hole 44 that is coupled to the intermediate shaft S so as to be able to transmit torque. The leg shaft 46 projects in the radial direction from the circumferentially divided position of the boss 42. In the present embodiment, as shown in FIG. 3B, the cross section of each leg shaft 46 exemplifies a case where the major axis has a substantially elliptical shape perpendicular to the axial direction of the joint. The cross-sectional shape of the shaft 46 is not limited to this, and may be a perfect circle, for example.
各脚軸４６の外周にローラ・アセンブリ３が配置してある。ローラ・アセンブリ３は、複数の転動体３４を介して相対回転自在のアウタ・ローラ３２とインナ・ローラ３６とで構成されている。転動体３４はここでは針状ころで、アウタ・ローラの円筒形内周面およびインナ・ローラ３６の円筒形外周面が、針状ころが転動する軌道面となっている。図３（Ｂ）に示すように、針状ころ３４は、できるだけ多くのころを入れた、保持器のない、いわゆる総ころ状態で組み込まれている。アウタ・ローラ３２の内周面に形成した輪溝に装着したワッシャ３８でインナ・ローラ３６および転動体３４の抜け止めをしてある。 The roller assembly 3 is disposed on the outer periphery of each leg shaft 46. The roller assembly 3 includes an outer roller 32 and an inner roller 36 that are rotatable relative to each other via a plurality of rolling elements 34. Here, the rolling elements 34 are needle rollers, and the cylindrical inner peripheral surface of the outer roller and the cylindrical outer peripheral surface of the inner roller 36 are raceways on which the needle rollers roll. As shown in FIG. 3 (B), the needle rollers 34 are incorporated in a so-called full roller state in which as many rollers as possible are inserted and there is no cage. The inner roller 36 and the rolling element 34 are prevented from coming off by a washer 38 attached to a ring groove formed on the inner peripheral surface of the outer roller 32.
インナ・ローラ３６の内周面の母線形状は軸方向の中央部が凸となった曲線である。このため、インナ・ローラ３６ひいてはローラ・アセンブリ３は、脚軸４６に対し、回転、首振り、軸方向移動が可能である。 The generatrix shape of the inner peripheral surface of the inner roller 36 is a curve having a convex central portion in the axial direction. Therefore, the inner roller 36 and thus the roller assembly 3 can rotate, swing, and move in the axial direction with respect to the leg shaft 46.
アウタ・ローラ３２の外周面は球面の一部すなわち部分球面状であり、外側継手部材２のトラック溝２４のローラ案内面とアンギュラコンタクトする。アウタ・ローラ３２とローラ案内面とがアンギュラコンタクトをなすことによって、ローラ・アセンブリ３の姿勢が一層安定し、アウタ・ローラ３２がローラ案内面上をより少ない抵抗で転動することができる。なお、別の実施の形態として、アウタ・ローラ３２とローラ案内面とがサーキュラコンタクトをなすようにしてもよい。 The outer peripheral surface of the outer roller 32 is a part of a spherical surface, that is, a partial spherical surface, and is in angular contact with the roller guide surface of the track groove 24 of the outer joint member 2. Since the outer roller 32 and the roller guide surface form an angular contact, the posture of the roller assembly 3 is further stabilized, and the outer roller 32 can roll on the roller guide surface with less resistance. As another embodiment, the outer roller 32 and the roller guide surface may form a circular contact.
