JPH08159154A - Center bearing support - Google Patents
Center bearing supportInfo
- Publication number
- JPH08159154A JPH08159154A JP6323992A JP32399294A JPH08159154A JP H08159154 A JPH08159154 A JP H08159154A JP 6323992 A JP6323992 A JP 6323992A JP 32399294 A JP32399294 A JP 32399294A JP H08159154 A JPH08159154 A JP H08159154A
- Authority
- JP
- Japan
- Prior art keywords
- bearing support
- center bearing
- bellows portion
- dynamic damper
- bellows part
- 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.)
- Pending
Links
- 230000002093 peripheral effect Effects 0.000 claims abstract description 5
- 239000013013 elastic material Substances 0.000 claims description 4
- 239000000463 material Substances 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000000465 moulding Methods 0.000 description 3
- 239000002184 metal Substances 0.000 description 2
- 238000013016 damping Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000004073 vulcanization Methods 0.000 description 1
Classifications
-
- 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
- F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
- F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
- F16C27/066—Ball or roller bearings
-
- 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
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
- F16F7/104—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted
- F16F7/108—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted on plastics springs
-
- 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
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Motor Power Transmission Devices (AREA)
- Support Of The Bearing (AREA)
- Vibration Prevention Devices (AREA)
- Mounting Of Bearings Or Others (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、自動車の駆動系におい
て、プロペラシャフトを回転自在にかつ弾性的に支持す
るセンターベアリングサポートに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a center bearing support for rotatably and elastically supporting a propeller shaft in an automobile drive system.
【０００２】[0002]
【従来の技術】従来から、図２に示すように、ベアリン
グ２を支持する内環１の外周側に、ベロー部４を備えた
ゴム状弾性材製の弾性体３を介して外環５を接続したセ
ンターベアリングサポートが知られている（例えば、実
開平４−２５０２６号公報参照）。2. Description of the Related Art Conventionally, as shown in FIG. 2, an outer ring 5 is provided on the outer peripheral side of an inner ring 1 supporting a bearing 2 via an elastic body 3 made of a rubber-like elastic material having a bellows section 4. A connected center bearing support is known (see, for example, Japanese Utility Model Laid-Open No. 4-25026).
【０００３】上記従来のセンターベアリングサポートに
おいては、弾性体３がベロー部４を備えていて、その変
形自由度が大きく設定されており、よって優れた耐久性
が発揮されるが、その反面で、ベロー部４が入力振動に
対して共振することがあるために、図３に実線で示すよ
うに、高周波数域における動ばね定数が高くなってしま
う不都合がある。In the above-mentioned conventional center bearing support, the elastic body 3 is provided with the bellows portion 4 and the degree of freedom of deformation thereof is set to be large, so that excellent durability is exhibited, but on the other hand, Since the bellows section 4 may resonate with the input vibration, there is a disadvantage that the dynamic spring constant in the high frequency range becomes high as shown by the solid line in FIG.
【０００４】ベロー部４が入力振動に対して共振するこ
とにより動ばね定数が高くなるメカニズムは、以下のよ
うに説明されるものである。すなわち、図４の振動系モ
デルに示すように、内環１の加振振幅をＸ（ｍｍ）、ベ
ロー部４の凸部４ａ（図２参照）の振幅をＹ（ｍｍ）、
外環５の反力をＰ（ｋｇｆ）、ベロー部４の脚部４ｂ，
４ｃ（図２参照）のばね定数をＫ1 ＝Ｋ2 ＝２Ｋ、動ば
ね定数をＫｄとすると、共振していない場合（Ｙ＝Ｘ／
２）は Ｋｄ＝Ｐ／Ｘ Ｐ＝Ｋ1 ・Ｙ＝Ｋ2 ・Ｙ＝２Ｋ・Ｘ／２＝Ｋ・Ｘ ∴Ｋｄ＝Ｋ であるのに対して、共振している場合（Ｙ≧Ｘ／２、仮
にＹ＝Ｘとおくと）は Ｋｄ＝Ｐ／Ｘ Ｐ＝Ｋ1 ・Ｘ＝２Ｋ・Ｘ ∴Ｋｄ＝２Ｋ であることから、ベロー部４が共振することにより動ば
ね定数が高くなる。The mechanism in which the dynamic spring constant increases due to the resonance of the bellows portion 4 with respect to the input vibration is explained as follows. That is, as shown in the vibration system model of FIG. 4, the vibration amplitude of the inner ring 1 is X (mm), the amplitude of the convex portion 4a (see FIG. 2) of the bellows portion 4 is Y (mm),
The reaction force of the outer ring 5 is P (kgf), the leg portion 4b of the bellows portion 4,
If the spring constant of 4c (see FIG. 2) is K 1 = K 2 = 2K and the dynamic spring constant is Kd, no resonance occurs (Y = X /
2) is Kd = P / X P = K 1 · Y = K 2 · Y = 2K · X / 2 = K · X ∴Kd = K, but when resonating (Y ≧ X / 2. If Y = X), Kd = P / X P = K 1 .X = 2K.X ∴Kd = 2K. Therefore, the bellows section 4 resonates to increase the dynamic spring constant.
