JP3944936B2 - In-cylinder direct injection internal combustion engine - Google Patents

In-cylinder direct injection internal combustion engine Download PDF

Info

Publication number
JP3944936B2
JP3944936B2 JP05871597A JP5871597A JP3944936B2 JP 3944936 B2 JP3944936 B2 JP 3944936B2 JP 05871597 A JP05871597 A JP 05871597A JP 5871597 A JP5871597 A JP 5871597A JP 3944936 B2 JP3944936 B2 JP 3944936B2
Authority
JP
Japan
Prior art keywords
combustion chamber
fuel
cylinder
combustion engine
internal combustion
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.)
Expired - Lifetime
Application number
JP05871597A
Other languages
Japanese (ja)
Other versions
JPH10252478A (en
Inventor
雅司 的場
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nissan Motor Co Ltd
Original Assignee
Nissan Motor Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Nissan Motor Co Ltd filed Critical Nissan Motor Co Ltd
Priority to JP05871597A priority Critical patent/JP3944936B2/en
Publication of JPH10252478A publication Critical patent/JPH10252478A/en
Application granted granted Critical
Publication of JP3944936B2 publication Critical patent/JP3944936B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/12—Other methods of operation
    • F02B2075/125—Direct injection in the combustion chamber for spark ignition engines, i.e. not in pre-combustion chamber
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Landscapes

  • Ignition Installations For Internal Combustion Engines (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)