このようなドライブシャフトは、上述のように、ステム部２６が延長されているため、回転に伴い振れが生じるおそれがある。ステム部２６はスプライン軸２８によってデファレンシャルと嵌合されているが、嵌合長が短いため、ドライブシャフトの振れを抑えるほどの結合力は有さない。本実施形態では、ドライブシャフトの振れを抑えるため、ステム部２６に軸受１を装着し、その軸受１をブラケットに固定し、さらにブラケットを車両に取り付けることによりステム部２６を回転自在に支持している（図示省略）。マウス部２２は他の部分に比べ重く、振れによる荷重が大きいため、軸受１はステム部２６のできるだけマウス部２２の近傍を支持することが望ましい。 As described above, such a drive shaft has a possibility that the stem 26 is shaken with rotation because the stem portion 26 is extended. The stem portion 26 is fitted to the differential by the spline shaft 28. However, since the fitting length is short, the stem portion 26 does not have a coupling force enough to suppress the drive shaft shake. In the present embodiment, in order to suppress drive shaft deflection, the bearing 1 is mounted on the stem portion 26, the bearing 1 is fixed to the bracket, and the bracket portion is attached to the vehicle so that the stem portion 26 is rotatably supported. (Not shown). Since the mouse part 22 is heavier than other parts and has a large load due to vibration, it is desirable that the bearing 1 supports the stem part 26 as close to the mouse part 22 as possible.
図２に示すように、軸受１は、ステム部２６の円筒面２６ａに固定される軸受内輪１ａと、軸受内輪１ａに対して回転する軸受外輪１ｂと、これらの間に保持される複数個のボール１ｃとで構成される。軸受内輪１ａと軸受外輪１ｂとの間の隙間の両端開口部は、シール部材１ｄによりシールされている。軸受内輪１ａの内周面１ａ１は、ステム部２６の円筒面２６ａに圧入されている。また、軸受１は、軸受内輪１ａがステム部２６のマウス部２２近傍に設けられた肩部２６ｂの肩面２６ｂ１とダストカバー１０とによって軸方向両側から挾持されることにより、ステム部２６の円筒面２６ａ上に軸方向に位置決め固定される。 As shown in FIG. 2, the bearing 1 includes a bearing inner ring 1a fixed to the cylindrical surface 26a of the stem portion 26, a bearing outer ring 1b rotating with respect to the bearing inner ring 1a, and a plurality of pieces held between them. It is comprised with the ball | bowl 1c. Both end openings of the gap between the bearing inner ring 1a and the bearing outer ring 1b are sealed by a sealing member 1d. The inner peripheral surface 1 a 1 of the bearing inner ring 1 a is press-fitted into the cylindrical surface 26 a of the stem portion 26. In addition, the bearing 1 has a cylindrical inner stem 1a because the bearing inner ring 1a is clamped from both sides in the axial direction by the shoulder surface 26b1 of the shoulder portion 26b provided in the vicinity of the mouth portion 22 of the stem portion 26 and the dust cover 10. It is positioned and fixed in the axial direction on the surface 26a.
ダストカバー１０は、断面Ｌ字形の金属板等からなるプレス成形品で、図４（Ａ）のように、ステム部２６の円筒面２６ａと嵌合する筒部１１と、筒部１１のホイール側端部から外径方向に延在する鍔部１２とからなる。筒部１１が円筒面２６ａに圧入固定されることで、軸受１をある程度の軸力で軸方向に固定することができるが、もし軸力が不足し、軸受１がステム部２６上で軸方向にずれると、動力伝達能力に支障をきたしたり、他部品と干渉したりするなどの不具合が生じる。かかる不具合を回避するために、本発明では、筒部１１のデフ側端部に係止部１１ａを有し、この係止部１１ａがステム部２６の円筒面２６ａに設けられた環状溝３０と係合することにより、軸受１を軸方向に確実に固定する。 The dust cover 10 is a press-formed product made of a metal plate or the like having an L-shaped cross section. As shown in FIG. 4A, the dust cover 10 is fitted to the cylindrical surface 26a of the stem portion 26 and the wheel side of the cylindrical portion 11 It consists of a flange 12 extending in the outer diameter direction from the end. Since the cylindrical portion 11 is press-fitted and fixed to the cylindrical surface 26a, the bearing 1 can be fixed in the axial direction with a certain axial force. However, if the axial force is insufficient, the bearing 1 is axially fixed on the stem portion 26. If it is shifted to, problems such as hindering the power transmission ability and interference with other parts occur. In order to avoid such inconvenience, in the present invention, a locking portion 11a is provided at the differential side end of the cylindrical portion 11, and this locking portion 11a is provided with an annular groove 30 provided on the cylindrical surface 26a of the stem portion 26. By engaging, the bearing 1 is securely fixed in the axial direction.
