JP4478944B2 - Fluid metering valve and fuel injection pump using the same - Google Patents

Fluid metering valve and fuel injection pump using the same Download PDF

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JP4478944B2
JP4478944B2 JP2004365509A JP2004365509A JP4478944B2 JP 4478944 B2 JP4478944 B2 JP 4478944B2 JP 2004365509 A JP2004365509 A JP 2004365509A JP 2004365509 A JP2004365509 A JP 2004365509A JP 4478944 B2 JP4478944 B2 JP 4478944B2
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fluid
fuel
valve member
stopper
valve
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JP2006170115A (en
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薫 小田
宏史 井上
信男 太田
禎次 稲熊
豊 丹羽
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Denso Corp
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Denso Corp
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Priority to EP05027654A priority patent/EP1674717B1/en
Priority to US11/304,728 priority patent/US7819637B2/en
Priority to DE602005009644T priority patent/DE602005009644D1/en
Priority to CNB2005100229168A priority patent/CN100520050C/en
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Description

本発明は、流体流量を調量する流体調量弁およびそれを用いた燃料噴射ポンプに関するものである。   The present invention relates to a fluid metering valve for metering a fluid flow rate and a fuel injection pump using the fluid metering valve.

流体入口から流入し流体出口から流出する流体流量を調量する流体調量弁として、燃料噴射ポンプに用いられているように、電磁弁を用いたものが知られている（例えば、特許文献１、２、３参照）。これら燃料噴射ポンプでは、燃料加圧室の燃料入口側に流体調量弁を設置し、流体調量弁が開閉することにより燃料加圧室と燃料入口との連通を断続している。そして、電磁駆動部を通電制御することにより燃料加圧時における流体調量弁の閉弁タイミングを制御し、燃料吐出量を調整している。   As a fluid metering valve for metering the flow rate of fluid flowing in from a fluid inlet and flowing out from a fluid outlet, one using a solenoid valve as used in a fuel injection pump is known (for example, Patent Document 1). 2, 3). In these fuel injection pumps, a fluid metering valve is provided on the fuel inlet side of the fuel pressurizing chamber, and the fluid metering valve is opened and closed to intermittently connect the fuel pressurizing chamber and the fuel inlet. Then, by controlling energization of the electromagnetic drive unit, the valve closing timing of the fluid metering valve at the time of fuel pressurization is controlled to adjust the fuel discharge amount.

特公昭５０−６０４３号公報Japanese Patent Publication No. 50-6043 特開平１０−１４１１７７号公報JP-A-10-141177 特開２００２−４８０３３号公報JP 2002-48033 A

しかしながら、特許文献１、２、３の流体調量弁では、電磁駆動部に通電して磁気吸引力で可動部材を移動させることにより、流体調量弁を閉弁したり、流体調量弁の開弁状態を保持する。このようにギャップを介して吸引側から離れている可動部材を磁力により吸引し移動させる構成では、可動部材を吸引するために大きな磁気吸引力が必要である。その結果、電磁駆動部が大型化したり、磁気吸引力を発生させるための電力消費量が増加するという問題がある。また、ギャップを介して可動部材を吸引する構成では、電磁駆動部に通電してから可動部材を吸引して移動させる応答性を高めるために、あるいは流体調量弁の開弁時の通路面積を増加するためにギャップを大きくするためには、磁気吸引力を増加する必要がある。その結果、電磁駆動部が大型化したり、磁気吸引力を発生させるための電力消費量が増加するという問題がある。   However, in the fluid metering valves of Patent Literatures 1, 2, and 3, the fluid metering valve is closed by energizing the electromagnetic drive unit and moving the movable member with a magnetic attraction force. Keep the valve open. In such a configuration in which the movable member that is separated from the suction side via the gap is attracted and moved by magnetic force, a large magnetic attraction force is required to attract the movable member. As a result, there is a problem that the electromagnetic drive unit becomes large or the power consumption for generating the magnetic attractive force increases. Further, in the configuration in which the movable member is sucked through the gap, the passage area when the fluid metering valve is opened is increased in order to increase the responsiveness of sucking and moving the movable member after energizing the electromagnetic drive unit. In order to increase the gap to increase, it is necessary to increase the magnetic attractive force. As a result, there is a problem that the electromagnetic drive unit becomes large or the power consumption for generating the magnetic attractive force increases.

本発明は上記問題を解決するためになされたものであり、電磁駆動部を小型化し電力消費量を低減する流体調量弁を提供することにある。   The present invention has been made to solve the above-described problems, and it is an object of the present invention to provide a fluid metering valve that reduces the power consumption by reducing the size of the electromagnetic drive unit.

