JPH03149449A - Electromotive differential type thrust generator - Google Patents
Electromotive differential type thrust generatorInfo
- Publication number
- JPH03149449A JPH03149449A JP28676589A JP28676589A JPH03149449A JP H03149449 A JPH03149449 A JP H03149449A JP 28676589 A JP28676589 A JP 28676589A JP 28676589 A JP28676589 A JP 28676589A JP H03149449 A JPH03149449 A JP H03149449A
- Authority
- JP
- Japan
- Prior art keywords
- bevel gear
- hollow shaft
- shaft
- main body
- gear
- 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.)
- Granted
Links
- 230000005540 biological transmission Effects 0.000 abstract description 2
- 230000036316 preload Effects 0.000 description 3
- 235000015842 Hesperis Nutrition 0.000 description 2
- 235000012633 Iberis amara Nutrition 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 206010000369 Accident Diseases 0.000 description 1
- 239000003638 chemical reducing agent Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 230000020169 heat generation Effects 0.000 description 1
- 230000002265 prevention Effects 0.000 description 1
Abstract
Description
【発明の詳細な説明】
(産業上の利用分野)
この発明は、従来主として気圧又は油圧シリンダによる
推力発生の直進アクチュエータに替ってあらゆる分野に
おいて利用可能な、より強力で作動正確なる直進するア
クチュエータとしての純電動差動式推力発生装置に関す
るものである。Detailed Description of the Invention (Industrial Field of Application) The present invention provides a linear actuator that is more powerful and more accurate in operation and can be used in all fields in place of the conventional linear actuator that generates thrust mainly by pneumatic or hydraulic cylinders. The present invention relates to a pure electric differential thrust generator.
(従来の技術)
従来、直進推力発生装置として最も利用されているのは
気圧又は油圧シリンダで、我国でも年間′数百万本のも
のが生産されている。特に航空機の繰舵装置の大半jよ
油圧方式で多数の油圧シリンダが使用されている。油圧
方式の利点は圧力を上げれば、い(らでも推力が上り、
その上シリンダ本体も小形化が図れるので現在ジェット
戦闘機からジャンボジェット機さらに宇宙ロケットの制
御システムにも利用されている。然しこの方式の欠点は
油圧を高くすればする程油圧ポンプや油圧配管の肉厚は
厚く重くなり、大形化すればする程重量増加となり、か
つパツキン類や弁類の破損率も高く安全性は逆に低下す
る。従って最近では油圧を低くする傾向にあり、そのた
めに大きなピストン径や油圧配管径となって油量も増加
している。(Prior Art) Conventionally, pneumatic or hydraulic cylinders have been most used as linear thrust generating devices, and several million cylinders are produced annually in Japan. In particular, most of the steering systems for aircraft are hydraulic, and a large number of hydraulic cylinders are used. The advantage of the hydraulic system is that by increasing the pressure, the thrust increases
Furthermore, since the cylinder body can be made smaller, it is currently used in control systems for jet fighters, jumbo jets, and even space rockets. However, the disadvantage of this method is that the higher the hydraulic pressure, the thicker and heavier the hydraulic pump and hydraulic piping become, and the larger the size, the heavier the weight, and the higher the risk of damage to seals and valves, making it less safe. On the contrary, it decreases. Therefore, recently there has been a trend to lower the oil pressure, which has led to larger piston diameters and larger hydraulic piping diameters, and an increase in the amount of oil.
勿論一般の産業機械用の油圧シリンダも同様で信頼性の
高い機械はど油圧力を低く設定して安定化を図っている
。Of course, the same applies to hydraulic cylinders for general industrial machinery, and in highly reliable machines, the hydraulic pressure is set low to stabilize it.
(発明が解決しようとする問題点)
最近の航空機事故においても油圧システムによる原因が
問題となり、更に輸送能力が巨大化する程より多くの人
命が失われる傾向である。(Problems to be Solved by the Invention) Recent aircraft accidents have also been caused by hydraulic systems, and as transportation capacity increases, more lives tend to be lost.