【０００５】[0005]
【発明が解決しようとする課題】本発明は以上の点に鑑
み、ベロー部が入力振動に対して共振するのを抑え、も
って高周波数域において動ばね定数が極端に高くなるこ
とがないようにしたセンターベアリングサポートを提供
することを目的とする。SUMMARY OF THE INVENTION In view of the above points, the present invention suppresses the bellows portion from resonating with respect to input vibration, and thus prevents the dynamic spring constant from becoming extremely high in a high frequency range. The purpose is to provide a center bearing support.
【０００６】[0006]
【課題を解決するための手段】上記目的を達成するた
め、本発明のセンターベアリングサポートは、ベアリン
グを支持する内環の外周側に、ベロー部を備えたゴム状
弾性材製の弾性体を介して外環を接続したセンターベア
リングサポートにおいて、前記ベロー部に、このベロー
部の振動を抑えるダイナミックダンパを設けることにし
た。In order to achieve the above object, the center bearing support of the present invention includes an elastic body made of a rubber-like elastic material and having a bellows portion on the outer peripheral side of an inner ring for supporting the bearing. In the center bearing support to which the outer ring is connected, a dynamic damper that suppresses the vibration of the bellows portion is provided in the bellows portion.
【０００７】[0007]
【作用】上記構成を備えた本発明のセンターベアリング
サポートにおいては、ベロー部に設けられたダイナミッ
クダンパがベロー部の振動に対して共振して、ベロー部
が振動するのが抑えられる。したがってベロー部が入力
振動に対して共振するのが抑えられるために、高周波数
域において動ばね定数が極端に高くなるのを防止するこ
とが可能となる。In the center bearing support of the present invention having the above structure, the dynamic damper provided in the bellows portion resonates with the vibration of the bellows portion, and the vibrations of the bellows portion can be suppressed. Therefore, since the bellows portion is suppressed from resonating with respect to the input vibration, it becomes possible to prevent the dynamic spring constant from becoming extremely high in the high frequency range.
【０００８】従来においては、数百Ｈｚ（図３の例で
は、８００Ｈｚ近辺）に共振のピークがあり、これに対
するダイナミックダンパとしては、同程度の周波数に固
有振動数をもち、かつ共振によって振動している部分の
質量の１０〜２０％程度の慣性質量を有していれば、充
分に効果が現れる。よってこの慣性質量を構成するマス
部は、これを弾性体と同一材質で一体成形すれば充分で
ある。またこのダイナミックダンパは、ベロー部の振動
を抑えるためにベロー部に設けられるものであって、こ
れらの点において、図５に示すセンターベアリングサポ
ートとは異なるものである。この図５のセンターベアリ
ングサポートにおいては、ダイナミックダンパ６が、そ
の共振作用によりプロペラシャフトの振動を抑えるべく
弾性体３のベロー部４以外の部分に設けられており（こ
の位置に設けられているために、このダイナミックダン
パ６ではベロー部４の振動を抑えることができない）、
かつ比較的大きな慣性質量を確保するために金属製のマ
スを備えている（実開平４−２５０２６号公報参照）。Conventionally, there is a resonance peak at several hundreds of Hz (near 800 Hz in the example of FIG. 3), and a dynamic damper for this has a natural frequency at a similar frequency and vibrates due to resonance. If the inertial mass is about 10% to 20% of the mass of the portion where it is present, the effect is sufficiently exhibited. Therefore, it is sufficient for the mass portion forming the inertial mass to be integrally formed of the same material as the elastic body. Further, this dynamic damper is provided in the bellows portion in order to suppress the vibration of the bellows portion, and in these respects, it is different from the center bearing support shown in FIG. In the center bearing support of FIG. 5, the dynamic damper 6 is provided at a portion other than the bellows portion 4 of the elastic body 3 in order to suppress the vibration of the propeller shaft due to its resonance action (since it is provided at this position. In addition, this dynamic damper 6 cannot suppress the vibration of the bellows portion 4),
In addition, a metal mass is provided to secure a relatively large inertial mass (see Japanese Utility Model Laid-Open No. 4-25026).