請求項１から３記載の発明によると、弁部材とストッパとの間に磁気吸引力を発生させることにより、上流側と下流側との差圧により下流側に移動してストッパに係止された開弁位置に弁部材を保持するので、小さい磁気吸引力で開弁位置に弁部材を保持できる。これにより、電磁駆動部を小型化し、電力消費量を低減できる。電磁駆動部への通電をオフすれば、上流側と下流側との差圧により弁部材が往復移動し、流体入口側と流体出口側との連通を弁部材が断続する。 According to the first to third aspects of the invention, by generating a magnetic attractive force between the valve member and the stopper, it is moved to the downstream side by the differential pressure between the upstream side and the downstream side and is locked to the stopper. Since the valve member is held at the valve open position, the valve member can be held at the valve open position with a small magnetic attractive force. Thereby, an electromagnetic drive part can be reduced in size and power consumption can be reduced. When the energization to the electromagnetic drive unit is turned off, the valve member reciprocates due to the differential pressure between the upstream side and the downstream side, and the valve member interrupts communication between the fluid inlet side and the fluid outlet side.

また、弁部材がストッパに係止された状態で弁部材とストッパとの間に磁気吸引力を働かせるので、弁部材のリフト量を大きくし流体入口からの流体流入量を増加しても、磁気吸引力を増加する必要はない。
また、調量弁の弁部材は、磁気吸引力ではなく、差圧の変化により開弁方向および閉弁方向に移動するので、電磁駆動部への通電をオンしてから磁気吸引力により開弁方向または閉弁方向に弁部材が移動するよりも応答性が向上する。 In addition, since a magnetic attraction force is applied between the valve member and the stopper while the valve member is locked to the stopper, even if the lift amount of the valve member is increased to increase the fluid inflow amount from the fluid inlet, There is no need to increase the suction power.
In addition, the valve member of the metering valve moves in the valve opening direction and the valve closing direction due to a change in the differential pressure, not in the magnetic attraction force. The responsiveness is improved as compared with the movement of the valve member in the direction or the valve closing direction.

請求項２記載の発明では、ストッパに形成した流体通路を通って弁部材側とプランジャ側との間で燃料が流通する。したがって、プランジャの下降により流体室に燃料を吸入し、プランジャのリフトにより加圧された流体室の燃料を流体出口から吐出できる。
請求項３記載の発明では、弁部材がストッパに係止された状態でも、弁部材とストッパとの当接箇所の周囲に形成された流体通路を通り、プランジャの下降にともない流体室に燃料を吸入できる。 In the second aspect of the invention, fuel flows between the valve member side and the plunger side through the fluid passage formed in the stopper. Therefore, the fuel can be sucked into the fluid chamber by the lowering of the plunger, and the fuel in the fluid chamber pressurized by the lift of the plunger can be discharged from the fluid outlet.
According to the third aspect of the present invention, even when the valve member is locked to the stopper, the fuel passes through the fluid passage formed around the contact portion between the valve member and the stopper, and fuel is supplied to the fluid chamber as the plunger descends. Inhalable.

本発明の複数の実施形態を図に基づいて説明する。
（第１実施形態）
本発明の第１実施形態による燃料噴射ポンプを図１に示す。燃料噴射ポンプ１０は、高圧燃料の吐出量を流体調量弁である調量弁２０により調量するものであり、例えば、ディーゼルエンジンやガソリンエンジンのインジェクタに燃料を供給する高圧サプライポンプである。 A plurality of embodiments of the present invention will be described with reference to the drawings.
(First embodiment)
A fuel injection pump according to a first embodiment of the present invention is shown in FIG. The fuel injection pump 10 measures the discharge amount of high-pressure fuel by a metering valve 20 that is a fluid metering valve, and is, for example, a high-pressure supply pump that supplies fuel to an injector of a diesel engine or a gasoline engine.

プランジャ１２は、ハウジング２２に往復移動自在に支持されており、タペット１４とともに往復移動する。タペット１４はスプリング１６の付勢力によりカム２に向けて押し付けられており、カム２の回転に伴いタペット１４の外側底面はカム２と摺動する。
ハウジング２２は、調量弁２０のハウジングと、燃料加圧室２００を形成するシリンダとを兼ねている。ハウジング２２には、燃料加圧室２００、燃料入口２１０および燃料出口２１２が形成されている。特許請求の範囲に記載した「流体室」、「流体入口」、「流体出口」は、それぞれ燃料加圧室２００、燃料入口２１０、燃料出口２１２に相当する。 The plunger 12 is supported by the housing 22 so as to be reciprocally movable, and reciprocates together with the tappet 14. The tappet 14 is pressed toward the cam 2 by the urging force of the spring 16, and the outer bottom surface of the tappet 14 slides with the cam 2 as the cam 2 rotates.
The housing 22 serves as the housing of the metering valve 20 and the cylinder that forms the fuel pressurizing chamber 200. A fuel pressurizing chamber 200, a fuel inlet 210, and a fuel outlet 212 are formed in the housing 22. The “fluid chamber”, “fluid inlet”, and “fluid outlet” recited in the claims correspond to the fuel pressurizing chamber 200, the fuel inlet 210, and the fuel outlet 212, respectively.