係止部１１ａは、デフ側へ向けて縮径するテーパ形状を呈する。係止部１１ａの軸方向寸法Ｌ１は、２〜５ｍｍの範囲内に設定することが望ましい。２ｍｍ以下だとステム部２６の円筒面２６ａに設けられた環状溝３０との十分な係合力が得られず、係止部１１ａが環状溝３０から外れるおそれがあり、５ｍｍ以上だと部材が大きくなりすぎ、ステム部２６の形状等を制限するおそれがあるからである。また、係止部１１ａの軸方向に対する傾斜角θは、１０°〜３０°の範囲内に設定することが望ましい。１０°以下だとステム部２６との十分な係合力が得られず、３０°以上だと、ダストカバー１０をステム部２６に挿入する際に、係止部１１ａとステム部２６とが過度に干渉し、部材の損傷等を招くおそれがあるからである。 The locking portion 11a has a tapered shape that is reduced in diameter toward the differential side. The axial dimension L 1 of the engaging portion 11a is preferably set in the range of 2 to 5 mm. If it is 2 mm or less, sufficient engagement force with the annular groove 30 provided on the cylindrical surface 26 a of the stem portion 26 cannot be obtained, and the locking portion 11 a may be detached from the annular groove 30. This is because there is a possibility that the shape of the stem portion 26 may be limited. Moreover, it is desirable to set the inclination angle θ of the locking portion 11a with respect to the axial direction within a range of 10 ° to 30 °. If it is 10 ° or less, sufficient engagement force with the stem portion 26 cannot be obtained. If it is 30 ° or more, when the dust cover 10 is inserted into the stem portion 26, the locking portion 11a and the stem portion 26 are excessively formed. This is because they may interfere and cause damage to the member.
ダストカバー１０の鍔部１２は、筒部１１のホイール側の端部に外径側に突出して設けられた当接部１２ａと、軸受１の内輪１ａと外輪１ｂとの間の隙間を覆い、軸受１の内部への異物の侵入を防ぐカバー部１２ｂとを一体に有する。カバー部１２ｂは、本実施形態では軸方向に垂直な平面である。当接部１２ａが軸受１の内輪１ａのデフ側端面１ａ３と軸方向で当接することにより、カバー部１２ｂは、外輪１ｂのデフ側端面１ｂ１と軸方向に離隔して配置される。カバー部１２ｂと外輪１ｂのデフ側端面１ｂ１との軸方向間隔Ｌ２（図４（Ａ）では、当接部１２ａとカバー部１２ｂとの軸方向間隔で示す）は、０．５〜２．０ｍｍに設定するのが良い。０．５ｍｍ以下だと、外輪１ｂの回転時にカバー部１２ｂと外輪１ｂとが干渉し、回転を妨げる恐れがあり、２．０ｍｍ以上だと、異物の侵入を防止する効果が十分に得られないためである。 The flange portion 12 of the dust cover 10 covers a gap between the abutting portion 12a provided at the end on the wheel side of the cylindrical portion 11 so as to protrude toward the outer diameter side, and the inner ring 1a and the outer ring 1b of the bearing 1. A cover portion 12b that prevents foreign matter from entering the inside of the bearing 1 is integrally provided. The cover portion 12b is a plane perpendicular to the axial direction in the present embodiment. When the abutting portion 12a abuts on the differential side end surface 1a3 of the inner ring 1a of the bearing 1 in the axial direction, the cover portion 12b is spaced apart from the differential side end surface 1b1 of the outer ring 1b in the axial direction. (In FIG. 4 (A), the illustrated axial distance between the contact portion 12a and the cover portion 12b) axial spacing L 2 between the differential side end surface 1b1 of the cover portion 12b and the outer ring 1b is 0.5-2. It is good to set to 0 mm. If it is 0.5 mm or less, the cover portion 12b and the outer ring 1b may interfere with each other during rotation of the outer ring 1b, and the rotation may be hindered. If it is 2.0 mm or more, the effect of preventing intrusion of foreign matter cannot be sufficiently obtained. Because.