【０００９】[0009]
【実施例】つぎに本発明の実施例を図面にしたがって説
明する。Embodiments of the present invention will now be described with reference to the drawings.
【００１０】図１に示すように、ベアリング２を支持す
る内環１の外周側に、ベロー部４を備えたゴム状弾性材
製の弾性体３を介して外環５が接続されており、ベロー
部４の凸部４ａの先端（山部頂上）に、このベロー部４
の振動を抑えるダイナミックダンパ７が設けられてい
る。このダイナミックダンパ７は、環状のステー部８と
環状のマス部９とを備えて、弾性体３ないしベロー部４
に対して同一材質で一体成形されており、このダイナミ
ックダンパ７の共振作用により、ベロー部４が振動する
のが抑えられ、これによりベロー部４が入力振動に対し
て共振するのが抑えられる。したがって、図３に破線で
示したように、高周波数域において動ばね定数が極端に
高くなるのを防止することができる。尚、符号４ｂ，４
ｃはそれぞれベロー部４の脚部、符号１０は、内環１に
嵌着されたベアリング押え環、符号１１は、外環５に嵌
着されたブラケットである。As shown in FIG. 1, an outer ring 5 is connected to an outer peripheral side of an inner ring 1 supporting a bearing 2 through an elastic body 3 made of a rubber-like elastic material having a bellows portion 4. At the tip (top of the mountain portion) of the convex portion 4a of the bellows portion 4, the bellows portion 4
Is provided with a dynamic damper 7 for suppressing the vibration. The dynamic damper 7 includes an annular stay portion 8 and an annular mass portion 9, and includes the elastic body 3 or the bellows portion 4.
On the other hand, they are integrally formed of the same material. Due to the resonance action of the dynamic damper 7, the bellows portion 4 is suppressed from vibrating, and thus the bellows portion 4 is suppressed from resonating with respect to the input vibration. Therefore, as shown by the broken line in FIG. 3, it is possible to prevent the dynamic spring constant from becoming extremely high in the high frequency range. Incidentally, reference numerals 4b and 4
Reference characters 10 are leg portions of the bellows portion 4, reference numeral 10 is a bearing pressing ring fitted to the inner ring 1, and reference numeral 11 is a bracket fitted to the outer ring 5.
【００１１】上記したように、ダイナミックダンパ７の
ステー部８およびマス部９を弾性体３ないしベロー部４
に対して同一材質で一体成形すれば、他に部品が要ら
ず、かつ弾性体３の加硫成形と同時にダイナミックダン
パ７を成形することができるために、工程上またはコス
ト的に極めて有利である。また確保すべき慣性質量の大
きさからして、これで充分であることも上記したとおり
である。但し、このことは本発明の技術的範囲を限定す
るものではない。すなわち、本発明において、マス部９
は金属等剛材製の重量物をベロー部４にインサート成
形、アウトサート成形または後付けしたものであっても
良い。またダイナミックダンパ７を設ける位置は、これ
がベロー部４に直接繋っていれば何処でも良いが、凸部
４ａの先端に設けた場合が最も制振効果が大きい。As described above, the stay portion 8 and the mass portion 9 of the dynamic damper 7 are connected to the elastic body 3 or the bellows portion 4.
