JP4534881B2 - Regulating valve - Google Patents

Regulating valve Download PDF

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Publication number
JP4534881B2
JP4534881B2 JP2005193767A JP2005193767A JP4534881B2 JP 4534881 B2 JP4534881 B2 JP 4534881B2 JP 2005193767 A JP2005193767 A JP 2005193767A JP 2005193767 A JP2005193767 A JP 2005193767A JP 4534881 B2 JP4534881 B2 JP 4534881B2
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Prior art keywords
piston
hole
opening area
fuel
breathing hole
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Expired - Fee Related
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JP2005193767A
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JP2007009840A (en
Inventor
宏行 島居
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Denso Corp
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Denso Corp
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Priority to JP2005193767A priority Critical patent/JP4534881B2/en
Priority to DE200610000317 priority patent/DE102006000317B4/en
Publication of JP2007009840A publication Critical patent/JP2007009840A/en
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Publication of JP4534881B2 publication Critical patent/JP4534881B2/en
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16KVALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/06Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for adjusting the opening pressure
    • F16K17/065Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for adjusting the opening pressure with differential piston
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0011Constructional details; Manufacturing or assembly of elements of fuel systems; Materials therefor
    • F02M37/0023Valves in the fuel supply and return system
    • F02M37/0029Pressure regulator in the low pressure fuel system
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/0047Layout or arrangement of systems for feeding fuel
    • F02M37/0052Details on the fuel return circuit; Arrangement of pressure regulators
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0001Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012Valves
    • F02M63/0031Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012Valves
    • F02M63/0031Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/005Pressure relief valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012Valves
    • F02M63/0031Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0056Throttling valves, e.g. having variable opening positions throttling the flow
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16KVALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/08Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for providing a large discharge passage
    • F16K17/082Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for providing a large discharge passage with piston

Description

本発明は、燃料圧力を調圧するためのレギュレートバルブに関する。   The present invention relates to a regulating valve for regulating fuel pressure.

従来、ディーゼル機関等の蓄圧式燃料噴射システムに用いられる燃料噴射ポンプが公知である(特許文献1参照)。この燃料噴射ポンプには、燃料タンクから燃料を汲み上げるフィードポンプの吐出圧(フィードポンプより吐出される燃料圧力)を調圧するためのレギュレートバルブが用いられている。
このレギュレートバルブは、例えば、図5に示す様に、一端側に流入口100が開口し、側面にリリーフ孔110と息抜き孔120とが形成された筒状のバルブボディ130と、このバルブボディ130の内部に往復動可能に挿入されるピストン140と、このピストン140の背後(反流入口側)に配設されるスプリング150等より構成され、リリーフ孔110に対するピストン140の開弁位置に応じて、フィードポンプの吐出圧を所定の値に調圧している。
Conventionally, a fuel injection pump used in a pressure accumulation fuel injection system such as a diesel engine is known (see Patent Document 1). This fuel injection pump uses a regulating valve for regulating the discharge pressure of the feed pump that pumps fuel from the fuel tank (fuel pressure discharged from the feed pump).
For example, as shown in FIG. 5, the regulated valve includes a cylindrical valve body 130 having an inlet 100 opened on one end side and a relief hole 110 and a breathing hole 120 formed on a side surface, and the valve body The piston 140 is inserted into the interior of the piston 130 so as to be able to reciprocate, and a spring 150 or the like disposed behind the piston 140 (on the counterflow inlet side), depending on the valve opening position of the piston 140 relative to the relief hole 110. Thus, the discharge pressure of the feed pump is regulated to a predetermined value.

なお、図5(a)はレギュレートバルブの断面図、図5(b)はバルブボディ130の展開図であり、同図(b)には、ピストン140がリリーフ孔110を開き始める開弁位置でのピストン後端面の位置(a)、ピストン140がリリーフ孔110を全開する全開位置でのピストン後端面の位置(b)、スプリング150の許容ストローク分だけスプリング150が圧縮される位置(以後、ピストン140の最大リフト位置と呼ぶ)までピストン140が移動した時のピストン後端面の位置(c)を示している。スプリング150の許容ストロークとは、スプリング150の使用範囲を表すものであり、通常の使用状態において、許容ストローク以上に圧縮されることはない。
特開2000−240531号公報
5A is a sectional view of the regulating valve, FIG. 5B is a development view of the valve body 130, and FIG. 5B shows the valve opening position at which the piston 140 starts to open the relief hole 110. The position of the piston rear end surface at (a), the position of the piston rear end surface at the fully open position where the piston 140 fully opens the relief hole 110 (b), the position where the spring 150 is compressed by the allowable stroke of the spring 150 (hereinafter, The position (c) of the piston rear end surface when the piston 140 moves to the maximum lift position of the piston 140 is shown. The allowable stroke of the spring 150 represents the use range of the spring 150, and is not compressed more than the allowable stroke in a normal use state.
JP 2000-240531 A

ところが、上記のレギュレートバルブは、フィードポンプの入口で異常に過大な負圧が発生した場合、あるいはフィードポンプに吸入される燃料にエアーが混入した場合等に、フィードポンプの吐出圧が不安定になるため、ピストン140が大きな振幅で往復運動を繰り返す。この時、ピストン140のリフト量(スプリング150を圧縮する方向への移動量)が過大になると、スプリング150が許容ストローク以上に全圧縮(密着)して損傷する原因となる。また、ピストン140との間にスプリング150を支持しているプラグ160がバルブボディ130から抜け落ちる原因ともなる。   However, with the above-mentioned regulating valve, the discharge pressure of the feed pump is unstable when an abnormally excessive negative pressure is generated at the inlet of the feed pump or when air is mixed into the fuel sucked into the feed pump. Therefore, the piston 140 repeats reciprocating motion with a large amplitude. At this time, if the lift amount of the piston 140 (the amount of movement in the direction in which the spring 150 is compressed) becomes excessive, the spring 150 is fully compressed (adhered) to the allowable stroke or more and may be damaged. In addition, the plug 160 supporting the spring 150 between the piston 140 and the piston 140 may come off from the valve body 130.