環状溝３０は、図４（Ｂ）に示すように、テーパ面３０ａと、溝底３０ｃと、溝底３０ｃのデフ側端部に形成された軸方向に垂直な内壁３０ｂとで構成される。図５に示すように、環状溝３０の軸方向寸法Ｌ４は、係止部１１ａの軸方向寸法Ｌ１より大きく設定される。これにより、環状溝３０に係止部１１ａが係合した状態において、係止部１１ａが、円筒面２６ａと環状溝３０との境界に形成される角部と干渉することにより、ダストカバー１０がステム部２６の円筒面２６ａから浮き上がることを防止できる。また、環状溝３０の溝深さＬ５は、挿入前の自然状態の係止部１１ａ（図５の一点鎖線で示す）の径方向寸法Ｌ３よりも小さく設定される。これにより、環状溝３０に係止部１１ａが係合した状態において、係止部１１ａは弾性力により溝底３０ｃに押し付けられ、係止部１１ａと環状溝３０との係合が外れることを防止できる。また、溝深さＬ５は、係止部１１ａと確実に係合するために一定以上の深さを有し、例えば０．３ｍｍ以上に設定される。環状溝３０の形状を以上のように設定すると、係止部１１ａと環状溝３０との係合を強固にすることができ、軸受１はダストカバー１０によって確実に固定される。 As shown in FIG. 4B, the annular groove 30 includes a tapered surface 30a, a groove bottom 30c, and an inner wall 30b perpendicular to the axial direction formed at the differential side end of the groove bottom 30c. As shown in FIG. 5, the axial dimension L 4 of the annular groove 30 is set larger than the axial dimension L 1 of the engaging portion 11a. Thereby, in a state where the engaging portion 11a is engaged with the annular groove 30, the engaging portion 11a interferes with a corner portion formed at the boundary between the cylindrical surface 26a and the annular groove 30, whereby the dust cover 10 is It is possible to prevent the stem portion 26 from floating from the cylindrical surface 26a. Further, groove depth L 5 of the annular groove 30 is set smaller than the radial dimension L 3 of the locking portion 11a of the natural state before insertion (indicated by a chain line in FIG. 5). As a result, in a state in which the locking portion 11a is engaged with the annular groove 30, the locking portion 11a is pressed against the groove bottom 30c by elastic force, and the engagement between the locking portion 11a and the annular groove 30 is prevented from being released. it can. Further, the groove depth and L 5 have a certain level of depth to ensure engagement with the locking portion 11a, it is set to, for example more than 0.3 mm. When the shape of the annular groove 30 is set as described above, the engagement between the locking portion 11a and the annular groove 30 can be strengthened, and the bearing 1 is securely fixed by the dust cover 10.