我国においても回航ジャンボ機の事故以来通産省始め国
を挙げてこの対策として油圧システムに替わる純電気シ
ステムの開発が進められており、最近では油圧配管をな
くす目的で油圧シリンダに制御モータと油圧ポンプを直
結併設させた電気油圧シリンダも開発されている。然し
油の持っている粘性、圧縮性、発火性及び劣化性等の特
性により無人制御の為の精度維持や信頼性及び安全性等
に今一つの問題点を抱えている。In Japan, since the accident involving a jumbo jet, the Ministry of International Trade and Industry and the rest of the country have been working to develop pure electric systems to replace hydraulic systems as a countermeasure.Recently, a control motor and hydraulic pump have been directly connected to a hydraulic cylinder in order to eliminate hydraulic piping. An attached electro-hydraulic cylinder has also been developed. However, due to the characteristics of oil such as viscosity, compressibility, flammability, and deterioration, there are still problems in maintaining accuracy, reliability, and safety for unmanned control.
(問題点を解決するための手段)
そこでこの発明は、上記のとおり従来の気圧や油圧によ
る推力発生シリンダに替えて電動機の回転力を差動式傘
歯車機構により任意に減速して出力歯車の中空軸内に形
設した送りねじナツトを回転し、この送りねじナツトに
嵌大して本体内部に送りねじ軸を貫通し、この両端また
は一端を基台上に固定し、この減速機構により本体をも
って微調整可能で強大な超精密運動を可能とする純電動
推力発生装置を提供することを目的としている。(Means for Solving the Problems) Therefore, as described above, the present invention aims to arbitrarily reduce the rotational force of an electric motor using a differential bevel gear mechanism in place of the conventional thrust generating cylinder using air pressure or oil pressure, and generate output gears. The feed screw nut formed in the hollow shaft is rotated, the feed screw nut is fitted onto the feed screw nut, the feed screw shaft is passed through the inside of the main body, both ends or one end of which are fixed on the base, and this speed reduction mechanism is used to hold the main body slightly. The purpose is to provide a pure electric thrust generator that is adjustable and enables powerful, ultra-precise movement.
(実施例)
上記の目的を達成するため本発明は、その実施例を図面
を参照して説明すると、円筒体の本体(A)を設け、該
本体(A)の内部に固定子(3)を取付け、回転子(2
)を電動機中空軸(1)に嵌合し、続いて固定傘歯車(
6)を推力軸受(9)を介して嵌合し、さらに中空軸端
を傾斜偏心(14)させ、この外周部に推力軸受(15
)を嵌入して前記固定傘歯車と噛合う入力両面傘歯車(
7)を軸承させる。次にこの入力傘歯車(7)と噛合う
出力傘歯車(8)を設け、この出力軸内部に予圧ボール
ねじ送りナツト(12)を嵌合し、出力傘歯車(8)の
外周には多数の推力軸受(lO)を組合せて本体(A)
に固定し、かつ固定傘歯車(6)の歯数(Nl)、入力
傘歯車(7)の歯数(N2)及び(N3)並びに出力歯
車(8)の歯数(N4)等の歯面同士を予圧するととも
に予圧筒(13)をもって歯間隙間を零に保持させる。(Embodiment) In order to achieve the above object, the present invention provides an embodiment of the present invention with reference to the drawings. Install the rotor (2
) onto the motor hollow shaft (1), and then fit the fixed bevel gear (
6) through the thrust bearing (9), the hollow shaft end is tilted eccentrically (14), and the thrust bearing (15) is fitted on the outer circumference of the shaft.
) into which the input double-sided bevel gear meshes with the fixed bevel gear (
7) is supported on the shaft. Next, an output bevel gear (8) that meshes with this input bevel gear (7) is provided, and a preload ball screw feed nut (12) is fitted inside this output shaft, and a large number of screws are attached to the outer periphery of the output bevel gear (8). The thrust bearing (lO) is combined to form the main body (A).
and the number of teeth (Nl) of the fixed bevel gear (6), the number of teeth (N2) and (N3) of the input bevel gear (7), and the number of teeth (N4) of the output gear (8), etc. They are preloaded together and the gap between the teeth is maintained at zero using a preload cylinder (13).
さらに上記送りねじナツト(12)に嵌入する送りねじ
軸(11)を電動子中空軸内まで貫通し、この両端を基
台(B)上に固定して成るものである。Further, a feed screw shaft (11) fitted into the feed screw nut (12) passes through the hollow shaft of the armature, and its both ends are fixed on the base (B).
