JP2017180449A - Oil tank piston of fuel injection pump - Google Patents

Oil tank piston of fuel injection pump Download PDF

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Publication number
JP2017180449A
JP2017180449A JP2017004743A JP2017004743A JP2017180449A JP 2017180449 A JP2017180449 A JP 2017180449A JP 2017004743 A JP2017004743 A JP 2017004743A JP 2017004743 A JP2017004743 A JP 2017004743A JP 2017180449 A JP2017180449 A JP 2017180449A
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Prior art keywords
piston
fuel injection
injection pump
oil tank
cylinder
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JP2017180449A5 (en
JP6497594B2 (en
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チュル リ，スー
Soo Chul Lee
チュル リ，スー
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HANBIT PRECISION Co Ltd
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HANBIT PRECISION Co Ltd
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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
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/06—Pumps peculiar thereto
    • F02M45/066—Having specially arranged spill port and spill contour on the piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • 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
    • F02M59/025—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 a single 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
    • F02M59/02—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
    • 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
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • 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
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/24—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke
    • F02M59/26—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders
    • F02M59/265—Varying fuel delivery in quantity or timing with constant-length-stroke pistons having variable effective portion of stroke caused by movements of pistons relative to their cylinders characterised by the arrangement or form of spill port of spill contour on the 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
    • F02M59/44—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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0408—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/053—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement with actuating or actuated elements at the inner ends of the cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
    • F04B11/0075—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons connected in series
    • F04B11/0083—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons connected in series the pistons having different cross-sections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0091—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using a special shape of fluid pass, e.g. throttles, ducts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/18—Lubricating
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/04—Fuel-injection apparatus having means for avoiding effect of cavitation, e.g. erosion

Abstract

PROBLEM TO BE SOLVED: To provide an oil tank piston of a fuel injection pump capable of eliminating increased fatigue and wear rate and fastening phenomenon that may occur due to a reciprocating motion of a piston of a fuel injection pump for four-strokes for a long period of time and a high pressure fuel injection characteristics.SOLUTION: An oil tank piston of a fuel injection pump of this invention installed in a cylinder to compress fuel while performing a reciprocating motion in a vertical direction shows a feature that it comprises a control edge formed at an upper stage of the piston to enable a fuel injection amount to be adjusted; a piston body arranged at a lower part of the control edge to perform a vertical reciprocating motion while being contacted with the cylinder; a neck part arranged at the middle part of the piston body and having its diameter gradually decreased; and several open holes formed at the neck part, passing through the piston in a direction crossing with the shaft and formed in parallel with it along an axial direction.SELECTED DRAWING: Figure 2

Description

本発明は、燃料噴射ポンプのオイルタンクピストンに関する。さらに詳しくは、船舶用エンジンに燃料を供給することのできる燃料噴射ポンプのオイルタンクピストンに関する。 The present invention relates to an oil tank piston of a fuel injection pump. More specifically, the present invention relates to an oil tank piston of a fuel injection pump that can supply fuel to a marine engine.

ディーゼルを燃料として用いるエンジンにおける燃料噴射ポンプは、燃料を高圧で圧縮して燃焼室に設けられたインジェクター（Ｉｎｊｅｃｔｏｒ）に送出するものであり、燃料を実質的に圧縮して送出する噴射装置は、プランジャー及びバレルからなる。 A fuel injection pump in an engine using diesel as a fuel compresses fuel at a high pressure and sends it to an injector provided in a combustion chamber. An injection device that substantially compresses fuel and sends it out, It consists of a plunger and a barrel.

この種の噴射装置は、ピストンの役割を果たすプランジャー（Ｐｌｕｎｇｅｒ）がシリンダーの役割を果たすバレル（Ｂａｒｒｅｌ）の内部において往復運動することにより燃料を圧縮して送ることになる。 In this type of injection device, a plunger acting as a piston reciprocates inside a barrel acting as a cylinder, and the fuel is compressed and sent.

図１は、従来の技術による燃料噴射ポンプの噴射装置を示す断面図である。 FIG. 1 is a cross-sectional view showing a conventional fuel injection pump injection device.

図１を参照すると、従来の技術による燃料噴射ポンプの噴射装置１は、燃料を圧縮又は圧縮解除するためのピストン１０及び前記ピストン１０が係合されるバレル２０を備える。 Referring to FIG. 1, an injection device 1 of a conventional fuel injection pump includes a piston 10 for compressing or decompressing fuel and a barrel 20 to which the piston 10 is engaged.