調量弁２０は、ハウジング２２と、ストッパ３０、弁部材４０、付勢部材としてのスプリング４２、および電磁駆動部としてのコイル５０を有している。ストッパ３０、弁部材４０およびスプリング４２は燃料加圧室２００に設置されている。ストッパ３０は、弁部材４０の燃料下流側に設けられており、例えば、磁性材の表面を非磁性材でコーティングすることにより、板状に形成されている。図１の（Ｂ）に示すように、ストッパ３０の外周に４個の切り欠き形が形成されている。この切り欠きにより、ストッパ３０とハウジング２２の内周面との間に流体通路である燃料通路２０２が形成されている。   The metering valve 20 includes a housing 22, a stopper 30, a valve member 40, a spring 42 as an urging member, and a coil 50 as an electromagnetic drive unit. The stopper 30, the valve member 40 and the spring 42 are installed in the fuel pressurizing chamber 200. The stopper 30 is provided on the fuel downstream side of the valve member 40. For example, the stopper 30 is formed in a plate shape by coating the surface of a magnetic material with a nonmagnetic material. As shown in FIG. 1B, four notches are formed on the outer periphery of the stopper 30. By this notch, a fuel passage 202 that is a fluid passage is formed between the stopper 30 and the inner peripheral surface of the housing 22.

弁部材４０およびスプリング４２は、燃料入口２１０および燃料出口２１２とともにストッパ３０に対してプランジャ１２と反対側に設置されている。弁部材４０は、例えば、磁性材、または磁性材の表面を非磁性材でコーティングすることによりカップ状に形成されている。弁部材４０は、スプリング４２の付勢力により、ハウジング２２の燃料入口２１０側に設けた弁座２３に向けて付勢されている。弁部材４０が弁座２３に着座すると、燃料入口２１０が閉塞される。コイル５０への通電をオンすると、弁部材４０とストッパ３０との間に磁気吸引力が働く。コイル５０への通電は、電子制御装置（ＥＣＵ）７０により制御される。
燃料吐出弁６０は、燃料出口２１２に設置されている。燃料加圧室２００の圧力が所定圧以上になると、スプリング６４の付勢力に抗してボール６２が弁座６６から離座し、燃料加圧室２００の燃料が燃料出口２１２から吐出される。 The valve member 40 and the spring 42 are installed on the opposite side of the plunger 12 with respect to the stopper 30 together with the fuel inlet 210 and the fuel outlet 212. The valve member 40 is formed in a cup shape, for example, by coating the surface of a magnetic material or a magnetic material with a nonmagnetic material. The valve member 40 is urged toward the valve seat 23 provided on the fuel inlet 210 side of the housing 22 by the urging force of the spring 42. When the valve member 40 is seated on the valve seat 23, the fuel inlet 210 is closed. When energization of the coil 50 is turned on, a magnetic attractive force acts between the valve member 40 and the stopper 30. Energization of the coil 50 is controlled by an electronic control unit (ECU) 70.
The fuel discharge valve 60 is installed at the fuel outlet 212. When the pressure in the fuel pressurizing chamber 200 becomes equal to or higher than a predetermined pressure, the ball 62 separates from the valve seat 66 against the biasing force of the spring 64, and the fuel in the fuel pressurizing chamber 200 is discharged from the fuel outlet 212.