なお、停電時の逆推力を防ぐために電磁ブレーキ(4)
を設け、かつ正確な位置決めをするためエンコーダ(5
)を設置可能の構造としている。In addition, an electromagnetic brake (4) is installed to prevent reverse thrust during a power outage.
and an encoder (5) for accurate positioning.
) can be installed.
まり図面において(16)は本体スライド用のリニアガ
イドである。In the drawing, (16) is a linear guide for sliding the main body.
(作用)
上記のように構成された電動差動式推力発生装置は、両
面差動傘歯車の固定傘歯車(6)の歯数(Nu)、入力
傘歯車(7)の入力側歯数(NZ)、同歯車(7)の出
力側歯数(N1)及び出力歯車(8)の歯数(N4)を
任意の歯数に選定することにより、lO倍から数1.0
00倍のトルクが得られることができる。(Function) The electric differential thrust generator configured as described above has the number of teeth (Nu) of the fixed bevel gear (6) of the double-sided differential bevel gear, the number of teeth on the input side of the input bevel gear (7) ( NZ), by selecting the number of teeth on the output side (N1) of the same gear (7) and the number of teeth (N4) of the output gear (8) to arbitrary numbers of teeth, the number of teeth can be reduced from 10 times to several 1.0.
00 times more torque can be obtained.
その減速比は近似的に I Nl XN3
− = 1−□
Nz XN4
で表わされる。例えばN、=27、Nz 、 N3 。The reduction ratio is approximately I Nl XN3
− = 1−□ Nz XN4. For example, N, = 27, Nz, N3.
N、=30とすれば
1 27X30 3
− = 1− = −
R30x30 30
■
=十□
となり出力歯車(8)は1/10の正回転となり、従っ
てそのトルクは電動機トルクの10倍となる。If N, = 30, then 1 27 x 30 3 - = 1 - = - R30 x 30 30 ■ = 10□, and the output gear (8) will rotate 1/10 in the normal direction, and therefore its torque will be 10 times the motor torque.
又別の例としてNI=37.Nz =40.N3 =5
4、N、=50とすれば
1 37X54
− = 1−□
R40X50
1.998 1
= 1−− = +□
2.000 1,000
となり、出力歯車(8)はl/l、000の正目転とな
り、従ってトルクは電動機トルクの1.000倍となる
。Another example is NI=37. Nz =40. N3 = 5
If 4, N, = 50, then 1 37X54 - = 1-□ R40X50 1.998 1 = 1-- = +□ 2.000 1,000, and the output gear (8) is l/l, 000 square. Therefore, the torque is 1.000 times the motor torque.
なお正確な位置決めの場合は、電動機軸(1)にto、
oooパルスのエンコーダ(5)を取付け、一例として
減速比1/R=1/100とすれば、100X1万パル
ス=100万パルス71回出力軸回転となり、従来の電
動機の回転制御をスイッチング制御で行えば大凡士lO
度の誤差(1回転360度)であるが、機構的にこの精
度を100倍に向上することができる。またサーボモー
タを利用すれば高負荷時でも、極限に近い精度の位置決
めが始めて可能になったと言うことができる。For accurate positioning, attach the to,
If an ooo pulse encoder (5) is installed and the reduction ratio is 1/R = 1/100 as an example, then 100 x 10,000 pulses = 1,000,000 pulses will rotate the output shaft 71 times, and conventional motor rotation control can be performed using switching control. For example, Daibanshi lO
This is a degree error (360 degrees per rotation), but mechanically this accuracy can be improved 100 times. It can also be said that the use of servo motors has made it possible for the first time to perform positioning with near-ultimate precision even under high loads.
又本装置の出力側に電動機を、入力側にねじナツトを組
み替えれば、そっくりそのまま増速装置となるのは当然
である。Also, by rearranging the electric motor on the output side of this device and the screw nut on the input side, it is natural that the device can be used as a speed increasing device.