On the other hand, if the same material is integrally molded, no other parts are required and the dynamic damper 7 can be molded simultaneously with the vulcanization molding of the elastic body 3, which is extremely advantageous in terms of process or cost. . Also, as described above, this is sufficient in view of the size of the inertial mass to be secured. However, this does not limit the technical scope of the present invention. That is, in the present invention, the mass portion 9
May be formed by insert-molding, outsert-molding or post-mounting a heavy material such as a metal on the bellows portion 4. The dynamic damper 7 may be provided at any position as long as it is directly connected to the bellows portion 4, but the vibration damping effect is greatest when the dynamic damper 7 is provided at the tip of the convex portion 4a.
【００１２】[0012]
【発明の効果】本発明は、以下の効果を奏する。The present invention has the following effects.
【００１３】すなわち、上記構成を備えた本発明のセン
ターベアリングサポートにおいては、ベロー部に設けら
れたダイナミックダンパがベロー部の振動に対して共振
して、ベロー部が振動するのが抑えられる。したがって
ベロー部が入力振動に対して共振するのが抑えられるた
めに、高周波数域において動ばね定数が極端に高くなる
のを防止することができる。That is, in the center bearing support of the present invention having the above structure, the dynamic damper provided in the bellows portion is suppressed from resonating with the vibration of the bellows portion and vibrating the bellows portion. Therefore, since the bellows portion is suppressed from resonating with respect to the input vibration, it is possible to prevent the dynamic spring constant from becoming extremely high in the high frequency range.
【図１】本発明の実施例に係るセンターベアリングサポ
ートの半裁断面図FIG. 1 is a half cutaway view of a center bearing support according to an embodiment of the present invention.
【図２】従来例に係るセンターベアリングサポートの半
裁断面図FIG. 2 is a half sectional view of a center bearing support according to a conventional example.
【図３】動ばね定数の測定値または計算値を示すグラフ
図FIG. 3 is a graph showing a measured value or a calculated value of a dynamic spring constant.
【図４】同センターベアリングサポートの振動系モデル
を示す説明図FIG. 4 is an explanatory view showing a vibration system model of the center bearing support.
【図５】他の従来例に係るセンターベアリングサポート
の半裁断面図FIG. 5 is a half cutaway view of a center bearing support according to another conventional example.
１ 内環 ２ ベアリング ３ 弾性体 ４ ベロー部 ４ａ 凸部 ４ｂ，４ｃ 脚部 ５ 外環 ７ ダイナミックダンパ ８ ステー部 ９ マス部 １０ ベアリング押え環 １１ ブラケット 1 Inner ring 2 Bearing 3 Elastic body 4 Bellow part 4a Convex part 4b, 4c Leg part 5 Outer ring 7 Dynamic damper 8 Stay part 9 Mass part 10 Bearing retaining ring 11 Bracket
Claims (1)
の外周側に、ベロー部（４）を備えたゴム状弾性材製の
弾性体（３）を介して外環（５）を接続したセンターベ
アリングサポートにおいて、前記ベロー部（４）に、こ
のベロー部（４）の振動を抑えるダイナミックダンパ
（７）を設けたことを特徴とするセンターベアリングサ
ポート。1. An inner ring (1) for supporting a bearing (2)
In a center bearing support in which an outer ring (5) is connected to an outer peripheral side of the outer ring (5) through an elastic body (3) made of a rubber-like elastic material having a bellows portion (4), the bellows portion (4) is provided with A center bearing support characterized by having a dynamic damper (7) for suppressing the vibration of the portion (4).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6323992A JPH08159154A (en) | 1994-12-02 | 1994-12-02 | Center bearing support |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP6323992A JPH08159154A (en) | 1994-12-02 | 1994-12-02 | Center bearing support |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH08159154A true JPH08159154A (en) | 1996-06-18 |
Family
ID=18160921
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP6323992A Pending JPH08159154A (en) | 1994-12-02 | 1994-12-02 | Center bearing support |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH08159154A (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10326037B4 (en) * | 2002-08-28 | 2012-05-16 | Gkn Driveline North America,Inc.(N.D.Ges.D.Staates Delaware) | Center bearing resonance absorber |
