JP2003269278A - Accumulator-distributor type fuel injection pump - Google Patents
Accumulator-distributor type fuel injection pumpInfo
- Publication number
- JP2003269278A JP2003269278A JP2002065438A JP2002065438A JP2003269278A JP 2003269278 A JP2003269278 A JP 2003269278A JP 2002065438 A JP2002065438 A JP 2002065438A JP 2002065438 A JP2002065438 A JP 2002065438A JP 2003269278 A JP2003269278 A JP 2003269278A
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- valve
- fuel injection
- injection pump
- control valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Landscapes
- Fuel-Injection Apparatus (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、蓄圧室に蓄圧した
高圧燃料を、分配手段により各気筒へ分配して供給する
電子制御方式の蓄圧式分配型燃料噴射ポンプの構成に関
する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a structure of an electronically controlled pressure accumulation type distribution type fuel injection pump in which high pressure fuel accumulated in a pressure accumulation chamber is distributed and supplied to each cylinder by a distribution means.
【０００２】[0002]
【従来の技術】近年、ディーゼルエンジンにおいては、
ますます排気エミッション規制が厳しくなる傾向にあっ
て、低燃費で且つＮＯｘとパーティキュレートの低減等
が望まれており、これに対応するため、燃焼効率を向上
すべく燃料噴射圧の高圧化が進んできている。そして、
燃料噴射圧の高圧化とともに、蓄圧室内に蓄圧した高圧
燃料を、噴射弁から噴射する蓄圧式の燃料噴射ポンプが
増加してきている。この蓄圧式の燃料噴射ポンプには、
蓄圧室に蓄圧した高圧燃料を、噴射制御弁を通じて分配
軸へ供給し、分配軸にて各気筒へ分配した後に、噴射弁
から高圧噴射を行う、蓄圧式分配型燃料噴射ポンプに構
成されたものがある。2. Description of the Related Art Recently, in diesel engines,
Exhaust emission regulations are becoming more and more stringent, and there is a demand for low fuel consumption and reduction of NOx and particulates. To meet this demand, the fuel injection pressure is being increased to improve combustion efficiency. is made of. And
With the increase in fuel injection pressure, there is an increasing number of pressure-accumulation fuel injection pumps that inject high-pressure fuel accumulated in a pressure accumulator from an injection valve. In this pressure accumulation type fuel injection pump,
A high-pressure fuel accumulated in the pressure accumulator is supplied to the distribution shaft through the injection control valve, is distributed to each cylinder by the distribution shaft, and is then configured to form a pressure accumulation type fuel injection pump that performs high pressure injection from the injection valve. There is.
【０００３】[0003]
【発明が解決しようとする課題】前述の蓄圧式分配型燃
料噴射ポンプにおいては、正確な量の燃料を送油できる
こと、機関の回転速度に応じて最も適切な時期に燃料を
送油できること、機関の負荷や回転数に応じて燃料の送
油量が細かく調整できること等が求められている。ま
た、蓄圧式分配型燃料噴射ポンプの噴射制御弁では、弁
の微量な形状の変化により噴射特性等の性能のばらつき
が生じ易く、これを適切に補正することが求められてい
る。本発明は、前記要求に対応するための噴射制御弁を
備えた蓄圧式分配型燃料噴射ポンプを提案しようとする
ものである。In the above-mentioned pressure accumulation type distribution type fuel injection pump, it is possible to feed an accurate amount of fuel, to feed the fuel at the most appropriate time according to the engine speed, It is required that the amount of fuel to be sent can be finely adjusted according to the load and the number of revolutions of the engine. Further, in the injection control valve of the pressure accumulation type distribution type fuel injection pump, variations in performance such as injection characteristics are likely to occur due to slight changes in the shape of the valve, and it is required to appropriately correct this. The present invention is intended to propose a pressure accumulation type distribution type fuel injection pump provided with an injection control valve for meeting the above demand.
【０００４】[0004]
【課題を解決するための手段】本発明の解決しようとす
る課題は以上の如くであり、次にこの課題を解決するた
めの手段を説明する。The problem to be solved by the present invention is as described above, and the means for solving this problem will be described below.
【０００５】即ち、請求項１においては、蓄圧室に蓄圧
した高圧燃料を、分配手段により各気筒へ分配して供給
する蓄圧式分配型燃料噴射ポンプにおいて、噴射制御弁
を入口側弁体と出口側弁体とで構成し、出口側弁体にラ
ンド部を設けて該ランド部とコマンドピストンとの間の
圧力を大気圧と略同一に保持するとともに、入口側弁体
の有効径と出口側弁体のランド部径を略同一としたもの
である。That is, in the first aspect of the present invention, in the pressure accumulation type distribution type fuel injection pump in which the high pressure fuel accumulated in the pressure accumulation chamber is distributed to the respective cylinders by the distribution means and supplied, the injection control valve is provided with an inlet valve body and an outlet. Side valve body, and a land portion is provided on the outlet side valve body to keep the pressure between the land portion and the command piston substantially equal to atmospheric pressure, and the effective diameter of the inlet side valve body and the outlet side. The diameter of the land portion of the valve body is substantially the same.
【０００６】請求項２においては、蓄圧室に蓄圧した高
圧燃料を、分配手段により各気筒へ分配して供給する蓄
圧式分配型燃料噴射ポンプにおいて、噴射制御弁を入口
側弁体と出口側弁体とで構成し、出口側弁体にランド部
を設けて該ランド部とコマンドピストンとの間の圧力を
大気圧と略同一に保持するとともに、入口側弁体の有効
径と出口側弁体のランド部径を、±３０パーセントの範
囲内において相違させたものである。According to a second aspect of the present invention, in a pressure accumulation type distribution type fuel injection pump in which the high pressure fuel accumulated in the pressure accumulation chamber is distributed to each cylinder by the distribution means and is supplied, the injection control valve includes an inlet side valve body and an outlet side valve. And a land portion is provided on the outlet side valve body to keep the pressure between the land portion and the command piston substantially equal to the atmospheric pressure, and the effective diameter of the inlet side valve body and the outlet side valve body. The diameter of the land portion is different within a range of ± 30%.
【０００７】請求項３においては、蓄圧室に蓄圧した高
圧燃料を、分配手段により各気筒へ分配して供給する蓄
圧式分配型燃料噴射ポンプにおいて、噴射制御弁を入口
側弁体と出口側弁体とで構成し、該入口側弁体をスプー
ル弁側構成体とポペット弁側構成体とに分割して構成し
たものである。According to another aspect of the present invention, in the pressure-accumulation distribution type fuel injection pump in which the high-pressure fuel accumulated in the pressure accumulator is distributed to each cylinder by the distribution means and supplied, the injection control valve includes an inlet valve body and an outlet valve. The valve body is composed of a body and the inlet side valve body is divided into a spool valve side structure and a poppet valve side structure.
【０００８】請求項４においては、請求項３に記載の蓄
圧式分配型燃料噴射ポンプにおいて、前記噴射制御弁の
入口側弁体を構成するスプール弁側構成体とポペット弁
側構成体との間に薄板状部材を介装可能としたものであ
る。According to a fourth aspect of the present invention, in the pressure-accumulation distribution type fuel injection pump according to the third aspect, between the spool valve side constituent member and the poppet valve side constituent member constituting the inlet side valve member of the injection control valve. In addition, a thin plate member can be interposed.
【０００９】請求項５においては、蓄圧室に蓄圧した高
圧燃料を、分配手段により各気筒へ分配して供給する蓄
圧式分配型燃料噴射ポンプにおいて、噴射制御弁の入口
側に構成されるポペット弁部とスプール弁部との間に油
路を形成し、該油路に少なくとも一部の断面積を変更可
能とした可変絞り調整部を設けたものである。According to another aspect of the present invention, in the pressure-accumulation type distribution fuel injection pump in which the high-pressure fuel accumulated in the pressure accumulator is distributed to the respective cylinders by the distribution means and is supplied, the poppet valve arranged on the inlet side of the injection control valve. An oil passage is formed between the portion and the spool valve portion, and a variable throttle adjusting portion is provided in the oil passage, at least a part of which can be changed in cross-sectional area.
