JP5265893B2 - Internal combustion engine injection pump and internal combustion engine - Google Patents
Internal combustion engine injection pump and internal combustion engine Download PDFInfo
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- JP5265893B2 JP5265893B2 JP2007203936A JP2007203936A JP5265893B2 JP 5265893 B2 JP5265893 B2 JP 5265893B2 JP 2007203936 A JP2007203936 A JP 2007203936A JP 2007203936 A JP2007203936 A JP 2007203936A JP 5265893 B2 JP5265893 B2 JP 5265893B2
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- injection pump
- frustoconical
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- 238000002347 injection Methods 0.000 title claims description 37
- 239000007924 injection Substances 0.000 title claims description 37
- 238000002485 combustion reaction Methods 0.000 title claims description 15
- 239000000446 fuel Substances 0.000 claims description 21
- 230000002411 adverse Effects 0.000 description 2
- 238000005260 corrosion Methods 0.000 description 2
- 230000007797 corrosion Effects 0.000 description 2
- 238000007689 inspection Methods 0.000 description 2
- 230000001174 ascending effect Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/38—Pumps characterised by adaptations to special uses or conditions
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
Description
本発明は、請求項1の前文に記載の内燃機関の噴射ポンプ、即ち燃料噴射ポンプに関する。本発明は、請求項10の前文に記載の内燃機関にも関する。
The present invention relates to an injection pump for an internal combustion engine, that is, a fuel injection pump according to the preamble of claim 1. The invention also relates to an internal combustion engine according to the preamble of
内燃機関において実際に知られている傾斜切欠き(リード)制御式の高圧燃料噴射ポンプの場合、通常、プランジャが利用され、吸込み室並びに高圧室が高圧噴射ポンプのプランジャと協働する。噴射ポンプの吸込み室並びに高圧室は、通常、2個の吸込み孔を介して互いに接続され、高圧噴射ポンプのプランジャは、その第1位置で、吸込み孔を閉鎖し、かくして、吸込み室から高圧室への燃料流を阻止する。プランジャは第2位置で吸込み孔を開け、かくして、吸込み室からの燃料による高圧室の充填を可能とする。燃料は高圧ポンプの吸込み室に所謂前置搬送装置を介して到達し、吸込み室から吸込み孔を通して高圧室に到達し、詳しくは、噴射ポンプのプランジャの位置に関係して到達する。プランジャの位置はカムを介して制御される。プランジャが吸込み孔を閉じている場合、吸込み室から高圧室への燃料流は阻止され、燃料は高圧室内において、内燃機関のシリンダ内に所定圧力で噴射が行われるほどに圧縮される。プランジャの制御縁が吸込み孔を再び開け始めるや否や、噴射過程が終了し、そして、(プランジャの下降運動中)吸込み室から噴射ポンプの高圧室への燃料の搬送が行われる。 In the case of a high-pressure fuel injection pump of an inclination notch (lead) control type that is actually known in an internal combustion engine, a plunger is usually used, and the suction chamber and the high-pressure chamber cooperate with the plunger of the high-pressure injection pump. The suction chamber and the high-pressure chamber of the injection pump are usually connected to each other via two suction holes, and the plunger of the high-pressure injection pump closes the suction hole in its first position, and thus from the suction chamber to the high-pressure chamber. Block fuel flow to The plunger opens the suction hole at the second position, thus allowing the high pressure chamber to be filled with fuel from the suction chamber. The fuel reaches the suction chamber of the high-pressure pump through a so-called pre-conveying device, reaches the high-pressure chamber from the suction chamber through the suction hole, and specifically reaches the high-pressure chamber in relation to the position of the plunger of the injection pump. The position of the plunger is controlled via a cam. When the plunger closes the suction hole, the fuel flow from the suction chamber to the high-pressure chamber is blocked, and the fuel is compressed in the high-pressure chamber such that the fuel is injected at a predetermined pressure into the cylinder of the internal combustion engine. As soon as the plunger's control edge begins to reopen the suction hole, the injection process ends, and (during the downward movement of the plunger) fuel is transferred from the suction chamber to the high pressure chamber of the injection pump.
従って吸込み孔の範囲にかかる圧力は、激しく且つ衝撃的に変動し、このため吸込み孔の範囲にキャビテーションが生ずる。キャビテーションにより、吸込み孔の表面が腐食される。キャビテーションは噴射ポンプの点検間隔とその寿命に相当の影響を与える。 Therefore, the pressure applied to the suction hole range fluctuates violently and impactfully, and cavitation occurs in the suction hole range. The surface of the suction hole is corroded by cavitation. Cavitation has a considerable impact on the inspection interval and life of the injection pump.