但し、レギュレートバルブには、ピストン140の背後にダンパ室170が形成され、このダンパ室170が息抜き孔120を通じてフィードポンプの入口に接続されている(図2参照)。これにより、ダンパ室170に充填された燃料のダンパ効果によってピストン140の過大リフトを防止する機能を持たせているが、現状では、必ずしも息抜き孔120の仕様(孔の大きさ、位置等)が適切であるとは言えず、現状では十分なダンパ効果が得られていない。なお、ダンパ効果を高めるために息抜き孔120の開口面積を小さくすることも考えられるが、その場合、リリーフ孔110を開閉するピストン140の動きが抑制されるため、レギュレートバルブの応答性が悪化する問題が生じる。   However, in the regulating valve, a damper chamber 170 is formed behind the piston 140, and this damper chamber 170 is connected to the inlet of the feed pump through the breathing hole 120 (see FIG. 2). As a result, the function of preventing the piston 140 from being overlifted by the damper effect of the fuel filled in the damper chamber 170 is provided. However, at present, the specifications of the breathing hole 120 (the size and position of the hole) are not necessarily limited. It cannot be said that it is appropriate, and a sufficient damper effect is not obtained at present. Although it is conceivable to reduce the opening area of the breathing hole 120 in order to enhance the damper effect, in this case, the movement of the piston 140 that opens and closes the relief hole 110 is suppressed, so that the responsiveness of the regulating valve deteriorates. Problems arise.

本発明は、上記事情に基づいて成されたもので、その目的は、応答性を損なうことなく、ピストンの制動能力を高めることにより、ピストンの過大リフトを防止できるレギュレートバルブを提供することにある。   The present invention has been made based on the above circumstances, and an object of the present invention is to provide a regulating valve capable of preventing an excessive lift of the piston by increasing the braking performance of the piston without impairing the responsiveness. is there.

(請求項1の発明)
本発明のレギュレートバルブは、ピストンがスプリングを圧縮する方向へ移動する際に、ピストンがリリーフ孔を全開するまでは、ピストンの移動に伴い息抜き孔の開口面積が減少し、ピストンの移動量に対して息抜き孔の開口面積が減少する割合を示す開口面積特性の傾きが小さく設定され、ピストンがリリーフ孔を全開した後は、開口面積特性の傾きが大きく設定されるように、息抜き孔は、開口面積特性の傾きが小さくなる様に形成された第1の息抜き孔と、開口面積特性の傾きが大きくなる様に形成された第2の息抜き孔とを有し、第1の息抜き孔と第2の息抜き孔とが独立して設けられていることを特徴とする。
息抜き孔の開口面積特性は、その傾きが大きくなる程、ピストンの移動量(スプリングを圧縮する方向への移動量)に対して息抜き孔の開口面積が減少する割合が大きくなることを示している。
(Invention of Claim 1)
In the regulating valve of the present invention, when the piston moves in the direction of compressing the spring, the opening area of the breathing hole decreases with the movement of the piston until the piston fully opens the relief hole. set inclination is smaller opening area characteristic indicating a rate of opening area of the breather hole is decreased for, after the piston is fully opened the relief hole, the so that the inclination of the opening area characteristics are set larger, breather hole, The first breathing hole formed so that the inclination of the opening area characteristic becomes small and the second breathing hole formed so that the inclination of the opening area characteristic becomes large. The two breathing holes are provided independently .
The opening area characteristic of the breathing hole shows that the ratio of the opening area of the breathing hole decreasing with respect to the moving amount of the piston (moving amount in the direction of compressing the spring) increases as the inclination increases. .

つまり、開口面積特性の傾きが大きくなる程、ピストンが少し移動するだけで、息抜き孔の開口面積が大きく減少することを表している。従って、開口面積特性の傾きが小さい場合と大きい場合とを比較すると、小さい場合より大きい場合の方が、ダンパ室に充填された燃料によるダンパ効果が大きくなるため、ピストンの制動能力が高くなる。これにより、息抜き孔の開口面積特性の傾きが小さく設定される領域、つまりピストンがリリーフ孔を全開するまでは、ピストンの制動能力を低く抑えることにより、レギュレートバルブの応答性を確保できる。また、息抜き孔の開口面積特性の傾きが大きく設定される領域、つまりピストンがリリーフ孔を全開した後は、ピストンの制動能力を高くすることで、ピストンの過大リフトを防止できる。   That is, as the inclination of the opening area characteristic increases, the opening area of the breathing hole is greatly reduced by only a slight movement of the piston. Therefore, comparing the case where the slope of the opening area characteristic is small and the case where the inclination is large, the damper effect by the fuel filled in the damper chamber becomes larger when the inclination is larger than the case where the opening area characteristic is large. Thus, until the piston is fully opened, that is, until the piston fully opens the relief hole, the responsiveness of the regulating valve can be secured. Further, after the opening of the relief hole has a large slope, that is, after the piston has fully opened the relief hole, it is possible to prevent excessive lift of the piston by increasing the braking performance of the piston.