【００１０】請求項６においては、請求項５に記載の蓄
圧式分配型燃料噴射ポンプにおいて、前記絞り調整部
を、油路の断面積を調整する絞り部材と、該絞り部材を
電子制御可能なアクチュエータとで構成したものであ
る。According to a sixth aspect of the present invention, in the pressure-accumulation distribution type fuel injection pump according to the fifth aspect, the throttle adjusting portion is a throttle member for adjusting a cross-sectional area of an oil passage, and the throttle member can be electronically controlled. It is composed of an actuator.
【００１１】[0011]
【発明の実施の形態】次に、本発明の実施の形態を説明
する。図１は本発明に係る燃料噴射ポンプにおける燃料
噴射時の状態を示す概略図、図２は同じく燃料噴射ポン
プにおける燃料無噴射時の状態を示す概略図、図３は燃
料噴射ポンプを示す断面図、図４は噴射制御弁を示す断
面図である。図５は噴射制御弁の弁体を示す図、図６は
噴射制御弁の入口側弁体の構造を示す図、図７は噴射制
御弁の入口側弁体の構造の別実施例を示す図である。図
８は絞り構造の別実施例を示す断面図である。図９は噴
射ノズルの噴射圧の径時変化を示す図である。BEST MODE FOR CARRYING OUT THE INVENTION Next, embodiments of the present invention will be described. FIG. 1 is a schematic diagram showing a fuel injection state of the fuel injection pump according to the present invention, FIG. 2 is a schematic diagram showing a fuel injection state of the fuel injection pump, and FIG. 3 is a sectional view showing the fuel injection pump. 4 is a sectional view showing the injection control valve. 5 is a diagram showing a valve body of the injection control valve, FIG. 6 is a diagram showing a structure of an inlet side valve body of the injection control valve, and FIG. 7 is a diagram showing another embodiment of a structure of an inlet side valve body of the injection control valve. Is. FIG. 8 is a sectional view showing another embodiment of the diaphragm structure. FIG. 9 is a diagram showing the change over time of the injection pressure of the injection nozzle.
【００１２】まず、本発明に係る蓄圧式分配型燃料噴射
ポンプの概略構成について説明する。図１乃至図４に示
す如く、蓄圧式分配型燃料噴射ポンプに構成される燃料
噴射ポンプ１は、高圧燃料が蓄圧される蓄圧室３１、該
蓄圧室３１へ燃料を圧送するプランジャ７、蓄圧室３１
から圧送される燃料を各気筒の噴射ノズル２９へ分配し
て供給する分配軸９等を具備している。First, a schematic structure of a pressure accumulation type distribution type fuel injection pump according to the present invention will be described. As shown in FIGS. 1 to 4, a fuel injection pump 1 configured as a pressure accumulation type distribution type fuel injection pump includes a pressure accumulation chamber 31 in which high-pressure fuel is accumulated, a plunger 7 that pressure-feeds the fuel to the pressure accumulation chamber 31, and a pressure accumulation chamber. 31
It is provided with a distribution shaft 9 and the like that distributes and supplies the fuel pressure-fed from each cylinder to the injection nozzle 29 of each cylinder.
【００１３】前記プランジャ７は、カム軸４に形成され
るカム５により、タペット１１を介して上下摺動駆動さ
れ、該プランジャ７の上方に形成されるプランジャ室７
ａは、逆止弁２８を介して蓄圧室３１と接続されてい
る。また、プランジャ室７ａは、圧力制御弁２７を介し
て低圧側油路３２と接続されている。そして、圧力制御
弁２７がオン状態のときにはプランジャ室７ａと低圧側
油路３２とが分断され、オフ状態のときにはプランジャ
室７ａと低圧側油路３２とが連通するように構成してい
る。The plunger 7 is vertically slid through a tappet 11 by a cam 5 formed on a cam shaft 4, and a plunger chamber 7 formed above the plunger 7 is driven.
a is connected to the pressure accumulating chamber 31 via the check valve 28. Further, the plunger chamber 7 a is connected to the low pressure side oil passage 32 via the pressure control valve 27. When the pressure control valve 27 is in the on state, the plunger chamber 7a and the low pressure side oil passage 32 are separated from each other, and when the pressure control valve 27 is in the off state, the plunger chamber 7a and the low pressure side oil passage 32 communicate with each other.
【００１４】前記蓄圧室３１に油路７５を介して噴射制
御弁２６が接続され、該噴射制御弁２６に油路７６を介
して分配軸９が接続され、該分配軸９は、噴射ノズル２
９に接続される各気筒の吐出弁１８と連通可能に構成さ
れている。また、蓄圧室３１には、安全弁２４が接続さ
れるとともに、該蓄圧室３１内の圧力を検出する圧力セ
ンサ３０が付設されており、該蓄圧室３１内の圧力が一
定圧以上となった場合には、該圧力を低圧側ドレン油路
１００へ逃がすようにしている。The injection control valve 26 is connected to the pressure accumulating chamber 31 via an oil passage 75, the distribution shaft 9 is connected to the injection control valve 26 via an oil passage 76, and the distribution shaft 9 is connected to the injection nozzle 2
9 is connected to the discharge valve 18 of each cylinder. When the safety valve 24 is connected to the pressure accumulating chamber 31, a pressure sensor 30 for detecting the pressure inside the pressure accumulating chamber 31 is additionally provided, and when the pressure inside the pressure accumulating chamber 31 becomes a certain pressure or more. First, the pressure is released to the drain oil passage 100 on the low pressure side.
【００１５】噴射制御弁２６内には入口側弁体４０、出
口側弁体４２、及びコマンドピストン４３が摺動自在に
収納されており、入口側弁体４０はスプリング４１によ
り蓄圧室３１側に付勢されている。なお、噴射制御弁２
６は、いわゆる三方弁に構成されており、入口側弁体４
０が反蓄圧室３１側に摺動した状態では、蓄圧室３１
は、分配軸９及び吐出弁１８を介して噴射ノズル２９に
連通し、逆に入口側弁体４０が蓄圧室３１側に摺動した
状態では、吐出弁１８と低圧側油路３２が、分配軸９及
び油路７７を介して連通するように構成されている。An inlet side valve element 40, an outlet side valve element 42, and a command piston 43 are slidably accommodated in the injection control valve 26, and the inlet side valve element 40 is connected to the pressure accumulating chamber 31 side by a spring 41. Being energized. The injection control valve 2
6 is configured as a so-called three-way valve, and the inlet side valve body 4
When 0 slides to the side of the pressure-accumulation chamber 31 side, the pressure-accumulation chamber 31
Is communicated with the injection nozzle 29 via the distribution shaft 9 and the discharge valve 18, and conversely, in the state where the inlet side valve body 40 slides toward the accumulator chamber 31 side, the discharge valve 18 and the low pressure side oil passage 32 are distributed. It is configured to communicate with each other via the shaft 9 and the oil passage 77.
【００１６】噴射制御弁２６の反蓄圧室３１側端部は、
制御室３４を経てパイロットバルブ２５と接続されてお
り、該制御室３４はバイパス油路３３を介して蓄圧室３
１と接続されている。パイロットバルブ２５は、制御室
３４と低圧側油路３２との連通を断接するものであり、
該パイロットバルブ２５がオン状態のときに制御室３４
と低圧側油路３２とが連通し、オフ状態のときに制御室
３４と低圧側油路３２とが分断されるように構成してい
る。また、前記パイロットバルブ２５、圧力制御弁２
７、及び圧力センサ３０は、電子制御装置（以下「ＥＣ
Ｕ」と記載する）２０と接続されている。The end of the injection control valve 26 on the side opposite to the accumulator chamber 31 is
It is connected to the pilot valve 25 via the control chamber 34, and the control chamber 34 is connected to the pressure accumulating chamber 3 via the bypass oil passage 33.
It is connected to 1. The pilot valve 25 connects and disconnects the communication between the control chamber 34 and the low pressure side oil passage 32,
When the pilot valve 25 is in the ON state, the control chamber 34
And the low pressure side oil passage 32 are communicated with each other, and the control chamber 34 and the low pressure side oil passage 32 are separated from each other in the off state. In addition, the pilot valve 25 and the pressure control valve 2
7 and the pressure sensor 30 are electronic control devices (hereinafter referred to as “EC
U ”).