Description

【０００１】
【発明の属する技術分野】
この発明は、筒内直噴式内燃機関に関する。
【０００２】
【従来の技術】
従来の筒内直噴式内燃機関としては、例えば図５、図６に示すようなものがある（特開平５−７１３４３号公報参照のこと）。
この従来技術は、燃料噴射弁２１を燃焼室内に配置すると共にピストン２５の冠面上に深皿状の凹部２６が形成されている。暖機完了後の機関低負荷運転時には、圧縮行程末期に凹部２６内に燃料を噴射して凹部２６内に形成された混合気を点火プラグ２８により着火する。暖機完了前の機関低負荷運転時には、吸気行程初期に凹部２６内に燃料を噴射する。機関高負荷運転時には常に吸気行程中に燃料を噴射する。
ここで、吸気ポートはヘリカルポート形状としてシリンダ２４内にスワール流を生じせしめるようにしてあり、点火プラグ２８は、燃焼室の略中心部に設置される。
尚、図中２２は吸気バルブ、２３は排気バルブ、２７は凸部、２８ａはギャップ部である。
【０００３】
【発明が解決しようとする課題】
しかしながら、このような従来の筒内直噴式内燃機関にあっては、燃料を受ける凹部２６を深皿状とし、且つ点火プラグ２８が燃焼室の略中心に設置されるため、吸排気方向中心線（燃焼室の平面視で２つの吸気バルブ同士の中心部から燃焼室中心部を通って２つの排気バルブ同士の中心部へ向かう線）に沿って噴射されて凹部２６で受けられた燃料噴霧の多くは、凹部２６内及びシリンダ２４内のスワール流により、点火プラグ２８を通り過ぎた位置から巻上げられるために、着火性が悪化するという問題点があった。
この発明は、このような従来の問題点を解決することを目的としている。
【０００４】
【課題を解決するための手段】
前記目的を解決するための手段として本発明請求項１記載の筒内直噴式内燃機関では、
燃焼室に臨んで所定の取付け角度、取付け方向で設置され、燃焼室の平面視で２つの吸気バルブ同士の中心部から燃焼室中心部を通って２つの排気バルブ同士の中心部へ向かう線である吸排気方向中心線の方向に、燃焼室の側面視で斜め下向きに、燃料を直接シリンダ内に噴射する燃料噴射弁と、
燃焼室形状と相対し上死点付近で燃焼室内に突出する凸部と、燃料噴射弁下から排気側まで伸び前記燃料噴射弁から噴射された燃料を受ける円形の深皿状の凹部とを冠面上に設けたピストンと、
吸気通路内に設置されシリンダ内に吸入される空気を制御してシリンダ内にスワール流を生じさせる吸気制御弁と、を有する火花点火式筒内直噴内燃機関において、
燃料に着火する点火プラグを、燃焼室の平面視で、前記吸排気方向中心線からずらして、当該部位での前記スワール流の流れ方向で下流側に、１つ設置した。
請求項２記載の筒内直噴式内燃機関では、請求項１記載の筒内直噴式内燃機関において、前記点火プラグは、ギャップ部がピストン凹部に相対する範囲内となるように設置されている。
請求項３記載の筒内直噴式内燃機関では、請求項１記載の筒内直噴式内燃機関において、前記点火プラグは、ギャップ部がピストン凹部に相対する範囲外、且つピストン凸部の略稜線上となるように設置されている。
【０００５】
【発明の実施の形態】
以下、この発明を図面に基づいて説明する。
図１、図２は、この発明の実施の形態１を示す図である。
まず、構成を説明すると、燃料噴射弁１は、２本の吸気バルブ２の間において吸排気方向中心線（燃焼室の平面視で２つの吸気バルブ同士の中心部から燃焼室中心部を通って２つの排気バルブ同士の中心部へ向かう線）１１上において所定の角度でシリンダヘッドに設置されている。
ピストン５の冠面形状は、燃焼室形状と相対するような凸部７を有した凸形状とし、且つ燃料噴射弁１の下から排気側まで伸びる深皿状の凹部６が設けられ、噴射された燃料を受けられるような構成としている。
吸気通路内には、シリンダ４内に一定のスワール流を生じさせるための吸気制御弁が設置してある。
シリンダヘッドには、燃料に着火するための点火プラグ８が、燃焼室の吸排気方向中心線１１よりもスワール流下流側且つ前記凹部６に相対する範囲内にギャップ部８ａが存在するような位置に設置してある。
【０００６】
次に作用を説明する。
燃料噴射弁１から噴射された燃料の大部分は吸排気方向に進行してピストン５の凹部６で受けられ、自身の運動エネルギと凹部内スワール流１０によって凹部６内において吸排気方向中心線１１よりスワール下流側に流されて巻き上げられる。また、燃料噴霧は所定の噴霧角を有するために吸排気方向中心線１１よりもスワール流上流側に存在する燃料もあるが、凹部６から巻き上がる際には、シリンダ内スワール流９に流されてスワール流下流に流される。その際、凹部６は深皿状としてあるために巻き上がるまでの時間が比較的長くなり凹部内スワール流１０に流される傾向がさらに強くなる。
点火プラグ８は吸排気方向中心線１１よりもスワール下流側に位置するため、凹部６より巻き上げられた燃料は点火プラグ８近傍を通過することになり、且つ燃料はピストン５冠面からの熱をもらって気化が促進されるために着火性が向上すると共に、液体燃料を多く含む直接噴霧との干渉が回避されるためにくすぶりが極力抑制され、着火性がさらに向上される。
【０００７】
図３、図４には実施の形態２を示す。
この実施の形態２は、点火プラグ８のギャップ部８ａをスワール下流側且つピストン５の凹部６と相対する範囲外に設置してある。
機関回転数が比較的高い領域等の早期噴射開始が要求される場合は、凹部６で受けられずに排気側に達する燃料が多くなるが、ピストン５の凸部７の稜線７ａ上に点火プラグ８が設置してあるため、シリンダ内スワール流９によって流された燃料が、凸部７で点火プラグ８寄りにせりあげられ、着火性が確保される。
【０００８】
【発明の効果】
以上説明してきたように、この発明によれば、その構成をピストン冠面に形成し噴射された燃料を受ける凹部を深皿状とし、且つ点火プラグを、前記吸排気方向中心線からずらして、スワール流下流側に設置する構成としたため、凹部内及びシリンダ内スワール流によって流されて巻き上がる燃料への着火性が向上するという効果が得られる。
また、点火プラグのギャップの位置を燃焼室内にさらに突き出して設置することができるため、さらなる着火性の向上が図れ、より広い運転領域に対応できる。
【図面の簡単な説明】
【図１】 本発明の実施の形態１にかかる筒内直噴式内燃機関の平面図である。
【図２】 実施の形態１にかかる筒内直噴式内燃機関の側面図である。
【図３】 本発明の実施の形態２にかかる筒内直噴式内燃機関の平面図である。
【図４】 実施の形態２にかかる筒内直噴式内燃機関の側面図である。
【図５】 従来例にかかる筒内直噴式内燃機関の平面図である。
【図６】 従来例にかかる筒内直噴式内燃機関の側面図である。
【符号の説明】
１ 燃料噴射弁
２ 吸気バルブ
３ 排気バルブ
４ シリンダ
５ ピストン
６ 凹部
７ 凸部
７ａ 稜線
８ 点火プラグ
８ａ ギャップ部
９ シリンダ内スワール流
１０ 凹部内スワール流
１１ 吸排気方向中心線 [0001]
BACKGROUND OF THE INVENTION
The present invention relates to a direct injection type internal combustion engine.
[0002]
[Prior art]
Examples of conventional in-cylinder direct injection internal combustion engines include those shown in FIGS. 5 and 6 (see Japanese Patent Laid-Open No. 5-71343).
In this prior art, the fuel injection valve 21 is disposed in the combustion chamber, and a deep dish-shaped recess 26 is formed on the crown surface of the piston 25. At the time of engine low load operation after completion of warm-up, fuel is injected into the recess 26 at the end of the compression stroke, and the air-fuel mixture formed in the recess 26 is ignited by the spark plug 28. At the time of engine low load operation before the completion of warm-up, fuel is injected into the recess 26 at the beginning of the intake stroke. During engine high load operation, fuel is always injected during the intake stroke.
Here, the intake port is formed in a helical port shape so as to generate a swirl flow in the cylinder 24, and the spark plug 28 is installed at substantially the center of the combustion chamber.
In the figure, 22 is an intake valve, 23 is an exhaust valve, 27 is a convex portion, and 28a is a gap portion.
[0003]
[Problems to be solved by the invention]
However, in such a conventional in-cylinder direct injection internal combustion engine, the recess 26 for receiving the fuel has a deep dish shape, and the ignition plug 28 is installed at the approximate center of the combustion chamber. (Line in the plan view of the combustion chamber from the center of the two intake valves to the center of the two exhaust valves through the center of the combustion chamber) In many cases, the swirl flow in the concave portion 26 and the cylinder 24 causes the ignition plug to be wound up from a position past the spark plug 28, resulting in a problem that the ignitability is deteriorated.
An object of the present invention is to solve such a conventional problem.
[0004]
[Means for Solving the Problems]
In a direct injection type internal combustion engine according to claim 1, as means for solving the above-mentioned object,
It is installed at a predetermined mounting angle and mounting direction facing the combustion chamber, and is a line from the center of the two intake valves through the center of the combustion chamber to the center of the two exhaust valves in a plan view of the combustion chamber. A fuel injection valve that injects fuel directly into the cylinder in a direction of a certain intake / exhaust direction center line, obliquely downward in a side view of the combustion chamber;
Confronted with the shape of the combustion chamber and projecting into the combustion chamber near the top dead center, and a circular deep dish-shaped recess extending from the bottom of the fuel injection valve to the exhaust side and receiving the fuel injected from the fuel injection valve A piston provided on the surface;