また、ステム部２６に環状溝３０が形成されることにより、後述するダストカバー１０をステム部２６へ圧入する際、ダストカバー１０のホイール側端部と環状溝３０とが係合し、それ以上の圧入ができなくなるおそれがある。上記のように、環状溝３０の軸受１側にテーパ面３０ａを設けることにより、圧入時におけるダストカバー１０と環状溝３０との係合を回避できるため、挿入をスムーズに行うことができる。テーパ面３０ａの軸方向に対する傾斜角を２０°〜３０°に設定すると、ダストカバー１０と環状溝３０との係合を確実に回避できるため好ましい。さらに、ダストカバー１０の筒部１１の軸方向寸法は環状溝３０の軸方向寸法よりも大きく設定される。筒部１１全体が環状溝３０に嵌まり込んでしまうと、所定位置までダストカバー１０を挿入することができないためである。 Further, since the annular groove 30 is formed in the stem portion 26, when the dust cover 10 described later is press-fitted into the stem portion 26, the wheel side end portion of the dust cover 10 and the annular groove 30 are engaged, and more May not be able to be pressed. As described above, by providing the tapered surface 30a on the bearing 1 side of the annular groove 30, the engagement between the dust cover 10 and the annular groove 30 during press-fitting can be avoided, so that the insertion can be performed smoothly. It is preferable to set the inclination angle of the tapered surface 30a with respect to the axial direction to 20 ° to 30 ° because the engagement between the dust cover 10 and the annular groove 30 can be surely avoided. Further, the axial dimension of the cylindrical portion 11 of the dust cover 10 is set larger than the axial dimension of the annular groove 30. This is because the dust cover 10 cannot be inserted to a predetermined position if the entire cylindrical portion 11 is fitted into the annular groove 30.
軸受１のホイール側には、ホイール側からの異物の侵入を防ぐダストカバー２０が配置される。ダストカバー２０は筒部２０ａと鍔部２０ｂとを有する断面Ｌ字型に形成される。筒部２０ａはステム部２６の肩部２６ｂの外周面に圧入される。鍔部２０ｂは、軸受１の外輪１ｂとの干渉を防ぐために、軸受１と軸方向に離隔して配置される。鍔部２０ｂと軸受１との軸方向間隔は、上記と同じ理由により、０．５〜２．０ｍｍの範囲内に設定することが望ましい。 A dust cover 20 is disposed on the wheel side of the bearing 1 to prevent entry of foreign matter from the wheel side. The dust cover 20 is formed in an L-shaped cross section having a cylindrical portion 20a and a flange portion 20b. The cylindrical portion 20a is press-fitted into the outer peripheral surface of the shoulder portion 26b of the stem portion 26. In order to prevent interference with the outer ring 1b of the bearing 1, the flange portion 20b is spaced apart from the bearing 1 in the axial direction. The axial interval between the flange 20b and the bearing 1 is desirably set within a range of 0.5 to 2.0 mm for the same reason as described above.
次に、軸受１のステム部２６への固定方法を説明する。 Next, a method for fixing the bearing 1 to the stem portion 26 will be described.
まず、ダストカバー２０をステム部２６のデフ側端部から圧入し、ステム部２６の肩部２６ｂの外周面に固定する。このとき、鍔部２０ｂの軸方向位置はステム部の肩面２６ｂ１よりもホイール側に位置する。 First, the dust cover 20 is press-fitted from the differential side end portion of the stem portion 26 and fixed to the outer peripheral surface of the shoulder portion 26 b of the stem portion 26. At this time, the axial direction position of the collar part 20b is located on the wheel side with respect to the shoulder surface 26b1 of the stem part.
次に、軸受１をステム部２６のデフ側端部から圧入し、内輪１ａのホイール側端面１ａ２をステム部２６の肩面２６ｂ１に当接させる。 Next, the bearing 1 is press-fitted from the differential side end portion of the stem portion 26, and the wheel side end surface 1 a 2 of the inner ring 1 a is brought into contact with the shoulder surface 26 b 1 of the stem portion 26.