【００１７】このように構成される燃料噴射ポンプ１に
おいては、プランジャ室７ａ内に燃料タンク７０から燃
料が供給されており、蓄圧時には図１に示す如く、ＥＣ
Ｕ２０の制御により圧力制御弁２７がオン状態となって
プランジャ室７ａと低圧側油路３２とが分断され、カム
５によって上方摺動するプランジャ７によりプランジャ
室７ａ内の燃料が圧縮されて蓄圧室３１へ圧送される。
なお、蓄圧室３１へ圧送された燃料は逆止弁２８により
逆流が防止されており、該蓄圧室３１内は適宜圧力に蓄
圧されている。一方、蓄圧を要しないときは図２に示す
如く、圧力制御弁２７がオフ状態となってプランジャ室
７ａと低圧側油路３２とが連通し、プランジャ室７ａの
燃料は低圧側油路３２へドレンされる。In the fuel injection pump 1 thus constructed, the fuel is supplied from the fuel tank 70 into the plunger chamber 7a, and when the pressure is accumulated, as shown in FIG.
The pressure control valve 27 is turned on by the control of U20 to disconnect the plunger chamber 7a from the low pressure side oil passage 32, and the fuel in the plunger chamber 7a is compressed by the plunger 7 sliding upward by the cam 5 to accumulate the pressure in the pressure accumulation chamber. It is pumped to 31.
The check valve 28 prevents backflow of the fuel that has been pressure-fed to the pressure accumulation chamber 31, and the pressure inside the pressure accumulation chamber 31 is appropriately accumulated. On the other hand, when pressure accumulation is not required, as shown in FIG. 2, the pressure control valve 27 is turned off so that the plunger chamber 7a communicates with the low pressure side oil passage 32, and the fuel in the plunger chamber 7a flows to the low pressure side oil passage 32. Drained.
【００１８】バイパス油路３３により蓄圧室３１と接続
される前記制御室３４には、該蓄圧室３１から絞り３３
ａを介して燃料が供給されている。燃料噴射時には、Ｅ
ＣＵ２０の制御により噴射制御弁２６のパイロットバル
ブ２５がオンされて制御室３４と低圧側油路３２とが連
通されると、制御室３４の圧力が低下するため、噴射制
御弁２６のコマンドピストン４３の蓄圧室３１方向への
押圧が解除される。従って、該入口側弁体４０は、蓄圧
室３１の圧力により反蓄圧室３１側に付勢されて反蓄圧
室３１側に摺動し、蓄圧室３１と分配軸９とが連通す
る。これにより、蓄圧室３１内の燃料が分配軸９へ圧送
されて各気筒へ分配され、吐出弁１８を経て噴射ノズル
２９から噴射されることとなる。The control chamber 34, which is connected to the pressure accumulating chamber 31 by the bypass oil passage 33, has a throttle 33 from the pressure accumulating chamber 31.
Fuel is supplied via a. At the time of fuel injection, E
When the pilot valve 25 of the injection control valve 26 is turned on by the control of the CU 20 and the control chamber 34 and the low pressure side oil passage 32 are communicated with each other, the pressure in the control chamber 34 decreases, so the command piston 43 of the injection control valve 26 is reduced. Is released from the pressure accumulating chamber 31. Therefore, the inlet side valve element 40 is biased to the anti-accumulation chamber 31 side by the pressure of the accumulator chamber 31 and slides to the anti-accumulation chamber 31 side, and the accumulator chamber 31 and the distribution shaft 9 communicate with each other. As a result, the fuel in the pressure accumulating chamber 31 is pressure-fed to the distribution shaft 9 and distributed to each cylinder, and is injected from the injection nozzle 29 through the discharge valve 18.
【００１９】一方、燃料無噴射時には、図２に示す如
く、ＥＣＵ２０の制御により噴射制御弁２６のパイロッ
トバルブ２５がオフされ、蓄圧室３１から絞り３３ａを
介して燃料が供給される前記制御室３４と低圧側油路３
２とが分断されるため、供給された燃料により該制御室
３４内の圧力が上昇して、噴射制御弁２６のコマンドピ
ストン４３が蓄圧室３１側へ押圧される。これにより、
出口側弁体４２を介して入口側弁体４０が蓄圧室３１側
に摺動するとともに、噴射制御弁２６から吐出弁１８ま
での間の油路７６・７７と低圧側油路３２とが連通し、
燃料噴射管内圧力が低下して噴射が終了する。なお、ス
プリング４１は、入口側弁体４０を蓄圧室３１側に付勢
しており、起動時の蓄圧室３１の圧力上昇にも利用され
る。On the other hand, at the time of no fuel injection, as shown in FIG. 2, the pilot valve 25 of the injection control valve 26 is turned off by the control of the ECU 20, and the control chamber 34 to which fuel is supplied from the pressure accumulating chamber 31 through the throttle 33a. And low pressure side oil passage 3
2 is separated, the pressure in the control chamber 34 rises due to the supplied fuel, and the command piston 43 of the injection control valve 26 is pressed toward the pressure accumulating chamber 31 side. This allows
The inlet side valve body 40 slides toward the pressure accumulation chamber 31 side via the outlet side valve body 42, and the oil passages 76 and 77 between the injection control valve 26 and the discharge valve 18 communicate with the low pressure side oil passage 32. Then
The pressure in the fuel injection pipe drops and the injection ends. The spring 41 biases the inlet-side valve element 40 toward the pressure accumulating chamber 31 and is also used to increase the pressure in the pressure accumulating chamber 31 at the time of startup.
【００２０】次に、前記プランジャ７、蓄圧室３１、分
配軸９、圧力制御弁２７、及びパイロットバルブ２５等
の、燃料噴射ポンプ１の各構成部材の配置構成等につい
て説明する。Next, the arrangement and the like of each component of the fuel injection pump 1 such as the plunger 7, the pressure accumulating chamber 31, the distributing shaft 9, the pressure control valve 27, and the pilot valve 25 will be described.
【００２１】図３、図４に示す如く、燃料噴射ポンプ１
の下部には、カム５が固設されるカム軸４が横設され、
該カム軸４の一端部は、カム軸受１２を介してカム軸ハ
ウジング２に回転自在に軸支されている。カム軸ハウジ
ング２の上方には、プランジャ７、蓄圧室３１、及び分
配軸９等の各構成部材のハウジングである、ブロック状
部材のハイドロリックヘッド３が連設されている。As shown in FIGS. 3 and 4, the fuel injection pump 1
The cam shaft 4 on which the cam 5 is fixedly installed is provided in the lower part of the
One end of the cam shaft 4 is rotatably supported by the cam shaft housing 2 via a cam bearing 12. Above the cam shaft housing 2, a block-shaped hydraulic head 3 that is a housing for each of the constituent members such as the plunger 7, the pressure accumulating chamber 31, and the distribution shaft 9 is continuously provided.
【００２２】ハイドロリックヘッド３に嵌装されたプラ
ンジャバレル８に上下摺動自在に嵌挿されたプランジャ
７に対し、略直交方向に配設されたカム軸４の下方にカ
ム５が配設されている。そして、プランジャ７の下端に
付設されたタペット１１はカム５に当接するとともに、
スプリング１６等の付勢手段により下方へ付勢され、該
カム５の回転によりプランジャ７が上下往復動するよう
に構成されている。A cam 5 is arranged below a cam shaft 4 which is arranged substantially orthogonal to a plunger 7 which is slidably fitted in a plunger barrel 8 which is fitted in the hydraulic head 3. ing. The tappet 11 attached to the lower end of the plunger 7 contacts the cam 5 and
The plunger 7 is urged downward by an urging means such as a spring 16, and the plunger 7 reciprocates up and down by the rotation of the cam 5.
【００２３】また、プランジャ７の上端部には、該プラ
ンジャ７による燃料圧送の制御用電磁弁である前記圧力
制御弁２７が配設され、該圧力制御弁２７はその弁体が
カム軸４の軸方向と略直交する方向、すなわち、上下方
向に摺動するように配置されている。Further, the pressure control valve 27, which is an electromagnetic valve for controlling fuel pressure feeding by the plunger 7, is arranged at the upper end of the plunger 7, and the valve body of the pressure control valve 27 is of the cam shaft 4. It is arranged to slide in a direction substantially orthogonal to the axial direction, that is, in the vertical direction.
