JP3975337B2

JP3975337B2 - Flow rate adjusting device and flow rate adjusting method for fluid injection valve

Info

Publication number: JP3975337B2
Application number: JP2002123919A
Authority: JP
Inventors: 喜久新美; 利昌道関; 正儀問山; 義智上野
Original assignee: Denso Corp
Current assignee: Denso Corp
Priority date: 2001-04-26
Filing date: 2002-04-25
Publication date: 2007-09-12
Anticipated expiration: 2022-04-25
Also published as: JP2003013821A

Description

【０００１】
【発明の属する技術分野】
本発明は、流体噴射弁の流量調整装置および流量調整方法に関し、特に内燃機関（以下、内燃機関」をエンジンという）に燃料を噴射する燃料噴射弁の流量調整装置および流量調整方法に関する。
【０００２】
【従来の技術】
車両に搭載するエンジンの燃料噴射弁として、弁ボディの噴孔上流側に形成した弁座からノズルニードルの当接部が離座または弁座に当接部が着座することにより、噴孔から流体を噴射または遮断するものが知られている。
【０００３】
このような燃料噴射弁においては、一般に、ノズルニードルのリフト量を調整可能なリフト量調整手段を備えており、燃料噴射弁の組付け時に上記のリフト量調整手段を調整することにより、エンジンの仕様に応じたノズルニードルのリフト量の調整が行われ、燃料噴射弁の流量が調整されている。リフト量調整手段としては、例えば圧入材を被圧入材に圧入してなる圧入連結部材を有するリフト量調整手段が知られている。
【０００４】
【発明が解決しようとする課題】
ところで、従来の燃料噴射弁の流量調整方法としては、燃料噴射弁の静的流量（規定圧力下でノズルニードルを最大リフト位置に保持したときに単位時間当たりに噴射される量）をノズルニードルのリフト量に換算し、上記リフト量が所定の規格内に収まるように、圧入材としての固定鉄心を被圧入材としての燃料コネクタ部とは別体に形成し、燃料コネクタ部に対して軸方向に固定鉄心を圧入することにより燃料噴射弁の噴射量調整を行っている。この場合、例えば荒圧入、リハーサル圧入および精密圧入と多段階に圧入工程を分けて圧入位置を調整し、ニードルバルブを目標リフト量に調整する方法が考えられる。
【０００５】
ところが、上記の方法では、圧入荷重に対する設備とワークとの圧入方向への変形量を固定値としていたのでは、多段圧入時の圧入荷重にばらつきが生じ、精密圧入後の精度が悪化するという問題があった。以下、従来の流量調整方法の問題について詳細に説明する。
(1) 固定鉄心を燃料コネクタ部に荒圧入、リハーサル圧入および精密圧入と多段階に圧入する方法では、リハーサル圧入および精密圧入の条件を同一にし、リハーサル圧入により精密圧入時のリハーサルを実施して精密圧入における事前補正を実施することが考えられる。ところが、実際問題として圧入の設備条件を合わせたとしても、部品精度を合わせて管理することは極めて困難であり、コスト高に繋がる。したがって、実際に部品のできばえ等によるばらつきは避けられないため、精密圧入時とリハーサル圧入時とで圧入荷重に差が生じると、その分だけ精密圧入後の調整精度が悪化する。
(2) 多段階に圧入、リフト測定、圧入と繰り返すと、圧入時に静止摩擦と動摩擦とを繰り返すこととなり、静止摩擦から動摩擦に移行するエネルギ以下（設備側移動量に対してワーク側移動量が追従しない領域）では、設備的に圧入量を送ることは可能であるが、しかし、実際には固定鉄心は移動していないため、固定鉄心の移動量を制御することは困難である。したがって、多段階に圧入する方法では、再圧入等の微少な調整には不向きである。
【０００６】
(3) 燃料噴射弁の流量調整値をニードルバルブのリフト量に換算するためにはリフト量と流量の相関が必要となる。そもそも、燃料噴射弁の静的流量を構成する要素に噴孔流量とシート流量とがあり、シート流量を構成する要素にリフト量が挙げられる。そして、リフト量で静的流量を調整する場合、噴孔流量の下でリフト量と流量の相関が必要であり、その相関にはデータの信頼性が絡むために所定の管理幅（信頼区間）が必要となり、リフト量における管理値は製品特性上の許容値以上に厳しく管理しなければならないという問題がある。
【０００７】
本発明は、このような問題を解決するためになされたものであり、容易に調整可能で、調整精度を向上する流体噴射弁の流量調整装置および流量調整方法を提供することを目的とする。
本発明の他の目的は、調整時間を短縮することが可能な流体噴射弁の流量調整装置および流量調整方法を提供することにある。
本発明のさらに他の目的は、部品精度のばらつきによる影響を防止する流体噴射弁の流量調整装置および流量調整方法を提供することにある。
【０００８】
【課題を解決するための手段】
本発明の請求項１記載の流体噴射弁の流量調整装置によると、補正量設定手段により、圧入荷重に対する圧入連結部材の圧入方向への変形量または歪み量の計測値または計算値と、圧入手段の圧入材との当接部における圧入荷重に対する圧入方向への変位量の計測値または計算値から圧入材の移動目標値を補正し設定する。また、制御手段により、流体供給手段内を通過する流体の流量、荷重検知手段および移動量検知手段の出力信号、ならびに補正量設定手段の設定する補正量に応じて圧入材の被圧入材に対する圧入量を調整する。このため、圧入の操作量は誤差要素を考慮した移動目標値に設定されるので、圧入荷重を印加したことによる変形誤差を除いた圧入量が得られる。したがって、圧入工程の後で部材が変形誤差の分だけ弾性復元し、圧入工程中の弾性変形による製造誤差を生じることがなく、精度のよい調整を行うことができる。さらに、静的流量を測定しながら圧入材の圧入量を調整するため、弁部材のリフト量への製品要求を換算させる必要がなく、容易に調整可能であり、調整精度を向上するとともに、調整時間を短縮することができる。
【０００９】
また、静的流量を測定しながら圧入材の圧入量を調整することにより、静的流量と弁部材のリフト量とを複合させることが可能となり、製造上の許容値で管理できるようになるため、管理が容易になり部品精度のばらつきによる影響を防止することができる。
【００１０】
本発明の請求項２記載の流体噴射弁の流量調整装置によると、制御手段は第１の圧入工程および第２の圧入工程に分けて圧入手段を操作し、補正量設定手段は、第１の圧入工程における圧入時の圧入荷重から第２の圧入工程における圧入時の荷重を予測し、圧入材の移動目標値を補正する。したがって、第１の圧入工程の結果を第２の圧入工程に反映することができ、高精度な圧入精度が得られ、調整精度の向上を図ることができる。
【００１１】
本発明の請求項３記載の流体噴射弁の流量調整装置によると、制御手段は連続的に圧入手段を操作し、補正量設定手段は、圧入部が静止摩擦から動摩擦に移行した状態の圧入荷重から圧入材の移動目標値を補正する。したがって、微調整可能な連続圧入を実施することにより動摩擦域で調整可能となり、圧入部の静止摩擦力と動摩擦力との変動等による誤差が生じることがなく、極めて高精度の圧入調整を行うことができる。
【００１２】
本発明の請求項４記載の流体噴射弁の流量調整方法によると、圧入連結部材内に流体を供給する流体供給手段に流体を圧送し、圧入荷重に対する圧入連結部材の圧入方向への変形量または歪み量の計測値または計算値と、圧入材を被圧入材に向けて押圧する圧入手段の圧入材との当接部における圧入荷重に対する圧入方向への変位量の計測値または計算値とから圧入材の移動目標値を補正し設定し、流体供給手段内を通過する流体の流量、圧入材の被圧入材に対する圧入荷重またはその反力、基準位置に対する圧入材の圧入方向への移動量、ならびに圧入材の移動目標値の補正量に応じて圧入材の被圧入材に対する圧入量を調整する。このため、圧入の操作量は誤差要素を考慮した移動目標値に設定されるので、圧入荷重を印加したことによる変形誤差を除いた圧入量が得られる。したがって、圧入工程の後で部材が変形誤差の分だけ弾性復元し、圧入工程中の弾性変形による製造誤差を生じることがなく、精度のよい調整を行うことができる。さらに、静的流量を測定しながら圧入材の圧入量を調整するため、弁部材のリフト量への製品要求を換算させる必要がなく、容易に調整可能であり、調整精度を向上するとともに、調整時間を短縮することができる。
【００１３】
また、静的流量を測定しながら圧入材の圧入量を調整することにより、静的流量と弁部材のリフト量とを複合させることが可能となり、製造上の許容値で管理できるようになるため、管理が容易になり部品精度のばらつきによる影響を防止することができる。
【００１４】
本発明の請求項５記載の流体噴射弁の流量調整方法によると、第１の圧入工程および第２の圧入工程に分けて圧入手段を操作し、第１の圧入工程における圧入時の圧入荷重から第２の圧入工程における圧入時の荷重を予測し、圧入材の移動目標値を補正する。したがって、第１の圧入工程の結果を第２の圧入工程に反映することができ、高精度な圧入精度が得られ、調整精度の向上を図ることができる。
【００１５】
本発明の請求項６記載の流体噴射弁の流量調整方法によると、圧入部が静止摩擦から動摩擦に移行した状態の圧入荷重から圧入材の移動目標値を補正する。したがって、微調整可能な連続圧入を実施することにより動摩擦域で調整可能となり、圧入部の静止摩擦力と動摩擦力との変動等による誤差が生じることがなく、極めて高精度の圧入調整を行うことができる。
【００１７】
本発明の請求項７記載の流体噴射弁の流量調整方法によると、第一圧入工程、第二圧入工程および第三圧入工程において、圧入荷重の安定値が計測される。これにより、圧入材が被圧入材に対し確実に移動していることを確認可能となる。また、第二圧入工程の後の加圧リフト量および無加圧リフト量を求めることにより、圧入荷重の有無による流体噴射弁の弾性変形にともなって生じるリフト量の誤差を含めて最終リフト量とするための目標移動量が計算される。そのため、圧入荷重がない無加圧状態における弁部材の最終リフト量を目標として、圧入材を圧入することができる。また、第二圧入工程における圧入材の移動量、計算リフト量、加圧リフト量、無加圧リフト量および最終リフト量から、最終リフト量とするための目標移動量を算出することにより、第三圧入工程における圧入材の移動量が低減される。そのため、第三圧入工程における圧入材の被圧入材への圧入移動量は圧入の総量に比較して小さくなり、圧入荷重の変化が低減される。したがって、流体噴射弁の流量を容易に調整可能であり、調整精度を向上することができる。
【００１８】
【発明の実施の形態】
以下、本発明の実施例を図面に基づいて説明する。
本発明をガソリンエンジン用燃料供給装置の燃料噴射弁に適用した第１実施例を図１〜図７に示す。