An intake control valve to cause a swirl flow in the cylinder is installed in the intake passage by controlling the air sucked into the cylinder, the spark ignition type in-cylinder direct-injection internal combustion engine having,
The spark plug for igniting the fuel, in a plan view of the combustion chamber, offset from the inlet and exhaust direction center line, on the downstream side in the flow direction of the swirl flow in the site and placed one.
In the direct injection type internal combustion engine according to claim 2, in the direct injection type internal combustion engine according to claim 1, the spark plug is installed such that the gap portion is in a range facing the piston recess.
4. The direct injection type internal combustion engine according to claim 3, wherein the spark plug is located outside a range where the gap portion faces the piston concave portion and substantially on the ridge line of the piston convex portion. It is installed to become.
[0005]
DETAILED DESCRIPTION OF THE INVENTION
The present invention will be described below with reference to the drawings.
1 and 2 are views showing Embodiment 1 of the present invention.
First, the structure will be described. The fuel injection valve 1 has a center line between the two intake valves 2 in the intake / exhaust direction (from the center of the two intake valves through the center of the combustion chamber in a plan view of the combustion chamber). The line toward the center of the two exhaust valves) 11 is installed on the cylinder head at a predetermined angle.
The crown surface shape of the piston 5 is a convex shape having a convex portion 7 as opposed to the combustion chamber shape, and a deep dish-shaped concave portion 6 extending from the bottom of the fuel injection valve 1 to the exhaust side is provided and injected. It is configured to receive the fuel.
An intake control valve for generating a constant swirl flow in the cylinder 4 is installed in the intake passage.
In the cylinder head, the spark plug 8 for igniting the fuel is positioned such that the gap portion 8a exists in a range downstream of the swirl flow from the center line 11 in the intake and exhaust directions of the combustion chamber and in the range facing the recess 6 It is installed in.
[0006]
Next, the operation will be described.
Most of the fuel injected from the fuel injection valve 1 travels in the intake / exhaust direction and is received by the recess 6 of the piston 5, and the center line 11 in the intake / exhaust direction in the recess 6 by its own kinetic energy and the swirl flow 10 in the recess. More swirled downstream of the swirl. Further, since the fuel spray has a predetermined spray angle, some fuel exists on the upstream side of the swirl flow with respect to the intake / exhaust direction center line 11. The swirl flows downstream. At that time, since the concave portion 6 has a deep dish shape, the time until the concave portion is rolled up becomes relatively long, and the tendency to be swept into the swirl flow 10 in the concave portion is further increased.
Since the spark plug 8 is located downstream of the swirl with respect to the center line 11 in the intake / exhaust direction, the fuel wound up from the recess 6 passes through the vicinity of the spark plug 8, and the fuel absorbs heat from the crown surface of the piston 5. Since the vaporization is promoted and the ignitability is improved, the smoldering is suppressed as much as possible because interference with the direct spray containing a large amount of liquid fuel is avoided, and the ignitability is further improved.
[0007]
3 and 4 show a second embodiment.
In the second embodiment, the gap portion 8 a of the spark plug 8 is installed on the downstream side of the swirl and outside the range facing the concave portion 6 of the piston 5.
When early injection start is required, such as in a region where the engine speed is relatively high, the amount of fuel that reaches the exhaust side without being received by the recess 6 increases, but the spark plug is placed on the ridge line 7a of the projection 7 of the piston 5 Since 8 is installed, the fuel flowed by the in-cylinder swirl flow 9 is raised toward the spark plug 8 by the convex portion 7, and ignitability is ensured.
[0008]
【The invention's effect】
As described above, according to the present invention, the concave portion for receiving the injected fuel is formed in the piston crown surface, and the spark plug is shifted from the intake / exhaust direction center line . Since it is configured to be installed on the downstream side of the swirl flow, the effect of improving the ignitability of the fuel that is swept up by the swirl flow in the recess and in the cylinder is obtained.
Further, since the position of the spark plug gap can be further protruded into the combustion chamber, the ignitability can be further improved and a wider operating range can be accommodated.
[Brief description of the drawings]
FIG. 1 is a plan view of a direct injection type internal combustion engine according to a first embodiment of the present invention.
FIG. 2 is a side view of the direct injection type internal combustion engine according to the first embodiment.
FIG. 3 is a plan view of a direct injection type internal combustion engine according to a second embodiment of the present invention.
FIG. 4 is a side view of a direct injection type internal combustion engine according to a second embodiment.
FIG. 5 is a plan view of a direct injection type internal combustion engine according to a conventional example.
FIG. 6 is a side view of a direct injection type internal combustion engine according to a conventional example.
[Explanation of symbols]
1 fuel injection valve 2 intake valve 3 exhaust valves 4 cylinder 5 piston 6 recess 7 protrusions 7a ridge 8 spark plug 8a gap 9 cylinder swirl flow 10 recess swirl flow 11 intake and exhaust direction center line