【００２４】さらに、プランジャ７の側方には、分配軸
９が該プランジャ７と軸心を平行に配設されており、該
分配軸９は、ハイドロリックヘッド３に嵌装される分配
軸スリーブ１０に回転自在に嵌挿されるとともに、該分
配軸９の下端部に連結した分配駆動軸３９により回転駆
動される。該分配駆動軸３９及び分配軸９は、カム軸４
の軸方向と略直交する方向に配置されており、分配駆動
軸３９とカム軸４とが傘歯車１９により接続されてい
る。これにより、カム軸４により傘歯車１９を介して、
分配軸９を回転駆動可能としている。なお、ハイドロリ
ックヘッド３における分配軸９の周囲には、気筒数分の
吐出弁１８が嵌装されている。Further, a distribution shaft 9 is disposed on the side of the plunger 7 so that its axis is parallel to the plunger 7, and the distribution shaft 9 is fitted to the hydraulic head 3 by a distribution shaft sleeve. The rotary shaft 10 is rotatably fitted in the rotary shaft 10 and is rotationally driven by a distribution drive shaft 39 connected to the lower end of the distribution shaft 9. The distribution drive shaft 39 and the distribution shaft 9 are the cam shaft 4
The drive shaft 39 and the cam shaft 4 are connected to each other by a bevel gear 19. Thereby, via the bevel gear 19 by the cam shaft 4,
The distribution shaft 9 can be driven to rotate. In addition, around the distribution shaft 9 in the hydraulic head 3, the discharge valves 18 for the number of cylinders are fitted.
【００２５】ハイドロリックヘッド３における、分配軸
９の反プランジャ７側の側方部分には、嵌装穴３ｃが形
成されて、ここに前記噴射制御弁２６が嵌装され、カム
軸４の軸方向と略直交する方向に配置されている。すな
わち、噴射制御弁２６は、入口側弁体４０及び出口側弁
体４２がカム軸４の軸方向と略直交する方向に摺動する
ように配置されている。また、噴射制御弁２６の上端部
には前記パイロットバルブ２５が配設されており、該パ
イロットバルブ２５は、その弁体がカム軸４の軸方向と
略直交する方向、すなわち、上下方向に摺動するように
配置されている。A fitting hole 3c is formed in a side portion of the hydraulic head 3 on the side opposite to the plunger 7 of the distributing shaft 9, and the injection control valve 26 is fitted therein, and the fitting hole 3c is fitted therein. It is arranged in a direction substantially orthogonal to the direction. That is, the injection control valve 26 is arranged so that the inlet side valve body 40 and the outlet side valve body 42 slide in a direction substantially orthogonal to the axial direction of the cam shaft 4. Further, the pilot valve 25 is arranged at the upper end of the injection control valve 26, and the pilot valve 25 slides in a direction in which its valve body is substantially orthogonal to the axial direction of the cam shaft 4, that is, the vertical direction. It is arranged to move.
【００２６】そして、燃料噴射ポンプ１の機能部材であ
る、前記プランジャ７、分配軸９、及び噴射制御弁２６
はハイドロリックヘッド３内に配設され、該ハイドロリ
ックヘッド３の一端部側からカム軸４の軸方向に、プラ
ンジャ７、分配軸９、及び噴射制御弁２６の順に、略直
列配置されている。なお、蓄圧室３１内の圧力を検出す
る圧力センサ３０はハイドロリックヘッド３の一側面に
取り付けられている。Then, the plunger 7, the distribution shaft 9, and the injection control valve 26, which are the functional members of the fuel injection pump 1, are described.
Is arranged in the hydraulic head 3, and the plunger 7, the distribution shaft 9, and the injection control valve 26 are arranged substantially in series in the axial direction of the cam shaft 4 from one end side of the hydraulic head 3. . The pressure sensor 30 that detects the pressure in the pressure accumulating chamber 31 is attached to one side surface of the hydraulic head 3.
【００２７】また、ハイドロリックヘッド３には、カム
軸４の軸方向と略平行に、軸方向に穴部が穿設され、蓄
圧室３１を構成している。該蓄圧室３１は、単数又は複
数構成され、複数の場合は互いにハイドロリックヘッド
３に形成される油路によって連通されている。蓄圧室３
１を構成するハイドロリックヘッド３の穴部の開口部
は、プラグや安全弁２４、圧力センサ３０等により閉塞
されている。Further, the hydraulic head 3 is provided with a hole in the axial direction substantially parallel to the axial direction of the cam shaft 4 to form a pressure accumulating chamber 31. The pressure accumulating chamber 31 is composed of a single or a plurality of chambers, and in the case of a plurality of chambers, the accumulating chambers 31 are connected to each other by an oil passage formed in the hydraulic head 3. Accumulation chamber 3
The opening portion of the hole portion of the hydraulic head 3 constituting 1 is closed by a plug, a safety valve 24, a pressure sensor 30 and the like.
【００２８】蓄圧室３１内へ送出され蓄圧された高圧燃
料は、パイロットバルブ２５がオンとなるよう制御され
ているときには、油路７５を通じて噴射制御弁２６へ導
入され、該噴射制御弁２６から油路７６を通じて分配軸
９へ導出される。分配軸９へ送出された燃料は、各気筒
に対応する油路７７を通じて吐出弁１８へ案内され、各
気筒の噴射ノズル２９から噴射される。The high-pressure fuel delivered into the pressure accumulating chamber 31 and accumulated therein is introduced into the injection control valve 26 through the oil passage 75 when the pilot valve 25 is controlled to be turned on. It is led to the distribution axis 9 via the path 76. The fuel delivered to the distribution shaft 9 is guided to the discharge valve 18 through the oil passage 77 corresponding to each cylinder, and is injected from the injection nozzle 29 of each cylinder.
【００２９】以上のように、本燃料噴射ポンプ１におけ
る燃料の高圧経路を構成する、プランジャ７、分配軸
９、圧力制御弁２７、逆止弁２８、噴射制御弁２６、圧
力センサ３０、安全弁２４、吐出弁１８、パイロットバ
ルブ２５、及び蓄圧室３１等といった機能部材は全て、
一つのブロック状部材にて構成されるハイドロリックヘ
ッド３に纏めて配設されている。As described above, the plunger 7, the distribution shaft 9, the pressure control valve 27, the check valve 28, the injection control valve 26, the pressure sensor 30, and the safety valve 24 which constitute the high pressure passage of the fuel in the fuel injection pump 1 of the present invention. , The discharge valve 18, the pilot valve 25, the pressure accumulating chamber 31, and the like are all functional members.
The hydraulic heads 3 are integrally arranged in one block-shaped member.
【００３０】ここで、本発明に係る噴射制御弁２６の構
造について説明する。Here, the structure of the injection control valve 26 according to the present invention will be described.
【００３１】図４及び図５に示す如く、噴射制御弁２６
は、略同軸上に配設した出口側弁体４２及び入口側弁体
４０を、シリンダ４７・４８に形成された噴射制御弁室
７２・７３に上下摺動自在に内装して構成されている。
出口側弁体４２及び入口側弁体４０は、これらの間に介
装したスプリング４１によって互いに離間する方向に付
勢されており、摺動方向の一側に配置される入口側弁体
４０と、他側に配置される出口側弁体４２の両側にポペ
ット弁を形成している。As shown in FIGS. 4 and 5, the injection control valve 26
Is configured such that the outlet-side valve body 42 and the inlet-side valve body 40, which are disposed substantially coaxially, are vertically slidably mounted in the injection control valve chambers 72 and 73 formed in the cylinders 47 and 48. .
The outlet-side valve element 42 and the inlet-side valve element 40 are urged in a direction in which they are separated from each other by a spring 41 interposed therebetween, and the inlet-side valve element 40 arranged on one side in the sliding direction. The poppet valves are formed on both sides of the outlet side valve element 42 arranged on the other side.