次に、ダストカバー１０をステム部２６のデフ側端部から圧入する。圧入中は、ステム部２６の外周面２６ａに案内された係止部１１ａが拡径方向に弾性変形する。その後、係止部１１ａが環状溝３０と対向すると同時に、弾性的に復元して環状溝３０に嵌まり込む。このとき、当接部１２ａが内輪１ａのデフ側端面１ａ３と当接すると同時に、係止部１１ａの端部が、円筒面２６ａに形成された環状溝３０の内壁３０ｂと当接する。このとき、当接部１２ａ、さらには筒部１１に設けられた係止部１１ａが僅かに弾性変形することで、ダストカバー１０が軸方向かつ伸張方向の弾性力を生じるので、ダストカバー１０をガタなくステム部２６に固定することができ、軸受１の位置決め効果を高めることができる。 Next, the dust cover 10 is press-fitted from the differential side end portion of the stem portion 26. During the press-fitting, the locking portion 11a guided by the outer peripheral surface 26a of the stem portion 26 is elastically deformed in the diameter expansion direction. Thereafter, the locking portion 11 a faces the annular groove 30 and at the same time is elastically restored and fitted into the annular groove 30. At this time, the abutting portion 12a abuts on the differential side end surface 1a3 of the inner ring 1a, and at the same time, the end of the locking portion 11a abuts on the inner wall 30b of the annular groove 30 formed in the cylindrical surface 26a. At this time, the dust cover 10 generates an elastic force in the axial direction and in the extension direction by slightly elastically deforming the abutting portion 12a and further the locking portion 11a provided on the cylinder portion 11, so that the dust cover 10 is It can fix to the stem part 26 without backlash, and can improve the positioning effect of the bearing 1.
以上のように、本発明のダストカバー１０によると、従来は複数の部材で行われていた、軸受１のステム部２６の円筒面２６ａへの固定と、軸受１内部への異物の侵入の防止とを同時に達成することができる。よって、従来のようにサークリップなどの固定具が不要となるため、部材数が減ることによるコストの低減と、工程数が減ることによる生産性の向上を図ることができる。 As described above, according to the dust cover 10 of the present invention, the fixing of the stem portion 26 of the bearing 1 to the cylindrical surface 26a and the prevention of foreign matter intrusion into the inside of the bearing 1 are conventionally performed by a plurality of members. Can be achieved at the same time. Therefore, since a fixing tool such as a circlip is not required as in the prior art, the cost can be reduced by reducing the number of members, and the productivity can be improved by reducing the number of processes.
本発明の実施形態は上記に限られない。上記ではダストカバー１０が、ステム部２６に設けられた環状溝３０と係合する場合を示しているが、例えば、ステム部２６に丘部を設け、この丘部とダストカバー１０を係合することにより、軸受１の軸方向の位置決めを行うこともできる。 The embodiment of the present invention is not limited to the above. Although the dust cover 10 has shown the case where it engages with the annular groove 30 provided in the stem part 26 above, for example, a hill part is provided in the stem part 26 and this hill part and the dust cover 10 are engaged. Thus, the bearing 1 can be positioned in the axial direction.
あるいは、上記の実施形態では、カバー部１２ｂは軸方向に垂直な平面であるが、例えば図６に示すように、外径へ向けてデフ側へ傾斜したテーパ状に形成してもよい。このとき、鍔部１２のうち外輪１ｂと対向する部分と、外輪１ｂのデフ側端面１ｂ１との隙間の最小値が、軸方向間隔がＬ２となる。 Alternatively, in the above embodiment, the cover portion 12b is a plane perpendicular to the axial direction. However, as shown in FIG. 6, for example, the cover portion 12b may be formed in a tapered shape inclined toward the outer diameter toward the differential side. At this time, the outer ring 1b facing the portion of the flange portion 12, the minimum value of the gap between the differential side end surface 1b1 of the outer ring 1b becomes axial spacing and L 2.