さらに、第1の息抜き孔と第2の息抜き孔とを独立に設けているので、それぞれの息抜き孔の加工が容易である。また、第1の息抜き孔および第2の息抜き孔の大きさ(孔径)と数を適宜に選択することで、要求される開口面積特性の傾きに対応できる。 Furthermore, since the first breathing hole and the second breathing hole are provided independently, the processing of each breathing hole is easy. In addition, by appropriately selecting the size (hole diameter) and the number of the first breathing holes and the second breathing holes, it is possible to cope with the required inclination of the opening area characteristics.

(請求項の発明)
請求項に記載したレギュレートバルブにおいて、第2の息抜き孔は、ピストンがスプリングの許容ストローク分だけスプリングを圧縮する方向へ移動するまでの間に、ピストンによって全閉されることを特徴とする。
本発明によれば、ピストンが第2の息抜き孔を全閉すると、ダンパ室に燃料が閉じ込められる、つまり息抜き孔を通じて燃料が出入りできなくなるため、大きなダンパ効果を得ることができ、ピストンの振動を速やかに収束させることが可能である。
(Invention of Claim 2 )
2. The regulating valve according to claim 1 , wherein the second breathing hole is fully closed by the piston until the piston moves in the direction of compressing the spring by an allowable stroke of the spring. .
According to the present invention, when the piston fully closes the second breathing hole, the fuel is trapped in the damper chamber, that is, the fuel cannot enter and exit through the breathing hole, so that a large damper effect can be obtained and the vibration of the piston is reduced. It is possible to quickly converge.

(請求項の発明)
請求項1または2に記載したレギュレートバルブは、フィードポンプによって燃料タンクから汲み上げられた燃料を加圧してコモンレールへ圧送する燃料噴射ポンプに用いられ、フィードポンプより供給される燃料の圧力を調圧することを特徴とする。
本発明によれば、フィードポンプの入口で異常に過大な負圧が発生した場合、あるいはフィードポンプに吸入される燃料にエアーが混入した場合等に、レギュレートバルブの応答性が損なわれることなく、ピストンの過大リフトを防止して、フィードポンプの吐出圧を安定させることができる。
(Invention of Claim 3 )
The regulating valve according to claim 1 or 2 is used in a fuel injection pump that pressurizes fuel pumped from a fuel tank by a feed pump and pumps the fuel to a common rail, and regulates the pressure of the fuel supplied from the feed pump. It is characterized by that.
According to the present invention, when an excessively high negative pressure is generated at the inlet of the feed pump, or when air is mixed into the fuel sucked into the feed pump, the responsiveness of the regulator valve is not impaired. The piston can be prevented from being lifted excessively, and the discharge pressure of the feed pump can be stabilized.

本発明を実施するための最良の形態を以下の実施例により詳細に説明する。   The best mode for carrying out the present invention will be described in detail by the following examples.

図1(a)はレギュレートバルブ1の断面図、図1(b)はバルブボディ18の展開図、図2は燃料噴射ポンプ2の構成を示す模式図である。
実施例1に示すレギュレートバルブ1は、例えば、ディーゼル機関用の蓄圧式燃料噴射システムに用いられる燃料噴射ポンプ2(図2参照)に内蔵されている。
燃料噴射ポンプ2は、燃料タンク3より燃料を汲み上げて吐出するフィードポンプ4と、このフィードポンプ4より供給される燃料を加圧してコモンレール(図示せず)へ圧送する高圧ポンプ5と、フィードポンプ4の吐出圧を調圧するレギュレートバルブ1とを備えている。
FIG. 1A is a sectional view of the regulating valve 1, FIG. 1B is a development view of the valve body 18, and FIG. 2 is a schematic diagram showing the configuration of the fuel injection pump 2.
The regulator valve 1 shown in the first embodiment is built in, for example, a fuel injection pump 2 (see FIG. 2) used in a pressure accumulation fuel injection system for a diesel engine.
The fuel injection pump 2 includes a feed pump 4 that pumps and discharges fuel from a fuel tank 3, a high-pressure pump 5 that pressurizes fuel supplied from the feed pump 4 and pumps it to a common rail (not shown), and a feed pump And a regulating valve 1 that regulates the discharge pressure of 4.

フィードポンプ4は、燃料タンク3より汲み上げた燃料をフィルタ6を通して吸引し、所定の圧力まで加圧して高圧ポンプ5に送り出すもので、例えば、周知のトロコイドポンプによって構成され、高圧ポンプ5と共通のカム軸7を介してディーゼル機関により駆動される。
高圧ポンプ5は、カム軸7の回転運動を往復運動に変換するカム手段と、このカム手段の往復運動が伝達されてシリンダ8の内部を往復動するプランジャ9とを有する。
カム手段は、カム軸7に設けられた偏心カム10と、この偏心カム10に軸受(図示せず)を介して相対回転可能に嵌合するカムリング11とで構成される。
プランジャ9は、カム手段より往復運動が伝達されることで、シリンダ8の内部を上死点から下死点へ向かって移動する吸入行程と、シリンダ8の内部を下死点から上死点へ向かって移動する圧送行程とを繰り返す。
The feed pump 4 sucks the fuel pumped up from the fuel tank 3 through the filter 6, pressurizes the fuel up to a predetermined pressure, and sends it to the high-pressure pump 5. The feed pump 4 is constituted by, for example, a well-known trochoid pump, It is driven by a diesel engine through a cam shaft 7.
The high-pressure pump 5 includes cam means for converting the rotational motion of the cam shaft 7 into reciprocating motion, and a plunger 9 that reciprocates inside the cylinder 8 by transmitting the reciprocating motion of the cam means.
The cam means includes an eccentric cam 10 provided on the cam shaft 7 and a cam ring 11 fitted to the eccentric cam 10 via a bearing (not shown) so as to be relatively rotatable.
The plunger 9 receives a reciprocating motion from the cam means, thereby moving the inside of the cylinder 8 from the top dead center toward the bottom dead center, and the inside of the cylinder 8 from the bottom dead center to the top dead center. The pumping stroke that moves toward the head is repeated.