図２に示すように、流体噴射弁としての燃料噴射弁１の燃料コネクタ部２１内に、弁ボディ２９、弁部材としてのノズルニードル３６、可動鉄心２５、固定鉄心２６、アジャスティングパイプ４１、スプリング２４およびフィルタ１１が収容されている。
【００１９】
燃料コネクタ部２１は磁性部と非磁性部からなるパイプ材であり、例えば複合磁性材で形成されている。燃料コネクタ部２１の一部を加熱して非磁性化することにより、図２において下方の燃料噴射側から磁性筒部２１ｃ、非磁性筒部２１ｂ、磁性筒部２１ａをこの順で形成している。非磁性筒部２１ｂと磁性筒部２１ｃとの境界近傍に可動鉄心２５が収納されている。燃料コネクタ部２１の内部空間は可動鉄心収納孔を構成している。磁性筒部２１ｃの燃料噴射側に弁ボディ２９および噴孔プレート２８が収納されている。燃料コネクタ部２１の図２において上方の燃料上流側に燃料中の異物を除去するフィルタ１１が取付けられている。
【００２０】
筒状の弁ボディ２９は磁性筒部２１ｃに圧入されており、磁性筒部２１ｃの内壁にレーザ溶接により固定されている。カップ状の噴孔プレート２８は磁性筒部２１ｃに圧入されており、磁性筒部２１ｃの内壁にレーザ溶接により固定され、弁ボディ２９の燃料噴射側端面に当接している。噴孔プレート２８は薄板状に形成されており、中央部に図示しない複数の噴孔が形成されている。ノズルニードル３６はステンレスからなる有底筒状体である。ノズルニードル３６の燃料噴射側は燃料上流側に比べて小径の円柱状に形成されている。可動鉄心２５は磁性ステンレス等の強磁性材料からなる段付きの筒状体である。
【００２１】
固定鉄心２６は、磁性ステンレス等の強磁性材料からなる円筒体である。固定鉄心２６の可動鉄心２５との当接面には、めっきによりクロム薄膜を形成している。固定鉄心２６の内壁にアジャスティングパイプ４１が圧入固定されている。スプリング２４の一端は可動鉄心２５に当接し、スプリング２４の他端はアジャスティングパイプ４１に当接している。アジャスティングパイプ４１の圧入量によりスプリング２４の付勢力が調整されている。圧入に替え、アジャスティングパイプ４１を固定鉄心２６にねじ結合する構成でもよい。
【００２２】
スプール３０は燃料コネクタ部２１の外周に装着されており、スプール３０の外周にコイル３１が巻回されている。燃料コネクタ部２１の外周に形成された樹脂モールド１３の外壁から突出するようにコネクタ部１６が設けられており、コイル３１と電気的に接続しているターミナル１２がコネクタ部１６に埋設されている。ターミナル１２は部分的に樹脂製のリブ１７により覆われている。
【００２３】
磁性部材２３はコイル３１の外周を覆っている。磁性部材１８はコイル３１の燃料上流側に中心角約２５０度の扇状にリブ１７をさけるように設けられている。樹脂モールド１５は磁性部材１８、２３の外周に形成され樹脂モールド１３と結合している。ノズルニードル３６、固定鉄心２６、磁性筒部２１ａ、２１ｃ、磁性部材１８、２３は、コイル３１への通電オン中に発生する磁束が通る磁気回路を構成する。
【００２４】
フィルタ１１を通じて円筒部材１４内に流入する燃料は、アジャスティングパイプ４１の内部空間、アジャスティングパイプ４１の内部空間、固定鉄心２６の内部空間、アーマチュア２５の内部空間、ノズルニードル３６の内部通路３６ａを経て出口孔３６ｂから図示しない燃料溜まり孔に導かれ、ノズルニードル３６の当接部と弁ボディ２９の弁座とのシート部位に到る。ノズルニードル３６の当接部が弁ボディ２９の弁座に着座すると燃料溜まり孔と噴孔との連通が遮断され、ノズルニードル３６の当接部が弁ボディ２９の弁座から離座すると燃料溜まり孔と噴孔との連通が開放される。
【００２５】
上記構成の燃料噴射弁１においては、燃料コネクタ部２１の内周に固定鉄心２６を圧入により固定しているため、固定鉄心２６の圧入量を調整することで、ノズルニードル３６のリフト量（固定鉄心２６と可動鉄心２５との間のギャップ量）を簡単に調整できる。ここで、燃料コネクタ部２１および固定鉄心２６はリフト量調整手段を構成している。
【００２６】
次に、燃料噴射弁１の流量調整装置のシステム構成について、図１を用いて説明する。
【００２７】
流量調整装置１００は、圧入材としての固定鉄心２６を被圧入材としての燃料コネクタ部２１に所定長さだけ圧入して圧入連結部材２０を形成し、燃料噴射弁１０の流量を調整する装置であって、ポンプ５０と、流体供給手段５１と、流量計測手段としての流量計５２と、燃料コネクタ部２１をクランプし保持するシリンダ１１１と、固定鉄心２６を燃料コネクタ部２１に向けて押圧する圧入手段としての加圧装置１２０と、圧入荷重Ｆに対する固定鉄心２６および燃料コネクタ部２１の圧入方向への変形量または歪み量の計測値または計算値Ｓ１（Ｆ）、ならびに加圧装置１２０の固定鉄心２６との当接部における圧入荷重Ｆに対する圧入方向への変位量の計測値または計算値Ｓ２（Ｆ）から固定鉄心２６の移動目標値を補正し設定する図示しない補正量設定手段と、固定鉄心２６の燃料コネクタ部２１に対する圧入荷重Ｆまたはその反力−Ｆを検知する荷重検知手段としての荷重計１１５と、基準位置に対する固定鉄心２６の圧入方向への移動量(圧入量)を検知する移動量検知手段としてのリニアアクチュエータ１１６と、流量計５２、荷重計１１５およびリニアアクチュエータ１１６の出力信号、ならびに上記補正量設定手段の設定する補正量を入力し、加圧装置１２０を操作する制御手段としてのコントローラ１３０とから構成される。
【００２８】
流体供給手段５１は、ポンプ５０により燃料タンク１５０から圧送される流体としての試験油を燃料噴射弁１０に供給するための通路を有する流体供給手段であり、ポンプ５０から後述する圧入パンチ１２２に形成される供給口１２２ａまで延びている。
【００２９】
流量計５２は、流体供給手段５１に設けられ、流体供給手段５１内を通過した試験油の流量を計測してコントローラ１３０にパルス信号として発信するものであって、ギヤポンプ式（体積式）流量計である。流量計測手段５２は、試験油の流量を正確に計測できるように、流量計測手段５２の出入口の圧力差を検出し、補正可能な構成となっている。
【００３０】
シリンダ１１１は、位置の基準となる安定したテーブル１１９の下に設置されており、加圧装置１２０は上記テーブル１１９の上に設置されている。圧入連結部材２０を製造する際は、燃料コネクタ部２１をシリンダ１１１により保持するとともに、燃料コネクタ部２１の圧入部に固定鉄心２６をセットして加圧装置１２０により圧入する。加圧装置１２０は、フレーム１２１を介してテーブル１１９に立設されており、固定鉄心２６に当接する圧入パンチ１２２と、荷重計１１５およびリニアアクチュエータ１１６を介して圧入パンチ１２２に当接する図示しない制御装置を有するサーボモータ１２３とを備える。圧入パンチ１２２には、流体供給手段５１と、固定鉄心２６および燃料コネクタ部２１の内部とに連通する供給口１２２ａが形成されている。
【００３１】
加圧装置１２０が固定鉄心２６を加圧する加圧力（圧入荷重Ｆ）を検知する荷重計１１５の出力は、図示しないオペアンプによって増巾された後、図示しないＡ／Ｄ変換器によりディジタル信号に変換されてコントローラ１３０に入力される。また固定鉄心２６の圧入位置を計測するリニアアクチュエータ１１６は、サーボモータ１２３の底面に接触し、基準位置からの距離に比例した数のパルス信号を発信し、発信されたパルス信号は図示しないパルスカウンターでカウント(積算)され、図示しないエンコーダでコード化されてコントローラ１３０に入力される。
【００３２】
コントローラ１３０は、ハードウェアとしてのマイクロコンピュータと、ソフトウェアとしてのアプリケーションプログラムとからなっている。そして、圧入荷重Ｆに対する固定鉄心２６および燃料コネクタ部２１の圧入方向への変形量または歪み量の計測値、あるいは計算値Ｓ１（Ｆ）、加圧装置１２０の固定鉄心２６との当接部における圧入荷重Ｆに対する圧入方向への変位量の計測値または計算値Ｓ２（Ｆ）、圧入連結部材２０の製造データ等はキーボード等の図示しない入力手段から入力され、流量調整装置１００に関するデータは図示しない表示装置や図示しない印字装置に出力することができる。
【００３３】
第１実施例の流量調整装置１００においては、コントローラ１３０は、圧入荷重Ｆに対する補正量Ｓ１（Ｆ）、Ｓ２（Ｆ）を考慮せずに目標圧入長さ（図３に示すＬ１）の近傍にまで固定鉄心２６を圧入するように加圧装置１２０を操作する荒圧入制御と、荒圧入後の目標圧入長さ（Ｌ１）までの残余の長さ分（図３に示すＬ２）を２段階に分け、それぞれ圧入荷重Ｆに対する補正量Ｓ１（Ｆ）、Ｓ２（Ｆ）を加味して圧入長を決めて圧入を行う第１の圧入工程としてのリハーサル圧入工程および第２の圧入工程としての精密圧入工程の本圧入制御とを行うようにしている。なお、コントローラ１３０は、上記荒圧入制御においても、圧入荷重Ｆに対するＳ１（Ｆ）、Ｓ２（Ｆ）を考慮してこれを加味して圧入制御を行うことも可能である。
【００３４】
ここで、補正量Ｓ１（Ｆ）、Ｓ２（Ｆ）を加味する理由について説明する。圧入荷重によって圧入材及び被圧入材に生じる変形と、同じ圧入荷重によって圧力装置に生じる変形とは、圧入量に対する誤差許容量が小さくなると無視できなくなり、目標の精度が得られなくなる。すなわち、図４（Ａ）および（Ｂ）に示す圧入パンチ１２２から圧入連結部材２０に加えられた圧力荷重により圧入連結部材２０が弾性変形し、その変位の圧入方向成分の加算値Ｓ１（Ｆ）（誤差要素）を含んだものがリニアアクチュエータ１１６によって計測されることとなる。なお、図４（Ａ）および（Ｂ）において、ａは設備側移動量を示し、ｂは製品側移動量を示している。
【００３５】
同様に、固定鉄心２６に圧入荷重Ｆを加えることにより、圧入荷重Ｆとその反力−Ｆによって流量調整装置１００が変形する。例えば圧入パンチ１２２は、サーボモータ１２３による圧入方向への推力と、上記反力−Ｆによる反対方向の力とを受けて弾性変形し、フレーム１２１も僅かに弾性変形する。それらの変形の加算値Ｓ２（Ｆ）は固定鉄心２６との当接点における圧入方向の位置ずれとなって表れ、誤差要素Ｓ２（Ｆ）を含んだものがリニアアクチュエータ１１６によって計測されることとなる。
【００３６】
このため、上記誤差要素Ｓ１（Ｆ）、Ｓ２（Ｆ）を考慮することなく圧入操作量を目標圧入長さ（Ｌ１）そのものとして制御すれば、図５（Ａ）および（Ｂ）に示すように、工程終了後の弾性復元により上記Ｓ１（Ｆ）、Ｓ２（Ｆ）が製造誤差となる。ここで、図５（Ａ）は、図４（Ａ）および（Ｂ）における設備側移動量（ａ）と製品側移動量（ｂ）との関係を示しており、図５（Ｂ）は時間に対する圧入方向の荷重および移動量の変化量を示している。
【００３７】
上記補正量（加算値）Ｓ１（Ｆ）、Ｓ２（Ｆ）は、実測またはコンピュータシミュレーション等の計算により定めることができ、通常の弾性変形の領域では、圧入荷重Ｆに対する１次関数として設定することができる。すなわち図３に示すように、圧入荷重なし時のＣ（調整後目標値）はＡからＢの移動量と流量変化から計算できる。そして、荷重あり時でのｃ（荷重あり時調整目標値）も各圧入時のａ、ｂおよびｃに圧入荷重に差がなければ、圧入方向の圧入荷重Ｆから計算できる。よって、圧入方向の変形量を予め設定しておけば、問題のないレベルで調整可能である。したがって、圧入荷重差が発生した場合のａからｂ１よりｃ１を計算し、荷重変化分を最終圧入時（精密圧入時）の補正を加えることにより、精度よく目標圧入長さに合致した圧入が行える。