【００３２】出口側弁体４２の上方にはコマンドピスト
ン４３が略同軸上に配設されており、該コマンドピスト
ン４３が収納される制御室３４に摺動自在に内装して構
成されている。前記制御室３４の圧によって制御される
コマンドピストン４３によって押圧される、該コマンド
ピストン４３に当接する出口側弁体４２と、蓄圧室３１
の圧力により押圧される入口側弁体４０により、噴射ノ
ズル２９に接続される油路を高圧側あるいは低圧側へ切
り換える構成としている。A command piston 43 is disposed above the outlet side valve body 42 substantially coaxially, and is slidably mounted inside a control chamber 34 in which the command piston 43 is housed. The outlet side valve element 42, which is pressed by the command piston 43 controlled by the pressure of the control chamber 34, is in contact with the command piston 43, and the accumulator chamber 31.
The inlet-side valve body 40 that is pressed by the pressure of 2 switches the oil passage connected to the injection nozzle 29 to the high-pressure side or the low-pressure side.
【００３３】また、入口側弁体４０の下方には蓄圧室３
１より噴射制御弁２６へ燃料を送るための油路７５が、
噴射制御弁２６の側方には該噴射制御弁２６より噴射ノ
ズル２９へ燃料を送るための油路７６が、噴射制御弁２
６の出口側弁体４２の側方に低圧側油路３２へと繋がる
油路７１が、噴射制御弁室７３と接続されている。The pressure accumulating chamber 3 is provided below the inlet side valve element 40.
The oil passage 75 for sending fuel from 1 to the injection control valve 26 is
An oil passage 76 for sending fuel from the injection control valve 26 to the injection nozzle 29 is provided beside the injection control valve 26.
An oil passage 71, which is connected to the low pressure side oil passage 32, is connected to the injection control valve chamber 73 on the side of the outlet side valve body 42 of No. 6.
【００３４】そして、図１に示す燃料噴射時において、
前記制御室３４の圧力が低下して、蓄圧室３１の圧力に
より入口側弁体４０及び出口側弁体４２が上方付勢され
ると、出口側弁体４２が上部バルブシート３６ａに着座
して閉じるとともに、入口側弁体４０が開いて蓄圧室３
１と噴射ノズル２９側とが連通する。逆に、図２に示す
燃料無噴射時において、制御室３４内の圧力が上昇して
ピストン４３が下方に押圧されると、ピストン４３と入
口側弁体４０との面積差により、出口側弁体４２を介し
て入口側弁体４０が下方へ摺動して、該入口側弁体４０
が下部バルブシート３６ｂに着座して閉じるとともに、
噴射ノズル２９側の油路と低圧側油路３２とが連通する
こととなる。At the time of fuel injection shown in FIG. 1,
When the inlet side valve body 40 and the outlet side valve body 42 are biased upward by the pressure in the control chamber 34 and the pressure in the pressure accumulating chamber 31, the outlet side valve body 42 is seated on the upper valve seat 36a. When closed, the valve body 40 on the inlet side opens to open the accumulator chamber 3
1 communicates with the injection nozzle 29 side. On the contrary, when the pressure in the control chamber 34 rises and the piston 43 is pressed downward during the fuel non-injection shown in FIG. 2, the area difference between the piston 43 and the inlet side valve body 40 causes the outlet side valve The inlet side valve body 40 slides downward through the body 42, and the inlet side valve body 40
Sits on the lower valve seat 36b and closes,
The oil passage on the injection nozzle 29 side and the low pressure side oil passage 32 communicate with each other.
【００３５】図６に示す如く、前記入口側弁体４０に
は、摺動方向の一側にポペット弁部４４を構成し、他側
にスプール弁部４５を構成している。そして、本噴射制
御弁２６においては、スプール弁部４５とポペット弁部
４４の位置関係を決定するプリストローク９０によっ
て、噴射ノズル２９による噴射時期を決定する構成とし
ている。前記プリストローク９０は、加工時に発生する
弁体４０・４２や該弁体４０・４２を挿入保持するシリ
ンダ４７の加工公差によって、仕上がり寸法にばらつき
が生じると、各機関によって変化してしまい、これによ
り各機関で噴射特性のばらつきが発生するという不具合
が生じる。As shown in FIG. 6, the inlet valve body 40 has a poppet valve portion 44 on one side in the sliding direction and a spool valve portion 45 on the other side. In the main injection control valve 26, the injection timing of the injection nozzle 29 is determined by the prestroke 90 that determines the positional relationship between the spool valve portion 45 and the poppet valve portion 44. The pre-stroke 90 varies depending on each engine when the finished dimensions vary due to the machining tolerance of the valve bodies 40 and 42 generated during machining and the cylinder 47 into which the valve bodies 40 and 42 are inserted and held. As a result, there occurs a problem that the injection characteristics vary among the engines.
【００３６】そこで、噴射特性のばらつきを低減させる
ために必要な相対位置関係の寸法公差（例えば、１０ミ
クロン以下）に寸法管理するために、噴射制御弁２６の
入口側弁体４０を、スプール弁部４５側とポペット弁部
４４側が別部材にあるように分割した構成としている。
すなわち、入口側弁体４０をスプール弁側構成体４０ａ
とポペット弁側構成体４０ｂとで構成している。そし
て、組立時には、シリンダ４７とスプール弁側構成体４
０ａとポペット弁側構成体４０ｂとの組み合わせによ
り、噴射制御弁２６を組み立てた状態でプリストローク
９０が寸法公差以内となるように各部材を選択すること
によって、プリストローク９０のばらつきを低減させる
ようにしている。このようにして、弁体加工時の寸法誤
差により生じる各弁体寸法のばらつきを解消して、噴射
時期がばらつく不具合を解消している。Therefore, in order to control the dimension of the relative positional relationship (for example, 10 μm or less) necessary for reducing the variation of the injection characteristic, the inlet side valve element 40 of the injection control valve 26 is changed to the spool valve. The part 45 side and the poppet valve part 44 side are divided so that they are separate members.
That is, the inlet valve body 40 is replaced with the spool valve side structure body 40a.
And the poppet valve side structure 40b. Then, at the time of assembly, the cylinder 47 and the spool valve side structure 4
0a and the poppet valve side structure 40b are combined to reduce the variation of the prestroke 90 by selecting each member so that the prestroke 90 is within the dimensional tolerance in the state where the injection control valve 26 is assembled. I have to. In this way, variations in valve element dimensions caused by dimensional errors during valve element processing are eliminated, and the problem of variations in injection timing is eliminated.
【００３７】なお、図７に示す如く、スプール弁側構成
体４０ａとポペット弁側構成体４０ｂとの間に薄板状部
材であるシム４６などを介装して、該シム４６によって
微量にプリストローク９０の調整をするよう構成するこ
ともできる。As shown in FIG. 7, a thin plate-like member such as a shim 46 is interposed between the spool valve-side component 40a and the poppet valve-side component 40b, and a small amount of prestroke is performed by the shim 46. It can also be configured to make 90 adjustments.
【００３８】さらに、噴射制御弁２６において、圧力上
昇の波形を調整するため、弁体内に一体的に絞りを設け
たものもあるが、この場合、絞りの径の変更のために弁
体そのものの交換が必要となり、要求特性の異なる機種
に広く対応するためには、多くの異なる絞り面積の弁体
を製造しなくてはならず、弁体の種類が増加して生産性
の低下に繋がる不具合がある。Further, in the injection control valve 26, there is one in which a throttle is integrally provided in the valve body in order to adjust the waveform of the pressure rise. In this case, however, the valve body itself is changed to change the diameter of the throttle. In order to be widely compatible with models with different required characteristics, it is necessary to manufacture valve bodies with many different throttle areas, which leads to an increase in the types of valve bodies and a drop in productivity. There is.