Claims (3)

燃焼室に臨んで所定の取付け角度、取付け方向で設置され、燃焼室の平面視で２つの吸気バルブ同士の中心部から燃焼室中心部を通って２つの排気バルブ同士の中心部へ向かう線である吸排気方向中心線の方向に、燃焼室の側面視で斜め下向きに、燃料を直接シリンダ内に噴射する燃料噴射弁と、
燃焼室形状と相対し上死点付近で燃焼室内に突出する凸部と、燃料噴射弁下から排気側まで伸び前記燃料噴射弁から噴射された燃料を受ける円形の深皿状の凹部とを冠面上に設けたピストンと、
吸気通路内に設置されシリンダ内に吸入される空気を制御してシリンダ内にスワール流を生じさせる吸気制御弁と、を有する火花点火式筒内直噴内燃機関において、
燃料に着火する点火プラグを、燃焼室の平面視で、前記吸排気方向中心線からずらして、当該部位での前記スワール流の流れ方向で下流側に、１つ設置したことを特徴とする筒内直噴式内燃機関。It is installed at a predetermined mounting angle and mounting direction facing the combustion chamber, and is a line from the center of the two intake valves through the center of the combustion chamber to the center of the two exhaust valves in a plan view of the combustion chamber. A fuel injection valve that injects fuel directly into the cylinder in a direction of a certain intake / exhaust direction center line, obliquely downward in a side view of the combustion chamber;
Confronted with the shape of the combustion chamber and projecting into the combustion chamber near the top dead center, and a circular deep dish-shaped recess extending from the bottom of the fuel injection valve to the exhaust side and receiving the fuel injected from the fuel injection valve A piston provided on the surface;
In a spark ignition type cylinder direct injection internal combustion engine having an intake control valve that is installed in an intake passage and controls air sucked into the cylinder to generate a swirl flow in the cylinder,
The spark plug for igniting the fuel, in a plan view of the combustion chamber, offset from the inlet and exhaust direction center line, on the downstream side in the flow direction of the swirl flow in the site, cylindrical, wherein one that placed the Internal direct injection internal combustion engine. 前記点火プラグは、ギャップ部がピストン凹部に相対する範囲内となるように設置されたことを特徴とする請求項１記載の筒内直噴式内燃機関。  The in-cylinder direct injection internal combustion engine according to claim 1, wherein the spark plug is installed so that the gap portion is within a range facing the piston recess. 前記点火プラグは、ギャップ部がピストン凹部に相対する範囲外、且つピストン凸部の略稜線上となるように設置されたことを特徴とする請求項１記載の筒内直噴式内燃機関。  The in-cylinder direct injection internal combustion engine according to claim 1, wherein the spark plug is installed such that the gap portion is outside the range facing the piston recess and is substantially on the ridge line of the piston protrusion.
JP05871597A 1997-03-13 1997-03-13 In-cylinder direct injection internal combustion engine Expired - Lifetime JP3944936B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP05871597A JP3944936B2 (en) 1997-03-13 1997-03-13 In-cylinder direct injection internal combustion engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP05871597A JP3944936B2 (en) 1997-03-13 1997-03-13 In-cylinder direct injection internal combustion engine