この高圧ポンプ5は、プランジャ9の吸入行程によって、フィードポンプ4より吐出された燃料が吸入弁12を押し開いてシリンダ8の内部に吸入され、プランジャ9の圧送行程によって、シリンダ8の内部に吸入された燃料が加圧され、吐出弁13を押し開いてコモンレールへ圧送される。
なお、フィードポンプ4より吐出された燃料は、フィードポンプ4と吸入弁12との間に設けられる電磁弁14により調量されてシリンダ8の内部に吸入され、それ以外の余剰燃料は、フィードギャラリ15を通ってカム室16に供給され、そのカム室16から溢れ出た燃料が、リターン通路17を通って燃料タンク3へ還流する。
カム室16には、上記のカム手段が配設され、フィードギャラリ15を通って供給される燃料により潤滑される。
In the high-pressure pump 5, the fuel discharged from the feed pump 4 is pushed into the cylinder 8 by the suction stroke of the plunger 9 and is sucked into the cylinder 8, and is sucked into the cylinder 8 by the pressure feed stroke of the plunger 9. The pressurized fuel is pressurized, and the discharge valve 13 is pushed open to be pumped to the common rail.
The fuel discharged from the feed pump 4 is metered by the electromagnetic valve 14 provided between the feed pump 4 and the suction valve 12 and sucked into the cylinder 8, and the surplus fuel other than that is fed into the feed gallery. The fuel that has been supplied to the cam chamber 16 through 15 and overflowed from the cam chamber 16 returns to the fuel tank 3 through the return passage 17.
The cam chamber 16 is provided with the above cam means and is lubricated by the fuel supplied through the feed gallery 15.

レギュレートバルブ1は、図1(a)に示す様に、筒状のバルブボディ18と、このバルブボディ18の内部に往復動可能に挿入されるピストン19と、このピストン19を一方向(図示左方向)に付勢するスプリング20等より構成される。
バルブボディ18は、一端側(図示左側)の開口部が燃料の流入口21として形成され、他端側の開口部がプラグ22によって閉塞されている。流入口21は、上記のフィードギャラリ15に接続され(図2参照)、このフィードギャラリ15を介してフィードポンプ4より送り出された燃料の一部が流入する。
As shown in FIG. 1A, the regulating valve 1 includes a cylindrical valve body 18, a piston 19 that is reciprocally inserted into the valve body 18, and the piston 19 in one direction (illustrated). It is composed of a spring 20 or the like that urges in the left direction.
The valve body 18 has an opening on one end side (left side in the drawing) as a fuel inlet 21 and an opening on the other end side closed by a plug 22. The inflow port 21 is connected to the feed gallery 15 (see FIG. 2), and a part of the fuel sent out from the feed pump 4 flows through the feed gallery 15.

バルブボディ18の側面には、リリーフ孔23と息抜き孔24とが形成され、共にフィードポンプ4の吸入側に接続されている(図2参照)。
リリーフ孔23は、ピストン19によって開閉され、ピストン19がリリーフ孔23を開いた時に流入口21と連通する。
息抜き孔24は、バルブボディ18の内部でピストン19とプラグ22との間に形成されるダンパ室25と連通可能に設けられ、ピストン19がリリーフ孔23を閉じる方向(閉弁方向と呼ぶ)へ移動して息抜き孔24を開くことでダンパ室25と連通し、ピストン19がリリーフ孔23を開く方向(開弁方向と呼ぶ)へ移動して息抜き孔24を閉じると、ダンパ室25との連通が遮断される。
ダンパ室25は、ピストン19が息抜き孔24を開いた時に、その息抜き孔24を通じてフィードポンプ4の吸入側と連通する。
A relief hole 23 and a breathing hole 24 are formed on the side surface of the valve body 18, and both are connected to the suction side of the feed pump 4 (see FIG. 2).
The relief hole 23 is opened and closed by the piston 19, and communicates with the inlet 21 when the piston 19 opens the relief hole 23.
The breathing hole 24 is provided in the valve body 18 so as to be able to communicate with a damper chamber 25 formed between the piston 19 and the plug 22, and the piston 19 closes the relief hole 23 (referred to as a valve closing direction). By moving and opening the breathing hole 24, it communicates with the damper chamber 25. When the piston 19 moves in the direction of opening the relief hole 23 (referred to as the valve opening direction) and closes the breathing hole 24, it communicates with the damper chamber 25. Is cut off.
The damper chamber 25 communicates with the suction side of the feed pump 4 through the breathing hole 24 when the piston 19 opens the breathing hole 24.