【００３９】そこで、図５に示す如く、噴射制御弁２６
の入口側と、該入口側からスプール弁部４５との間を連
絡する油路５１を設け、該油路５１の面積、すなわち、
燃料の通路面積が可変となる絞り調整部１５を設けて、
絞り面積を容易に変更可能として、該絞りを具備する個
々の機関に最適な噴射圧力波形を得ることを可能として
いる。詳しくは、噴射制御弁２６の入口側弁体４０が挿
入されているシリンダ４７に、噴射制御弁２６の入口側
と、スプール弁部４５手前側とを連絡する油路５１を設
け、該油路５１の中途部に絞り調整部１５を設けて、こ
こに、絞り調整部１５の絞り部材として、一側面に切欠
を形成した軸体である絞り変更軸４９を挿設している。
そして、該絞り変更軸４９の回動により油路の絞り調整
部１５の断面積を変更可能としている。Therefore, as shown in FIG. 5, the injection control valve 26
And an oil passage 51 that connects the inlet side of the oil passage 51 to the spool valve portion 45 from the inlet side, and the area of the oil passage 51, that is,
By providing the throttle adjusting unit 15 that makes the passage area of the fuel variable,
By making it possible to easily change the throttle area, it is possible to obtain an optimum injection pressure waveform for each engine equipped with the throttle. Specifically, an oil passage 51 that connects the inlet side of the injection control valve 26 and the front side of the spool valve portion 45 is provided in the cylinder 47 in which the inlet side valve body 40 of the injection control valve 26 is inserted. A diaphragm adjusting unit 15 is provided in the middle of 51, and a diaphragm changing shaft 49 which is a shaft body having a notch formed on one side surface is inserted therein as a diaphragm member of the diaphragm adjusting unit 15.
The cross-sectional area of the throttle adjusting portion 15 of the oil passage can be changed by rotating the throttle changing shaft 49.
【００４０】上述の如く構成した絞り調整部では、同一
形状の構成部材によって、多種多様の絞り面積を設定す
ることが可能となり、機種によって最適な絞り面積を、
弁体及び絞り部材の種類を増加させることなく実現する
ことができる。また、個々の機関によって絞り面積が調
節可能となるため、個々の機体に最適な絞り面積を提供
することができて、良好な燃料噴射特性を得ることがで
きる。In the diaphragm adjusting section constructed as described above, it is possible to set a wide variety of diaphragm areas by using the same-shaped constituent members.
It can be realized without increasing the types of valve bodies and throttle members. Further, since the throttle area can be adjusted by each engine, it is possible to provide an optimal throttle area for each aircraft and obtain good fuel injection characteristics.
【００４１】また、図８に示す如く、前記絞り変更軸４
９をアクチュエータ５０と連結し、該アクチュエータ５
０をＥＣＵ２０により制御する構成として、機関の状況
（例えば、高圧燃料噴射あるいは低圧燃料噴射）に応じ
て絞り面積を変更するよう構成することもできる。Further, as shown in FIG. 8, the aperture changing shaft 4
9 is connected to the actuator 50, and the actuator 5
As a configuration in which 0 is controlled by the ECU 20, the throttle area can be changed according to the state of the engine (for example, high pressure fuel injection or low pressure fuel injection).
【００４２】図９に示す図表では、噴射ノズル２９の噴
射圧を時間の関数として示しており、図５に示す絞り面
積が大のときの噴射圧（８５）、絞り面積が小のときの
噴射圧（８６）とが示されている。In the chart shown in FIG. 9, the injection pressure of the injection nozzle 29 is shown as a function of time. The injection pressure (85) when the throttle area is large and the injection when the throttle area is small shown in FIG. The pressure (86) is shown.
【００４３】上述の図から、絞り面積が小のときの噴射
圧（８６）は、絞り面積が大のときの噴射圧（８５）に
対して、噴射圧上昇時においてその圧力上昇程度が緩や
かであることがわかる。従って、絞り面積を変化させる
アクチュエータ５０を電子制御することによって、絞り
面積を自在に変更し、機関の状況に応じた最適の噴射の
圧力波形を得ることができる。すなわち、例えば、エン
ジンを低速回転させるときには、絞り面積を小として噴
射圧が緩やかに上昇するようにし、エンジンを高速回転
させるときには絞り面積を大として噴射圧が急に上昇す
るようにして、機関の負荷や回転数に応じて燃焼に最適
な燃料の噴射の圧力波形を選択することができる。From the above figures, the injection pressure (86) when the throttle area is small is smaller than the injection pressure (85) when the throttle area is large when the injection pressure increases. I know there is. Therefore, by electronically controlling the actuator 50 that changes the throttle area, the throttle area can be freely changed and an optimum injection pressure waveform according to the engine condition can be obtained. That is, for example, when the engine is rotated at a low speed, the throttle area is made small so that the injection pressure gradually rises, and when the engine is rotated at a high speed, the throttle area is made large so that the injection pressure suddenly rises. It is possible to select a fuel injection pressure waveform that is most suitable for combustion, depending on the load and the number of revolutions.
【００４４】上述の如く構成された噴射制御弁２６及び
コマンドピストン４３において、断面略円形に形成され
る噴射制御弁２６とコマンドピストン４３の径は、これ
らの必要動作速度により決定される。一般的に、噴射制
御弁２６に対しコマンドピストン４３の径が大径となる
ように構成されるが、異なる径を有する弁体に同じ圧力
が掛かると径の大きい弁体側へ動かす力が発生するた
め、噴射制御弁２６とコマンドピストン４３との径の差
により、噴射終了時に高圧の流体が低圧側へ抜ける際に
流出圧が発生すると、噴射制御弁２６が閉じるのを妨げ
る方向の力が働いてしまうという不具合が生じる。In the injection control valve 26 and the command piston 43 configured as described above, the diameters of the injection control valve 26 and the command piston 43, which are formed in a substantially circular cross section, are determined by their required operating speeds. Generally, the diameter of the command piston 43 with respect to the injection control valve 26 is configured to be large, but when the same pressure is applied to valve bodies having different diameters, a force to move to the larger diameter valve body side is generated. Therefore, if an outflow pressure is generated when the high-pressure fluid is discharged to the low-pressure side at the end of injection due to the difference in diameter between the injection control valve 26 and the command piston 43, a force that prevents the injection control valve 26 from closing acts. There is a problem that it will end up.
【００４５】そこで、図５に示す如く、噴射制御弁２６
の出口側弁体４２にランド部４２ｂを形成し、該ランド
部４２ｂとコマンドピストン４３の間の圧力を略大気圧
に保持するとともに、噴射制御弁２６の入口側弁体４０
の有効径Ｒｃと出口側弁体４２のランド部４２ｂの径Ｒ
ａを略同一となるよう形成して、入口側弁体４０と出口
側弁体４２に加わる圧力バランスを良好に保持できるよ
うにしている。すなわち、入口側弁体４０の有効径Ｒｃ
と出口側弁体４２のランド部径Ｒａを略同一にすること
によって、噴射制御弁２６の動きが流出圧に影響されに
くくなり、噴射を安定させることができるのである。Therefore, as shown in FIG. 5, the injection control valve 26
The outlet side valve element 42 is formed with a land portion 42b, the pressure between the land portion 42b and the command piston 43 is maintained at substantially atmospheric pressure, and the inlet side valve element 40 of the injection control valve 26 is formed.
Effective diameter Rc and the diameter R of the land portion 42b of the outlet side valve element 42
By forming a so as to be substantially the same, the pressure balance applied to the inlet side valve body 40 and the outlet side valve body 42 can be maintained well. That is, the effective diameter Rc of the inlet side valve body 40
By making the land diameter Ra of the outlet side valve body 42 substantially the same, the movement of the injection control valve 26 is less likely to be affected by the outflow pressure, and the injection can be stabilized.
【００４６】なお、出口側弁体４２のランド部４２ｂの
径Ｒａと、出口側弁体４２の有効径Ｒｂは略同一であ
り、従って、出口側弁体４２の有効径Ｒｂと入口側弁体
４０の有効径Ｒｃは略同一となるよう構成している。The diameter Ra of the land portion 42b of the outlet side valve body 42 and the effective diameter Rb of the outlet side valve body 42 are substantially the same, and therefore the effective diameter Rb of the outlet side valve body 42 and the inlet side valve body The effective diameters Rc of 40 are configured to be substantially the same.
