JPS6014932Y2 - fuel injection valve - Google Patents
fuel injection valveInfo
- Publication number
- JPS6014932Y2 JPS6014932Y2 JP8325480U JP8325480U JPS6014932Y2 JP S6014932 Y2 JPS6014932 Y2 JP S6014932Y2 JP 8325480 U JP8325480 U JP 8325480U JP 8325480 U JP8325480 U JP 8325480U JP S6014932 Y2 JPS6014932 Y2 JP S6014932Y2
- Authority
- JP
- Japan
- Prior art keywords
- nozzle
- valve
- fuel injection
- fuel
- lift
- 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
Links
Landscapes
- Fuel-Injection Apparatus (AREA)
Description
【考案の詳細な説明】
本件考案はディーゼル機関の最適燃焼、燃料消費効率の
改善を四指したものである。[Detailed explanation of the invention] This invention aims at improving the optimal combustion and fuel consumption efficiency of diesel engines.
ディーゼル機関のノズルバルブの噴口面積の設定は、通
常は高速、高負荷域で燃焼状態が最適になるように設定
されており、低速の部分負荷時は噴口面積が広すぎ、噴
霧粒径も粗くそれが原因で青白煙の発生や炭化水素の増
加等の不具合につながっていたのである。The nozzle area of a diesel engine's nozzle valve is normally set to optimize combustion conditions at high speeds and high loads, but at low speeds and partial loads, the nozzle area is too wide and the spray particle size becomes coarse. This led to problems such as the generation of blue-white smoke and an increase in hydrocarbons.
本件考案においては、ノズルバルブに噴口を設け、且つ
、サックレスの外開弁形式において、ノズルバルブのリ
フト幅を、フィードポンプのフィード圧によりピストン
を使って制御することにより噴口面積を変化させ、低速
負荷域における最適噴口面積を得させようとするもので
ある。In this invention, the nozzle valve is provided with a nozzle port, and in a suckless outward-opening valve type, the lift width of the nozzle valve is controlled using a piston by the feed pressure of the feed pump, thereby changing the nozzle area and reducing the speed at low speed. The aim is to obtain the optimum nozzle area in the load range.
本件考案の目的は以上の如くであり、添付の図面に示し
た実施例の構成に基づいて本件考案の構成を説明すると
。The purpose of the present invention is as described above, and the structure of the present invention will be explained based on the structure of the embodiment shown in the attached drawings.
第１図は本考案の燃料噴射弁の断面図と燃料回路図であ
る。FIG. 1 is a sectional view and a fuel circuit diagram of the fuel injection valve of the present invention.
第２図、第３図はノズルバルブとノズルボディーの拡大
断面図
第４図はノズルバルブの側面図
第５図はノズルリフトｈ、噴口面積Ａ１フィードポンプ
Ｐの関係を示すグラフである。2 and 3 are enlarged sectional views of the nozzle valve and the nozzle body. FIG. 4 is a side view of the nozzle valve. FIG. 5 is a graph showing the relationship between the nozzle lift h, the nozzle area A1, and the feed pump P.
ノズル本体１の上部にフィードポンプ１１からの燃料が
フィード圧によって送油される継手１ｃの挿入部が設け
られており、フィード圧を持った燃料油はピストン２を
押しつける。An insertion part of a joint 1c is provided in the upper part of the nozzle body 1, through which fuel from the feed pump 11 is sent under feed pressure, and the fuel oil having the feed pressure presses against the piston 2.
又、ノズル本体の側面に高圧燃料管の入口部１ａと燃料
灰油管の出口部１ｂが設けられている。Further, an inlet portion 1a for a high-pressure fuel pipe and an outlet portion 1b for a fuel ash oil pipe are provided on the side surface of the nozzle body.
高圧燃料はノズル本体１内の油路１ｄからノズルボディ
ー５内の油路５ａに受継がれ、次にノズルバルブ３内の
油路３ａから噴口３ｂ、３ｃへ至る。The high-pressure fuel is transferred from the oil passage 1d in the nozzle body 1 to the oil passage 5a in the nozzle body 5, and then from the oil passage 3a in the nozzle valve 3 to the injection ports 3b and 3c.
燃料噴射ポンプ１０内の燃料噴射ポンプカム軸１９の回
転により、高圧油が周期的に噴口部へ送られ、高圧燃料
送油時にノズルバルブ３をノズルスプリング８に抗して
押し下げ噴口３ｃｙ３ｂをシリンダーヘッド内に開口し
、高圧燃料を霧状にして噴射する。By rotating the fuel injection pump camshaft 19 in the fuel injection pump 10, high-pressure oil is periodically sent to the nozzle part, and when high-pressure fuel is being fed, the nozzle valve 3 is pushed down against the nozzle spring 8, and the nozzle 3cy3b is pushed into the cylinder head. It opens and injects high-pressure fuel in the form of a mist.
噴射の際バルブステム部３ｅよりリークした燃料油は燃
料炭油管出口１ｂより燃料タンク１５へ戻る。Fuel oil leaking from the valve stem portion 3e during injection returns to the fuel tank 15 from the fuel coal oil pipe outlet 1b.