次に、図１および図２に基づいて燃料噴射ポンプ１０の作動について説明する。
（１）吸入工程
図２の（Ａ）、（Ｂ）に示すように、カム２の回転にともないプランジャ１２が上死点から下死点に向けて下降し、燃料加圧室２００の圧力が低下すると、弁部材４０の上流側である燃料入口２１０側と下流側である燃料加圧室２００とから弁部材４０が受ける差圧が変化する。そして、燃料加圧室２００の燃料圧力により弁部材４０が弁座２３に着座する方向に受ける力とスプリング４２の付勢力との和が、燃料入口２１０側の燃料圧力により弁部材４０が弁座２３から離座する方向に受ける力よりも小さくなると、弁部材４０は弁座２３から離座し、ストッパ３０に係止される。これにより、燃料入口２１０から燃料加圧室２００に燃料が吸入される。弁部材４０がストッパ３０に係止されている図２の（Ｂ）に示す状態においても、弁部材４０とストッパ３０との当節箇所の周囲に燃料通路２０２が形成されているので、燃料通路２０２を通り燃料加圧室２００のプランジャ１２側にも燃料が吸入される。 Next, the operation of the fuel injection pump 10 will be described with reference to FIGS. 1 and 2.
(1) Suction Step As shown in FIGS. 2A and 2B, as the cam 2 rotates, the plunger 12 descends from the top dead center toward the bottom dead center, and the pressure in the fuel pressurizing chamber 200 is reduced. When the pressure decreases, the differential pressure received by the valve member 40 from the fuel inlet 210 side which is the upstream side of the valve member 40 and the fuel pressurization chamber 200 which is the downstream side changes. The sum of the force received in the direction in which the valve member 40 is seated on the valve seat 23 by the fuel pressure in the fuel pressurizing chamber 200 and the urging force of the spring 42 is calculated by the fuel pressure on the fuel inlet 210 side. When the force is less than the force received in the direction away from the valve seat 23, the valve member 40 moves away from the valve seat 23 and is locked by the stopper 30. As a result, fuel is sucked into the fuel pressurizing chamber 200 from the fuel inlet 210. Even in the state shown in FIG. 2B where the valve member 40 is locked to the stopper 30, the fuel passage 202 is formed around the joint between the valve member 40 and the stopper 30. The fuel is sucked into the plunger 12 side of the fuel pressurizing chamber 200 through 202.

ＥＣＵ７０は、カム２の回転角度信号から、プランジャ１２が下死点に達する前のストッパ３０に弁部材４０が係止されストッパ３０と弁部材４０とが当接している状態で、コイル５０への通電をオンする（図２のＴｓ）。ストッパ３０と弁部材４０とが当接しているので、ストッパ３０に弁部材４０が係止された開弁状態を保持するために必要な磁気吸引力は小さくてよい。   The ECU 70 determines from the rotation angle signal of the cam 2 that the valve member 40 is locked to the stopper 30 before the plunger 12 reaches the bottom dead center, and the stopper 30 and the valve member 40 are in contact with each other. Energization is turned on (Ts in FIG. 2). Since the stopper 30 and the valve member 40 are in contact with each other, the magnetic attraction force required to maintain the valve open state in which the valve member 40 is locked to the stopper 30 may be small.

（２）戻し工程
図２の（Ｃ）に示すように、プランジャ１２が下死点から上死点に向かってリフトすると、燃料通路２０２を介して弁部材４０側の燃料加圧室２００の燃料圧力が上昇するので、弁部材４０が弁座２３に向けて受ける力は大きくなる。しかし、コイル５０への通電はオンされた状態であり、ストッパ３０と弁部材４０との間に磁気吸引力が働いているので、弁部材４０はストッパ３０に係止された開弁位置に保持される。これにより、燃料入口２１０の開いた状態が保持されるので、プランジャ１２のリフトにより加圧された燃料加圧室２００の燃料は、燃料入口２１０から低圧側に流出する。 (2) Returning step As shown in FIG. 2C, when the plunger 12 is lifted from the bottom dead center toward the top dead center, the fuel in the fuel pressurizing chamber 200 on the valve member 40 side through the fuel passage 202. Since the pressure rises, the force that the valve member 40 receives toward the valve seat 23 increases. However, energization of the coil 50 is in an on state, and a magnetic attractive force is acting between the stopper 30 and the valve member 40. Therefore, the valve member 40 is held in the valve-opened position locked to the stopper 30. Is done. As a result, the open state of the fuel inlet 210 is maintained, so that the fuel in the fuel pressurizing chamber 200 pressurized by the lift of the plunger 12 flows out from the fuel inlet 210 to the low pressure side.