前記ピストン１０は、前記バレル２０の内部に上下方向に往復運動自在に係合される。前記ピストン１０は、カム軸のカムにより往復駆動される。前記ピストン１０には、ピストン室２１と連通する逃げ溝（Ｒｅｌｉｅｆ ｇｒｏｏｖｅ）（図示せず）が形成され、逃げ溝と連通するコントロールリード（Ｃｏｎｔｒｏｌ Ｌｅａｄ）（図示せず）が形成されている。 The piston 10 is engaged with the barrel 20 so as to be reciprocally movable in the vertical direction. The piston 10 is reciprocated by a cam of a cam shaft. The piston 10 is formed with a relief groove (not shown) communicating with the piston chamber 21 and a control lead (not shown) communicating with the relief groove.

前記バレル２０は、内部及び外部にそれぞれピストン室２１及び排油室２２が形成され、前記ピストン室２１と前記排油室２２を連通させるカットオフ孔２３が形成されている。これにより、前記ピストン１０が上昇してそのの外周面が前記カットオフ孔２３を閉じるときから燃料の圧縮が始まり、所定の圧力に達すると、前記ピストン室２１の上部のデリバリーバルブ（Ｄｅｌｉｖｅｒｙ ｖａｌｖｅ）（図示せず）が開かれて圧縮される燃料がインジェクターを介して噴射される。 In the barrel 20, a piston chamber 21 and an oil discharge chamber 22 are formed inside and outside, respectively, and a cut-off hole 23 that connects the piston chamber 21 and the oil discharge chamber 22 is formed. As a result, the compression of the fuel starts when the piston 10 rises and the outer peripheral surface thereof closes the cut-off hole 23. When a predetermined pressure is reached, the delivery valve (Delivery valve) at the top of the piston chamber 21 is reached. (Not shown) is opened and fuel to be compressed is injected through the injector.

ここで、従来の技術による燃料噴射ポンプの噴射装置１は、前記ピストン１０が下側から上側に向かって移動する場合、前記ピストン室２１の圧力が上昇することにより、内部の燃料が圧縮される。この状態で、前記ピストン１０が前記カットオフ孔２３を閉じた状態で上側から下側に向かって移動することにより、前記ピストン室２１の内部の燃料が膨張して低圧が形成される。この状態で、前記ピストン１０がさらに下降することにより、前記カットオフ孔２３が開かれると、前記排油室２２の燃料が急速に前記ピストン室２１に移動してキャビテーション（Ｃａｖｉｔａｔｉｏｎ）現象が起こる。 Here, in the injection device 1 of the conventional fuel injection pump, when the piston 10 moves from the lower side toward the upper side, the pressure in the piston chamber 21 increases, and the internal fuel is compressed. . In this state, when the piston 10 moves from the upper side to the lower side with the cut-off hole 23 closed, the fuel inside the piston chamber 21 expands to form a low pressure. In this state, when the piston 10 further descends and the cut-off hole 23 is opened, the fuel in the oil discharge chamber 22 rapidly moves to the piston chamber 21 and a cavitation phenomenon occurs.

これにより、従来の技術による燃料噴射ポンプの噴射装置１は、燃料が圧縮された状態で前記ピストン１０が上側から下側に向かって移動することにより、前記ピストン１０の上側を基準として前記ピストン室２１と前記排油室２２との間に圧力差が生じる。このため、従来の技術による燃料噴射ポンプの噴射装置１は、前記ピストン室２１と前記排油室２２との間の圧力差により起こるキャビテーション現象により前記ピストン１０の外周面、前記バレル２０の内面及び前記カットオフ孔２３の表面が浸食される。 Thereby, the injection device 1 of the fuel injection pump according to the conventional technique moves the piston 10 from the upper side to the lower side in a state where the fuel is compressed, so that the piston chamber is based on the upper side of the piston 10. A pressure difference is generated between the oil discharge chamber 22 and the oil discharge chamber 22. For this reason, the fuel injection pump injection device 1 according to the prior art has an outer peripheral surface of the piston 10, an inner surface of the barrel 20 and a cavitation phenomenon caused by a pressure difference between the piston chamber 21 and the oil discharge chamber 22. The surface of the cut-off hole 23 is eroded.