従来はこれだけで燃料噴射弁が構成されていたが、本件
考案の燃料噴射弁Ｂにおいては、ノズルスプリング８の
上部にフィードポンプのフィード圧によって上下動され
るピストン２を構成し、フィードポンプ１１がディーゼ
ル機関の高速回転に伴い高速回転し、フィード圧を高め
た時はピストン２が押し下げられ、ストッパー６は下端
に達して止まるので、ノズルバルブ３の上部係合片９は
ストッパー６の上端までいっばいに下降でき、ノズルバ
ルブ３も第２図のリフト幅（ｈｍａｘ）まで下降するこ
とができ、上下２列に並べられた噴口３ｂ、３ｃのどち
らも露出し、噴口面積は最大である。Conventionally, a fuel injection valve was configured with only this, but in the fuel injection valve B of the present invention, a piston 2 that is moved up and down by the feed pressure of the feed pump is configured on the upper part of the nozzle spring 8, and the feed pump 11 is When the diesel engine rotates at high speed and the feed pressure is increased, the piston 2 is pushed down and the stopper 6 stops when it reaches the lower end, so the upper engagement piece 9 of the nozzle valve 3 moves all the way to the upper end of the stopper 6. The nozzle valve 3 can also be lowered to the lift width (hmax) shown in FIG. 2, and both of the nozzle ports 3b and 3c arranged in two rows above and below are exposed, and the nozzle area is maximum.
逆にエンジン回転数が落ちて、フィードポンプ１１の回
転数も比例して落ち、フィード圧が下がると、ピストン
２は上方へ移動し、ストッパー６もそれにつれて、リフ
ト制御用スプリング７の弾力により上方へ移動する。Conversely, when the engine speed decreases, the feed pump 11 rotation speed decreases proportionally, and the feed pressure decreases, the piston 2 moves upward, and the stopper 6 moves upward due to the elasticity of the lift control spring 7. Move to.
ノズルバルブ３の係合片９の下端が上方へ移動したスト
ッパー６の上端に接当して、成る程度以上の下降を制限
されるのである。The lower end of the engaging piece 9 of the nozzle valve 3 comes into contact with the upper end of the stopper 6 that has moved upward, and the lowering of the nozzle valve 3 is restricted beyond that level.
リフト幅は第３図の（ｈｍｉ ｎ）を最低限としている
。The minimum lift width is (hmin) in FIG. 3.
第３図においては、上側の噴口３ｂは開口せず、下側の
噴射口３Ｃのみ開口するので噴口面積が狭くなるのであ
る。In FIG. 3, the upper nozzle 3b is not opened, and only the lower nozzle 3C is open, so the nozzle area becomes narrow.
第１図において４はケースナツト、１２は調圧弁である
。In FIG. 1, 4 is a case nut, and 12 is a pressure regulating valve.
第５図は回転速度の変化に伴い、比例的にフィードポン
プ圧力Ｐ１噴ロ面積Ａ１ノズルリフト幅りが変化する状
態を示している。FIG. 5 shows a state in which the feed pump pressure P1 injection area A1 nozzle lift width changes proportionally as the rotational speed changes.
第４図には本実施例の上下２段に並べた噴口配置を示し
ているが、噴口の配置は機関の特性に応じて種々の配置
が考えられる。Although FIG. 4 shows the arrangement of the nozzles arranged in two stages, upper and lower, in this embodiment, various arrangements of the nozzles can be considered depending on the characteristics of the engine.
第６図は本考案の燃料噴射弁の平面図 第７図は噴射角度を示す燃料噴射弁の側面断面図 第８図は同じく側面図である。Figure 6 is a plan view of the fuel injection valve of the present invention. Figure 7 is a side sectional view of the fuel injection valve showing the injection angle. FIG. 8 is also a side view.
噴射角度θをも噴口面積と同調して変化することができ
る。The injection angle θ can also be changed in sync with the nozzle area.
例えば、ノズルバルブ３の下端の開口しやすい噴口を狭
い角度とし、上方の高速の時に開口する噴口を広い角度
の噴射角θに構成することにより、ディーゼル機関の回
転数に応じた噴射角度を得ることができるものである。For example, by configuring the nozzle at the lower end of the nozzle valve 3, which is easy to open, at a narrow angle, and the upper nozzle, which opens at high speed, at a wide injection angle θ, an injection angle corresponding to the rotation speed of the diesel engine can be obtained. It is something that can be done.