（３）圧送工程
戻し工程中にコイル５０への通電をオフすると（図２のＴｅ）、弁部材４０とストッパ３０との間に磁気吸引力が働かなくなる。その結果、弁部材４０が燃料加圧室２００の燃料圧力により弁座２３に着座する方向に受ける力とスプリング４２の付勢力との和が、燃料入口２１０側の燃料圧力により弁部材４０が弁座２３から離座する方向に受ける力よりも大きくなるので、弁部材４０は差圧により弁座２３に着座し、燃料入口２１０は閉塞される。この状態でプランジャ１２がさらに上死点に向けてリフトすると、燃料加圧室２００の燃料が加圧され燃料圧力が上昇する。そして、燃料加圧室２００の燃料圧力が所定圧以上になると、スプリング６４の付勢力に抗してボール６２が弁座６６から離座し、燃料吐出弁６０が開弁する。これにより、燃料加圧室２００で加圧された燃料が燃料出口２１２から吐出される。
そして、上記（１）、（２）、（３）の工程を繰り返すことにより、燃料噴射ポンプ１０から燃料が吐出される。 (3) Pressure feeding process When the energization to the coil 50 is turned off during the returning process (Te in FIG. 2), the magnetic attractive force does not work between the valve member 40 and the stopper 30. As a result, the sum of the force that the valve member 40 receives in the direction in which the valve member 40 is seated on the valve seat 23 due to the fuel pressure in the fuel pressurizing chamber 200 and the biasing force of the spring 42 is Since the force is greater than the force received in the direction away from the seat 23, the valve member 40 is seated on the valve seat 23 by the differential pressure, and the fuel inlet 210 is closed. When the plunger 12 is further lifted toward the top dead center in this state, the fuel in the fuel pressurizing chamber 200 is pressurized and the fuel pressure rises. When the fuel pressure in the fuel pressurizing chamber 200 exceeds a predetermined pressure, the ball 62 separates from the valve seat 66 against the biasing force of the spring 64, and the fuel discharge valve 60 is opened. As a result, the fuel pressurized in the fuel pressurizing chamber 200 is discharged from the fuel outlet 212.
Then, fuel is discharged from the fuel injection pump 10 by repeating the steps (1), (2), and (3).

図２において、コイル５０への通電をオンするタイミングＴｓは、プランジャ１２が上死点に達したＴ１と吸入工程中のＴ２との間であれば、どのタイミングであってもよい。
ところで、ストッパ３０と弁部材４０との間に働く磁気吸引力は小さいので、例えば弁部材４０が燃料入口２１０側の弁座２３に着座しているタイミイングＴ１でコイル５０への通電をオンしても、弁部材４０は磁気吸引力により下流側のストッパ３０に向けて移動するのではなく、差圧により下流側に移動しストッパ３０に係止される。 In FIG. 2, the timing Ts at which the coil 50 is turned on may be any timing as long as it is between T1 when the plunger 12 reaches top dead center and T2 during the suction process.
By the way, since the magnetic attractive force acting between the stopper 30 and the valve member 40 is small, for example, the energization to the coil 50 is turned on at the timing T1 where the valve member 40 is seated on the valve seat 23 on the fuel inlet 210 side. However, the valve member 40 does not move toward the downstream stopper 30 by the magnetic attractive force, but moves downstream by the differential pressure and is locked to the stopper 30.

タイミングＴ２は、コイル５０への通電をオンしてから弁部材４０とストッパ３０との間に磁気吸引力が働くまでの応答遅れを考慮し、プランジャ１２が下死点から上死点に向けてリフトしても、ストッパ３０に弁部材４０が係止されている開弁状態を保持できる最も遅いタイミングである。   Timing T2 considers a response delay until the magnetic attractive force acts between the valve member 40 and the stopper 30 after turning on the coil 50, and the plunger 12 moves from the bottom dead center to the top dead center. Even when the valve is lifted, it is the latest timing at which the valve opening state where the valve member 40 is locked to the stopper 30 can be maintained.

図３、図４は、コイル５０への通電をオンからオフするタイミングを変更し、燃料吐出量を調整した例である。コイル５０への通電をオフからオンするタイミングＴｓは、図２と同じである。
図３では、図２においてコイル５０への通電をオフするタイミングＴｅよりも早く、プランジャ１２が下死点に達する前のタイミングＴｅ１でコイル５０への通電をオフするので、戻し工程がほとんどなく、プランジャ１２が下死点から上死点に向けてリフトを開始すると、燃料入口２１０がすぐに閉塞され、圧送工程が開始される。この場合、燃料吐出量は最大になる。コイル５０への通電をオフし続けても、図３と同じ燃料入口２１０の開閉状態となり、燃料吐出量は最大となる。 FIGS. 3 and 4 are examples in which the fuel discharge amount is adjusted by changing the timing at which the coil 50 is energized from on to off. The timing Ts for turning on the coil 50 from OFF to ON is the same as in FIG.
In FIG. 3, the energization to the coil 50 is turned off at the timing Te1 before the plunger 12 reaches the bottom dead center earlier than the timing Te at which the energization to the coil 50 is turned off in FIG. When the plunger 12 starts to lift from the bottom dead center to the top dead center, the fuel inlet 210 is immediately closed and the pumping process is started. In this case, the fuel discharge amount is maximized. Even if the power supply to the coil 50 is kept off, the fuel inlet 210 is opened and closed as in FIG. 3, and the fuel discharge amount is maximized.