ピストン19は、流入口21より流入する燃料の圧力変動により、バルブボディ18の内部を移動してリリーフ孔23の開口面積を可変する。
スプリング20は、ピストン19の背後(ダンパ室25)に配設され、ピストン19の前面に作用する燃料圧力(フィードポンプ4の吐出圧)に抗してピストン19を一方向に付勢している。これにより、ピストン19は、自身の前面に作用するフィードポンプ4の吐出圧と、背面に作用するダンパ室25の燃料圧力+スプリング20の反力とが釣り合った位置にバランスされる。
The piston 19 moves inside the valve body 18 due to the pressure fluctuation of the fuel flowing in from the inlet 21 and varies the opening area of the relief hole 23.
The spring 20 is disposed behind the piston 19 (damper chamber 25), and biases the piston 19 in one direction against the fuel pressure (discharge pressure of the feed pump 4) acting on the front surface of the piston 19. . As a result, the piston 19 is balanced at a position where the discharge pressure of the feed pump 4 acting on the front surface of the piston 19 and the fuel pressure of the damper chamber 25 acting on the back surface plus the reaction force of the spring 20 are balanced.

次に、上記レギュレートバルブ1の特徴を従来品と比較しながら説明する。
従来のレギュレートバルブは、図6に示す様に、(a)ピストン140がリリーフ孔110を開き始める開弁位置では、息抜き孔120の略全体が開口しており、(b)ピストン140がリリーフ孔110を全開する全開位置でも、息抜き孔120の略半分程度が開口している。これにより、少なくともピストン140がリリーフ孔110を全開するまでの間は、ダンパ室170の燃料によるダンパ効果が小さいため、ピストン140がスムーズに動くことができ、その結果、レギュレートバルブの応答性が確保されている。
Next, the features of the regulating valve 1 will be described in comparison with a conventional product.
As shown in FIG. 6, in the conventional regulating valve, (a) at the valve opening position where the piston 140 starts to open the relief hole 110, substantially the entire breathing hole 120 is open, and (b) the piston 140 is relief. Even at the fully open position where the hole 110 is fully opened, approximately half of the breathing hole 120 is open. Thereby, at least until the piston 140 fully opens the relief hole 110, the damper effect by the fuel in the damper chamber 170 is small, so that the piston 140 can move smoothly, and as a result, the responsiveness of the regulating valve is reduced. It is secured.

しかし、ピストン140がリリーフ孔110を全開した後、さらに最大リフト位置まで移動しても、息抜き孔120がピストン140によって全閉されることはなく、図6(c)に示す様に、息抜き孔120の一部が開いている。また、息抜き孔120の開口面積特性を見ると、図6(d)に示す様に、ピストン140がリリーフ孔110を全開するまでと全開した後とで、息抜き孔120の開口面積が減少する割合、つまり開口面積特性の傾きが大きく変化することはない。この場合、ピストン140の移動により息抜き孔120の開口面積が減少するに連れて、ダンパ室170の燃料が息抜き孔120より流出する際の抵抗が大きくなるため、ダンパ室170の燃料によるダンパ効果も次第に大きくなるが、ピストン140がリリーフ孔110を全開した後、息抜き孔120の開口面積が急激に減少する訳ではないので、ダンパ効果が急激に大きくなることはない。   However, even if the piston 140 moves to the maximum lift position after the relief hole 110 is fully opened, the breathing hole 120 is not fully closed by the piston 140, as shown in FIG. 6C. A part of 120 is open. Further, looking at the opening area characteristics of the breathing hole 120, as shown in FIG. 6D, the rate at which the opening area of the breathing hole 120 decreases between when the piston 140 fully opens the relief hole 110 and after it fully opens. That is, the inclination of the opening area characteristic does not change greatly. In this case, as the opening area of the breathing hole 120 decreases due to the movement of the piston 140, the resistance when the fuel in the damper chamber 170 flows out of the breathing hole 120 increases. Although gradually increasing, after the piston 140 fully opens the relief hole 110, the opening area of the breathing hole 120 does not decrease rapidly, so that the damper effect does not increase rapidly.

これに対し、実施例1に示すレギュレートバルブ1は、図3に示す様に、ピストン19がスプリング20を開弁方向へ移動する際に、ピストン19がリリーフ孔23を全開するまでは、息抜き孔24の開口面積特性の傾きが小さく設定され、ピストン19がリリーフ孔23を全開した後は、開口面積特性の傾きが大きく設定されている。具体的には、ピストン19がリリーフ孔23を全開するまでの開口面積特性の傾きを従来と同等に設定し、ピストン19がリリーフ孔23を全開した後は、開口面積特性の傾きが従来より大きくなる様に設定している。この開口面積特性は、図1に示す様に、息抜き孔24を第1の息抜き孔24aと第2の息抜き孔24bとに分割することで実現される。   On the other hand, as shown in FIG. 3, the regulating valve 1 shown in the first embodiment has a breather until the piston 19 fully opens the relief hole 23 when the piston 19 moves the spring 20 in the valve opening direction. The inclination of the opening area characteristic of the hole 24 is set to be small, and after the piston 19 fully opens the relief hole 23, the inclination of the opening area characteristic is set to be large. Specifically, the inclination of the opening area characteristic until the piston 19 fully opens the relief hole 23 is set to be equal to the conventional one, and after the piston 19 fully opens the relief hole 23, the inclination of the opening area characteristic is larger than the conventional one. It is set to be. As shown in FIG. 1, this opening area characteristic is realized by dividing the breathing hole 24 into a first breathing hole 24a and a second breathing hole 24b.