【００４７】但し、燃料噴射時に流出する燃料の流れに
よる流体力が、噴射制御弁２６の動作に与える影響が大
きいと判断できるときには、噴射制御弁２６の入口側弁
体４０の有効径Ｒｃを出口側弁体４２のランド部径Ｒａ
より±３０パーセントの範囲で大きく又は小さくして弁
体の圧力バランスを調整することもできる。流出圧発生
時において燃料の流体力による影響が大きい際には、入
口側弁体４０の有効径Ｒｃ及び出口側弁体４２のランド
部径Ｒａが全く同一であると、噴射制御弁２６の動きが
流出圧発生時に不安定になることがある。そこで、入口
側弁体４０の有効径Ｒｃ及び出口側弁体４２のランド部
径Ｒａにわずかの差を設けることにより、各弁体４０・
４２に発生する圧力差による力と流体力とが均衡して、
燃料による流体力の影響を最小とすることができる。However, when it can be judged that the fluid force due to the flow of the fuel flowing out at the time of fuel injection has a great influence on the operation of the injection control valve 26, the effective diameter Rc of the inlet side valve body 40 of the injection control valve 26 is set to the outlet. Land portion diameter Ra of the side valve element 42
It is also possible to adjust the pressure balance of the valve body by increasing or decreasing within the range of ± 30%. When the influence of the fluid force of the fuel is large when the outflow pressure is generated, if the effective diameter Rc of the inlet side valve body 40 and the land portion diameter Ra of the outlet side valve body 42 are exactly the same, the injection control valve 26 moves. May become unstable when outflow pressure occurs. Therefore, by providing a slight difference between the effective diameter Rc of the inlet side valve body 40 and the land portion diameter Ra of the outlet side valve body 42, each valve body 40
The force due to the pressure difference generated at 42 and the fluid force are balanced,
The influence of the fluid force due to the fuel can be minimized.
【００４８】[0048]
【発明の効果】本発明は、以上のように構成したので、
以下に示すような効果を奏する。Since the present invention is constructed as described above,
The following effects are achieved.
【００４９】即ち、請求項１に示す如く、蓄圧室に蓄圧
した高圧燃料を、分配手段により各気筒へ分配して供給
する蓄圧式分配型燃料噴射ポンプにおいて、噴射制御弁
を入口側弁体と出口側弁体とで構成し、出口側弁体にラ
ンド部を設けて該ランド部とコマンドピストンとの間の
圧力を大気圧と略同一に保持するとともに、入口側弁体
の有効径と出口側弁体のランド部径を略同一としたの
で、噴射制御弁の動作に関わる流出圧の影響を低減させ
ることができる。That is, as described in claim 1, in the pressure accumulation type distribution type fuel injection pump in which the high pressure fuel accumulated in the pressure accumulation chamber is distributed to each cylinder by the distribution means and supplied, the injection control valve serves as the inlet side valve body. The outlet side valve body is provided with a land portion on the outlet side valve body to maintain the pressure between the land portion and the command piston at substantially the same level as the atmospheric pressure. Since the diameters of the land portions of the side valve bodies are made substantially the same, the influence of the outflow pressure on the operation of the injection control valve can be reduced.
【００５０】請求項２に示す如く、蓄圧室に蓄圧した高
圧燃料を、分配手段により各気筒へ分配して供給する蓄
圧式分配型燃料噴射ポンプにおいて、噴射制御弁を入口
側弁体と出口側弁体とで構成し、出口側弁体にランド部
を設けて該ランド部とコマンドピストンとの間の圧力を
大気圧と略同一に保持するとともに、入口側弁体の有効
径と出口側弁体のランド部径を、±３０パーセントの範
囲内において相違させたので、流出圧発生時において燃
料の流体力による影響が大きい際に、燃料による流体力
の影響を最小とすることができる。According to a second aspect of the present invention, in a pressure accumulation type distribution type fuel injection pump in which the high pressure fuel accumulated in the pressure accumulator is distributed to the respective cylinders by the distribution means and is supplied, the injection control valve includes an inlet valve body and an outlet side. A valve body, and a land portion is provided on the outlet side valve body to maintain the pressure between the land portion and the command piston substantially equal to the atmospheric pressure, and the effective diameter of the inlet side valve body and the outlet side valve. Since the land diameters of the body are made different within the range of ± 30%, the influence of the fluid force of the fuel can be minimized when the influence of the fluid force of the fuel is large when the outflow pressure is generated.
【００５１】請求項３に示す如く、蓄圧室に蓄圧した高
圧燃料を、分配手段により各気筒へ分配して供給する蓄
圧式分配型燃料噴射ポンプにおいて、噴射制御弁を入口
側弁体と出口側弁体とで構成し、該入口側弁体をスプー
ル弁側構成体とポペット弁側構成体とに分割して構成し
たので、各構成部材を選択して組み合わせることによっ
て噴射制御弁の寸法公差を調整することができる。According to a third aspect of the present invention, in a pressure accumulation type distribution type fuel injection pump in which the high pressure fuel accumulated in the pressure accumulation chamber is distributed to each cylinder by the distribution means and is supplied, an injection control valve is provided at the inlet side valve body and the outlet side. Since the inlet side valve body is divided into a spool valve side constituent body and a poppet valve side constituent body, the dimensional tolerance of the injection control valve can be reduced by selecting and combining the respective constituent members. Can be adjusted.
【００５２】請求項４に示す如く、請求項３に記載の蓄
圧式分配型燃料噴射ポンプにおいて、前記噴射制御弁の
入口側弁体を構成するスプール弁側構成体とポペット弁
側構成体との間に薄板状部材を介装可能としたので、シ
ムによって噴射制御弁の寸法公差の調整が容易にでき
る。According to a fourth aspect of the present invention, in the pressure-accumulation distribution type fuel injection pump according to the third aspect, the spool valve side constituent body and the poppet valve side constituent body which constitute the inlet side valve body of the injection control valve are formed. Since the thin plate member can be interposed therebetween, the dimensional tolerance of the injection control valve can be easily adjusted by the shim.
【００５３】請求項５に示す如く、蓄圧室に蓄圧した高
圧燃料を、分配手段により各気筒へ分配して供給する蓄
圧式分配型燃料噴射ポンプにおいて、噴射制御弁の入口
側に構成されるポペット弁部とスプール弁部との間に油
路を形成し、該油路に少なくとも一部の断面積を変更可
能とした可変絞り調整部を設けたので、構成部品を偏光
することなく絞り面積を調節することができる。According to the fifth aspect of the present invention, in the pressure accumulation type distribution type fuel injection pump in which the high pressure fuel accumulated in the pressure accumulation chamber is distributed to the respective cylinders by the distribution means and supplied, the poppet arranged at the inlet side of the injection control valve. Since the oil passage is formed between the valve portion and the spool valve portion, and the variable passage adjusting portion capable of changing the cross-sectional area of at least a part thereof is provided in the oil passage, the throttle area can be reduced without polarizing the components. It can be adjusted.
【００５４】請求項６に示す如く、請求項５に記載の蓄
圧式分配型燃料噴射ポンプにおいて、前記絞り調整部
を、油路の断面積を調整する絞り部材と、該絞り部材を
電子制御可能なアクチュエータとで構成したので、機関
の状況に応じて最適な径に絞り面積を変更することがで
きる。According to a sixth aspect of the present invention, in the pressure-accumulation distribution type fuel injection pump according to the fifth aspect, the throttle adjusting portion is a throttle member for adjusting the cross-sectional area of the oil passage, and the throttle member can be electronically controlled. Since it is composed of various actuators, it is possible to change the throttle area to an optimum diameter according to the condition of the engine.
【図１】本発明に係る燃料噴射ポンプにおける燃料噴射
時の状態を示す概略図。FIG. 1 is a schematic diagram showing a state during fuel injection in a fuel injection pump according to the present invention.
【図２】同じく燃料噴射ポンプにおける燃料無噴射時の
状態を示す概略図。FIG. 2 is a schematic diagram showing a state of the fuel injection pump when no fuel is injected.
【図３】燃料噴射ポンプを示す断面図。FIG. 3 is a sectional view showing a fuel injection pump.
【図４】噴射制御弁を示す断面図。FIG. 4 is a sectional view showing an injection control valve.
【図５】噴射制御弁の弁体を示す図。FIG. 5 is a view showing a valve body of an injection control valve.
【図６】噴射制御弁の入口側弁体の構造を示す図。FIG. 6 is a view showing a structure of an inlet side valve body of the injection control valve.
【図７】噴射制御弁の入口側弁体の構造の別実施例を示
す図。FIG. 7 is a diagram showing another embodiment of the structure of the valve body on the inlet side of the injection control valve.
【図８】絞り構造の別実施例を示す断面図。FIG. 8 is a sectional view showing another embodiment of the diaphragm structure.