【００３８】
次に、上記の構成の流量調整装置１００の作動について、図１および図６を用いて説明する。
(1) 図６のステップＳ１において、ポンプ５０から流体供給手段５１に圧送される試験油を圧入連結部材２０に送出し、流量計５２により試験油の流量を計測する。そして、図６のステップＳ２において、操作圧入量を目標値(目標圧入長さ)Ｌ１の９０％程度の値、すなわち目標圧入長さ（Ｌ１）から所定長（Ｌ２）を引いた長さ（Ｌ１−Ｌ２）に設定し、サーボモータ１２３の制御装置に指令する。これが荒圧入工程である。荒圧入工程でのモータの最大回転数は、圧入距離が長く、圧入時間を稼ぐため、これ以降の本圧入工程でのモータの回転数より高く設定される。また、各圧入時における静的流量Ｑの値を所定値となるように圧入量を調整する。
【００３９】
(2) 次に、図６のステップＳ３において、荒圧入後における固定鉄心２６の圧入量をリニアアクチュエータ１１６により計測する。また、本圧入時の圧入荷重Ｆ１を荷重計１１５で計測する。
(3) 次に、図６のステップＳ４において、荒圧入後の固定鉄心２６の計測した圧入長さと目標圧入長さ（Ｌ１）との差を求め、この差の所定長に圧入荷重Ｆ１に対する補正量Ｓ１（Ｆ１）、Ｓ２（Ｆ２）を加えた圧入長さで圧入操作量を決定する。次いで図６のステップＳ５において、リハーサル圧入工程を行う。
【００４０】
(4) 次に、図６のステップＳ６において、リハーサル圧入工程後における固定鉄心２６の圧入長をリニアアクチュエータ１１６により計測する。またリハーサル圧入時の圧入荷重Ｆ２を荷重計１１５で計測する。
(5) 次に、図６のステップＳ７において、リハーサル圧入工程後の固定鉄心２６の計測した圧入長さと目標圧入長さ（Ｌ１）との差（Ｌ３）を求め、この差（Ｌ３）に圧入荷重Ｆ２に対する補正量Ｓ１（Ｆ２）、Ｓ２（Ｆ２）を加えた長さで圧入操作量を決定する。次いで図６のステップＳ８において、精密圧入工程を行うことで終了する。
【００４１】
以上が連続的な流量調整方法の流れである。第１実施例においては、流量計５２からのパルス信号を入力し、そのパルス信号のパルス巾である時間を計測することで流量として計測確認し、流量計測しながらサーボモータ１２３に回転指令を与え、圧入パンチ１２２により固定鉄心２６を押圧する一連の動作を多段階に並行して行っている。
【００４２】
以上説明したように、第１実施例の流量調整装置１００を用いて圧入を行えば、各圧入時の圧入荷重から精密圧入時の荷重を推測し移動目標値を補正する。このため、圧入の操作量は誤差要素を考慮した移動目標値に設定されるので、圧入荷重を印加したことによる変形誤差を除いた圧入量が得られる。したがって、圧入工程の後で部材が変形誤差の分だけ弾性復元し、圧入工程中の弾性変形による製造誤差を生じることがなく、精度のよい調整を行うことができる。さらに、静的流量を測定しながら固定鉄心２６の圧入量を調整するため、ニードルリフト量への製品要求を換算させる必要がなく、容易に調整可能であり、調整精度を向上するとともに、調整時間を短縮することができる。
【００４３】
また、静的流量を構成する要素として噴孔流量とシート流量があり、シート流量を構成する中にニードルリフト量が挙げられる。従来のように、ニードル流量で静的流量を調整する場合、噴孔流量下でニードルリフトとの相関が必要である。そして、その相関には、データの信頼性が絡むため、所定の管理幅（信頼区間）が必要である。したがって、ニードルリフト量で調整する場合、製造上のリフト管理値は、製品特性上の許容値より厳しい値となることが一般的である。一方、第１実施例においては、図７に示すように、製造上の許容値で管理できるため、部品精度のばらつきによる影響を防止することができる。
【００４４】
（第２実施例）
第２実施例を図８に示す。
第２実施例においては、圧入材を被圧入材に連続的に圧入調整するものであり、流量調整装置の構成については図１に示す第１実施例と実質的に同一であるため、流量調整装置の構成についての説明を省略する。
【００４５】
図５に示す第１実施例では、多段階に圧入工程を分けて圧入位置を調整し、静止摩擦と動摩擦とを繰り返すため、設備側移動量（ａ）に対して製品側移動量（ｂ）が追従しない領域（スティック領域）以上に移動量を設定する必要がある。このことは、製品の変形分と設備変形分とが考えられるが、このような領域では微調整が不可能である。そこで、第２実施例においては、図８に示すように、連続的に一旦静止摩擦から動摩擦に移行したら、その状態を保ちながら圧入していき、その状態毎の荷重から移動目標値をフィードバック補正して調整することで、微小な流量調整が可能となり加工精度の向上が図れる。ここで、図８（Ａ）は、設備側移動量（ａ）と製品側移動量（ｂ）との関係を示しており、図８（Ｂ）は時間に対する圧入方向の荷重および移動量の変化量を示している。
【００４６】
第２実施例においては、微調整可能な連続式圧入を行うことにより動摩擦域で調整可能であるため、圧入部の静止摩擦力と動摩擦力との変動等による誤差が生じることがなく、多段階の圧入調整に比べて極めて高精度の圧入調整を実施することができる。
【００４７】
（第３実施例）
本発明の第３実施例について説明する。
第３実施例においては、圧入材を被圧入材を段階的に圧入調整するものであり、流量調整装置の構成については図１に示す第１実施例と実質的に同一であるため、流量調整装置の構成についての説明を省略する。
【００４８】
第３実施例による燃料噴射弁１の流量調整方法を図９に基づいて説明する。
(1) 図９のステップＳ１１において、燃料噴射弁１のリフト量を計測する。ここで計測される燃料噴射弁１のリフト量は、上述したようにノズルニードル３６のリフト量（固定鉄心２６と可動鉄心２５との間のギャップ量）であり、個々の燃料噴射弁１に固有のリフト量である。また、燃料噴射弁１のリフト量とともに、このリフト量に対応する個々の燃料噴射弁１に固有の噴射量を計測する。噴射量の計測は、燃料噴射弁１に試験油を供給することにより実施する。
そして、ステップ１２において、ステップＳ１１で計測された燃料噴射弁１に固有のリフト量および噴射量から、その燃料噴射弁１に固有のリフト量と噴射量との相関関係を算出する。算出されるリフト量と噴射量との相関関係は、例えば相関式あるいはマップからなる相関データとして流量調整装置１００の図示しない記憶部に記憶される。
【００４９】
(2) 次に、ステップＳ１３において、固定鉄心２６を燃料コネクタ部２１に第一所定リフト量まで圧入する（第一圧入工程）。このとき、圧入荷重の安定値Ｐおよび圧入材である固定鉄心２６の移動量を計測する。
(3) 第一圧入工程が完了すると、ステップＳ１４において、計測された圧入荷重の安定値Ｐを固定鉄心２６に加えた状態で燃料噴射弁１へ試験油を供給し、燃料噴射弁１の第一噴射量ａを計測する（第一計測工程）。
そして、ステップＳ１５において、計測された燃料噴射弁１の第一噴射量ａならびにステップＳ１２で算出した相関データに基づいて、計測された第一噴射量ａに対応する計算リフト量Ａを算出する。
【００５０】
(4) 次に、ステップＳ１６において、固定鉄心２６を燃料コネクタ部２１に第二所定リフト量まで圧入する（第二圧入工程）。このとき、圧入荷重の安定値Ｑおよび固定鉄心２６の移動量Ｘを計測する。
(5) 第二圧入工程が完了すると、ステップＳ１７において、圧入荷重の安定値Ｑを維持した状態すなわち安定値Ｑで固定鉄心２６を押圧しながら燃料噴射弁１へ試験油を供給し、燃料噴射弁１の第二噴射量ｂを計測する（第二計測工程）。
【００５１】
(6) そして、ステップＳ１８において、ステップＳ１７で計測された第二噴射量ｂならびにステップ１２で算出された相関データに基づいて、計測された第二噴射量ｂに対応するリフト量を算出する。このとき算出されるリフト量は、第二圧入工程完了後において固定鉄心２６に安定値Ｑが加えられた加圧状態の加圧リフト量Ｂである。
(7) また、ステップＳ１９において、固定鉄心２６に加えられる圧入荷重を完全に解除した状態で燃料噴射弁１に試験油を供給し、燃料噴射弁１の第三噴射量ｃを計測する（第三計測工程）。
【００５２】
(8) そして、ステップＳ２０において、ステップＳ１９で計測された第三噴射量ｃならびにステップＳ１２で算出された相関データに基づいて、計測された第三噴射量ｃに対応するリフト量を算出する。このとき算出されるリフト量は、第二圧入工程完了後において固定鉄心２６に荷重が加えられていない無加圧状態の無加圧リフト量Ｃである。
(9) 加圧状態の加圧リフト量Ｂおよび無加圧状態の無加圧リフト量Ｃの算出が完了すると、ステップＳ２１において、ステップＳ１６で計測された第二圧入工程における固定鉄心２６の移動量Ｘ、ステップＳ１５で算出された計算リフト量Ａ、ステップＳ１８で算出された加圧リフト量Ｂ、ステップＳ２０で算出された無加圧リフト量Ｃ、ならびに最終リフト量から所定の相関式を用いて固定鉄心２６の目標移動量Ｌを算出する。最終リフト量とは、燃料噴射弁１に要求される噴射量に対応して設定されるノズルニードル３６のリフト量であり、所定の噴射量を達成するための各燃料噴射弁１に固有の値である。
【００５３】
(10) 次に、ステップＳ２２において、ステップＳ２１で算出された目標移動量Ｌに応じて固定鉄心２６を燃料コネクタ部２１へ圧入する（第三圧入工程）。
(11) 次に、ステップＳ２３において、第三圧入工程が実施された燃料噴射弁１に試験油を供給し、噴射量ｄを計測する（第四計測工程）。これにより、燃料噴射弁１の最終的な噴射量が計測され、固定鉄心２６の圧入量の調整が完了する。
【００５４】
以上の手順により、燃料噴射弁１の流量すなわち噴射量の調整が実施される。以上、第３実施例では、固定鉄心２６を燃料コネクタ部２１へ圧入することにより、圧入時における圧入装置および燃料噴射弁１の弾性変形による圧入精度の低下を抑制することができる。また、第一圧入工程、第二圧入工程および第三圧入工程を実行するごとに、燃料噴射弁１からの噴射量に基づいてリフト量を算出している。これにより、固定鉄心２６の圧入量を正確に決定することができ、燃料噴射弁１による燃料噴射量を正確に調整することができる。
【００５５】
以上説明した本発明の複数の実施例では、電磁式の燃料噴射弁の流量調整に本発明を適用したが、本発明では、機械式あるいは磁力式の噴射弁の流量調整に適用してもよい。
【図面の簡単な説明】
【図１】本発明の第１実施例による燃料噴射弁の流量調整装置を示すシステム構成図である。
【図２】本発明の第１実施例の燃料噴射弁を示す縦断面図である。
【図３】本発明の第１実施例による燃料噴射弁の流量調整方法を説明するためのグラフ図である。
【図４】（Ａ）および（Ｂ）は、本発明の第１実施例による燃料噴射弁の流量調整方法を説明するための模式図である。