第1の息抜き孔24aと第2の息抜き孔24bは、共に断面円形に開口する丸孔であり、第1の息抜き孔24aの方が第2の息抜き孔24bより内径が大きく設けられ、且つ第2の息抜き孔24bより第1の息抜き孔24aの方が閉弁側に位置している。
第1の息抜き孔24aは、ピストン19がリリーフ孔23を全開するまでの開口面積特性の傾きを実現するもので、ピストン19がリリーフ孔23を全開した時点で、ピストン19によって全閉される。
第2の息抜き孔24bは、ピストン19がリリーフ孔23を全開した後の開口面積特性の傾きを実現するもので、ピストン19がリリーフ孔23を全開してから最大リフト位置まで移動する間に、ピストン19によって全閉される。
Both the first breathing hole 24a and the second breathing hole 24b are round holes having a circular cross section, and the first breathing hole 24a has a larger inner diameter than the second breathing hole 24b, and The first breathing hole 24a is located closer to the valve closing side than the second breathing hole 24b.
The first breathing hole 24 a realizes an inclination of the opening area characteristic until the piston 19 fully opens the relief hole 23, and is fully closed by the piston 19 when the piston 19 fully opens the relief hole 23.
The second breathing hole 24b realizes the inclination of the opening area characteristic after the piston 19 fully opens the relief hole 23. While the piston 19 moves to the maximum lift position after the relief hole 23 is fully opened, The piston 19 is fully closed.

次に、レギュレートバルブ1の作用および効果を説明する。
レギュレートバルブ1は、流入口21より流入する燃料の圧力(フィードポンプ4の吐出圧)と、ダンパ室25の燃料圧力+スプリング20の反力とが釣り合った位置にピストン19がバランスされ、そのピストン19の開弁位置に応じて、フィードポンプ4の吐出圧を所定の圧力に調圧する。
ここで、フィードポンプ4の入口で異常に過大な負圧が発生する、あるいはフィードポンプ4に吸入される燃料にエアーが混入すると、フィードポンプ4の吐出圧が不安定になるため、ピストン19が大きな振幅で往復運動を繰り返す。
Next, the operation and effect of the regulating valve 1 will be described.
In the regulating valve 1, the piston 19 is balanced at a position where the pressure of the fuel flowing in from the inlet 21 (discharge pressure of the feed pump 4) and the fuel pressure of the damper chamber 25 + the reaction force of the spring 20 are balanced. The discharge pressure of the feed pump 4 is adjusted to a predetermined pressure according to the valve opening position of the piston 19.
Here, if an abnormally excessive negative pressure is generated at the inlet of the feed pump 4 or if air is mixed into the fuel sucked into the feed pump 4, the discharge pressure of the feed pump 4 becomes unstable. Repeat reciprocating motion with large amplitude.

これに対し、実施例1に示すレギュレートバルブ1は、ピストン19が開弁方向へ移動する際に、ピストン19がリリーフ孔23を全開するまでは、息抜き孔24の開口面積特性の傾きが従来と同等に設定され、ピストン19がリリーフ孔23を全開した後は、開口面積特性の傾きが従来より大きく設定されている。これにより、息抜き孔24の開口面積特性の傾きが小さく設定される領域、つまりピストン19がリリーフ孔23を全開するまでは、ダンパ効果によるピストン19の制動能力を低く抑えることによって、レギュレートバルブ1の応答性を確保できる。また、息抜き孔24の開口面積特性の傾きが大きく設定される領域、つまりピストン19がリリーフ孔23を全開した後は、ダンパ効果によるピストン19の制動能力が高くなることで、ピストン19の過大リフトを防止できる。   On the other hand, in the regulating valve 1 shown in the first embodiment, when the piston 19 moves in the valve opening direction, the inclination of the opening area characteristic of the breathing hole 24 is conventional until the piston 19 fully opens the relief hole 23. After the piston 19 fully opens the relief hole 23, the inclination of the opening area characteristic is set to be larger than in the prior art. As a result, the regulating valve 1 is kept low by suppressing the braking ability of the piston 19 due to the damper effect until the inclination of the opening area characteristic of the breathing hole 24 is set small, that is, until the piston 19 fully opens the relief hole 23. Responsiveness can be secured. In addition, after the piston 19 fully opens the relief hole 23, the braking capacity of the piston 19 due to the damper effect increases, so that the lift of the piston 19 is excessively lifted. Can be prevented.

この実施例1では、息抜き孔24を第1の息抜き孔24aと第2の息抜き孔24bとに分割しているので、第1の息抜き孔24aと第2の息抜き孔24bとを独立に加工でき、孔加工が容易である。また、第1の息抜き孔24aおよび第2の息抜き孔24bの大きさ(孔径)と数を適宜に選択することで、要求される開口面積特性の傾きに対応できる In the first embodiment, since the breathing hole 24 is divided into the first breathing hole 24a and the second breathing hole 24b, the first breathing hole 24a and the second breathing hole 24b can be processed independently. , Hole processing is easy. Further, by appropriately selecting the size (hole diameter) and the number of the first breathing holes 24a and the second breathing holes 24b, it is possible to cope with the required inclination of the opening area characteristics .