(発明の効果)
本発明は、以上説明したように構成されているので、以
下記述のような効果を奏するものである従来一般に用い
られる歯車減速機構やウォーム歯車、遊星歯車機構を組
合せると、可動部品点数だけでも数10点の部品機素か
ら成っているが、本発明においては僅か電動機軸、入力
両面傘歯車。(Effects of the Invention) Since the present invention is configured as described above, when it is combined with a gear reduction mechanism, a worm gear, and a planetary gear mechanism commonly used in the past, which achieve the effects described below, The number of moving parts alone consists of several tens of parts, but in the present invention, only a motor shaft and an input double-sided bevel gear are included.
出力傘歯車及び送りねじ軸の4個の機素しか可動部品が
ないことになり、部品の精度や誤差から発生する製品の
ばらつきは10分の1以下となった。又差動傘歯車機構
における各歯車の歯面両面を予圧できたので歯面間隙間
が零となり、ガタが皆無となった。従来の遊星減速機構
では少くとも3段歯車であれば6/100以上のガタが
発生していた。又高伝達効率のため従来ウォーム減速機
などで見られた滑り摩耗や発熱は全く無くなった。There are only four moving parts: the output bevel gear and the feed screw shaft, and product variations due to part precision and errors have been reduced to less than one-tenth. In addition, since both sides of the tooth surfaces of each gear in the differential bevel gear mechanism could be preloaded, the gap between the tooth surfaces became zero, and there was no backlash. In a conventional planetary reduction mechanism, at least a three-stage gear would have a play of 6/100 or more. Also, due to the high transmission efficiency, the sliding wear and heat generation that were seen with conventional worm reducers are completely eliminated.
本発明により純電動の高推カシリンダが完成されたので
、これを航空機や宇宙ロケットの制御機構に利用すれば
、従来の油圧系制御機構による油圧ポンプ、油圧シリン
ダ、各制御弁及び長大な油圧配管等の多くの機素を不要
とし、上記のように機素の少ない高精度、高信頼性の制
御が可能となり、且つ軽量にして低コストであり、事故
防止と人命尊重のため太きく貢献する画期的な発明と言
うことができるものである。Since the present invention has completed a pure electric high-thrust cylinder, if this is used in the control mechanism of aircraft and space rockets, it will be possible to use the hydraulic pump, hydraulic cylinder, each control valve, and long hydraulic piping using the conventional hydraulic system control mechanism. It eliminates the need for many elements, such as the above, and enables high-precision, highly reliable control with fewer elements as described above. It is also lightweight and low-cost, making a significant contribution to accident prevention and respect for human life. This can be called a groundbreaking invention.
図面は一部切欠けの正面縦断面図である。
1・・電動機中空軸 2・・回転子3・・固定子
4・・電磁ブレーキ5・・エンコーダ
6・・固定傘歯車7・・入力両面傘歯車
8・・出力傘歯車9・・固定歯車推力軸受
lO・出力歯車推力軸受 11・送りねじ軸12・送
りねじナット 13・予圧筒14・中空軸傾斜偏心
部
15・入力傘歯車推力軸受 16・リニアガイドA・・
本体 B・・基台N1 ・・固定傘歯車
の歯数The drawing is a partially cutaway front longitudinal sectional view. 1. Motor hollow shaft 2. Rotor 3. Stator 4. Electromagnetic brake 5. Encoder
6. Fixed bevel gear 7. Input double-sided bevel gear
8...Output bevel gear 9...Fixed gear thrust bearing lO.Output gear thrust bearing 11.Feed screw shaft 12.Feed screw nut 13.Preload cylinder 14.Hollow shaft inclined eccentric part 15.Input bevel gear thrust bearing 16.Linear Guide A...