【図５】本発明の第１実施例による燃料噴射弁の流量調整方法を説明するためのものであって、（Ａ）は設備側移動量と製品側移動量との関係を示し、（Ｂ）は時間に対する荷重および移動量の変化量を示す特性図である。
【図６】本発明の第１実施例による燃料噴射弁の流量調整方法を説明するためのフロー図である。
【図７】本発明の第１実施例による燃料噴射弁の流量調整方法を説明するためのものであって、ニードルリフト量と静的流量との関係を示す特性図である。
【図８】本発明の第２実施例による燃料噴射弁の流量調整方法を説明するためのものであって、（Ａ）は設備側移動量と製品側移動量との関係を示し、（Ｂ）は時間に対する荷重および移動量の変化量を示す特性図である。
【図９】本発明の第３実施例による燃料噴射弁の流量調整方法を説明するためのフロー図である。
【符号の説明】
１燃料噴射弁（流体噴射弁）
２０圧入連結部材（リフト量調整手段）
２１燃料コネクタ部（被圧入部材）
２６固定鉄心（圧入部材）
２９弁ボディ
３６ノズルニードル（弁部材）
５１流体供給手段
５２流量計（流量計測手段）
１００流量調整装置
１１５荷重計（荷重検知手段）
１１６リニアアクチュエータ（移動量検知手段）
１２０加圧装置（圧入手段）
１２３サーボモータ
１３０コントローラ（制御手段）[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a flow rate adjustment device and a flow rate adjustment method for a fluid injection valve, and more particularly to a flow rate adjustment device and a flow rate adjustment method for a fuel injection valve that injects fuel into an internal combustion engine (hereinafter, the internal combustion engine is referred to as an engine).
[0002]
[Prior art]
As a fuel injection valve for an engine mounted on a vehicle, the contact portion of the nozzle needle is separated from the valve seat formed on the upstream side of the injection hole of the valve body or the contact portion is seated on the valve seat, so that the fluid is discharged from the injection hole. Injecting or blocking is known.
[0003]
Such a fuel injection valve is generally provided with a lift amount adjusting means capable of adjusting the lift amount of the nozzle needle, and by adjusting the lift amount adjusting means when the fuel injection valve is assembled, The lift amount of the nozzle needle according to the specification is adjusted, and the flow rate of the fuel injection valve is adjusted. As a lift amount adjusting means, for example, a lift amount adjusting means having a press-fit connecting member formed by press-fitting a press-fit material into a press-fit material is known.
[0004]
[Problems to be solved by the invention]
By the way, as a conventional method for adjusting the flow rate of the fuel injection valve, the static flow rate of the fuel injection valve (the amount injected per unit time when the nozzle needle is held at the maximum lift position under a specified pressure) Converted to the lift amount, the fixed iron core as the press-fit material is formed separately from the fuel connector portion as the press-fit material so that the lift amount falls within a predetermined standard, and the axial direction with respect to the fuel connector portion The injection amount of the fuel injection valve is adjusted by press-fitting a fixed iron core into the cylinder. In this case, for example, a method of adjusting the press-fitting position by dividing the press-fitting process into multiple steps such as rough press-fitting, rehearsal press-fitting and precision press-fitting, and adjusting the needle valve to the target lift amount can be considered.
[0005]
However, in the above method, if the amount of deformation in the press-fitting direction between the equipment and the workpiece against the press-fitting load is a fixed value, the press-fitting load at the time of multi-stage press-fitting varies, and the accuracy after precision press-fitting deteriorates. was there. Hereinafter, the problem of the conventional flow rate adjustment method will be described in detail.
(1) In the method in which the fixed iron core is inserted into the fuel connector part in multiple stages with rough press-in, rehearsal press-in, and precision press-in, the rehearsal press-in and precision press-in conditions are the same, and rehearsal during precision press-in is performed by rehearsal press-in. It is conceivable to carry out pre-correction in precision press-fitting. However, even if the press-fitting equipment conditions are matched as an actual problem, it is extremely difficult to manage the parts with the same precision, which leads to high costs. Therefore, since variations due to the quality of parts are actually unavoidable, if there is a difference in the press-fitting load between the precision press-fitting and the rehearsal press-fitting, the adjustment accuracy after the precision press-fit is deteriorated accordingly.
(2) Repeating press-fitting, lift measurement, and press-fitting in multiple stages will repeat static friction and dynamic friction during press-fitting, and the energy below the transition from static friction to dynamic friction (the workpiece side movement amount is less than the equipment side movement amount). In the non-following area), it is possible to send the press-fitting amount in terms of equipment. However, since the fixed iron core does not actually move, it is difficult to control the moving amount of the fixed iron core. Therefore, the multi-stage press-fitting method is not suitable for fine adjustment such as re-press-fitting.