また、従来の技術による燃料噴射ポンプの噴射装置１は、キャビテーション現象により浸食された空間に圧力が漏れることにより、前記ピストン室２１の内部の圧力が低下する。これにより、従来の技術による燃料噴射ポンプの噴射装置１は、燃料を噴射する作業の効率性が低下するだけではなく、キャビテーション現象により前記バレル２０及び前記カットオフ孔２２が浸食されることにより、噴射装置の寿命が短くなるという問題がある。 Further, in the injection device 1 of the fuel injection pump according to the conventional technique, the pressure inside the piston chamber 21 is reduced by the pressure leaking into the space eroded by the cavitation phenomenon. Thereby, the injection device 1 of the fuel injection pump according to the conventional technique not only reduces the efficiency of the operation of injecting the fuel, but also erodes the barrel 20 and the cut-off hole 22 due to the cavitation phenomenon, There exists a problem that the lifetime of an injection device becomes short.

これを解消するために、大韓民国公開特許公報第１０−２０１５−００１０８７７号には、プランジャー内に流路を形成し、プランジャーの上側に流路を開閉する弁を設けることにより、プランジャー室の上側と下側との間の圧力差を減少させている。しかしながら、プランジャーに別途の流路を形成し、その流路を開閉する弁を設けることは構造を過度に複雑化させ、製造及び組立て工程にかかる時間及びコストを大幅に増大させてしまうという欠点がある。 In order to solve this problem, Korean Patent Publication No. 10-2015-0010877 discloses that a plunger chamber is provided by forming a flow path in the plunger and providing a valve for opening and closing the flow path above the plunger. The pressure difference between the upper side and the lower side is reduced. However, forming a separate flow path in the plunger and providing a valve that opens and closes the flow path makes the structure excessively complex and greatly increases the time and cost of the manufacturing and assembly process. There is.

大韓民国公開特許公報第１０−２０１５−００１０８７７号Korean Published Patent Publication No. 10-2015-0010877

本発明は、４行程用燃料噴射ポンプのピストンの長時間に亘っての往復運動及び高圧の燃料噴射特性に起因して発生し得る疲労と磨耗率の増加及び固着現象を解消するためのものである。 The present invention is intended to eliminate the increase in fatigue and wear rate and the sticking phenomenon that may occur due to the long-time reciprocation of the piston of the fuel injection pump for four strokes and the high-pressure fuel injection characteristics. is there.

本発明は、ピストンに簡単な加工をさらに行うことにより、簡単な構造でピストンの周りの圧力や温度を均一にすることができ、摩擦係数を減らして部品の寿命を向上させ、噴射効率を向上させることのできる燃料噴射ポンプのオイルタンクピストンを提供することを目的とする。 The present invention further simplifies the processing of the piston to make the pressure and temperature around the piston uniform with a simple structure, reduce the friction coefficient, improve the service life of the parts, and improve the injection efficiency. It is an object to provide an oil tank piston of a fuel injection pump that can be made to operate.

本発明は、シリンダー内に設けられて上下往復運動しながら燃料を圧縮する燃料噴射ポンプのピストンにおいて、ピストンの上段に形成され、燃料の噴射量が調節可能なコントロールエッジと、コントロールエッジの下部に配設され、シリンダーと接触しながら上下往復運動するピストンボディと、ピストンボディの両側から中央に進むにつれて直径が緩やかに小さくなるネック部と、ネック部に形成され、ピストンを軸と直交する方向に貫通し、複数が軸方向に沿って平行に形成される貫通孔と、を備える燃料噴射ポンプのオイルタンクピストンを提供する。 The present invention provides a piston of a fuel injection pump that is provided in a cylinder and compresses fuel while reciprocating up and down, and is formed at an upper stage of the piston and has a control edge with adjustable fuel injection amount, and a lower part of the control edge. A piston body that is arranged and reciprocates up and down while in contact with the cylinder, a neck portion that gradually decreases in diameter from the both sides of the piston body toward the center, and a neck portion that is formed in the direction perpendicular to the axis An oil tank piston of a fuel injection pump comprising: a through hole penetrating through and formed in parallel with each other along an axial direction.