図4(a)はレギュレートバルブ1の断面図、図4(b)はバルブボディ18の展開図である。実施例1では、息抜き孔24を第1の息抜き孔24aと第2の息抜き孔24bとに分割した一例を記載したが、参考例1に示す息抜き孔24は、図4に示す様に、第1の開口部24cと第2の開口部24dとで形成され、両開口部が連続して1つの息抜き孔24を形成している。
第1の開口部24cは、ピストン19がリリーフ孔23を全開するまでの開口面積特性の傾きを実現するもので、ピストン19がリリーフ孔23を全開した時点で、ピストン19によって全閉される。
第2の開口部24dは、ピストン19がリリーフ孔23を全開した後の開口面積特性の傾きを実現するもので、ピストン19がリリーフ孔23を全開してから最大リフト位置まで移動する間に、ピストン19によって全閉される。
4A is a sectional view of the regulating valve 1, and FIG. 4B is a development view of the valve body 18. As shown in FIG. In Example 1, although the example which divided | segmented the ventilation hole 24 into the 1st ventilation hole 24a and the 2nd ventilation hole 24b was described, the ventilation hole 24 shown in the reference example 1 is shown in FIG. The first opening 24c and the second opening 24d are formed, and both the openings continuously form one breathing hole 24.
The first opening 24 c realizes an inclination of the opening area characteristic until the piston 19 fully opens the relief hole 23, and is fully closed by the piston 19 when the piston 19 fully opens the relief hole 23.
The second opening 24d realizes the inclination of the opening area characteristic after the piston 19 fully opens the relief hole 23, and while the piston 19 moves to the maximum lift position after fully opening the relief hole 23, The piston 19 is fully closed.

この参考例1の構成においても、実施例1と同様の効果を得ることができる。すなわち、息抜き孔24の開口面積特性の傾きが小さく設定される領域、つまりピストン19がリリーフ孔23を全開するまでは、ダンパ効果によるピストン19の制動能力を低く抑えることによって、レギュレートバルブ1の応答性を確保できる。一方、息抜き孔24の開口面積特性の傾きが大きく設定される領域、つまりピストン19がリリーフ孔23を全開した後は、ダンパ効果によるピストン19の制動能力が高くなることで、ピストン19の過大リフトを防止できる。
また、第1の開口部24cおよび第2の開口部24dの開口面積と形状を適宜に設計することで、要求される開口面積特性の傾きに対応できる。
In the configuration of the reference example 1 , the same effect as that of the first embodiment can be obtained. That is, until the piston 19 fully opens the relief hole 23, the braking capacity of the piston 19 by the damper effect is kept low until the slope of the opening area characteristic of the breathing hole 24 is set small, that is, the regulation valve 1. Responsiveness can be secured. On the other hand, after the piston 19 has fully opened the relief hole 23, the braking capacity of the piston 19 due to the damper effect is increased after the opening area characteristics of the breathing hole 24 have a large inclination. Can be prevented.
Further, by appropriately designing the opening area and the shape of the first opening 24c and the second opening 24d, it is possible to cope with the required inclination of the opening area characteristic.

(a)レギュレートバルブの断面図、(b)バルブボディの展開図である(実施例1)。(A) It is sectional drawing of a regulating valve, (b) It is an expanded view of a valve body (Example 1). 燃料噴射ポンプの構成を示す模式図である。It is a schematic diagram which shows the structure of a fuel injection pump. 息抜き孔の開口面積特性図である(実施例1)。It is an opening area characteristic figure of a ventilation hole (Example 1). (a)レギュレートバルブの断面図、(b)バルブボディの展開図である(参考例1)。(A) It is sectional drawing of a regulated valve, (b) It is an expanded view of a valve body ( reference example 1 ). (a)レギュレートバルブの断面図、(b)バルブボディの展開図である(従来技術)。(A) It is sectional drawing of a regulating valve, (b) It is an expanded view of a valve body (prior art). (a)リリーフ孔開弁時を示すレギュレートバルブの断面図、(b)リリーフ孔全開時を示すレギュレートバルブの断面図、(c)ピストンの最大リフト位置を示すレギュレートバルブの断面図、(d)息抜き孔の開口面積特性図である(従来技術)。(A) A sectional view of the regulating valve when the relief hole is opened, (b) a sectional view of the regulating valve when the relief hole is fully opened, (c) a sectional view of the regulating valve showing the maximum lift position of the piston, (D) It is an opening area characteristic view of a ventilation hole (prior art).

符号の説明Explanation of symbols

1 レギュレートバルブ
2 燃料噴射ポンプ
3 燃料タンク
4 フィードポンプ
18 バルブボディ(ボディ)
19 ピストン
20 スプリング
21 流入口
23 リリーフ孔
24 息抜き孔
24a 第1の息抜き孔
24b 第2の息抜き孔
24c 第1の開口部
24d 第2の開口部
25 ダンパ室
1 Regulating valve 2 Fuel injection pump 3 Fuel tank 4 Feed pump 18 Valve body (body)
19 Piston 20 Spring 21 Inlet 23 Relief Hole 24 Breathing Hole 24a First Breathing Hole 24b Second Breathing Hole 24c First Opening 24d Second Opening 25 Damper Chamber

Claims (3)