[0006]
(3) In order to convert the flow rate adjustment value of the fuel injection valve into the lift amount of the needle valve, it is necessary to correlate the lift amount and the flow rate. In the first place, there are the nozzle hole flow rate and the seat flow rate as elements constituting the static flow rate of the fuel injection valve, and the lift amount is mentioned as an element constituting the seat flow rate. When adjusting the static flow rate with the lift amount, a correlation between the lift amount and the flow rate is necessary under the nozzle hole flow rate, and the correlation is related to the reliability of the data. Therefore, there is a problem that the control value for the lift amount must be strictly controlled more than the allowable value in the product characteristics.
[0007]
The present invention has been made to solve such a problem, and an object thereof is to provide a flow rate adjusting device and a flow rate adjusting method for a fluid injection valve that can be easily adjusted and improve the adjustment accuracy.
Another object of the present invention is to provide a fluid injection valve flow rate adjusting device and a flow rate adjusting method capable of reducing the adjustment time.
Still another object of the present invention is to provide a flow rate adjusting device and a flow rate adjusting method for a fluid injection valve that prevent the influence of variations in component accuracy.
[0008]
[Means for Solving the Problems]
According to the flow rate adjusting device for a fluid injection valve according to claim 1 of the present invention, the correction amount setting means includes a measured value or a calculated value of the amount of deformation or strain in the press-fitting direction of the press-fitting connection member with respect to the press-fitting load, and the press-fitting means. The movement target value of the press-fit material is corrected and set from the measured value or the calculated value of the displacement amount in the press-fit direction with respect to the press-fit load at the contact portion with the press-fit material. Further, the control means press-fits the press-fitting material into the press-fit material according to the flow rate of the fluid passing through the fluid supply means, the output signals of the load detection means and the movement amount detection means, and the correction amount set by the correction amount setting means. Adjust the amount. For this reason, the operation amount for press-fitting is set to a movement target value in consideration of an error element, so that a press-fitting amount excluding a deformation error due to application of a press-fitting load can be obtained. Therefore, the member is elastically restored by the deformation error after the press-fitting process, and a manufacturing error due to the elastic deformation during the press-fitting process does not occur, and accurate adjustment can be performed. Furthermore, since the press-fitting amount of the press-fitting material is adjusted while measuring the static flow rate, it is not necessary to convert the product requirement to the lift amount of the valve member, and it can be adjusted easily, improving the adjustment accuracy and adjusting. Time can be shortened.
[0009]
Also, by adjusting the press-fitting amount of the press-fitting material while measuring the static flow rate, it becomes possible to combine the static flow rate and the lift amount of the valve member, so that it can be managed with manufacturing tolerances. Therefore, the management becomes easy and the influence due to the variation of the component accuracy can be prevented.
[0010]
According to the fluid injection valve flow rate adjusting device of the second aspect of the present invention, the control means operates the press-fitting means in the first press-fitting process and the second press-fitting process, and the correction amount setting means is the first press-fitting process. The load at the time of press-fitting in the second press-fitting process is predicted from the press-fitting load at the time of press-fitting in the press-fitting process, and the movement target value of the press-fitted material is corrected. Therefore, the result of the first press-fitting process can be reflected in the second press-fitting process, so that a high-precision press-fitting precision can be obtained and the adjustment precision can be improved.
[0011]
According to the flow rate adjusting device for a fluid injection valve according to claim 3 of the present invention, the control means continuously operates the press-fitting means, and the correction amount setting means is a press-fit load in a state where the press-fitting portion has shifted from static friction to dynamic friction. To correct the target value of the press-fit material. Therefore, by performing continuous press-fitting that can be finely adjusted, adjustment is possible in the dynamic friction region, and errors due to fluctuations in the static friction force and dynamic friction force of the press-fitting part do not occur, and extremely high-precision press-fitting adjustment is performed. Can do.
[0012]
According to the flow rate adjusting method of the fluid injection valve according to claim 4 of the present invention, the fluid is pumped to the fluid supply means for supplying the fluid into the press-fit connection member, and the deformation amount of the press-fit connection member in the press-fit direction with respect to the press-fit load or Press-fit from the measured or calculated value of the strain amount and the measured or calculated value of the displacement in the press-fitting direction with respect to the press-fitting load at the contact portion of the press-fitting means that presses the press-fitted material against the press-fitted material The material movement target value is corrected and set, the flow rate of the fluid passing through the fluid supply means, the press-fitting load or reaction force of the press-fitting material against the press-fitting material, the amount of movement of the press-fitting material relative to the reference position in the press-fitting direction The press-fitting amount of the press-fitting material to the press-fitted material is adjusted according to the correction amount of the press-fitting material movement target value. For this reason, the operation amount for press-fitting is set to a movement target value in consideration of an error element, so that a press-fitting amount excluding a deformation error due to application of a press-fitting load can be obtained. Therefore, the member is elastically restored by the deformation error after the press-fitting process, and a manufacturing error due to the elastic deformation during the press-fitting process does not occur, and accurate adjustment can be performed. Furthermore, since the press-fitting amount of the press-fitting material is adjusted while measuring the static flow rate, it is not necessary to convert the product requirement to the lift amount of the valve member, and it can be adjusted easily, improving the adjustment accuracy and adjusting. Time can be shortened.
[0013]
Also, by adjusting the press-fitting amount of the press-fitting material while measuring the static flow rate, it becomes possible to combine the static flow rate and the lift amount of the valve member, so that it can be managed with manufacturing tolerances. Therefore, the management becomes easy and the influence due to the variation of the component accuracy can be prevented.
[0014]
According to the flow rate adjusting method of the fluid injection valve according to claim 5 of the present invention, the press-fitting means is operated separately in the first press-fitting step and the second press-fitting step, and the press-fitting load at the press-fitting in the first press-fitting step is determined. The load at the time of press-fitting in the second press-fitting process is predicted, and the movement target value of the press-fitted material is corrected. Therefore, the result of the first press-fitting process can be reflected in the second press-fitting process, so that a high-precision press-fitting precision can be obtained and the adjustment precision can be improved.
[0015]
According to the flow rate adjusting method for a fluid injection valve according to claim 6 of the present invention, the movement target value of the press-fit material is corrected from the press-fit load in a state where the press-fit portion has shifted from static friction to dynamic friction. Therefore, by performing continuous press-fitting that can be finely adjusted, adjustment is possible in the dynamic friction region, and errors due to fluctuations in the static friction force and dynamic friction force of the press-fitting part do not occur, and extremely high-precision press-fitting adjustment is performed. Can do.
[0017]
Of the present invention Claim 7 According to the flow rate adjusting method of the fluid injection valve described, the stable value of the press-fitting load is measured in the first press-fitting step, the second press-fitting step, and the third press-fitting step. Thereby, it becomes possible to confirm that the press-fitting material is reliably moved with respect to the press-fitting material. Further, by calculating the pressure lift amount and the non-pressure lift amount after the second press-fitting process, the final lift amount including the lift amount error caused by the elastic deformation of the fluid injection valve due to the presence or absence of the press-fitting load A target movement amount is calculated. Therefore, the press-fitting material can be press-fitted with the final lift amount of the valve member in a non-pressurized state without a press-fitting load as a target. In addition, by calculating the target movement amount for the final lift amount from the movement amount of the press-fitting material, the calculated lift amount, the pressurized lift amount, the non-pressurized lift amount and the final lift amount in the second press-fitting process, The amount of movement of the press-fitting material in the three press-fitting process is reduced. Therefore, the amount of press-fitting movement of the press-fitted material to the press-fitted material in the third press-fitting step is smaller than the total amount of press-fitting, and the change of the press-fitting load is reduced. Therefore, the flow rate of the fluid injection valve can be easily adjusted, and the adjustment accuracy can be improved.
[0018]
DETAILED DESCRIPTION OF THE INVENTION
Embodiments of the present invention will be described below with reference to the drawings.
A first embodiment in which the present invention is applied to a fuel injection valve of a fuel supply device for a gasoline engine is shown in FIGS.
As shown in FIG. 2, in the fuel connector portion 21 of the fuel injection valve 1 as a fluid injection valve, a valve body 29, a nozzle needle 36 as a valve member, a movable iron core 25, a fixed iron core 26, an adjusting pipe 41, a spring 24 and the filter 11 are accommodated.
[0019]
The fuel connector portion 21 is a pipe material composed of a magnetic portion and a non-magnetic portion, and is formed of, for example, a composite magnetic material. By heating a part of the fuel connector portion 21 to make it nonmagnetic, a magnetic cylinder portion 21c, a nonmagnetic cylinder portion 21b, and a magnetic cylinder portion 21a are formed in this order from the lower fuel injection side in FIG. . A movable iron core 25 is accommodated in the vicinity of the boundary between the nonmagnetic cylinder portion 21b and the magnetic cylinder portion 21c. The internal space of the fuel connector portion 21 constitutes a movable iron core accommodation hole. A valve body 29 and an injection hole plate 28 are accommodated on the fuel injection side of the magnetic cylinder portion 21c. A filter 11 that removes foreign matters in the fuel is attached to the upstream side of the fuel upstream of the fuel connector portion 21 in FIG.
[0020]
The cylindrical valve body 29 is press-fitted into the magnetic cylinder portion 21c, and is fixed to the inner wall of the magnetic cylinder portion 21c by laser welding. The cup-shaped injection hole plate 28 is press-fitted into the magnetic cylinder portion 21c, is fixed to the inner wall of the magnetic cylinder portion 21c by laser welding, and is in contact with the fuel injection side end face of the valve body 29. The nozzle hole plate 28 is formed in a thin plate shape, and a plurality of nozzle holes (not shown) are formed at the center. The nozzle needle 36 is a bottomed cylindrical body made of stainless steel. The fuel injection side of the nozzle needle 36 is formed in a cylindrical shape having a smaller diameter than the fuel upstream side. The movable iron core 25 is a stepped cylindrical body made of a ferromagnetic material such as magnetic stainless steel.