この点から出発して、本発明の課題は、内燃機関の新規な噴射ポンプおよび相応した内燃機関を提供することにある。 Starting from this point, the object of the invention is to provide a new injection pump for an internal combustion engine and a corresponding internal combustion engine.
この課題は請求項1に記載の内燃機関の噴射ポンプによって解決される。本発明に基づいて、吸込み孔が高圧室に隣接して円筒状区域を有し、この円筒状区域に少なくとも2個の裁頭円錐状区域が連続して続き、この裁頭円錐状区域の軸線が、円筒状区域の軸線に対して水平方向および/又は垂直方向に曲げられないし傾斜している。 This problem is solved by the internal combustion engine injection pump according to claim 1. According to the invention, the suction hole has a cylindrical area adjacent to the high-pressure chamber, which is followed by at least two frustoconical areas, the axis of the frustoconical area. Are bent or inclined horizontally and / or vertically with respect to the axis of the cylindrical section.
吸込み室を高圧噴射プランジャポンプの高圧室に接続する吸込み孔の幾何学形状は、その表面がキャビテーション発生領域で絞り込まれているように形状ないし輪郭づけられ、その結果キャビテーション気泡の破裂が、吸込み孔の表面に悪影響を与えることなく、燃料内で直接行われる。吸込み孔の壁部へのキャビテーション気泡の付着を助長する鋭い縁や急傾斜角を防止できる。それに応じて、全体として高圧噴射プランジャポンプの吸込み孔のキャビテーション腐食を低減でき、この結果高圧噴射プランジャポンプは長い寿命を示し、点検時間間隔が増大する。このため大幅な経費節減が可能となる。 The geometry of the suction hole connecting the suction chamber to the high pressure chamber of the high pressure injection plunger pump is shaped or contoured so that its surface is squeezed in the cavitation generating region, so that the cavitation bubble bursts, This is done directly in the fuel without adversely affecting the surface of the fuel. It is possible to prevent sharp edges and steep inclination angles that promote adhesion of cavitation bubbles to the wall of the suction hole. Accordingly, cavitation corrosion of the suction hole of the high-pressure injection plunger pump as a whole can be reduced, and as a result, the high-pressure injection plunger pump exhibits a long life and an inspection time interval increases. As a result, significant cost savings are possible.
裁頭円錐状区域の軸線が、円筒状区域の軸線に対し水平並びに垂直方向に曲げられ又は傾斜し、その際裁頭円錐状区域の軸線が互いに一致する、即ち重なり合うとよい。 The axis of the frustoconical section may be bent or inclined horizontally and perpendicularly to the axis of the cylindrical section, with the axes of the frustoconical section being coincident with each other, ie overlapping.
本発明に基づく内燃機関を請求項10に示す。
An internal combustion engine according to the present invention is shown in
本発明の有利な実施態様は従属請求項および以下の説明から明らかにする。以下図を参照して本発明の実施例を詳細に説明するが、本発明はこの実施例に限定されない。 Advantageous embodiments of the invention emerge from the dependent claims and the following description. Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. However, the present invention is not limited to the embodiments.
図1は、ディーゼルエンジンに対する所謂傾斜切欠き(リード)制御式の高圧噴射プランジャポンプの一部を断面図で示す。噴射ポンプはプランジャ10を有し、該プランジャ10は噴射ポンプの吸込み室11並びに高圧室12と協働する。代表的には、吸込み室11を高圧室12に2個の吸込み孔13を介して接続する。なお、唯一の又は2個以上の吸込み孔13を設けてもよい。プランジャ10の位置に応じ、プランジャ10は吸込み孔13を開閉する。プランジャ10が吸込み孔13を閉鎖している際(プランジャ10の最大上昇行程時)、噴射ポンプの吸込み室11から高圧室12への燃料流を阻止する。
FIG. 1 is a sectional view showing a part of a so-called inclined notch (lead) control type high-pressure injection plunger pump for a diesel engine. The injection pump has a
これに対しプランジャ10が吸込み孔13を開け、高圧室12に吸込み室11より低い圧力がかかったとき、吸込み孔13を通して燃料が流れ、高圧室12が噴射ポンプの吸込み室11からの燃料で充填される。
On the other hand, when the
高圧室12内の圧縮された燃料を内燃機関、特にディーゼルエンジンのシリンダに注入するために、図示しない燃料噴射ノズルが、(高圧)通路14を介して高圧燃料噴射プランジャポンプの高圧室12に接続される。
A fuel injection nozzle (not shown) is connected to the