一方、図４では、図２においてコイル５０への通電をオフするタイミングＴｅよりも遅いタイミングＴｅ２でコイル５０への通電をオフするので、戻し工程が長くなり、圧送工程が短くなっている。したがって、図２よりも燃料吐出量は減少する。
このように、コイル５０への通電タイミングを制御して調量弁２０が燃料入口２１０を開閉することにより、燃料吐出量を調整している。 On the other hand, in FIG. 4, the energization to the coil 50 is turned off at a timing Te2 later than the timing Te to deenergize the coil 50 in FIG. 2, so that the return process becomes longer and the pumping process becomes shorter. Accordingly, the fuel discharge amount is smaller than that in FIG.
Thus, the fuel discharge amount is adjusted by controlling the energization timing to the coil 50 and the metering valve 20 opening and closing the fuel inlet 210.

（第２、第３、第４実施形態）
本発明の第２実施形態を図５に、第３実施形態を図６に、第４実施形態を図７に示す。尚、第１実施形態と実質的に同一構成部分には同一符号を付し、説明を省略する。
第２、第３、第４実施形態の燃料噴射ポンプは、第１実施形態の燃料噴射ポンプ１０と調量弁の構成が異なっている。 (Second, third and fourth embodiments)
FIG. 5 shows a second embodiment of the present invention, FIG. 6 shows a third embodiment, and FIG. 7 shows a fourth embodiment. In addition, the same code | symbol is attached | subjected to the substantially same component as 1st Embodiment, and description is abbreviate | omitted.
The fuel injection pumps of the second, third, and fourth embodiments are different from the fuel injection pump 10 of the first embodiment in the configuration of the metering valve.

図５に示す第２実施形態の燃料噴射ポンプ８０では、調量弁８２のストッパ８４と弁部材８６とは、互いに相手側に向けて突出している突部を有しており、この突部同士が当接する。
図６に示す第３実施形態の燃料噴射ポンプ９０では、調量弁９２の弁部材９４はカップ状に形成されており、ストッパ３０に面する開口側に外側に広がるフランジ９６を有している。これにより、ストッパ３０に係止される弁部材９４の面積が増加するので、ストッパ３０に係止された状態で弁部材９４が傾くことを抑制する。
図７に示す第４実施形態の燃料噴射ポンプ１００では、調量弁１０２のストッパ１０４にスプリング４２を係止する凹部が形成されている。そして、ボール１０６および筒部材１０８が弁部材を構成している。 In the fuel injection pump 80 of the second embodiment shown in FIG. 5, the stopper 84 and the valve member 86 of the metering valve 82 have protrusions that protrude toward each other, and these protrusions Abut.
In the fuel injection pump 90 of the third embodiment shown in FIG. 6, the valve member 94 of the metering valve 92 is formed in a cup shape, and has a flange 96 that spreads outward on the opening side facing the stopper 30. . Thereby, since the area of the valve member 94 latched by the stopper 30 increases, the valve member 94 is prevented from being tilted while being latched by the stopper 30.
In the fuel injection pump 100 according to the fourth embodiment shown in FIG. 7, a recess for locking the spring 42 is formed on the stopper 104 of the metering valve 102. The ball 106 and the cylinder member 108 constitute a valve member.

以上説明した上記複数の実施形態では、差圧により下流側のストッパに係止されストッパと当接している弁部材とストッパとの間に磁気吸引力を働かせ、ストッパに係止された開弁位置に弁部材を保持するので、小さな磁気吸引力で開弁位置に弁部材を保持できる。その結果、電磁駆動部であるコイル５０を小型化し、コイル５０の電力消費量を低減できる。   In the plurality of embodiments described above, a valve opening position locked to the stopper by applying a magnetic attractive force between the stopper and the valve member that is locked to the stopper on the downstream side by the differential pressure and in contact with the stopper. Therefore, the valve member can be held at the valve open position with a small magnetic attraction force. As a result, the coil 50 which is an electromagnetic drive part can be reduced in size and the power consumption of the coil 50 can be reduced.