[0021]
The fixed iron core 26 is a cylindrical body made of a ferromagnetic material such as magnetic stainless steel. A chromium thin film is formed on the contact surface of the fixed iron core 26 with the movable iron core 25 by plating. An adjusting pipe 41 is press-fitted and fixed to the inner wall of the fixed iron core 26. One end of the spring 24 is in contact with the movable iron core 25, and the other end of the spring 24 is in contact with the adjusting pipe 41. The urging force of the spring 24 is adjusted by the amount of press-fitting of the adjusting pipe 41. Instead of press-fitting, a configuration in which the adjusting pipe 41 is screwed to the fixed iron core 26 may be used.
[0022]
The spool 30 is attached to the outer periphery of the fuel connector portion 21, and a coil 31 is wound around the outer periphery of the spool 30. The connector portion 16 is provided so as to protrude from the outer wall of the resin mold 13 formed on the outer periphery of the fuel connector portion 21, and the terminal 12 electrically connected to the coil 31 is embedded in the connector portion 16. . The terminal 12 is partially covered with a resin rib 17.
[0023]
The magnetic member 23 covers the outer periphery of the coil 31. The magnetic member 18 is provided on the fuel upstream side of the coil 31 so as to avoid the rib 17 in a fan shape with a central angle of about 250 degrees. The resin mold 15 is formed on the outer periphery of the magnetic members 18 and 23 and is coupled to the resin mold 13. The nozzle needle 36, the fixed iron core 26, the magnetic cylinder portions 21 a and 21 c, and the magnetic members 18 and 23 constitute a magnetic circuit through which a magnetic flux generated during energization of the coil 31 passes.
[0024]
The fuel flowing into the cylindrical member 14 through the filter 11 passes through the internal space of the adjusting pipe 41, the internal space of the adjusting pipe 41, the internal space of the fixed iron core 26, the internal space of the armature 25, and the internal passage 36a of the nozzle needle 36. Then, it is led from the outlet hole 36 b to a fuel reservoir hole (not shown) and reaches the seat portion between the contact portion of the nozzle needle 36 and the valve seat of the valve body 29. When the contact portion of the nozzle needle 36 is seated on the valve seat of the valve body 29, the communication between the fuel reservoir hole and the injection hole is blocked, and when the contact portion of the nozzle needle 36 is separated from the valve seat of the valve body 29, the fuel reservoir is stored. The communication between the hole and the nozzle hole is released.
[0025]
In the fuel injection valve 1 having the above configuration, the fixed iron core 26 is fixed to the inner periphery of the fuel connector portion 21 by press-fitting. Therefore, the lift amount (fixed) of the nozzle needle 36 is adjusted by adjusting the press-fitting amount of the fixed iron core 26. The gap amount between the iron core 26 and the movable iron core 25 can be easily adjusted. Here, the fuel connector portion 21 and the fixed iron core 26 constitute lift amount adjusting means.
[0026]
Next, the system configuration of the flow rate adjusting device of the fuel injection valve 1 will be described with reference to FIG.
[0027]
The flow rate adjusting device 100 is a device that adjusts the flow rate of the fuel injection valve 10 by press-fitting a fixed core 26 as a press-fit material into a fuel connector portion 21 as a press-fit material by a predetermined length to form a press-fit connecting member 20. The pump 50, the fluid supply means 51, the flow meter 52 as the flow rate measuring means, the cylinder 111 that clamps and holds the fuel connector portion 21, and the press-fitting that presses the fixed iron core 26 toward the fuel connector portion 21. Pressurizing device 120 as means, measured value or calculated value S1 (F) of a deformation amount or a deformation amount in the press-fitting direction of fixed iron core 26 and fuel connector portion 21 with respect to press-fitting load F, and fixed iron core of pressurizing device 120 The figure which correct | amends and sets the movement target value of the fixed iron core 26 from the measured value or calculated value S2 (F) of the displacement amount to the press-fit direction with respect to the press-fit load F in the contact part with 26. Correction amount setting means, a load meter 115 as load detecting means for detecting the press-fit load F or its reaction force -F with respect to the fuel connector portion 21 of the fixed iron core 26, and movement of the fixed iron core 26 in the press-fit direction with respect to the reference position The linear actuator 116 as the movement amount detecting means for detecting the amount (pressing amount), the output signals of the flow meter 52, the load meter 115 and the linear actuator 116, and the correction amount set by the correction amount setting means are inputted and added. It comprises a controller 130 as control means for operating the pressure device 120.
[0028]
The fluid supply means 51 is a fluid supply means having a passage for supplying test oil as a fluid pumped from the fuel tank 150 by the pump 50 to the fuel injection valve 10, and is formed in the press-in punch 122 described later from the pump 50. It extends to the supply port 122a.
[0029]
The flow meter 52 is provided in the fluid supply means 51, measures the flow rate of the test oil that has passed through the fluid supply means 51, and transmits it as a pulse signal to the controller 130, and is a gear pump type (volume type) flow meter. It is. The flow rate measuring means 52 is configured to detect and correct the pressure difference at the inlet / outlet of the flow rate measuring means 52 so that the flow rate of the test oil can be accurately measured.
[0030]
The cylinder 111 is installed under a stable table 119 serving as a position reference, and the pressurizing device 120 is installed on the table 119. When manufacturing the press-fit connecting member 20, the fuel connector portion 21 is held by the cylinder 111 and the fixed iron core 26 is set in the press-fit portion of the fuel connector portion 21 and press-fitted by the pressurizing device 120. The pressurizing device 120 is erected on the table 119 via the frame 121, and a press-fitting punch 122 that abuts against the fixed iron core 26 and a control (not shown) that abuts against the press-fitting punch 122 via the load meter 115 and the linear actuator 116. And a servo motor 123 having a device. The press-fitting punch 122 is formed with a supply port 122 a that communicates with the fluid supply means 51 and the fixed iron core 26 and the inside of the fuel connector portion 21.
[0031]
The output of the load meter 115 for detecting the pressurizing force (press-fit load F) by which the pressurizing device 120 presses the fixed iron core 26 is amplified by an operational amplifier (not shown) and then converted into a digital signal by an A / D converter (not shown). And input to the controller 130. The linear actuator 116 that measures the press-fit position of the fixed iron core 26 is in contact with the bottom surface of the servo motor 123 and transmits a number of pulse signals proportional to the distance from the reference position. The transmitted pulse signal is a pulse counter (not shown). Is counted (integrated), encoded by an encoder (not shown), and input to the controller 130.
[0032]
The controller 130 includes a microcomputer as hardware and an application program as software. Then, a measured value or a calculated value S1 (F) of a deformation amount or a distortion amount in the press-fitting direction of the fixed iron core 26 and the fuel connector portion 21 with respect to the press-fit load F, and a contact portion of the pressurizing device 120 with the fixed iron core 26. The measured value or calculated value S2 (F) of the displacement amount in the press-fitting direction with respect to the press-fitting load F, the manufacturing data of the press-fitting connecting member 20 and the like are input from an input unit (not shown) such as a keyboard, and the data regarding the flow rate adjusting device 100 is not shown. It can be output to a display device or a printing device (not shown).
[0033]
In the flow control device 100 of the first embodiment, the controller 130 is close to the target press-fitting length (L1 shown in FIG. 3) without considering the correction amounts S1 (F) and S2 (F) for the press-fitting load F. The rough press-fitting control for operating the pressurizing device 120 so as to press-fit the fixed iron core 26 and the remaining length (L2 shown in FIG. 3) up to the target press-fitting length (L1) after the rough press-fitting in two steps. The rehearsal press-fitting process as the first press-fitting process and the precision press-fitting process as the second press-fitting process are performed by taking into account the correction amounts S1 (F) and S2 (F) for the press-fitting load F, respectively. The main press-fitting control of the process is performed. Note that the controller 130 can also perform the press-fitting control in consideration of S1 (F) and S2 (F) with respect to the press-fitting load F in the rough press-fitting control.
[0034]
Here, the reason for adding the correction amounts S1 (F) and S2 (F) will be described. The deformation generated in the press-fitting material and the press-fitted material due to the press-fitting load and the deformation generated in the pressure device due to the same press-fitting load cannot be ignored if the error tolerance with respect to the press-fitting amount becomes small, and the target accuracy cannot be obtained. That is, the press-fit connecting member 20 is elastically deformed by the pressure load applied to the press-fit connecting member 20 from the press-fit punch 122 shown in FIGS. 4A and 4B, and the addition value S1 (F) of the press-fitting direction component of the displacement. What includes (error element) is measured by the linear actuator 116. In FIGS. 4A and 4B, a indicates the facility-side movement amount, and b indicates the product-side movement amount.
[0035]
Similarly, by applying a press-fit load F to the fixed iron core 26, the flow rate adjusting device 100 is deformed by the press-fit load F and its reaction force -F. For example, the press-fitting punch 122 is elastically deformed by receiving a thrust force in the press-fitting direction by the servo motor 123 and a force in the opposite direction by the reaction force −F, and the frame 121 is also slightly elastically deformed. The added value S2 (F) of these deformations appears as a displacement in the press-fitting direction at the contact point with the fixed iron core 26, and the one including the error element S2 (F) is measured by the linear actuator 116. .
[0036]
Therefore, if the press-fitting operation amount is controlled as the target press-fitting length (L1) itself without considering the error elements S1 (F) and S2 (F), as shown in FIGS. 5 (A) and 5 (B). The above-described S1 (F) and S2 (F) become manufacturing errors due to the elastic restoration after the process is completed. Here, FIG. 5 (A) shows the relationship between the equipment side movement amount (a) and the product side movement amount (b) in FIGS. 4 (A) and 4 (B), and FIG. 5 (B) shows the time. The amount of change in the load and amount of movement in the press-fitting direction with respect to is shown.
[0037]
The correction amounts (addition values) S1 (F) and S2 (F) can be determined by calculation such as actual measurement or computer simulation, and should be set as a linear function with respect to the press-fit load F in the normal elastic deformation region. Can do. That is, as shown in FIG. 3, C (target value after adjustment) when there is no press-fitting load can be calculated from the movement amount from A to B and the flow rate change. And c (the adjustment target value when there is a load) when there is a load can also be calculated from the press-fit load F in the press-fit direction if there is no difference in the press-fit load between a, b and c at each press-fit. Therefore, if a deformation amount in the press-fitting direction is set in advance, it can be adjusted at a level with no problem. Therefore, by calculating c1 from b1 when a press-fitting load difference occurs and correcting the load change at the time of final press-fitting (during precision press-fitting), press-fitting that matches the target press-fitting length can be performed accurately. .