また、本発明の他の態様によれば、貫通孔は、一方の側の直径は大きく、他方の側に進むにつれて直径が次第に小さくなるテーパー孔であることを特徴とする燃料噴射ポンプのオイルタンクピストンを提供する。 According to another aspect of the present invention, the through hole is a tapered hole having a large diameter on one side and gradually decreasing in diameter as it proceeds to the other side. Provide a piston.

さらに、本発明のさらに他の態様によれば、貫通孔は、テーパー孔の直径がさらに大きい側とテーパー孔の直径がさらに小さい側の方向が交互に形成されることを特徴とする燃料噴射ポンプのオイルタンクピストンを提供する。 Furthermore, according to still another aspect of the present invention, the fuel injection pump is characterized in that the through holes are alternately formed in directions in which the diameter of the tapered hole is larger and the direction of the smaller diameter of the tapered hole is smaller. Provides oil tank pistons.

本発明に係る燃料噴射ポンプのオイルタンクピストンは、ピストンに簡単な構造を追加してシリンダーの内部においてピストンの周りの温度及び圧力を均一にすることにより、耐摩耗性を向上させてピストン及びシリンダーの固着現象を防ぐことができる。 The oil tank piston of the fuel injection pump according to the present invention improves the wear resistance by adding a simple structure to the piston to make the temperature and pressure around the piston uniform inside the cylinder, thereby improving the wear resistance. The sticking phenomenon can be prevented.

また、本発明が提供する燃料噴射ポンプのオイルタンクピストンは、中央にネック部を形成してシリンダーと接触しない領域を形成することにより、摩擦係数を減らして噴射効率を向上させ、部品の寿命も向上させることができる。 In addition, the oil tank piston of the fuel injection pump provided by the present invention forms a neck portion in the center and forms an area that does not come into contact with the cylinder, thereby reducing the coefficient of friction and improving the injection efficiency, and the life of the parts. Can be improved.

さらに、本発明が提供する燃料噴射ポンプのオイルタンクピストンは、シリンダー内の上下側間の圧力差を減らしてキャビテーション現象の発生を防ぐことができる。 Furthermore, the oil tank piston of the fuel injection pump provided by the present invention can reduce the pressure difference between the upper and lower sides in the cylinder and prevent the occurrence of the cavitation phenomenon.

従来の技術による燃料噴射ポンプの噴射装置を示す断面図である。It is sectional drawing which shows the injection apparatus of the fuel injection pump by a prior art. 本発明の一実施形態による燃料噴射ポンプのオイルタンクピストンを示す図である。It is a figure which shows the oil tank piston of the fuel injection pump by one Embodiment of this invention. 従来の技術による燃料噴射ポンプを用いてノズル噴射テストを行った写真である。It is the photograph which performed the nozzle injection test using the fuel injection pump by a prior art. 本発明の一実施形態によるオイルタンクピストンを備える燃料噴射ポンプを用いてノズル噴射テストを行った写真である。It is the photograph which performed the nozzle injection test using the fuel injection pump provided with the oil tank piston by one Embodiment of this invention.

以下、添付図面に基づいて本発明について詳述する。 Hereinafter, the present invention will be described in detail with reference to the accompanying drawings.

図２は、本発明の一実施形態による燃料噴射ポンプのオイルタンクピストンを示す図である。 FIG. 2 is a view showing an oil tank piston of a fuel injection pump according to an embodiment of the present invention.

本発明の一実施形態による燃料噴射ポンプのオイルタンクピストン１００は、上部から順番に、最上段にシリンダーのカットオフ孔（図示せず）と遭遇する時期を調節することにより噴射量が調節可能なコントロールエッジ１１０が配設され、その下にシリンダー（図示せず）の内周面と接した状態で上下運動しながら燃料を圧縮するピストンボディ１２０が配設され、最下段にカム（図示せず）と接していてカム（図示せず）から動力が伝わるタベット１３０が配設される。 The oil tank piston 100 of the fuel injection pump according to the embodiment of the present invention can adjust the injection amount by adjusting the timing when the oil tank piston 100 encounters a cutoff hole (not shown) of the cylinder at the top in order from the top. A control edge 110 is disposed, and a piston body 120 that compresses fuel while moving up and down in contact with an inner peripheral surface of a cylinder (not shown) is disposed below the control edge 110, and a cam (not shown) is disposed at the bottom. ) And a tabbed 130 to which power is transmitted from a cam (not shown).