【図９】噴射ノズルの噴射圧の径時変化を示す図。FIG. 9 is a diagram showing changes over time in the injection pressure of the injection nozzle.
１ 燃料噴射ポンプ ３ ハイドロリックヘッド ４ カム軸 ５ カム ７ プランジャ ９ 分配軸 １５ 絞り調整部 ２６ 噴射制御弁 ２７ 圧力制御弁 ２９ 噴射ノズル ３１ 蓄圧室 ４０ 入口側弁体 ４０ａ スプール弁側構成体 ４０ｂ ポペット弁側構成体 ４２ 出口側弁体 ４２ｂ ランド部 ４３ コマンドピストン 1 Fuel injection pump 3 hydraulic head 4 cam shaft 5 cams 7 Plunger 9 distribution axes 15 Aperture adjustment section 26 Injection control valve 27 Pressure control valve 29 injection nozzle 31 Accumulation chamber 40 Inlet valve body 40a Spool valve side structure 40b Poppet valve side structure 42 Outlet valve body 42b Land section 43 Command piston
───────────────────────────────────────────────────── フロントページの続き (72)発明者 河原林 光義 大阪府大阪市北区茶屋町１番32号 ヤンマ ーディーゼル株式会社内 (72)発明者 小林 将 大阪府大阪市北区茶屋町１番32号 ヤンマ ーディーゼル株式会社内 (72)発明者 深江 伸宜 大阪府大阪市北区茶屋町１番32号 ヤンマ ーディーゼル株式会社内 Ｆターム(参考） 3G066 AA07 AB02 AC02 AC09 AD12 BA51 CA01S CA04U CA08 CA09 CA29 CA31 CA32T CA32U CA33 CA36 CA38 CD30 CE02 CE13 CE22 DA01 DC01 DC09 DC18 ─────────────────────────────────────────────────── ─── Continued front page (72) Inventor Mitsuyoshi Kawahara 1-32 Yanma, Chayamachi, Kita-ku, Osaka-shi, Osaka ー Diesel Co., Ltd. (72) Inventor Masaru Kobayashi 1-32 Yanma, Chayamachi, Kita-ku, Osaka-shi, Osaka ー Diesel Co., Ltd. (72) Inventor Nobuyoshi Fukae 1-32 Yanma, Chayamachi, Kita-ku, Osaka-shi, Osaka ー Diesel Co., Ltd. F-term (reference) 3G066 AA07 AB02 AC02 AC09 AD12 BA51 CA01S CA04U CA08 CA09 CA29 CA31 CA32T CA32U CA33 CA36 CA38 CD30 CE02 CE13 CE22 DA01 DC01 DC09 DC18
Claims (6)
により各気筒へ分配して供給する蓄圧式分配型燃料噴射
ポンプにおいて、噴射制御弁を入口側弁体と出口側弁体
とで構成し、出口側弁体にランド部を設けて該ランド部
とコマンドピストンとの間の圧力を大気圧と略同一に保
持するとともに、入口側弁体の有効径と出口側弁体のラ
ンド部径を略同一としたことを特徴とする蓄圧式分配型
燃料噴射ポンプ。1. A pressure accumulation type distribution type fuel injection pump in which high pressure fuel accumulated in a pressure accumulation chamber is distributed to each cylinder by a distribution means and supplied, wherein an injection control valve comprises an inlet side valve body and an outlet side valve body. Then, a land portion is provided on the outlet side valve element so that the pressure between the land portion and the command piston is kept substantially the same as the atmospheric pressure, and the effective diameter of the inlet side valve element and the land portion diameter of the outlet side valve element are 1. A pressure accumulation type distribution type fuel injection pump characterized in that
により各気筒へ分配して供給する蓄圧式分配型燃料噴射
ポンプにおいて、噴射制御弁を入口側弁体と出口側弁体
とで構成し、出口側弁体にランド部を設けて該ランド部
とコマンドピストンとの間の圧力を大気圧と略同一に保
持するとともに、入口側弁体の有効径と出口側弁体のラ
ンド部径を、±３０パーセントの範囲内において相違さ
せたことを特徴とする蓄圧式分配型燃料噴射ポンプ。2. A pressure accumulation type distribution type fuel injection pump in which high pressure fuel accumulated in a pressure accumulation chamber is distributed to each cylinder by a distribution means and is supplied, wherein an injection control valve is composed of an inlet side valve body and an outlet side valve body. Then, a land portion is provided on the outlet side valve element so that the pressure between the land portion and the command piston is kept substantially the same as the atmospheric pressure, and the effective diameter of the inlet side valve element and the land portion diameter of the outlet side valve element are Is different within a range of ± 30%, the pressure accumulation type distribution type fuel injection pump.
により各気筒へ分配して供給する蓄圧式分配型燃料噴射
ポンプにおいて、噴射制御弁を入口側弁体と出口側弁体
とで構成し、該入口側弁体をスプール弁側構成体とポペ
ット弁側構成体とに分割して構成したことを特徴とする
蓄圧式分配型燃料噴射ポンプ。3. A pressure-accumulation distribution fuel injection pump, in which high-pressure fuel accumulated in a pressure accumulator is distributed to each cylinder by a distribution means and supplied, wherein an injection control valve comprises an inlet-side valve element and an outlet-side valve element. Then, the pressure accumulation type distribution type fuel injection pump is characterized in that the inlet side valve body is divided into a spool valve side structure and a poppet valve side structure.
ポンプにおいて、前記噴射制御弁の入口側弁体を構成す
るスプール弁側構成体とポペット弁側構成体との間に薄
板状部材を介装可能としたことを特徴とする蓄圧式分配
型燃料噴射ポンプ。4. The pressure-accumulation distribution fuel injection pump according to claim 3, wherein a thin plate member is provided between a spool valve side structure and a poppet valve side structure which form an inlet side valve body of the injection control valve. A pressure-accumulation type distribution type fuel injection pump, which is characterized in that it can be interposed.
により各気筒へ分配して供給する蓄圧式分配型燃料噴射
ポンプにおいて、噴射制御弁の入口側に構成されるポペ
ット弁部とスプール弁部との間に油路を形成し、該油路
に少なくとも一部の断面積を変更可能とした可変絞り調
整部を設けたことを特徴とする蓄圧式分配型燃料噴射ポ
ンプ。5. A pressure accumulation type distribution type fuel injection pump which distributes and supplies high pressure fuel accumulated in a pressure accumulation chamber to each cylinder by a distribution means, and a poppet valve section and a spool valve which are arranged on an inlet side of an injection control valve. An accumulator type fuel injection pump, characterized in that an oil passage is formed between the oil passage and a variable throttle adjusting portion capable of changing at least part of its cross-sectional area.
ポンプにおいて、前記絞り調整部を、油路の断面積を調
整する絞り部材と、該絞り部材を電子制御可能なアクチ
ュエータとで構成したことを特徴とする蓄圧式分配型燃
料噴射ポンプ。6. The pressure-accumulation distribution fuel injection pump according to claim 5, wherein the throttle adjusting section is composed of a throttle member for adjusting a cross-sectional area of an oil passage, and an actuator capable of electronically controlling the throttle member. A pressure accumulation type distribution type fuel injection pump characterized by the above.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002065438A JP3877295B2 (en) | 2002-03-11 | 2002-03-11 | Accumulated distribution fuel injection pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2002065438A JP3877295B2 (en) | 2002-03-11 | 2002-03-11 | Accumulated distribution fuel injection pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2003269278A true JP2003269278A (en) | 2003-09-25 |
| JP3877295B2 JP3877295B2 (en) | 2007-02-07 |
Family
ID=29197742
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2002065438A Expired - Fee Related JP3877295B2 (en) | 2002-03-11 | 2002-03-11 | Accumulated distribution fuel injection pump |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3877295B2 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2579404A (en) * | 2018-11-30 | 2020-06-24 | Delphi Tech Ip Ltd | Head member for a HP pump of a fuel injection system |
-
2002
- 2002-03-11 JP JP2002065438A patent/JP3877295B2/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2579404A (en) * | 2018-11-30 | 2020-06-24 | Delphi Tech Ip Ltd | Head member for a HP pump of a fuel injection system |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3877295B2 (en) | 2007-02-07 |
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