Body B... Base N1... Number of teeth of fixed bevel gear
Claims (1)
空軸電動機及び1枚もしくは複数枚歯数差の中空軸両面
差動傘歯車機構を配設し、かつ前記電動機回転子中空軸
の一端を傾斜偏心させた同軸外周上に、上記差動傘歯車
機構の入力両面傘歯車を軸承させ、さらに同歯車機構の
出力傘歯車中空軸内部に送りねじナットを形設し、該送
りねじナットに嵌入する送りねじ軸を上記電動機の中空
軸内部まで貫通して成ることを特徴とする電動差動式推
力発生装置。A main body of an arbitrary rectangular parallelepiped or cylindrical body is provided, and a hollow shaft electric motor and a hollow shaft double-sided differential bevel gear mechanism with a difference in the number of teeth of one or more teeth are disposed in the main body, and a hollow shaft of the hollow shaft of the motor rotor is provided. The input double-sided bevel gear of the differential bevel gear mechanism is supported on the coaxial outer periphery with one end tilted and eccentric, and a feed screw nut is formed inside the hollow shaft of the output bevel gear of the gear mechanism, and the feed screw nut An electric differential thrust generator characterized in that a feed screw shaft inserted into the electric motor passes through the hollow shaft of the electric motor.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP1286765A JP2684430B2 (en) | 1989-11-01 | 1989-11-01 | Transmission differential thrust generator |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP1286765A JP2684430B2 (en) | 1989-11-01 | 1989-11-01 | Transmission differential thrust generator |
Publications (2)
Publication Number | Publication Date |
---|---|
JPH03149449A true JPH03149449A (en) | 1991-06-26 |
JP2684430B2 JP2684430B2 (en) | 1997-12-03 |
Family
ID=17708760
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP1286765A Expired - Lifetime JP2684430B2 (en) | 1989-11-01 | 1989-11-01 | Transmission differential thrust generator |
Country Status (1)
Country | Link |
---|---|
JP (1) | JP2684430B2 (en) |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5561199A (en) * | 1992-04-30 | 1996-10-01 | Sumitomo Chemical Company, Ltd. | Resin composition |
WO2005046030A1 (en) * | 2003-10-27 | 2005-05-19 | Robert Bosch Gmbh | Transmission drive unit |
JP2006088726A (en) * | 2004-09-21 | 2006-04-06 | Ogino Kogyo Kk | Electric power steering device |
JP2006103392A (en) * | 2004-10-01 | 2006-04-20 | Ogino Kogyo Kk | Wheel motor |
JP2007120621A (en) * | 2005-10-28 | 2007-05-17 | Ogino Kogyo Kk | Positioning device |
WO2009054325A1 (en) * | 2007-10-22 | 2009-04-30 | Jtekt Corporation | Transmission ratio variable mechanism and steering device for vehicle equipped with it |
WO2009054328A1 (en) * | 2007-10-22 | 2009-04-30 | Jtekt Corporation | Steering device for vehicle |
JP2009101802A (en) * | 2007-10-22 | 2009-05-14 | Jtekt Corp | Steering device for vehicle |
JP2010131740A (en) * | 2008-10-29 | 2010-06-17 | Kitagawa Iron Works Co Ltd | Index table of machine tool |
JP2010274771A (en) * | 2009-05-28 | 2010-12-09 | Jtekt Corp | Steering device for vehicle |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS58128550A (en) * | 1982-01-26 | 1983-08-01 | Nichimen Kk | Apparatus for locking and varying power transmitting characteristics of syncline face cycloidal gear mechanism |
JPS63185957U (en) * | 1987-05-25 | 1988-11-29 |
-
1989
- 1989-11-01 JP JP1286765A patent/JP2684430B2/en not_active Expired - Lifetime
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS58128550A (en) * | 1982-01-26 | 1983-08-01 | Nichimen Kk | Apparatus for locking and varying power transmitting characteristics of syncline face cycloidal gear mechanism |
JPS63185957U (en) * | 1987-05-25 | 1988-11-29 |
Cited By (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5561199A (en) * | 1992-04-30 | 1996-10-01 | Sumitomo Chemical Company, Ltd. | Resin composition |
WO2005046030A1 (en) * | 2003-10-27 | 2005-05-19 | Robert Bosch Gmbh | Transmission drive unit |
JP2006088726A (en) * | 2004-09-21 | 2006-04-06 | Ogino Kogyo Kk | Electric power steering device |
JP4520804B2 (en) * | 2004-09-21 | 2010-08-11 | 荻野工業株式会社 | Electric power steering device |
JP2006103392A (en) * | 2004-10-01 | 2006-04-20 | Ogino Kogyo Kk | Wheel motor |
JP2007120621A (en) * | 2005-10-28 | 2007-05-17 | Ogino Kogyo Kk | Positioning device |