[0038]
Next, the operation of the flow control device 100 having the above-described configuration will be described with reference to FIGS. 1 and 6.
(1) In step S 1 of FIG. 6, the test oil pumped from the pump 50 to the fluid supply means 51 is sent to the press-fit connecting member 20, and the flow rate of the test oil is measured by the flow meter 52. In step S2 of FIG. 6, the operation press-fit amount is a value about 90% of the target value (target press-fit length) L1, that is, a length (L1) obtained by subtracting a predetermined length (L2) from the target press-fit length (L1). -L2) and command the servo motor 123 control device. This is the rough press-fitting process. The maximum rotational speed of the motor in the rough press-fitting process is set higher than the rotational speed of the motor in the subsequent main press-fitting process in order to increase the press-fitting distance and increase the press-fitting time. Further, the press-fit amount is adjusted so that the value of the static flow rate Q at the time of each press-fit becomes a predetermined value.
[0039]
(2) Next, in step S <b> 3 of FIG. 6, the press-fitting amount of the fixed iron core 26 after the rough press-fitting is measured by the linear actuator 116. Further, the press-fitting load F1 at the time of the main press-fitting is measured by the load meter 115.
(3) Next, in step S4 in FIG. 6, the difference between the measured press-fitting length of the fixed iron core 26 after the rough press-fitting and the target press-fitting length (L1) is obtained, and the correction for the press-fitting load F1 is made to this predetermined length. The press-fitting operation amount is determined by the press-fitting length obtained by adding the amounts S1 (F1) and S2 (F2). Next, in step S5 of FIG. 6, a rehearsal press-fitting process is performed.
[0040]
(4) Next, in step S <b> 6 of FIG. 6, the press-fitting length of the fixed iron core 26 after the rehearsal press-fitting process is measured by the linear actuator 116. Further, the press-fitting load F2 at the time of rehearsal press-fitting is measured by the load meter 115.
(5) Next, in step S7 of FIG. 6, a difference (L3) between the measured press-fitting length of the fixed iron core 26 after the rehearsal press-fitting step and the target press-fitting length (L1) is obtained, and press-fitting is performed on this difference (L3). The press-fitting operation amount is determined by the length obtained by adding the correction amounts S1 (F2) and S2 (F2) to the load F2. Next, in step S8 of FIG. 6, the precision press-fitting process is performed to finish the process.
[0041]
The above is the flow of the continuous flow rate adjustment method. In the first embodiment, a pulse signal from the flow meter 52 is input, and the time that is the pulse width of the pulse signal is measured and confirmed as a flow rate, and a rotation command is given to the servo motor 123 while measuring the flow rate. A series of operations of pressing the fixed iron core 26 by the press-fitting punch 122 are performed in parallel in multiple stages.
[0042]
As described above, when press-fitting is performed using the flow rate adjusting device 100 of the first embodiment, the load at the time of precision press-fitting is estimated from the press-fitting load at the time of each press-fitting, and the movement target value is corrected. For this reason, since the operation amount of press-fitting is set to a movement target value in consideration of an error element, a press-fitting amount excluding a deformation error due to application of a press-fitting load can be obtained. Therefore, the member is elastically restored by the deformation error after the press-fitting process, and a manufacturing error due to the elastic deformation during the press-fitting process does not occur, and accurate adjustment can be performed. Further, since the press-fit amount of the fixed iron core 26 is adjusted while measuring the static flow rate, it is not necessary to convert the product requirement for the needle lift amount, and the adjustment can be easily performed, improving the adjustment accuracy, and adjusting time. Can be shortened.
[0043]
Moreover, there are a nozzle hole flow rate and a seat flow rate as elements constituting the static flow rate, and a needle lift amount can be cited as a component of the seat flow rate. When the static flow rate is adjusted with the needle flow rate as in the prior art, it is necessary to correlate with the needle lift under the nozzle hole flow rate. And since the reliability involves data reliability, a predetermined management width (confidence interval) is necessary. Therefore, when adjusting with the needle lift amount, the lift control value in manufacturing is generally a stricter value than the allowable value in product characteristics. On the other hand, in the first embodiment, as shown in FIG. 7, since it can be managed with manufacturing tolerances, it is possible to prevent the influence of variations in component accuracy.
[0044]
(Second embodiment)
A second embodiment is shown in FIG.
In the second embodiment, the press-fitting material is continuously press-fitted to the press-fitted material, and the flow rate adjusting device is substantially the same as the first embodiment shown in FIG. A description of the configuration of the apparatus is omitted.
[0045]
In the first embodiment shown in FIG. 5, the press-fitting process is divided into multiple stages, the press-fitting position is adjusted, and static friction and dynamic friction are repeated. Therefore, the product-side movement amount (b) with respect to the equipment-side movement amount (a). It is necessary to set the amount of movement more than the area that does not follow (stick area). This can be a product deformation and equipment deformation, but fine adjustment is impossible in such a region. Therefore, in the second embodiment, as shown in FIG. 8, once the transition from static friction to dynamic friction is continuously made, press-fitting is performed while maintaining the state, and the movement target value is feedback corrected from the load for each state. Thus, the flow rate can be finely adjusted, and the processing accuracy can be improved. Here, FIG. 8 (A) shows the relationship between the facility-side movement amount (a) and the product-side movement amount (b), and FIG. 8 (B) shows changes in the load and movement amount in the press-fitting direction with respect to time. Indicates the amount.
[0046]
In the second embodiment, the adjustment can be made in the dynamic friction region by performing continuous press-fitting that can be finely adjusted, so that an error due to fluctuations in the static friction force and the dynamic friction force of the press-fitting portion does not occur, and there are multiple steps. Compared with the press-fit adjustment, the press-fit adjustment with extremely high accuracy can be performed.
[0047]
(Third embodiment)
A third embodiment of the present invention will be described.
In the third embodiment, the press-fitting material is press-fitted and adjusted step by step, and the flow rate adjusting device is substantially the same as the first embodiment shown in FIG. A description of the configuration of the apparatus is omitted.
[0048]
A flow rate adjusting method for the fuel injection valve 1 according to the third embodiment will be described with reference to FIG.
(1) In step S11 of FIG. 9, the lift amount of the fuel injection valve 1 is measured. The lift amount of the fuel injection valve 1 measured here is the lift amount of the nozzle needle 36 (gap amount between the fixed iron core 26 and the movable iron core 25) as described above, and is specific to each fuel injection valve 1. Lift amount. In addition to the lift amount of the fuel injection valve 1, the injection amount specific to each fuel injection valve 1 corresponding to the lift amount is measured. The injection amount is measured by supplying test oil to the fuel injection valve 1.
In step 12, the correlation between the lift amount and the injection amount inherent to the fuel injection valve 1 is calculated from the lift amount and the injection amount inherent to the fuel injection valve 1 measured in step S11. The calculated correlation between the lift amount and the injection amount is stored in a storage unit (not shown) of the flow rate adjusting device 100 as correlation data including, for example, a correlation equation or a map.
[0049]
(2) Next, in step S13, the fixed iron core 26 is press-fitted into the fuel connector portion 21 to the first predetermined lift amount (first press-fitting step). At this time, the stable value P of the press-fitting load and the movement amount of the fixed iron core 26 that is the press-fitting material are measured.
(3) When the first press-fitting process is completed, in step S14, the test oil is supplied to the fuel injection valve 1 with the measured stable value P of the press-fitting load applied to the fixed iron core 26. One injection amount a is measured (first measurement step).
In step S15, a calculated lift amount A corresponding to the measured first injection amount a is calculated based on the measured first injection amount a of the fuel injection valve 1 and the correlation data calculated in step S12.
[0050]
(4) Next, in step S16, the fixed iron core 26 is press-fitted into the fuel connector portion 21 to the second predetermined lift amount (second press-fitting process). At this time, the stable value Q of the press-fit load and the movement amount X of the fixed iron core 26 are measured.
(5) When the second press-fitting process is completed, in step S17, test oil is supplied to the fuel injection valve 1 while pressing the fixed iron core 26 in a state where the stable value Q of the press-fitting load is maintained, that is, the stable value Q, and fuel injection The second injection amount b of the valve 1 is measured (second measurement step).
[0051]
(6) Then, in step S18, a lift amount corresponding to the measured second injection amount b is calculated based on the second injection amount b measured in step S17 and the correlation data calculated in step 12. The lift amount calculated at this time is the pressurized lift amount B in a pressurized state in which the stable value Q is added to the fixed iron core 26 after the completion of the second press-fitting process.
(7) In step S19, the test oil is supplied to the fuel injection valve 1 in a state where the press-fit load applied to the fixed iron core 26 is completely released, and the third injection amount c of the fuel injection valve 1 is measured (No. 1). Three measurement steps).
[0052]
(8) Then, in step S20, a lift amount corresponding to the measured third injection amount c is calculated based on the third injection amount c measured in step S19 and the correlation data calculated in step S12. The lift amount calculated at this time is a non-pressurized lift amount C in a non-pressurized state in which no load is applied to the fixed iron core 26 after the completion of the second press-fitting process.
(9) When the calculation of the pressurized lift amount B in the pressurized state and the non-pressurized lift amount C in the non-pressurized state is completed, the movement of the fixed iron core 26 in the second press-fitting process measured in step S16 in step S21. A predetermined correlation equation is used from the amount X, the calculated lift amount A calculated in step S15, the pressurized lift amount B calculated in step S18, the non-pressurized lift amount C calculated in step S20, and the final lift amount. Thus, the target movement amount L of the fixed iron core 26 is calculated. The final lift amount is a lift amount of the nozzle needle 36 set in correspondence with the injection amount required for the fuel injection valve 1, and is a value unique to each fuel injection valve 1 for achieving a predetermined injection amount. It is.