１ 軸受
１ａ 軸受内輪
１ｂ 軸受外輪
２ 外側継手部材
１０ ダストカバー
１１ 筒部
１１ａ 係止部
１２ 鍔部
１２ａ 当接部
１２ｂ カバー部
２６ ステム部
２６ａ 円筒面
３０ 環状溝
Ｊ1 摺動式等速自在継手
Ｊ2 固定式等速自在継手
Ｓ 中間シャフト
DESCRIPTION OF SYMBOLS 1 Bearing 1a Bearing inner ring 1b Bearing outer ring 2 Outer joint member 10 Dust cover 11 Cylindrical part 11a Locking part 12 Collar part 12a Contact part 12b Cover part 26 Stem part 26a Cylindrical surface 30 Annular groove J 1 Sliding constant velocity universal joint J 2 fixed type constant velocity universal joint S intermediate shaft
Claims (4)
シャフト部に固定したダストカバーで、軸受をシャフト部に対して軸方向で位置決めしたことを特徴とする動力伝達シャフト。 In a power transmission shaft having an outer joint member of a constant velocity universal joint, a shaft portion that transmits torque between the outer joint member, and a bearing fixed to the shaft portion,
A power transmission shaft characterized in that a bearing is positioned in an axial direction with respect to a shaft portion with a dust cover fixed to the shaft portion.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006013968A JP2007198399A (en) | 2006-01-23 | 2006-01-23 | Power transmission shaft |
| PCT/JP2006/320535 WO2007083420A1 (en) | 2006-01-23 | 2006-10-16 | Power transmission shaft |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2006013968A JP2007198399A (en) | 2006-01-23 | 2006-01-23 | Power transmission shaft |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JP2007198399A true JP2007198399A (en) | 2007-08-09 |
Family
ID=38287380
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2006013968A Withdrawn JP2007198399A (en) | 2006-01-23 | 2006-01-23 | Power transmission shaft |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2007198399A (en) |
| WO (1) | WO2007083420A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008221905A (en) * | 2007-03-09 | 2008-09-25 | Nsk Ltd | Steering device |
| WO2016009960A1 (en) * | 2014-07-15 | 2016-01-21 | Ntn株式会社 | Support bearing for constant velocity joint, and outer ring for constant velocity joint |
| JP2019052724A (en) * | 2017-09-15 | 2019-04-04 | キヤノン株式会社 | Snap ring for shaft and image formation apparatus |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109915471B (en) * | 2018-06-05 | 2021-01-19 | 万向钱潮股份有限公司 | Shaft and bearing matching structure |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3132443A1 (en) * | 1981-08-17 | 1983-02-24 | Skf Kugellagerfabriken Gmbh, 8720 Schweinfurt | ARRANGEMENT FOR THE AXIAL DEFINITION OF MACHINE ELEMENTS |
| JPS59179106U (en) * | 1983-05-18 | 1984-11-30 | エヌ・テ−・エヌ東洋ベアリング株式会社 | Bearing device for drive wheels |
| JP2005299738A (en) * | 2004-04-08 | 2005-10-27 | Nsk Ltd | Rolling bearing with flange |
| JP2005321078A (en) * | 2004-05-11 | 2005-11-17 | Nsk Ltd | Roller bearing and rolling bearing device |
-
2006
- 2006-01-23 JP JP2006013968A patent/JP2007198399A/en not_active Withdrawn
- 2006-10-16 WO PCT/JP2006/320535 patent/WO2007083420A1/en active Application Filing
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2008221905A (en) * | 2007-03-09 | 2008-09-25 | Nsk Ltd | Steering device |
| WO2016009960A1 (en) * | 2014-07-15 | 2016-01-21 | Ntn株式会社 | Support bearing for constant velocity joint, and outer ring for constant velocity joint |
| JP2016020717A (en) * | 2014-07-15 | 2016-02-04 | Ntn株式会社 | Support bearing of constant velocity joint and outer ring of constant velocity joint |
| JP2019052724A (en) * | 2017-09-15 | 2019-04-04 | キヤノン株式会社 | Snap ring for shaft and image formation apparatus |
| JP7058959B2 (en) | 2017-09-15 | 2022-04-25 | キヤノン株式会社 | Retaining ring for shaft, image forming device, sheet transfer device |
| US11578759B2 (en) | 2017-09-15 | 2023-02-14 | Canon Kabushiki Kaisha | Shaft retaining ring and image forming apparatus |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2007083420A1 (en) | 2007-07-26 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A300 | Application deemed to be withdrawn because no request for examination was validly filed |
Free format text: JAPANESE INTERMEDIATE CODE: A300 Effective date: 20090407 |