吸込み孔13は主に2つの部分、即ち吸込み室11に隣接した入口部16と、高圧室12に隣接した出口部15に分けられる。本発明では、各吸込み孔13の吸込み室11に隣接する入口部16は、吸込み孔13が殆どキャビテーション腐食を被らないよう輪郭づけている。即ち、吸込み孔13の入口部16を、吸込み孔の表面がキャビテーション発生領域で拡がり又は狭まるように形状づけ、もって最終的にキャビテーション気泡の破裂が、吸込み孔13に有害な影響を与えることなしに、燃料内で直接生ずるようにしている。
The
図1において各吸込み孔13の出口部15は円筒状区域17として形成され、各吸込み孔13の円筒状区域17の軸線には符号18を付している。各吸込み孔13の入口部16は、図1において2個の裁頭円錐状区域19、20で形成されている。入口部16の第1裁頭円錐状区域19は、出口部15の円筒状区域17に直接続き、第2裁頭円錐状区域20は第1裁頭円錐状区域19に続き、吸込み室11に開口している。
In FIG. 1, the
本発明に従い、入口部16の第1裁頭円錐状区域19、20の軸線は、出口部15の円筒状区域17に対し水平方向および/又は垂直方向に曲げられないし傾斜し、図示の実施例では、裁頭円錐状区域19、20の軸線は円筒状区域17の軸線18に対して水平方向および垂直方向に曲げられないし傾斜している。図示の実施例において、裁頭円錐状区域18、19の軸線は互いに一致し、即ち重なり合っている。両裁頭円錐状区域19、20の軸線は図1において符号21で示す。
In accordance with the present invention, the axis of the first
図1と図2に応じて、入口部16の両裁頭円錐状区域19、20の一致軸線21は、出口部15の円筒状区域17の軸線18に対し水平方向に左側に角度γだけ、垂直方向に上向きに角度δだけ曲げられないし傾斜している。これら角度γ、δは異なるとよいが、同じ大きさでもよい。また裁頭円錐状区域の軸線を円筒状区域に対し水平方向に右側に向かって、垂直方向に下向きに曲げないし傾斜させてもよい。
According to FIGS. 1 and 2, the
図1に応じて、各吸込み孔13の第1裁頭円錐状区域19は円錐半角αにより、各吸込み孔13の第2裁頭円錐状区域20は円錐半角βにより各々特徴づけられている。図1の実施例では、第1裁頭円錐状区域19の円錐半角αは、各吸込み孔13の第2裁頭円錐状区域20の円錐半角βより大きい。しかし他の例では、第1裁頭円錐状区域19の円錐半角αを各吸込み孔13の第2裁頭円錐状区域20の円錐半角βよりも小さくなし得る。
According to FIG. 1, the first
10 プランジャ、11 吸込み室、12 高圧室、13 吸込み孔、14 通路、15 出口部、16 入口部、17 円筒状区域、18、21 軸線、19、20 裁頭円錐状区域 10 Plunger, 11 Suction chamber, 12 High pressure chamber, 13 Suction hole, 14 Passage, 15 Outlet, 16 Inlet, 17 Cylindrical section, 18, 21 Axis, 19, 20 Triangular conical section
Claims (8)
吸込み孔(13)が高圧室(12)に隣接して円筒状区域(17)を有し、該円筒状区域(17)に少なくとも2個の裁頭円錐状区域(19、20)が連続して続き、該裁頭円錐状区域(19、20)の軸線(21)が、円筒状区域(17)の軸線(18)に対して水平方向および垂直方向の少なくとも一方向に曲げられ、
吸込み孔(13)が2個の裁頭円錐状区域(19、20)を有し、円筒状区域(17)に直接続く第1裁頭円錐状区域(19)が第1円錐半角(α)を有し、第1裁頭円錐状区域(19)に続き吸込み室(11)に開口する第2裁頭円錐状区域(20)が第2円錐半角(β)を有し、
第1円錐半角(α)が第2円錐半角(β)より大きいことを特徴とする内燃機関の噴射ポンプ。 The suction chamber (11) and the high-pressure chamber (12), which are provided with at least one plunger (10) and are connected to each other via two suction holes (13), in particular, the plunger (10) is the suction hole (13). When the plunger is closed, the fuel flow from the suction chamber (11) to the high pressure chamber (12) is blocked, and the fuel from the suction chamber (11) is opened when the plunger (10) opens the suction hole (13). In an inclined notch controlled injection pump cooperating with the plunger (10) so as to allow filling of the high pressure chamber (12) by
The suction hole (13) has a cylindrical section (17) adjacent to the high-pressure chamber (12), and at least two frustoconical sections (19, 20) are connected to the cylindrical section (17). Subsequently, the axis (21) of the frustoconical section (19, 20) is bent in at least one direction , horizontal and vertical, with respect to the axis (18) of the cylindrical section (17) ,
The suction hole (13) has two frustoconical sections (19, 20), the first frustoconical section (19) directly following the cylindrical section (17) is the first conical half angle (α) A second frustoconical area (20) opening into the suction chamber (11) following the first frustoconical area (19) has a second conical half angle (β);
An injection pump for an internal combustion engine, wherein the first conical half angle (α) is larger than the second conical half angle (β) .