コントロールエッジ１１０は、オイルタンクピストン１００の円周面に沿って所定の長さに見合う分だけ螺旋状に傾いた面を有することにより、シリンダーのカットオフ孔（図示せず）と遭遇する時期を調節することができて噴射量を調節することができる。 The control edge 110 has a spirally inclined surface corresponding to a predetermined length along the circumferential surface of the oil tank piston 100, so that a timing when the control edge 110 encounters a cutoff hole (not shown) of the cylinder can be detected. The injection amount can be adjusted.

ピストンボディ１２０は、シリンダー（図示せず）と接触したままで上下運動することにより、シリンダー内に流入した燃料を圧縮することができる。このとき、ピストンボディ１２０の中央に凹状に勾配を形成することにより、シリンダーと接触しない領域、すなわち、ネック部１２６が形成される。すなわち、ピストンボディ１２０は、シリンダー（図示せず）と接触する上段１２２と下段１２４、シリンダーと接触しない中段のネック部１２６からなる。 The piston body 120 can compress fuel flowing into the cylinder by moving up and down while being in contact with a cylinder (not shown). At this time, by forming a concave gradient in the center of the piston body 120, a region not in contact with the cylinder, that is, the neck portion 126 is formed. That is, the piston body 120 includes an upper stage 122 and a lower stage 124 that come into contact with a cylinder (not shown), and a middle neck part 126 that does not come into contact with the cylinder.

たとえ中段のネック部１２６がシリンダー（図示せず）と接触しないとしても、上段１２２と下段１２４がシリンダー（図示せず）と接触しているため、燃料を圧縮するのに影響しない。また、シリンダー（図示せず）と接触する面積が狭まることにより、全体的な摩擦係数を減らすことができて噴射効率を向上させ、部品の寿命を向上させることができる。なお、ネック部１２６には潤滑油が充填されてピストンボディ１２０とシリンダー（図示せず）との間の潤滑及び冷却の役割を果たしてもよい。 Even if the middle neck portion 126 is not in contact with a cylinder (not shown), the upper stage 122 and the lower stage 124 are in contact with the cylinder (not shown), so that the compression of the fuel is not affected. Further, since the area in contact with the cylinder (not shown) is reduced, the overall friction coefficient can be reduced, the injection efficiency can be improved, and the life of the parts can be improved. The neck portion 126 may be filled with lubricating oil to serve as a lubrication and cooling between the piston body 120 and a cylinder (not shown).

また、中段のネック部１２６には、ピストンボディ１２０を貫通する貫通孔１２８、１２９が形成される。貫通孔１２８、１２９はピストン１００の軸を通過し、ピストン１００の軸と直交する。また、複数の貫通孔１２８、１２９が軸に沿って、すなわち、上下に配置されることにより、ピストンボディ１２０の上下部間の圧力差が生じたときに上下に配置された貫通孔１２８、１２９に沿ってネック部１２６の潤滑油が流動することにより、キャビテーション現象を防ぐことができる。 Further, through holes 128 and 129 penetrating the piston body 120 are formed in the middle neck portion 126. The through holes 128 and 129 pass through the axis of the piston 100 and are orthogonal to the axis of the piston 100. Further, when the plurality of through holes 128 and 129 are arranged along the axis, that is, vertically, when a pressure difference between the upper and lower portions of the piston body 120 is generated, the through holes 128 and 129 which are vertically arranged are formed. As the lubricating oil in the neck portion 126 flows along the cavitation, the cavitation phenomenon can be prevented.

一方、貫通孔１２８、１２９の一方の端は直径が大きくて他方の端は直径が小さく、直径が次第に減少するテーパー孔である。貫通孔１２８、１２９がテーパー孔であるとき、ネック部１２６に充填された潤滑油は貫通孔１２８、１２９の直径の大きい側に潤滑油が流入して直径の小さい側に排出される。このため、複数の貫通孔１２８、１２９は互いに平行に形成され、直径の大きい側及び直径の小さい側が交互に同じ側に配置されることが好ましい。このように直径の大きい側及び直径の小さい側が交互に形成されると、ネック部１２６とシリンダー（図示せず）との間の隙間における潤滑油の円滑な流動が行われ、これにより、ピストンの冷却、潤滑がなお一層効率よく行われる。 On the other hand, one end of each of the through holes 128 and 129 is a tapered hole having a large diameter and the other end having a small diameter, and the diameter gradually decreases. When the through holes 128 and 129 are tapered holes, the lubricating oil filled in the neck portion 126 flows into the through holes 128 and 129 having a larger diameter and is discharged to the smaller diameter side. For this reason, it is preferable that the plurality of through holes 128 and 129 are formed in parallel with each other, and the side having the larger diameter and the side having the smaller diameter are alternately arranged on the same side. When the large-diameter side and the small-diameter side are alternately formed in this way, the lubricating oil smoothly flows in the gap between the neck portion 126 and the cylinder (not shown). Cooling and lubrication are performed even more efficiently.