また、弁部材がストッパに係止された状態で弁部材とストッパとの間に磁気吸引力を働かせるので、弁部材のリフト量を大きくし燃料入口２１０からの燃料吸入量を増加しても、磁気吸引力を増加する必要がない。
また、調量弁の弁部材は、磁気吸引力ではなく、差圧の変化により開弁方向および閉弁方向に移動するので、コル５０への通電をオンしてから磁気吸引力により開弁方向または閉弁方向に弁部材が移動するよりも応答性が向上する。 Further, since the magnetic attraction force acts between the valve member and the stopper while the valve member is locked to the stopper, even if the lift amount of the valve member is increased and the fuel intake amount from the fuel inlet 210 is increased, There is no need to increase the magnetic attractive force.
Further, the valve member of the metering valve moves in the valve opening direction and the valve closing direction due to a change in the differential pressure, not in the magnetic attraction force. Or responsiveness improves rather than a valve member moving to a valve closing direction.

（他の実施形態）
上記複数の実施形態では、ストッパを切り欠いて燃料通路２０２を形成したが、ハウジング２２の内周面側に燃料通路を形成してもよい。
また上記複数の実施形態では、燃料噴射ポンプの燃料吐出量を調量する調量弁として本発明の流体調量弁を適用したが、燃料噴射ポンプ以外にも、燃料入口から流入し燃料出口から流出する流体の流量を調整するのであれば、どのような用途に本発明の流体調量弁を使用してもよい。 (Other embodiments)
In the above embodiments, the stopper is notched to form the fuel passage 202, but the fuel passage may be formed on the inner peripheral surface side of the housing 22.
In the above embodiments, the fluid metering valve of the present invention is applied as a metering valve for metering the fuel discharge amount of the fuel injection pump. However, in addition to the fuel injection pump, the fluid metering valve flows from the fuel inlet and from the fuel outlet. The fluid metering valve of the present invention may be used for any application as long as the flow rate of the flowing fluid is adjusted.

（Ａ）は本発明の第１実施形態による燃料供給装置を示す断面図であり、（Ｂ）はストッパをプランジャ側から見た図である。(A) is sectional drawing which shows the fuel supply apparatus by 1st Embodiment of this invention, (B) is the figure which looked at the stopper from the plunger side. プランジャリフトと、燃料入口の開閉と、コイルへの通電との関係を示す説明図である。It is explanatory drawing which shows the relationship between plunger lift, opening and closing of a fuel inlet, and electricity supply to a coil. プランジャリフトと、燃料入口の開閉と、コイルへの通電との関係を示す他の説明図である。It is another explanatory drawing which shows the relationship between plunger lift, opening and closing of a fuel inlet, and electricity supply to a coil. プランジャリフトと、燃料入口の開閉と、コイルへの通電との関係を示す他の説明図である。It is another explanatory drawing which shows the relationship between plunger lift, opening and closing of a fuel inlet, and electricity supply to a coil. 本発明の第２実施形態による燃料供給装置を示す断面図である。It is sectional drawing which shows the fuel supply apparatus by 2nd Embodiment of this invention. 本発明の第３実施形態による燃料供給装置を示す断面図である。It is sectional drawing which shows the fuel supply apparatus by 3rd Embodiment of this invention. 本発明の第４実施形態による燃料供給装置を示す断面図である。It is sectional drawing which shows the fuel supply apparatus by 4th Embodiment of this invention.

符号の説明Explanation of symbols

１０、８０、９０、１００ 燃料供給装置、２０、８２、９２、１０２ 調量弁（流体調量弁）、２２ ハウジング、３０、８４、１０４ ストッパ、４０、８６、９４ 弁部材、４２ スプリング、５０ コイル（電磁駆動部）、６０ 燃料吐出弁、７０ ＥＣＵ（電子制御装置）、１０６ ボール（弁部材）、１０８ 筒部材（弁部材）、２００ 燃料加圧室（流体室）、２０２ 燃料通路（流体通路）、２１０ 燃料入口（流体入口）、２１２ 燃料出口（流体出口） 10, 80, 90, 100 Fuel supply device, 20, 82, 92, 102 Metering valve (fluid metering valve), 22 Housing, 30, 84, 104 Stopper, 40, 86, 94 Valve member, 42 Spring, 50 Coil (electromagnetic drive unit), 60 fuel discharge valve, 70 ECU (electronic control unit), 106 ball (valve member), 108 cylinder member (valve member), 200 fuel pressurization chamber (fluid chamber), 202 fuel passage (fluid) Passage), 210 fuel inlet (fluid inlet), 212 fuel outlet (fluid outlet)

Claims (3)