8. An internal combustion engine comprising a plurality of cylinders, each of which is provided with an injection pump for injecting fuel at a predetermined injection pressure, wherein the injection pump is formed according to one of claims 1 to 7. An internal combustion engine characterized by that.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE102006040465.3 | 2006-08-29 | ||
DE102006040465A DE102006040465A1 (en) | 2006-08-29 | 2006-08-29 | Injection pump i.e. chamfer-controlled piston high pressure fuel injection pump, for diesel -internal-combustion engine, has chambers connected with each other with piston such that piston is locked in position of suction borehole |
Publications (2)
Publication Number | Publication Date |
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JP2008057530A JP2008057530A (en) | 2008-03-13 |
JP5265893B2 true JP5265893B2 (en) | 2013-08-14 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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JP2007203936A Active JP5265893B2 (en) | 2006-08-29 | 2007-08-06 | Internal combustion engine injection pump and internal combustion engine |
Country Status (5)
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JP (1) | JP5265893B2 (en) |
KR (1) | KR101397849B1 (en) |
CN (1) | CN101135284B (en) |
DE (1) | DE102006040465A1 (en) |
FI (1) | FI20070468L (en) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102010028046A1 (en) * | 2010-04-21 | 2011-10-27 | Robert Bosch Gmbh | high pressure pump |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3141653A1 (en) * | 1981-10-21 | 1983-05-05 | L'Orange GmbH, 7000 Stuttgart | FUEL INJECTION PUMP, ESPECIALLY FOR A DIESEL INTERNAL COMBUSTION ENGINE |
AT388214B (en) * | 1983-02-17 | 1989-05-26 | Steyr Daimler Puch Ag | FUEL INJECTION UNIT FOR ONE CYLINDER OF A DIESEL ENGINE |
IT1200685B (en) * | 1985-07-22 | 1989-01-27 | Piaggio & C Spa | MECHANICAL FUEL INJECTION PUMP, IN PARTICULAR INTERNAL COMBUSTION COMBUSTION IGNITION PUMPS |
DE3902764C2 (en) * | 1989-01-31 | 2002-10-17 | Bosch Gmbh Robert | Fuel injection pump |
DE4240302A1 (en) * | 1992-12-01 | 1994-06-09 | Bosch Gmbh Robert | Pressure valve for IC engine - with throttle located in area of reduced cross=section of passage channel |
JP3604294B2 (en) * | 1998-12-11 | 2004-12-22 | 株式会社ボッシュオートモーティブシステム | Fuel injection pump |
DE19919430C1 (en) * | 1999-04-29 | 2000-10-19 | Bosch Gmbh Robert | Injection pump |
DE50211835D1 (en) * | 2001-04-06 | 2008-04-17 | Bosch Gmbh Robert | STAMPING INJECTION PUMP FOR A COMMON RAIL FUEL INJECTION SYSTEM |
JP2003206824A (en) * | 2001-11-09 | 2003-07-25 | Bosch Automotive Systems Corp | Injection pump, dme fuel supply device of diesel engine having it |
-
2006
- 2006-08-29 DE DE102006040465A patent/DE102006040465A1/en active Granted
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2007
- 2007-05-29 KR KR1020070052057A patent/KR101397849B1/en active IP Right Grant
- 2007-06-13 FI FI20070468A patent/FI20070468L/en not_active Application Discontinuation
- 2007-08-06 JP JP2007203936A patent/JP5265893B2/en active Active
- 2007-08-29 CN CN2007101483057A patent/CN101135284B/en active Active
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CN101135284B (en) | 2012-11-07 |
FI20070468L (en) | 2008-03-01 |
JP2008057530A (en) | 2008-03-13 |
FI20070468A0 (en) | 2007-06-13 |
CN101135284A (en) | 2008-03-05 |
DE102006040465A1 (en) | 2008-03-06 |
KR20080020453A (en) | 2008-03-05 |
KR101397849B1 (en) | 2014-05-20 |
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