したがって、ピストンの摩擦熱及びキャビテーション現象による固着を防ぐことができるというメリットがある。また、上下に配置された貫通孔１２８、１２９を介して潤滑油が流通可能になるので、シリンダーの内部の上下側の圧力が均一に保たれてキャビテーション現象の発生が防がれる。なお、シリンダーの内部の温度及び圧力が均一に保たれるので、耐摩耗性が向上する。 Therefore, there is an advantage that the piston can be prevented from sticking due to frictional heat and cavitation. Further, since the lubricating oil can flow through the upper and lower through holes 128 and 129, the pressure on the upper and lower sides inside the cylinder is kept uniform, and the occurrence of the cavitation phenomenon is prevented. In addition, since the temperature and pressure inside the cylinder are kept uniform, the wear resistance is improved.

図３は、従来の技術による燃料噴射ポンプを用いてノズル噴射テストを行った写真であり、図４は、本発明の一実施形態によるオイルタンクピストンを備える燃料噴射ポンプを用いてノズル噴射テストを行った写真である。 FIG. 3 is a photograph of a nozzle injection test using a conventional fuel injection pump, and FIG. 4 is a nozzle injection test using a fuel injection pump having an oil tank piston according to an embodiment of the present invention. It is the photograph which went.

テスト結果を比較すると、従来の燃料噴射ポンプに比べて、本発明の一実施形態によるピストンを備える燃料噴射ポンプを用いた場合、ノズルの噴射性能が格段に向上することを確認することができる。
Comparing the test results, it can be confirmed that the injection performance of the nozzle is remarkably improved when the fuel injection pump including the piston according to the embodiment of the present invention is used as compared with the conventional fuel injection pump.

Claims (3)

シリンダー内に設けられて上下往復運動しながら燃料を圧縮する燃料噴射ポンプのピストンにおいて、
ピストンの上段に形成され、燃料の噴射量が調節可能なコントロールエッジと、
コントロールエッジの下部に配設され、シリンダーと接触しながら上下往復運動するピストンボディと、
ピストンボディの両側から中央に進むにつれて直径が緩やかに小さくなるネック部と、
ネック部に形成され、ピストンを軸と直交する方向に貫通し、複数が軸方向に沿って平行に形成される貫通孔と、
を備える燃料噴射ポンプのオイルタンクピストン。 In the piston of the fuel injection pump that is provided in the cylinder and compresses the fuel while reciprocating up and down,
A control edge that is formed in the upper stage of the piston and that can adjust the fuel injection amount,
A piston body that is disposed below the control edge and reciprocates up and down while contacting the cylinder;
A neck that gradually decreases in diameter as it goes from both sides of the piston body to the center;
A through hole formed in the neck portion, penetrating the piston in a direction orthogonal to the axis, and a plurality of the holes formed in parallel along the axial direction;
An oil tank piston for a fuel injection pump. 貫通孔は、一方の側の直径は大きく、他方の側に進むにつれて直径が次第に小さくなるテーパー孔であることを特徴とする請求項１に記載の燃料噴射ポンプのオイルタンクピストン。 2. The oil tank piston of a fuel injection pump according to claim 1, wherein the through hole is a tapered hole having a large diameter on one side and gradually decreasing in diameter toward the other side. 貫通孔は、テーパー孔の直径がさらに大きい側とテーパー孔の直径がさらに小さい側の方向が交互に形成されることを特徴とする請求項２に記載の燃料噴射ポンプのオイルタンクピストン。 3. The oil tank piston of a fuel injection pump according to claim 2, wherein the through holes are alternately formed in a direction in which the diameter of the tapered hole is larger and the direction in which the diameter of the tapered hole is smaller.
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