WO2009054328A1 (en) * | 2007-10-22 | 2009-04-30 | Jtekt Corporation | Steering device for vehicle |
JP2009101803A (en) * | 2007-10-22 | 2009-05-14 | Jtekt Corp | Steering device for vehicle |
JP2009101802A (en) * | 2007-10-22 | 2009-05-14 | Jtekt Corp | Steering device for vehicle |
WO2009054325A1 (en) * | 2007-10-22 | 2009-04-30 | Jtekt Corporation | Transmission ratio variable mechanism and steering device for vehicle equipped with it |
US8181734B2 (en) | 2007-10-22 | 2012-05-22 | Jtekt Corporation | Motor vehicle steering system |
US8371977B2 (en) | 2007-10-22 | 2013-02-12 | Jtekt Corporation | Transmission ratio variable mechanism and motor vehicle steering system including the same |
JP2010131740A (en) * | 2008-10-29 | 2010-06-17 | Kitagawa Iron Works Co Ltd | Index table of machine tool |
JP2010274771A (en) * | 2009-05-28 | 2010-12-09 | Jtekt Corp | Steering device for vehicle |
Also Published As
Publication number | Publication date |
---|---|
JP2684430B2 (en) | 1997-12-03 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
CN201363397Y (en) | Worm-and-wheel mechanism for zero-clearance transmission and location | |
EP2169204B1 (en) | Actuator | |
JPH03149449A (en) | Electromotive differential type thrust generator | |
JPS6372947A (en) | Controlling speed change gear | |
GB2141203A (en) | Electromechanical linear actuator | |
US20100025610A1 (en) | Low profile valve actuator having high torque output | |
CN102076478B (en) | Extruder gear box | |
CN108036034B (en) | Bidirectional output type harmonic speed reducer | |
US5444348A (en) | Electric jack having a rotation-translation movement conversion system and with energy recovery | |
US3162098A (en) | Fluid actuator | |
Blinov et al. | Prospects of using electromechanical drives based on roller screw mechanisms in aerospace hardware | |
KR20100038146A (en) | Rotary reduction gear | |
US2905008A (en) | Means for preloading a ball spline assembly | |
US5174662A (en) | Device for applying braking torque to a shaft | |
US3930415A (en) | Motion converter | |
JP3887689B2 (en) | Linear actuator | |
JPH0348054A (en) | Actuator | |
US20230061853A1 (en) | Reverse directional thrust device by bidirectional translative movement | |
KR20210018816A (en) | Fixed ratio ground or friction drive | |
US4229984A (en) | Step by step motor and/or brake device | |
Suzumori et al. | Development of pneumatic wobble motors | |
DE102018126071A1 (en) | Linear actuator, especially for a vehicle clutch | |
CN105508543A (en) | Return-difference-free single-stage cycloidal cone gear speed reducer | |
JP2019058031A (en) | Series of electric actuators | |
CN219145182U (en) | Emergency locking electromechanical actuator capable of rotating at limited angle |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
S201 | Request for registration of exclusive licence |
Free format text: JAPANESE INTERMEDIATE CODE: R314201 |
|
R360 | Written notification for declining of transfer of rights |
Free format text: JAPANESE INTERMEDIATE CODE: R360 |
|
R360 | Written notification for declining of transfer of rights |
Free format text: JAPANESE INTERMEDIATE CODE: R360 |
|
R371 | Transfer withdrawn |
Free format text: JAPANESE INTERMEDIATE CODE: R371 |
|
S201 | Request for registration of exclusive licence |
Free format text: JAPANESE INTERMEDIATE CODE: R314201 |
|
R360 | Written notification for declining of transfer of rights |
Free format text: JAPANESE INTERMEDIATE CODE: R360 |
|
R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
R360 | Written notification for declining of transfer of rights |
Free format text: JAPANESE INTERMEDIATE CODE: R360 |
|
R371 | Transfer withdrawn |
Free format text: JAPANESE INTERMEDIATE CODE: R371 |
|
S201 | Request for registration of exclusive licence |
Free format text: JAPANESE INTERMEDIATE CODE: R314201 |
|
R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
EXPY | Cancellation because of completion of term | ||
FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20100815 Year of fee payment: 13 |