| JP2013064438A (en) * | 2011-09-16 | 2013-04-11 | Nok Corp | Center bearing support |
| JP2013226951A (en) * | 2012-04-26 | 2013-11-07 | Nok Corp | Center bearing support |
| CN105443573A (en) * | 2016-01-26 | 2016-03-30 | 河北书浩轴承有限公司 | High-speed seal deep groove ball bearing with aligning function |
| CN109790893A (en) * | 2016-09-26 | 2019-05-21 | 威巴克公司 | It is pivotally supported |
| WO2023120222A1 (en) * | 2021-12-20 | 2023-06-29 | Nok株式会社 | Center bearing support |
| JP2023130063A (en) * | 2022-03-07 | 2023-09-20 | Nok株式会社 | mount |
| WO2024122275A1 (en) * | 2022-12-08 | 2024-06-13 | 住友理工株式会社 | Cylindrical anti-vibration device for motor mount |
-
1994
- 1994-12-02 JP JP6323992A patent/JPH08159154A/en active Pending
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE10326037B4 (en) * | 2002-08-28 | 2012-05-16 | Gkn Driveline North America,Inc.(N.D.Ges.D.Staates Delaware) | Center bearing resonance absorber |
| JP2013064438A (en) * | 2011-09-16 | 2013-04-11 | Nok Corp | Center bearing support |
| CN106321629A (en) * | 2011-09-16 | 2017-01-11 | Nok株式会社 | Center bearing support |
| JP2013226951A (en) * | 2012-04-26 | 2013-11-07 | Nok Corp | Center bearing support |
| CN105443573A (en) * | 2016-01-26 | 2016-03-30 | 河北书浩轴承有限公司 | High-speed seal deep groove ball bearing with aligning function |
| US10876574B2 (en) | 2016-09-26 | 2020-12-29 | Vibracoustic Gmbh | Shaft bearing |
| CN109790893A (en) * | 2016-09-26 | 2019-05-21 | 威巴克公司 | It is pivotally supported |
| CN109790893B (en) * | 2016-09-26 | 2024-06-04 | 威巴克欧洲股份公司 | Shaft support |
| WO2023120222A1 (en) * | 2021-12-20 | 2023-06-29 | Nok株式会社 | Center bearing support |
| JPWO2023120222A1 (en) * | 2021-12-20 | 2023-06-29 | ||
| JP2023130063A (en) * | 2022-03-07 | 2023-09-20 | Nok株式会社 | mount |
| WO2024122275A1 (en) * | 2022-12-08 | 2024-06-13 | 住友理工株式会社 | Cylindrical anti-vibration device for motor mount |
| JP2024082463A (en) * | 2022-12-08 | 2024-06-20 | 住友理工株式会社 | Cylindrical vibration isolation device for motor mount |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US10006514B2 (en) | Damper | |
| JPH0510014U (en) | Bound stopper for vehicle suspension | |
| JPH08159154A (en) | Center bearing support | |
| US6869225B2 (en) | Center bearing support | |
| JPH0791526A (en) | Belt pulley | |
| JP2005106192A (en) | Tubular engine mount | |
| JP3266721B2 (en) | Propeller shaft center bearing | |
| JP2004150596A (en) | Anti-vibration support device | |
| JPH08210407A (en) | Member mount | |
| JPH085372Y2 (en) | Center bearing support | |
| JP4434396B2 (en) | Center bearing support | |
| JPH09303459A (en) | Anti-vibration device | |
| JPH0874918A (en) | Bumper spring | |
| JPH1053035A (en) | Center bearing support | |
| JPH0732225U (en) | Center bearing of propeller shaft | |
| JPH0642118Y2 (en) | Flywheel with damper | |
| JPH05180267A (en) | Damper pulley | |
| JPH0529563Y2 (en) | ||
| JPH0740409Y2 (en) | Center bearing support | |
| JP3045745B2 (en) | Hermetic electric compression | |
| JP2902462B2 (en) | Sliding bush assembly | |
| JPH089449Y2 (en) | Center bearing support | |
| JP3088686B2 (en) | Liquid filled type vibration damping device | |
| JPH0547313Y2 (en) | ||
| JPH03107582A (en) | Supporting device of compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A977 | Report on retrieval |
Free format text: JAPANESE INTERMEDIATE CODE: A971007 Effective date: 20040601 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20040609 |
|
| A02 | Decision of refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A02 Effective date: 20041020 |