流体入口から流入し流体出口から流出する流体流量を調量する流体調量弁において、
前記流体入口と前記流体出口との間に形成された流体室に設置されている弁部材であって、前記弁部材の上流側と下流側との差圧に応じて往復移動し、下流側に移動することにより前記流体入口と前記流体出口とを連通させる弁部材、
前記弁部材の下流側に設けられ前記弁部材を係止するストッパ、
及び、通電することにより前記弁部材と前記ストッパとの間に磁気吸引力を発生させ、差圧により前記ストッパに係止された開弁位置に前記弁部材を保持する電磁駆動部、
を有し、流体入口から流入し流体出口から流出する流体流量を調量する流体調量弁と、
往復移動することにより、前記流体入口から前記流体室に流入した燃料を加圧し、前記流体出口から吐出するプランジャと、
を備え、
前記流体入口、前記流体出口および前記弁部材は、前記ストッパに対して前記プランジャと反対側に形成されていることを特徴とする燃料噴射ポンプ。 In the fluid metering valve for metering the fluid flow rate flowing in from the fluid inlet and flowing out from the fluid outlet,
A valve member installed in a fluid chamber formed between the fluid inlet and the fluid outlet, and reciprocates according to a differential pressure between the upstream side and the downstream side of the valve member, A valve member for communicating the fluid inlet and the fluid outlet by moving;
A stopper provided on the downstream side of the valve member for locking the valve member;
And an electromagnetic drive unit that generates a magnetic attractive force between the valve member and the stopper by energization, and holds the valve member in a valve-opening position locked to the stopper by a differential pressure,
A fluid metering valve for metering the flow rate of fluid flowing in from the fluid inlet and flowing out from the fluid outlet;
A plunger that pressurizes fuel flowing into the fluid chamber from the fluid inlet by reciprocating and discharges the fuel from the fluid outlet;
With
The fuel injection pump, wherein the fluid inlet, the fluid outlet, and the valve member are formed on a side opposite to the plunger with respect to the stopper. 前記ストッパに流体通路が形成されていることを特徴とする請求項１記載の燃料噴射ポンプ。 Fuel injection pump according to claim 1, wherein the fluid passage is formed in the stopper. 前記弁部材と前記ストッパとの当接箇所の周囲に流体通路が形成されていることを特徴とする請求項１または２記載の燃料噴射ポンプ。 The fuel injection pump according to claim 1 or 2 , wherein a fluid passage is formed around a contact portion between the valve member and the stopper.
JP2004365509A 2004-12-17 2004-12-17 Fluid metering valve and fuel injection pump using the same Expired - Fee Related JP4478944B2 (en)

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JP2004365509A JP4478944B2 (en) 2004-12-17 2004-12-17 Fluid metering valve and fuel injection pump using the same
EP05027654A EP1674717B1 (en) 2004-12-17 2005-12-16 Solenoid valve, flow-metering valve, high-pressure fuel pump and fuel injection pump
US11/304,728 US7819637B2 (en) 2004-12-17 2005-12-16 Solenoid valve, flow-metering valve, high-pressure fuel pump and fuel injection pump
DE602005009644T DE602005009644D1 (en) 2004-12-17 2005-12-16 Solenoid valve, flow-regulating valve, high-pressure fuel pump and injection pump
CNB2005100229168A CN100520050C (en) 2004-12-17 2005-12-19 Electromagnetic valve and high-pressure fuel pump

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JP4327183B2 (en) 2006-07-31 2009-09-09 株式会社日立製作所 High pressure fuel pump control device for internal combustion engine
JP4600399B2 (en) * 2007-01-25 2010-12-15 トヨタ自動車株式会社 Control device for internal combustion engine
JP4353288B2 (en) * 2007-08-08 2009-10-28 トヨタ自動車株式会社 Fuel pump
JP5040692B2 (en) * 2008-02-04 2012-10-03 日産自動車株式会社 In-cylinder direct injection internal combustion engine fuel supply device
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JP4871972B2 (en) * 2009-04-20 2012-02-08 日立オートモティブシステムズ株式会社 High pressure fuel pump control device for internal combustion engine
DE102009045581A1 (en) * 2009-10-12 2011-04-14 Robert Bosch Gmbh Circuit for operating a solenoid valve
EP2740926B1 (en) * 2011-08-01 2016-03-30 Toyota Jidosha Kabushiki Kaisha Fuel injection pump
JP5677329B2 (en) * 2012-01-20 2015-02-25 日立オートモティブシステムズ株式会社 High pressure fuel supply pump with electromagnetically driven suction valve
JP6118790B2 (en) * 2014-12-25 2017-04-19 日立オートモティブシステムズ株式会社 High pressure fuel supply pump with electromagnetically driven suction valve
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