以上のように本考案は、ノズルバルブのリフト幅を制御
し、低速回転域では噴口面積を小とし、高速回転域では
噴口面積を大とすべく、ノズルバルブ３のリフト幅を決
めるストッパー６をリフト幅が小となる方向にスプリン
グ７にて押圧し、逆にストッパー６をリフト幅が大とな
る方向にピストン２にて押圧し、ピストン２を押す方向
にフィードポンプのフィード圧を加えたので、従来の噴
口面積は最高回転において最適の燃焼を行うべく決めら
れていた為に、低速回転域においては、噴口面積が広す
ぎて後ブレや青白煙、炭化水素の発生等の原因となって
いたが、本件考案により低速域では自動的にそれに見合
った噴口面積とすることにより、これらの燃焼の不具合
を解消することができ、この目的をフィードポンプのフ
ィード圧とピストンを利用することにより、容易に簡単
な構成で威し遂げたものである。As described above, the present invention uses the stopper 6 that determines the lift width of the nozzle valve 3 in order to control the lift width of the nozzle valve, to make the nozzle area small in the low speed rotation range and to increase the nozzle area in the high speed rotation range. The spring 7 is used to press the stopper 6 in the direction that the lift width becomes smaller, and the piston 2 is used to press the stopper 6 in the direction that the lift width becomes larger, and the feed pressure of the feed pump is applied in the direction that pushes the piston 2. In the past, the nozzle area was determined to achieve optimal combustion at the highest rotation speed, so in the low speed rotation range, the nozzle area was too wide, causing aftershock, blue-white smoke, and the generation of hydrocarbons. However, with this invention, these combustion problems can be solved by automatically adjusting the nozzle area to match the low speed range, and by using the feed pressure and piston of the feed pump for this purpose, It was easily accomplished with a simple configuration.
第１図は本考案の燃料噴射弁の断面図と燃料回路図、第
２図はノズルバルブを高速回転時にリフト幅いっばいに
下降させた状態の図面、第３図は低速回転時にリフト幅
を制限し、噴口面積を狭くした状態の図面、第４図はノ
ズルバルブの噴口部側面図、第５図はノズルリフトｈ１
噴口面積Ａ１フィードポンプＰの関係を示す図面、第６
図は本考案の燃料噴射弁の平面図、第７図は噴射角度を
示す燃料噴射弁の側面断面図、第８図は同じく側面図で
ある。
１３、 Ｂ’、 Ｂ″、Ｂ″・・・・・・燃料噴射弁、
１・・・・・・ノズル本体、２・・・・・・ピストン、
３・・・・・・ノズルバルブ、４・・・・・・ケースナ
ツト、５・・・・・・ノズルボディー、６・・・・・・
ストッパー、７・・・・・・リフト制限用スプリング、
訃・・・・・ノズルスプリング、９・・・・・・係合体
、１０・・・・・・燃料噴射ポンプ、１１・・・・・・
フィードポンプ。Figure 1 is a sectional view and fuel circuit diagram of the fuel injector of the present invention, Figure 2 is a drawing of the nozzle valve with the lift width lowered to the fullest extent during high speed rotation, and Figure 3 is a diagram of the nozzle valve with the lift width lowered during low speed rotation. Figure 4 is a side view of the nozzle valve nozzle area, and Figure 5 is the nozzle lift h1.
Drawing showing the relationship between the nozzle area A1 and the feed pump P, No. 6
The figure is a plan view of the fuel injection valve of the present invention, FIG. 7 is a side sectional view of the fuel injection valve showing the injection angle, and FIG. 8 is a side view. 13. B', B'', B''...Fuel injection valve,
1... Nozzle body, 2... Piston,
3... Nozzle valve, 4... Case nut, 5... Nozzle body, 6...
Stopper, 7...lift limiting spring,
Death: Nozzle spring, 9: Engagement body, 10: Fuel injection pump, 11:
feed pump.
Claims (1)
面積を小とし、高速回転域では噴口面積を大とすべく、
ノズルバルブ３のリフト幅を決めるストッパー６をリフ
ト幅が小となる方向にスプリング７にて押圧し、逆にス
トッパー６をリフト幅が大となる方向にピストン２にて
押圧し、ピストン２を押す方向にフィードポンプのフィ
ード圧を加えたことを特徴とする燃料噴射弁。The lift width of the nozzle valve is controlled to reduce the nozzle area in the low speed rotation range and to increase the nozzle area in the high speed rotation range.
The stopper 6, which determines the lift width of the nozzle valve 3, is pushed by the spring 7 in the direction where the lift width becomes smaller, and conversely, the stopper 6 is pushed by the piston 2 in the direction where the lift width becomes larger, thereby pushing the piston 2. A fuel injection valve characterized by applying feed pressure from a feed pump in the direction.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8325480U JPS6014932Y2 (en) | 1980-06-13 | 1980-06-13 | fuel injection valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP8325480U JPS6014932Y2 (en) | 1980-06-13 | 1980-06-13 | fuel injection valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS578363U JPS578363U (en) | 1982-01-16 |
| JPS6014932Y2 true JPS6014932Y2 (en) | 1985-05-11 |
Family
ID=29445582
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP8325480U Expired JPS6014932Y2 (en) | 1980-06-13 | 1980-06-13 | fuel injection valve |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS6014932Y2 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS62296735A (en) * | 1986-06-13 | 1987-12-24 | Agency Of Ind Science & Technol | Cooling device for motor |
-
1980
- 1980-06-13 JP JP8325480U patent/JPS6014932Y2/en not_active Expired
Also Published As
| Publication number | Publication date |
|---|---|
| JPS578363U (en) | 1982-01-16 |
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