筒形状の一端側に流入口が形成され、側面にリリーフ孔が開口するボディと、
このボディの内部に往復動可能に挿入され、前記リリーフ孔の開口面積を可変するピストンと、
前記ボディの内部で前記ピストンの反流入口側に形成されるダンパ室と、
このダンパ室に配設され、前記流入口より流入する燃料の圧力に抗して前記ピストンを付勢するスプリングと、
前記ダンパ室を形成する前記ボディの側面に開口し、前記ピストンの挙動に応じて前記ダンパ室の燃料が出入りする息抜き孔とを有し、
前記リリーフ孔を開口する前記ピストンの開弁位置に応じて、前記流入口より流入する燃料の圧力を所定の圧力に調圧するレギュレートバルブにおいて、
前記ピストンが前記スプリングを圧縮する方向へ移動する際に、前記ピストンが前記リリーフ孔を全開するまでは、前記ピストンの移動に伴い前記息抜き孔の開口面積が減少し、前記ピストンの移動量に対して前記息抜き孔の開口面積が減少する割合を示す前記開口面積特性の傾きが小さく設定され、前記ピストンが前記リリーフ孔を全開した後は、前記開口面積特性の傾きが大きく設定されるように、前記息抜き孔は、前記開口面積特性の傾きが小さくなる様に形成された第1の息抜き孔と、前記開口面積特性の傾きが大きくなる様に形成された第2の息抜き孔とを有し、前記第1の息抜き孔と前記第2の息抜き孔とが独立して設けられていることを特徴とするレギュレートバルブ。
A body in which an inflow port is formed on one end side of the cylindrical shape and a relief hole is opened on a side surface;
A piston that is reciprocally inserted into the body and changes the opening area of the relief hole;
A damper chamber formed on the counter-flow inlet side of the piston inside the body;
A spring disposed in the damper chamber and biasing the piston against the pressure of fuel flowing in from the inlet;
An opening on a side surface of the body forming the damper chamber, and a breather hole through which fuel in the damper chamber enters and exits according to the behavior of the piston,
In a regulating valve that adjusts the pressure of the fuel flowing in from the inflow port to a predetermined pressure according to the valve opening position of the piston that opens the relief hole,
When the piston moves in the direction of compressing the spring, the opening area of the breathing hole decreases with the movement of the piston until the piston fully opens the relief hole. the opening area of the breather hole is set smaller inclination of the opening area characteristic indicating the rate of reduction, after the piston is fully opened the relief hole, the so that the inclination is larger in the opening area characteristic Te, The breathing hole has a first breathing hole formed so that the inclination of the opening area characteristic becomes small, and a second breathing hole formed so that the inclination of the opening area characteristic becomes large, The regulating valve, wherein the first breathing hole and the second breathing hole are provided independently .
請求項1に記載したレギュレートバルブにおいて、
前記第2の息抜き孔は、前記ピストンが前記スプリングの許容ストローク分だけ前記スプリングを圧縮する方向へ移動するまでの間に、前記ピストンによって全閉されることを特徴とするレギュレートバルブ。
The regulated valve according to claim 1,
The regulator valve is characterized in that the second breathing hole is fully closed by the piston until the piston moves in a direction to compress the spring by an allowable stroke of the spring .
請求項1または2に記載したレギュレートバルブは、
フィードポンプによって燃料タンクから汲み上げられた燃料を加圧してコモンレールへ圧送する燃料噴射ポンプに用いられ、
前記フィードポンプより供給される燃料の圧力を調圧することを特徴とするレギュレートバルブ。
The regulating valve according to claim 1 or 2,
Used for fuel injection pumps that pressurize the fuel pumped from the fuel tank by the feed pump and pump it to the common rail.
A regulating valve that regulates the pressure of fuel supplied from the feed pump .
JP2005193767A 2005-07-01 2005-07-01 Regulating valve Expired - Fee Related JP4534881B2 (en)

Priority Applications (2)

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JP2005193767A JP4534881B2 (en) 2005-07-01 2005-07-01 Regulating valve
DE200610000317 DE102006000317B4 (en) 2005-07-01 2006-06-30 control valve

Applications Claiming Priority (1)

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DE102012200909A1 (en) * 2012-01-23 2013-07-25 Robert Bosch Gmbh High-pressure fuel pump of an injection system
DE102012200894A1 (en) * 2012-01-23 2013-07-25 Robert Bosch Gmbh High-pressure fuel pump of an injection system
JP2017101622A (en) * 2015-12-03 2017-06-08 株式会社デンソー Relief valve device, and high pressure pump using the same
CN109058537B (en) * 2018-09-29 2023-11-21 浙江鸿友压缩机制造有限公司 Pressure regulating device capable of maintaining pressure rapidly and adjusting trigger threshold along with set pressure
CN114458501A (en) * 2022-02-24 2022-05-10 哈尔滨工程大学 Pressure fluctuation absorbing device of spring piston-double throttle plate

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JPH03272340A (en) * 1990-03-20 1991-12-04 Tokico Ltd Attenuation force adjusting type hydraulic shock absorber
JPH07269519A (en) * 1994-03-30 1995-10-17 Shin Caterpillar Mitsubishi Ltd Cushioning structure for hydraulic cylinder
JPH08135249A (en) * 1994-11-04 1996-05-28 Kajima Corp Damping device for vibration-controlled structure
JPH1193797A (en) * 1997-09-25 1999-04-06 Denso Corp Fuel injection pump
JP2000071852A (en) * 1998-09-01 2000-03-07 Kyokuto Kaihatsu Kogyo Co Ltd Cargo receiving table elevating device for cargo handling vehicle
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