Publications (2)

Publication Number Publication Date
JPH10252478A JPH10252478A (en) 1998-09-22
JP3944936B2 true JP3944936B2 (en) 2007-07-18

Family

ID=13092200

Family Applications (1)

Application Number Title Priority Date Filing Date
JP05871597A Expired - Lifetime JP3944936B2 (en) 1997-03-13 1997-03-13 In-cylinder direct injection internal combustion engine

Country Status (1)

Country Link
JP (1) JP3944936B2 (en)

Also Published As

Publication number Publication date
JPH10252478A (en) 1998-09-22

Similar Documents

Publication Publication Date Title
US5617823A (en) Spark-ignited reciprocating piston engine having a subdivided combustion chamber
JP2002188448A (en) Cylinder fuel injection type gasoline engine where fuel is injected inside the cylinder
JP3693211B2 (en) In-cylinder injection engine
US3963003A (en) Combustion chamber arrangements for I.C. engines
JP2653226B2 (en) 2-stroke diesel engine
JP2000248945A (en) Cylinder direct injection engine
US6651611B2 (en) Combustion chamber for swirl flow two valve spark ignition direct injection engine
JP3612874B2 (en) In-cylinder injection engine
JPH11190217A (en) Direct injection type diesel engine
JP3627546B2 (en) Direct cylinder injection spark ignition engine
JP4316719B2 (en) In-cylinder injection control device
JP3944936B2 (en) In-cylinder direct injection internal combustion engine
JP4785540B2 (en) Internal combustion engine and its piston
JP3799675B2 (en) In-cylinder direct injection spark ignition engine
JP3280431B2 (en) In-cylinder fuel injection engine
KR100365113B1 (en) Structure of shape of piston head of direct injection type gasoline engine
KR100303979B1 (en) 3-valve gasoline engine
JP4320345B2 (en) Control unit for direct injection engine
JPS5926772B2 (en) Pre-chamber internal combustion engine
JPH036824Y2 (en)
JPH09217626A (en) Direct injection four valve diesel engine
JP3826510B2 (en) In-cylinder injection spark ignition engine
JPH0631146Y2 (en) Combustion chamber structure of two-cycle internal combustion engine
JP4004176B2 (en) Piston for in-cylinder injection engine and in-cylinder injection engine using this piston
JP4026406B2 (en) Direct-injection spark ignition internal combustion engine

Legal Events

Date Code Title Description
A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20060829

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20061012

RD02 Notification of acceptance of power of attorney

Free format text: JAPANESE INTERMEDIATE CODE: A7422

Effective date: 20061012

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20061212

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20070213

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20070320

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20070402

R150 Certificate of patent or registration of utility model

Free format text: JAPANESE INTERMEDIATE CODE: R150

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20110420

Year of fee payment: 4

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20120420

Year of fee payment: 5

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130420

Year of fee payment: 6

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20130420

Year of fee payment: 6

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20140420

Year of fee payment: 7

EXPY Cancellation because of completion of term