[0053]
(10) Next, in step S22, the fixed iron core 26 is press-fitted into the fuel connector portion 21 in accordance with the target movement amount L calculated in step S21 (third press-fitting process).
(11) Next, in step S23, test oil is supplied to the fuel injection valve 1 on which the third press-fitting step has been performed, and the injection amount d is measured (fourth measurement step). Thereby, the final injection amount of the fuel injection valve 1 is measured, and the adjustment of the press-fit amount of the fixed iron core 26 is completed.
[0054]
The flow rate of the fuel injection valve 1, that is, the injection amount is adjusted by the above procedure. As described above, in the third embodiment, by pressing the fixed iron core 26 into the fuel connector portion 21, it is possible to suppress a decrease in press-fitting accuracy due to elastic deformation of the press-fitting device and the fuel injection valve 1 during press-fitting. Further, the lift amount is calculated based on the injection amount from the fuel injection valve 1 every time the first press-fitting step, the second press-fitting step, and the third press-fitting step are executed. Thereby, the press-fitting amount of the fixed iron core 26 can be determined accurately, and the fuel injection amount by the fuel injection valve 1 can be adjusted accurately.
[0055]
In the embodiments of the present invention described above, the present invention is applied to the flow rate adjustment of an electromagnetic fuel injection valve. However, the present invention may be applied to the flow rate adjustment of a mechanical or magnetic injection valve. .
[Brief description of the drawings]
FIG. 1 is a system configuration diagram showing a fuel injection valve flow rate adjusting apparatus according to a first embodiment of the present invention;
FIG. 2 is a longitudinal sectional view showing a fuel injection valve according to a first embodiment of the present invention.
FIG. 3 is a graph for explaining a fuel injection valve flow rate adjusting method according to the first embodiment of the present invention;
FIGS. 4A and 4B are schematic views for explaining a flow rate adjusting method for a fuel injection valve according to the first embodiment of the present invention. FIGS.
FIG. 5 is a view for explaining a flow rate adjustment method for a fuel injection valve according to a first embodiment of the present invention, wherein (A) shows the relationship between the facility side movement amount and the product side movement amount; ) Is a characteristic diagram showing the amount of change in load and movement with respect to time.
FIG. 6 is a flowchart for explaining a flow rate adjusting method for a fuel injection valve according to the first embodiment of the present invention.
FIG. 7 is a characteristic diagram for explaining a flow rate adjusting method for a fuel injection valve according to the first embodiment of the present invention and showing a relationship between a needle lift amount and a static flow rate.
FIG. 8 is a view for explaining a flow rate adjusting method for a fuel injection valve according to a second embodiment of the present invention, wherein (A) shows the relationship between the facility side movement amount and the product side movement amount; ) Is a characteristic diagram showing the amount of change in load and movement with respect to time.
FIG. 9 is a flowchart for explaining a flow rate adjusting method for a fuel injection valve according to a third embodiment of the present invention.
[Explanation of symbols]
1 Fuel injection valve (fluid injection valve)
20 Press-fit connecting member (lift amount adjusting means)
21 Fuel connector (press-fit member)
26 Fixed iron core (press-fit member)
29 Valve body
36 Nozzle needle (valve member)
51 Fluid supply means
52 Flow meter (flow rate measuring means)
100 Flow control device
115 Load cell (load detection means)
116 linear actuator (movement amount detection means)
120 Pressurizing device (pressing means)
123 Servo motor
130 Controller (control means)

Claims

A valve body provided with a valve seat on the fluid upstream side of the nozzle hole, and a contact portion supported by the valve body so as to be reciprocally movable and seatable on the valve seat, wherein the contact portion is separated from the valve seat. A valve member that injects or shuts off fluid from the nozzle hole by sitting on the valve seat and the valve seat; and a press-fit connecting member that press-fits the press-fit material into the press-fit material. An apparatus for adjusting the flow rate of a fluid injection valve provided with an adjustable lift amount adjusting means,
Fluid supply means for supplying fluid into the press-fit connecting member;
A press-fitting means for pressing the press-fitting material against the press-fitted material;
A load detecting means for detecting a press-fit load or a reaction force of the press-fit material against the press-fit material; and
A moving amount detecting means for detecting a moving amount of the press-fitting material in the press-fitting direction with respect to a reference position;
A measured value or a calculated value of a deformation amount or a distortion amount of the press-fitting connection member in the press-fitting direction with respect to a press-fitting load, and a measured value of a displacement amount in the press-fitting direction with respect to the press-fitting load at a contact portion of the press-fitting means with the press-fitting material. Or correction amount setting means for correcting and setting the movement target value of the press-fit material from the calculated value;
Press-fitting of the press-fitting material into the press-fitted material according to the flow rate of the fluid passing through the fluid supply means, the output signals of the load detection means and the movement amount detection means, and the correction amount set by the correction amount setting means Control means for adjusting the amount;
A flow rate adjusting device for a fluid injection valve.

The control means operates the press-fitting means in a first press-fitting process and a second press-fitting process, and the correction amount setting means determines the second press-fitting from a press-fitting load at the time of press-fitting in the first press-fitting process. The fluid injection valve flow rate adjusting device according to claim 1, wherein a load at the time of press-fitting in a process is predicted, and a movement target value of the press-fitted material is corrected.

The control means continuously operates the press-fitting means, and the correction amount setting means corrects the movement target value of the press-fitted material from a press-fit load in a state where the press-fitting portion has shifted from static friction to dynamic friction. The fluid injection valve flow rate adjusting device according to claim 1.

A valve body provided with a valve seat on the fluid upstream side of the nozzle hole, and a contact portion supported by the valve body so as to be reciprocally movable and seatable on the valve seat, wherein the contact portion is separated from the valve seat. A valve member that injects or shuts off fluid from the nozzle hole by sitting on the valve seat and the valve seat; and a press-fit connecting member that press-fits the press-fit material into the press-fit material. A flow rate adjustment method for a fluid injection valve comprising an adjustable lift amount adjustment means,
Pumping fluid to fluid supply means for supplying fluid into the press-fit connecting member;
At a contact portion with the press-fitting material of a press-fitting means that presses the press-fitting material against the press-fitted material, and a measured value or a calculated value of a deformation amount or a strain amount in the press-fitting direction of the press-fitting connection member with respect to the press-fitting load Correcting and setting the movement target value of the press-fit material from the measured value or the calculated value of the displacement amount in the press-fit direction with respect to the press-fit load;
The flow rate of fluid passing through the fluid supply means, the press-fitting load or reaction force of the press-fitting material against the press-fitted material, the amount of movement of the press-fitting material in the press-fitting direction with respect to a reference position, and the target value of movement of the press-fitting material Adjusting the press-fitting amount of the press-fitting material with respect to the press-fitted material according to the correction amount;
A flow rate adjustment method for a fluid injection valve, comprising:

The step of adjusting the press-fitting amount of the press-fitting material to the press-fitted material includes a first press-fitting step and a second press-fitting step, and the step of correcting and setting the movement target value of the press-fitting material includes the first press-fitting 5. The fluid injection valve flow rate adjusting method according to claim 4, wherein a load at the time of press-fitting in the second press-fitting step is predicted from a press-fitting load at the time of press-fitting in the step, and a movement target value of the press-fitting material is corrected. .

5. The step of correcting and setting the movement target value of the press-fitting material corrects the movement target value of the press-fitting material from a press-fitting load in a state where the press-fitting portion has shifted from static friction to dynamic friction. Flow rate adjustment method for fluid injection valve.

A valve body provided with a valve seat upstream of the nozzle hole, and reciprocating to the valve body It has a contact portion that is movably supported and can be seated on the valve seat. The contact portion separates from the valve seat and seats on the valve seat to inject or block fluid from the nozzle hole. A flow rate adjustment method for a fluid injection valve, comprising: a valve member; and a press-fit connecting member formed by press-fitting a press-fit material into a press-fit material, and a lift amount adjusting means capable of adjusting a lift amount of the valve member. ,
  The correlation between the lift amount and the injection amount is predicted from the preset lift amount of the valve member and the injection amount of the fluid injection valve measured by supplying the fluid to the fluid injection valve. An injection amount prediction step;
  A first press-fitting step of press-fitting the press-fitted material into the press-fitted material to a first predetermined lift amount, and measuring a stable value of the press-fitting load and a movement amount of the press-fitted material;
  While pressing the press-fitting material with a stable value of the press-fitting load in the first press-fitting step, a test fluid is supplied to the fluid jet valve, and a first injection amount of the fluid jet valve at the first predetermined lift amount is measured. The first measurement step;
  A calculated lift amount calculating step of calculating a calculated lift amount of the valve member based on the correlation from the first injection amount;
  A second press-fitting step of press-fitting the press-fitting material into the press-fitted material to a second predetermined lift amount, and measuring a stable value of the press-fitting load and a movement amount of the press-fitting material;
  While pressing the press-fitting material with a stable value of the press-fitting load in the second press-fitting step, a test fluid is supplied to the fluid injection valve, and a second injection amount of the fluid injection valve at the second predetermined lift amount is measured. A second measuring step;
  A pressurizing lift amount calculating step of calculating a pressurizing lift amount after the second press-fitting step is completed based on the correlation from the second injection amount;
  After releasing the load that presses the press-fitting material, supplying a test fluid to the fluid injection valve, and measuring a third injection amount of the fluid injection valve;
  A pressureless lift amount calculating step of calculating a pressureless lift amount after the second press-fitting step is completed based on the correlation from the third injection amount;
  From the amount of movement of the press-fitting material, the calculated lift amount, the pressure lift amount, the pressureless lift amount, and the final lift amount corresponding to the required injection amount in the second press-fitting step, the valve member lift A target calculation step of calculating a target movement amount for making the amount the final lift amount;
  A third press-fitting step of press-fitting the press-fitting material into the press-fitted material based on the target movement amount calculated in the target calculation step;
  After releasing the load that presses the press-fitting material, a test fluid is supplied to the fluid injection valve, and a fourth measurement step of measuring the injection amount;
  A flow rate adjustment method for a fluid injection valve, comprising: