JP2006348836A - Fluid control device - Google Patents

Fluid control device Download PDF

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JP2006348836A
JP2006348836A JP2005175526A JP2005175526A JP2006348836A JP 2006348836 A JP2006348836 A JP 2006348836A JP 2005175526 A JP2005175526 A JP 2005175526A JP 2005175526 A JP2005175526 A JP 2005175526A JP 2006348836 A JP2006348836 A JP 2006348836A
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control valve
valve
passage
actuator
control valves
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JP4530920B2 (en
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Masaru Asari
大 浅利
Masami Oshima
正美 大島
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Honda Motor Co Ltd
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

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  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To reduce the load of an actuator which opens/closes first and second control valves while surely restricting the closing positions of the first and second control valves of a fluid control device. <P>SOLUTION: When the first and second control valves 19, 20 for opening/closing an intake passage 15 and a bypass passage 17, respectively, are driven to be opened/closed in mutually opposite directions by a common actuator, the first and second control valves 19, 20 connected to each other via a link means 21 consisting of first and second levers 39, 40 are energized to be closed by first and second torsion springs 41, 43. The closing positions of the first and second control valves 19, 20 are thereby surely restricted by the resilient force of the first and second torsion springs 41, 43 as well as the resilient force of the first torsion springs 41 is counterbalanced with that of the second torsion spring 43 even when the fist and second control valves are opened/closed in any direction. This reduces the size of the actuator and the consumption of driving energy while avoiding an increase in the load of the actuator due to the provision of the first and second torsion springs 41, 43. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

本発明は、流体が流通する第１通路と、第１通路から分岐して該第１通路を迂回する第２通路と、第１通路を開閉する第１制御バルブと、第２通路を開閉する第２制御バルブと、第１、第２制御バルブを開閉駆動する共通のアクチュエータとを備えた流体制御装置に関する。   The present invention provides a first passage through which a fluid flows, a second passage that branches from the first passage and bypasses the first passage, a first control valve that opens and closes the first passage, and opens and closes the second passage. The present invention relates to a fluid control device including a second control valve and a common actuator that opens and closes the first and second control valves.

ターボチャージャを備えたディーゼルエンジンの吸気通路にインタークーラを配置するとともに、このインタークーラをバイパスするバイパス通路の両端を吸気通路に接続し、吸気通路およびバイパス通路の分岐部の近傍にそれぞれ設けた２個の制御バルブを共通のアクチュエータで開閉駆動するものが、下記特許文献１により公知である。
特公平５−７４６８８号公報 An intercooler is disposed in an intake passage of a diesel engine equipped with a turbocharger, and both ends of a bypass passage that bypasses the intercooler are connected to the intake passage, and provided in the vicinity of branch portions of the intake passage and the bypass passage, respectively. Japanese Patent Application Laid-Open Publication No. 2004-151542 discloses that a single control valve is opened and closed by a common actuator.
Japanese Patent Publication No. 5-74688

アクチュエータで開閉される制御バルブの閉弁位置を確実に規制するには、その制御バルブをスプリング等の弾発手段で閉弁方向に付勢することが必要である。しかしながら、制御バルブを弾発手段で閉弁方向に付勢すると、アクチュエータで制御バルブを開弁する際に必要な駆動力が弾発手段の弾発力の分だけ大きくなるため、大型のアクチュエータが必要になったりアクチュエータの消費電力が増加したりする問題がある。   In order to reliably regulate the valve closing position of the control valve that is opened and closed by the actuator, it is necessary to bias the control valve in the valve closing direction by a resilient means such as a spring. However, when the control valve is urged in the valve closing direction by the resilient means, the driving force required to open the control valve by the actuator increases by the amount of the resilient force of the resilient means. There is a problem that it becomes necessary or the power consumption of the actuator increases.

本発明は前述の事情に鑑みてなされたもので、流体制御装置の第１、第２制御バルブの閉弁位置を確実に規制しながら、第１、第２制御バルブを開閉するアクチュエータの負荷を低減することを目的とする。   The present invention has been made in view of the above-described circumstances. The load on the actuator that opens and closes the first and second control valves is reliably controlled while the valve closing positions of the first and second control valves of the fluid control device are reliably regulated. The purpose is to reduce.

上記目的を達成するために、請求項１に記載された発明によれば、流体が流通する第１通路と、第１通路から分岐して該第１通路を迂回する第２通路と、第１通路を開閉する第１制御バルブと、第２通路を開閉する第２制御バルブと、第１、第２制御バルブを開閉駆動する共通のアクチュエータとを備えた流体制御装置において、第１制御バルブが開弁するときに第２制御バルブが閉弁し、第１制御バルブが閉弁するときに第２制御バルブが開弁するように該第１、第２制御バルブを連動手段で連結し、第１制御バルブを第１弾発手段で閉弁方向に付勢するとともに第２制御バルブを第２弾発手段で閉弁方向に付勢したことを特徴とする流体制御装置が提案される。   In order to achieve the above object, according to the first aspect of the present invention, a first passage through which a fluid flows, a second passage branched from the first passage and bypassing the first passage, In a fluid control device including a first control valve that opens and closes a passage, a second control valve that opens and closes a second passage, and a common actuator that opens and closes the first and second control valves, the first control valve includes: The first and second control valves are connected by interlocking means so that the second control valve is closed when the valve is opened, and the second control valve is opened when the first control valve is closed. A fluid control device is proposed in which one control valve is urged in the valve closing direction by the first elastic means and the second control valve is urged in the valve closing direction by the second elastic means.

また請求項２に記載された発明によれば、請求項１の構成に加えて、アクチュエータを第１制御バルブに接続し、第２弾発手段の弾発力を第１弾発手段の弾発力よりも強く設定したことを特徴とする流体制御装置が提案される。   According to the second aspect of the present invention, in addition to the configuration of the first aspect, the actuator is connected to the first control valve, and the elastic force of the second elastic means is the elastic force of the first elastic means. A fluid control device is proposed which is characterized by being set stronger than the force.

また請求項３に記載された発明によれば、請求項１または請求項２の構成に加えて、第１、第２制御バルブの全閉位置をそれぞれ規制するストッパ手段を設けたことを特徴とする流体制御装置が提案される。   According to a third aspect of the invention, in addition to the configuration of the first or second aspect, the stopper means for restricting the fully closed positions of the first and second control valves is provided. A fluid control device is proposed.

尚、実施例の上流側吸気通路１４および下流側吸気通路１５は本発明の第１通路に対応し、実施例の上流側バイパス通路１６および下流側バイパス通路１７は本発明の第２通路に対応し、実施例の第１捩じりばね４１は本発明の第１弾発手段に対応し、実施例の第２捩じりばね４３は本発明の第２弾発手段に対応し、実施例のストッパ突起３９ｂ，４０ｂおよびストッパボルト４２，４４は本発明のストッパ手段に対応する。   The upstream intake passage 14 and the downstream intake passage 15 of the embodiment correspond to the first passage of the present invention, and the upstream bypass passage 16 and the downstream bypass passage 17 of the embodiment correspond to the second passage of the present invention. The first torsion spring 41 of the embodiment corresponds to the first resilient means of the present invention, and the second torsion spring 43 of the embodiment corresponds to the second resilient means of the present invention. The stopper protrusions 39b and 40b and the stopper bolts 42 and 44 correspond to the stopper means of the present invention.

請求項１の構成によれば、第１通路および第２通路にそれぞれ設けた第１、第２制御バルブを共通のアクチュエータで相互に逆方向に開閉駆動する際に、連動手段で連結された第１、第２制御バルブをそれぞれ第１、第２弾発手段で閉弁方向に付勢したので、第１、第２弾発手段の弾発力で第１、第２制御バルブの閉弁位置を確実に規制することができるだけでなく、第１、第２制御バルブを何れの方向に開閉する場合でも第１、第２弾発手段の弾発力が相殺するので、第１、第２弾発手段を設けたことによるアクチュエータの負荷増大を回避して該アクチュエータの小型化や駆動エネルギーの節減を図ることができる。   According to the configuration of the first aspect, when the first and second control valves respectively provided in the first passage and the second passage are opened / closed in the opposite directions by the common actuator, the first and second control valves are connected by the interlocking means. Since the first and second control valves are energized in the valve closing direction by the first and second resilient means, respectively, the first and second control valves are closed by the resilient force of the first and second resilient means. In addition, the first and second bullets are canceled out in any direction when the first and second control valves are opened and closed, so that the first and second bullets cancel each other. By avoiding an increase in actuator load due to the provision of the emitting means, the actuator can be reduced in size and drive energy can be reduced.

請求項２の構成によれば、アクチュエータを第１制御バルブに接続したので、第２制御バルブは第１制御バルブにより連動手段を介して間接的に駆動されるが、第２制御バルブを閉弁方向に付勢する第２弾発手段の弾発力を第１制御バルブを閉弁方向に付勢する第１弾発手段の弾発力よりも強く設定したので、アクチュエータの駆動力に頼らずに第２制御バルブを確実に閉弁することができる。   According to the configuration of the second aspect, since the actuator is connected to the first control valve, the second control valve is indirectly driven by the first control valve via the interlocking means, but the second control valve is closed. Since the resilient force of the second resilient means biasing in the direction is set to be stronger than the resilient force of the first resilient means biasing the first control valve in the closing direction, it does not depend on the driving force of the actuator. In addition, the second control valve can be reliably closed.

請求項３の構成によれば、第１、第２制御バルブの全閉位置をそれぞれ規制するストッパ手段を設けたので、第１、第２制御バルブを精度良く全閉位置に停止させることができる。   According to the configuration of the third aspect, since the stopper means for restricting the fully closed positions of the first and second control valves is provided, the first and second control valves can be accurately stopped at the fully closed position. .

以下、本発明の実施の形態を、添付の図面に示した本発明の実施例に基づいて説明する。   DESCRIPTION OF THE PREFERRED EMBODIMENTS Embodiments of the present invention will be described below based on examples of the present invention shown in the accompanying drawings.

図１〜図６は本発明の一実施例を示すもので、図１はインタークーラ装置の全体正面図、図２は図１の２−２線拡大断面図、図３は図２の３−３線矢視図、図４は図３に対応する作用説明図、図５はインタークーラ装置の模式図、図７は第１、第２制御バルブのトルク特性を示すグラフである。   1 to 6 show an embodiment of the present invention. FIG. 1 is an overall front view of an intercooler device, FIG. 2 is an enlarged sectional view taken along line 2-2 of FIG. 1, and FIG. FIG. 4 is an operation explanatory view corresponding to FIG. 3, FIG. 5 is a schematic diagram of an intercooler device, and FIG. 7 is a graph showing torque characteristics of the first and second control valves.

図１および図５に示すように、自動車のディーゼルエンジン１１を過給するターボチャージャ１２で圧縮された吸気を冷却するインタークーラ１３は、その上流側が上流側吸気通路１４を介してターボチャージャ１２に接続され、その下流側が下流側吸気通路１５を介してディーゼルエンジン１１に接続される。上流側吸気通路１４から分岐する上流側バイパス通路１６と、下流側吸気通路１５から分岐する下流側バイパス通路１７との間に、ディーゼルエンジン１１の冷却水が流通するウオーマ１８が接続される。下流側吸気通路１５にはそれを開閉するバタフライバルブよりなる第１制御バルブ１９が設けられ、下流側バイパス通路１７にはそれを開閉するバタフライバルブよりなる第２制御バルブ２０が設けられる。第１、第２制御バルブ１９，２０は、第１制御バルブ１９が開弁しているときに第２制御バルブ２０が閉弁し、かつ第２制御バルブ２０が開弁しているときに第１制御バルブ１９が閉弁するように連動手段２１で連結されており、共通のアクチュエータ２２によって相互に連動して開閉駆動される。   As shown in FIGS. 1 and 5, an intercooler 13 that cools intake air compressed by a turbocharger 12 that supercharges a diesel engine 11 of an automobile has an upstream side connected to the turbocharger 12 via an upstream side intake passage 14. The downstream side is connected to the diesel engine 11 via the downstream side intake passage 15. A warmer 18 through which the cooling water of the diesel engine 11 flows is connected between an upstream bypass passage 16 branched from the upstream intake passage 14 and a downstream bypass passage 17 branched from the downstream intake passage 15. The downstream intake passage 15 is provided with a first control valve 19 comprising a butterfly valve for opening and closing it, and the downstream bypass passage 17 is provided with a second control valve 20 comprising a butterfly valve for opening and closing it. The first and second control valves 19 and 20 are closed when the first control valve 19 is opened and the second control valve 20 is closed and when the second control valve 20 is opened. 1 The control valve 19 is connected by an interlocking means 21 so as to be closed, and is driven to open and close in conjunction with each other by a common actuator 22.

図２〜図４に示すように、下流側吸気通路１５と一体に形成されて下流側バイパス通路１７の一部を含むバルブハウジング２３は、その開口部を覆うように３本のボルト２４…で固定されたカバー２５を備えており、カバー２５の外面にアクチュエータ２２が図示せぬボルトで固定される。下流側吸気通路１５を開閉する第１制御バルブ１９は、バルブハウジング２３に一対のボールベアリング２６，２７で回転自在に支持した第１バルブシャフト２８に固定され、下流バイパス通路１７を開閉する第２制御バルブ２０は、バルブハウジング２３に一対のボールベアリング２９，３０で回転自在に支持した第２バルブシャフト３１に固定される。   As shown in FIGS. 2 to 4, the valve housing 23 formed integrally with the downstream side intake passage 15 and including a part of the downstream side bypass passage 17 is composed of three bolts 24 so as to cover the opening. A fixed cover 25 is provided, and the actuator 22 is fixed to the outer surface of the cover 25 with a bolt (not shown). A first control valve 19 that opens and closes the downstream side intake passage 15 is fixed to a first valve shaft 28 that is rotatably supported by the valve housing 23 with a pair of ball bearings 26 and 27, and a second control valve 19 that opens and closes the downstream bypass passage 17. The control valve 20 is fixed to a second valve shaft 31 that is rotatably supported on the valve housing 23 by a pair of ball bearings 29 and 30.

アクチュエータ２２は電気モータ３２の出力軸３２ａの回転を減速して第１バルブシャフト２８に伝達する減速機構３３を備える。減速機構３３はバルブハウジング２３の内部に回転自在に支持した中間軸３４を備えており、電気モータ３２の出力軸３２ａと中間軸３４とが適宜の減速伝動手段３５を介して連結され、かつ中間軸３４に固定した第１スパーギヤ３７が第１バルブシャフト２８の端部に固定した第２スパーギヤ３８に噛合する。   The actuator 22 includes a speed reduction mechanism 33 that decelerates and transmits the rotation of the output shaft 32 a of the electric motor 32 to the first valve shaft 28. The speed reduction mechanism 33 includes an intermediate shaft 34 that is rotatably supported inside the valve housing 23, and the output shaft 32 a of the electric motor 32 and the intermediate shaft 34 are connected via an appropriate speed reduction transmission means 35. A first spur gear 37 fixed to the shaft 34 meshes with a second spur gear 38 fixed to the end of the first valve shaft 28.

第１、第２制御バルブ１９，２０の開閉を連動させる連動手段で２１は、第１バルブシャフト２８の軸端に固定した第１レバー３９と、第２バルブシャフト３１の軸端に固定した第２レバー４０とを備える。第１バルブシャフト２８の周囲を囲むように配置された第１捩じりばね４１の一端をバルブハウジング２３に設けたばね受け２３ａに係止し、かつ他端を第１レバー３９に設けたばね受け３９ａに係止することで、第１レバー３９は図３および図４の時計方向に、つまり第１制御バルブ１９が閉弁する方向に付勢される。第１制御バルブ１９の閉弁位置は、第１レバー３９に設けたストッパ突起３９ｂがバルブハウジング２３に位置調整可能に設けたストッパボルト４２に当接することで精度良く規制される（図４参照）。   The interlocking means 21 for interlocking opening and closing of the first and second control valves 19 and 20 includes a first lever 39 fixed to the shaft end of the first valve shaft 28 and a first lever 39 fixed to the shaft end of the second valve shaft 31. 2 levers 40. One end of a first torsion spring 41 disposed so as to surround the first valve shaft 28 is engaged with a spring receiver 23 a provided on the valve housing 23, and the other end is provided with a spring receiver 39 a provided on the first lever 39. The first lever 39 is biased in the clockwise direction of FIGS. 3 and 4, that is, in the direction in which the first control valve 19 is closed. The valve closing position of the first control valve 19 is regulated with high accuracy by the stopper projection 39b provided on the first lever 39 coming into contact with the stopper bolt 42 provided on the valve housing 23 so that the position can be adjusted (see FIG. 4). .

また第２バルブシャフト３１の周囲を囲むように配置された第２捩じりばね４３の一端をバルブハウジング２３に設けたばね受け２３ｂに係止し、かつ他端を第２レバー４０に設けたばね受け４０ａに係止することで、第２レバー４０は図３および図４の時計方向に、つまり第２制御バルブ２０が閉弁する方向に付勢される。第２制御バルブ２０の閉弁位置は、第２レバー４０に設けたストッパ突起４０ｂがバルブハウジング２３に位置調整可能に設けたストッパボルト４４に当接することで精度良く規制される（図３参照）。   Further, one end of a second torsion spring 43 disposed so as to surround the second valve shaft 31 is engaged with a spring receiver 23 b provided on the valve housing 23 and the other end is provided on a second lever 40. By engaging with 40a, the second lever 40 is urged in the clockwise direction of FIGS. 3 and 4, that is, in the direction in which the second control valve 20 is closed. The valve closing position of the second control valve 20 is accurately regulated by the stopper projection 40b provided on the second lever 40 coming into contact with the stopper bolt 44 provided on the valve housing 23 so that the position can be adjusted (see FIG. 3). .

第１レバー３９に設けたローラ４５が第２レバー４０に形成したカム面４０ｃに当接可能に対向しており、ローラ４５およびカム面４０ｃの当接により第１、第２レバー３９，４０は相互に連動して回転する。   A roller 45 provided on the first lever 39 is opposed to a cam surface 40c formed on the second lever 40 so that the roller 45 and the cam surface 40c are in contact with each other, and the first and second levers 39 and 40 are brought into contact with each other. Rotates in conjunction with each other.

次に、上記構成を備えた実施例の作用を説明する。   Next, the operation of the embodiment having the above configuration will be described.

ディーゼルエンジン１１が通常運転状態にあるとき、図３に示すように、第１制御バルブ１９が開弁して下流側吸気通路１５を開放し、かつ第２制御バルブ２０が閉弁して下流側バイパス通路１７を閉塞する。このとき、第１レバー３９のローラ４５が第２レバー４０のカム面４０ｃから僅かに離間し、かつ第２捩じりばね４３の弾発力で第２レバー４０のストッパ突起４０ｂがストッパボルト４４に当接することで、第２制御バルブ２０の閉弁位置を正確に規制してカジリの発生を防止することができる。この状態では、ターボチャージャ１２で圧縮された高温の吸気が上流側吸気通路１４および下流側吸気通路１５間のインタークーラ１３を通過するので、インタークーラ１３で吸気を冷却してディーゼルエンジン１１の出力を更に増加させることができる。   When the diesel engine 11 is in a normal operation state, as shown in FIG. 3, the first control valve 19 opens to open the downstream intake passage 15, and the second control valve 20 closes to the downstream side. The bypass passage 17 is closed. At this time, the roller 45 of the first lever 39 is slightly separated from the cam surface 40 c of the second lever 40, and the stopper projection 40 b of the second lever 40 is moved to the stopper bolt 44 by the elastic force of the second torsion spring 43. By abutting on the valve, the valve closing position of the second control valve 20 can be accurately regulated to prevent galling. In this state, since the high-temperature intake air compressed by the turbocharger 12 passes through the intercooler 13 between the upstream intake passage 14 and the downstream intake passage 15, the intake air is cooled by the intercooler 13 to output the diesel engine 11. Can be further increased.

ディーゼルエンジン１１の排気中のＰＭ（排気微粒子：Ｐａｒｔｉｃｕｌａｔｅ Ｍａｔｔｅｒ）を吸着して浄化処理するためのＰＭトラップを定期的に再生するためには、吸気温度を高めることで排気温度を高め、高温の排ガスでＰＭトラップ中のＰＭを燃焼させる必要がある。この場合には、アクチュエータ２２を駆動して開弁状態にある第１制御バルブ１９を閉弁するとともに、閉弁状態にある第２制御バルブ２０を開弁することで、図４に示すように、下流側吸気通路１５を閉塞して下流側バイパス通路１７を開放する。その結果、ターボチャージャ１２で圧縮された高温の吸気は、インタークーラ１３を通過することなく、上流側バイパス通路１６および下流側バイパス通路１７間のウオーマ１８を通過することで、更に加熱された状態でディーゼルエンジン１１に供給される。   In order to periodically regenerate PM traps for adsorbing and purifying PM (Particulate Matter) in the exhaust of the diesel engine 11, the exhaust gas temperature is increased by raising the intake air temperature, and the exhaust gas is hot. Therefore, it is necessary to burn the PM in the PM trap. In this case, the actuator 22 is driven to close the first control valve 19 in the open state, and the second control valve 20 in the closed state is opened, as shown in FIG. Then, the downstream side intake passage 15 is closed and the downstream side bypass passage 17 is opened. As a result, the high-temperature intake air compressed by the turbocharger 12 passes through the warmer 18 between the upstream bypass passage 16 and the downstream bypass passage 17 without passing through the intercooler 13, and is further heated. Is supplied to the diesel engine 11.

第１、第２制御バルブ１９，２０を図３の状態から図４の状態に開閉すべくアクチュエータ２２を駆動すると、電気モータ３２の出力軸３２ａの回転が減速伝動手段３５、中間軸３４、第１スパーギヤ３７および第２スパーギヤ３８を介して第１バルブシャフト２８に伝達され、第１バルブシャフト２８に設けた第１制御バルブ１９を閉弁位置へと駆動する。図４に示すように、第１制御バルブ１９が閉弁位置にあるとき、第１レバー３９のストッパ突起３９ｂがストッパボルト４２に当接することで、第１制御バルブ１９の閉弁位置を正確に規制してカジリの発生を防止することができる。   When the actuator 22 is driven to open and close the first and second control valves 19 and 20 from the state of FIG. 3 to the state of FIG. 4, the rotation of the output shaft 32 a of the electric motor 32 is caused by the speed reduction transmission means 35, the intermediate shaft 34, The first control valve 19 provided on the first valve shaft 28 is driven to the closed position by being transmitted to the first valve shaft 28 via the first spur gear 37 and the second spur gear 38. As shown in FIG. 4, when the first control valve 19 is in the valve closing position, the stopper protrusion 39b of the first lever 39 abuts against the stopper bolt 42, so that the valve closing position of the first control valve 19 is accurately set. It can be regulated to prevent galling.

第１制御バルブ１９と共に第１レバー３９が図３の位置から図４の位置へと時計方向に回転すると、第１レバー３９のローラ４５にカム面４０ｃを押圧された第２レバー４０が第２捩じりばね４３の弾発力に抗して反時計方向に回転することで、第２制御バルブ２０が開弁する。このとき、第１捩じりばね４１の弾発力は第１制御バルブ１９の回転を補助する方向に作用するが、第２捩じりばね４３の弾発力は第２制御バルブ２０の回転を阻止するように作用するため、第１、第２捩じりばね４１，４３の弾発力が相殺してアクチュエータ２２の負荷を軽減し、電気モータ３２の小型化を可能にするとともに消費電力の節減を図ることができる。   When the first lever 39 is rotated together with the first control valve 19 from the position of FIG. 3 to the position of FIG. 4, the second lever 40 whose cam surface 40 c is pressed by the roller 45 of the first lever 39 is the second lever 40. The second control valve 20 is opened by rotating counterclockwise against the elastic force of the torsion spring 43. At this time, the elastic force of the first torsion spring 41 acts in the direction of assisting the rotation of the first control valve 19, but the elastic force of the second torsion spring 43 is the rotation of the second control valve 20. Therefore, the elastic forces of the first and second torsion springs 41 and 43 cancel each other to reduce the load on the actuator 22, thereby enabling the electric motor 32 to be reduced in size and power consumption. Can be saved.

逆に、第１、第２制御バルブ１９，２０を図４の状態から図３の状態に開閉する場合には、先ずアクチュエータ２２の駆動力で第１制御バルブ１９が反時計方向に回転して開弁し、第１制御バルブ１９と一体の第１レバー３９のローラ４５にカム面４０ｃを追従させながら、第２捩じりばね４３の弾発力で第２レバー４０が時計方向に回転して制御バルブ２０が閉弁する。このとき、第１捩じりばね４１の弾発力は第１制御バルブ１９の回転を阻止する方向に作用するが、第２捩じりばね４３の弾発力は第２制御バルブ２０の回転を補助するように作用するため、第１、第２捩じりばね４１，４３の弾発力が相殺してアクチュエータ２２の負荷を軽減し、電気モータ３２の小型化を可能にするとともに消費電力の節減を図ることができる。 以上のように、共通のアクチュエータ２２で第１、第２制御バルブ１９，２０の一方を開弁して他方を閉弁するとき、第１、第２制御バルブ１９，２０を閉弁方向に付勢する第１、第２捩じりばね４１，４３の弾発力が相殺されるので、第１、第２捩じりばね４１，４３の弾発力で第１、第２制御バルブ１９，２０を確実に閉弁させながら、アクチュエータ２２の駆動力を節減することができる。   Conversely, when opening and closing the first and second control valves 19 and 20 from the state of FIG. 4 to the state of FIG. 3, the first control valve 19 is first rotated counterclockwise by the driving force of the actuator 22. The second lever 40 is rotated clockwise by the resilience of the second torsion spring 43 while the cam surface 40c follows the roller 45 of the first lever 39 integrated with the first control valve 19. As a result, the control valve 20 is closed. At this time, the elastic force of the first torsion spring 41 acts in a direction to prevent the rotation of the first control valve 19, but the elastic force of the second torsion spring 43 is the rotation of the second control valve 20. Therefore, the elastic forces of the first and second torsion springs 41 and 43 cancel each other, thereby reducing the load on the actuator 22 and allowing the electric motor 32 to be reduced in size and power consumption. Can be saved. As described above, when one of the first and second control valves 19 and 20 is opened by the common actuator 22 and the other is closed, the first and second control valves 19 and 20 are attached in the valve closing direction. Since the elastic forces of the first and second torsion springs 41 and 43 are canceled out, the elastic forces of the first and second torsion springs 41 and 43 cancel the first and second control valves 19 and 43. The driving force of the actuator 22 can be reduced while reliably closing the valve 20.

また第１制御バルブ１９はアクチュエータ２２によって直接駆動されるが、第２制御バルブ２０は第１制御バルブ１９によって連動手段２１を介して間接的に駆動されるものであり、しかも連動手段２１はローラ４５とカム面４０ｃとの接触により駆動力を伝達する構造であるため、アクチュエータ２２の駆動力によって第２制御バルブ２０を直接閉弁することはできず、第２制御バルブ２０は第２捩じりばね４３の弾発力で閉弁することになる。このとき、第１制御バルブ１９の第１捩じりばね４１の弾発力は第２制御バルブ２０を開弁する方向に作用するが、第２制御バルブ２０を閉弁する方向に作用する第２捩じりばね４３の弾発力を第１捩じりばね４１の弾発力よりも強く設定することで、第２制御バルブ２０を確実に開弁することができる。   The first control valve 19 is directly driven by the actuator 22, while the second control valve 20 is indirectly driven by the first control valve 19 via the interlocking means 21, and the interlocking means 21 is a roller. Since the driving force is transmitted by the contact between the cam 45 and the cam surface 40c, the second control valve 20 cannot be closed directly by the driving force of the actuator 22, and the second control valve 20 is in the second twisted state. The valve is closed by the elastic force of the spring 43. At this time, the elastic force of the first torsion spring 41 of the first control valve 19 acts in the direction of opening the second control valve 20, but the second force acting in the direction of closing the second control valve 20. By setting the resilient force of the second torsion spring 43 to be stronger than the resilient force of the first torsion spring 41, the second control valve 20 can be reliably opened.

図６のグラフの横軸は第１制御バルブ１９の位相であって、第１制御バルブ１９は位相０°の全閉位置と位相８０°の全開位置との間を回転する。レバー比は第２レバー４０のレバー長を第１レバー３９のレバー長で除算したもので、第１制御バルブ１９の位相の増加に伴ってレバー比は一旦減少した後に増加する。また第１、第２捩じりばね４１，４３の弾発力によるトルクは第１制御バルブ１９の位相の増加に伴ってリニアに変化する。第１バルブシャフト２８の軸トルクは、第１、第２捩じりばね４１，４３の弾発力によるトルクとレバー比とから算出されるもので、この第１バルブシャフト２８の軸トルクがアクチュエータ２２に加わる負荷になる。   The horizontal axis of the graph of FIG. 6 is the phase of the first control valve 19, and the first control valve 19 rotates between a fully closed position with a phase of 0 ° and a fully open position with a phase of 80 °. The lever ratio is obtained by dividing the lever length of the second lever 40 by the lever length of the first lever 39, and the lever ratio increases after decreasing once as the phase of the first control valve 19 increases. Further, the torque due to the elastic force of the first and second torsion springs 41 and 43 changes linearly with the increase in the phase of the first control valve 19. The axial torque of the first valve shaft 28 is calculated from the torque by the resilient force of the first and second torsion springs 41 and 43 and the lever ratio. The axial torque of the first valve shaft 28 is the actuator. 22 is a load applied.

以上、本発明の実施例を説明したが、本発明はその要旨を逸脱しない範囲で種々の設計変更を行うことが可能である。   Although the embodiments of the present invention have been described above, various design changes can be made without departing from the scope of the present invention.

例えば、本発明の流体制御装置は実施例のインタークーラ装置以外の任意の用途に適用することができる。   For example, the fluid control device of the present invention can be applied to any application other than the intercooler device of the embodiment.

またアクチュエータ２２は電気モータ３２を駆動源とするものに限定されず、油圧モータやソレノイド等の他の任意の駆動源を持つものに適用することができる。   The actuator 22 is not limited to the one having the electric motor 32 as a driving source, and can be applied to one having other arbitrary driving sources such as a hydraulic motor and a solenoid.

また連動手段２１は第１、第２レバー３９，４０を用いたものに限定されず、カム機構、リンク機構、ギヤ機構等の任意のものを採用することができる。   The interlocking means 21 is not limited to the one using the first and second levers 39 and 40, and any one of a cam mechanism, a link mechanism, a gear mechanism, and the like can be adopted.

また本発明の弾発手段は捩じりばね４１，４３に限定されず、任意の構造のばねを採用することができる。   The elastic means of the present invention is not limited to the torsion springs 41 and 43, and a spring having an arbitrary structure can be adopted.

インタークーラ装置の全体正面図Overall front view of intercooler device 図１の２−２線拡大断面図2-2 line enlarged sectional view of FIG. 図２の３−３線矢視図3-3 arrow view of FIG. 図３に対応する作用説明図Action explanatory diagram corresponding to FIG. インタークーラ装置の模式図Schematic diagram of intercooler device 第１、第２制御バルブのトルク特性を示すグラフGraph showing torque characteristics of first and second control valves

符号の説明Explanation of symbols

１４ 上流側吸気通路（第１通路）
１５ 下流側吸気通路（第１通路）
１６ 上流側バイパス通路（第２通路）
１７ 下流側バイパス通路（第２通路）
１９ 第１制御バルブ
２０ 第２制御バルブ
２１ 連動手段
２２ アクチュエータ
３９ｂ ストッパ突起（ストッパ手段）
４０ｂ ストッパ突起（ストッパ手段）
４１ 第１捩じりばね（第１弾発手段）
４２ ストッパボルト（ストッパ手段）
４３ 第２捩じりばね（第２弾発手段）
４４ ストッパボルト（ストッパ手段）
14 Upstream intake passage (first passage)
15 Downstream intake passage (first passage)
16 Upstream bypass passage (second passage)
17 Downstream bypass passage (second passage)
19 First control valve 20 Second control valve 21 Interlocking means 22 Actuator 39b Stopper protrusion (stopper means)
40b Stopper protrusion (stopper means)
41 1st torsion spring (1st spring means)
42 Stopper bolt (stopper means)
43 Second torsion spring (second spring means)
44 Stopper bolt (stopper means)

Claims (3)

流体が流通する第１通路（１４，１５）と、第１通路（１４，１５）から分岐して該第１通路（１４，１５）を迂回する第２通路（１６，１７）と、第１通路（１４，１５）を開閉する第１制御バルブ（１９）と、第２通路（１６，１７）を開閉する第２制御バルブ（２０）と、第１、第２制御バルブ（１９，２０）を開閉駆動する共通のアクチュエータ（２２）とを備えた流体制御装置において、
第１制御バルブ（１９）が開弁するときに第２制御バルブ（２０）が閉弁し、第１制御バルブ（１９）が閉弁するときに第２制御バルブ（２０）が開弁するように該第１、第２制御バルブ（１９，２０）を連動手段（２１）で連結し、第１制御バルブ（１９）を第１弾発手段（４１）で閉弁方向に付勢するとともに第２制御バルブ（２０）を第２弾発手段（４３）で閉弁方向に付勢したことを特徴とする流体制御装置。 A first passage (14, 15) through which a fluid flows, a second passage (16, 17) branched from the first passage (14, 15) and bypassing the first passage (14, 15); The first control valve (19) for opening and closing the passage (14, 15), the second control valve (20) for opening and closing the second passage (16, 17), and the first and second control valves (19, 20) A fluid control device comprising a common actuator (22) for opening and closing the
The second control valve (20) is closed when the first control valve (19) is opened, and the second control valve (20) is opened when the first control valve (19) is closed. The first and second control valves (19, 20) are connected by the interlocking means (21), and the first control valve (19) is urged in the valve closing direction by the first elastic means (41). 2. A fluid control device characterized in that the control valve (20) is urged in the valve closing direction by the second elastic means (43). アクチュエータ（２２）を第１制御バルブ（１９）に接続し、第２弾発手段（４３）の弾発力を第１弾発手段（４１）の弾発力よりも強く設定したことを特徴とする、請求項１に記載の流体制御装置。   The actuator (22) is connected to the first control valve (19), and the resilient force of the second resilient means (43) is set stronger than the resilient force of the first resilient means (41). The fluid control device according to claim 1. 第１、第２制御バルブ（１９，２０）の全閉位置をそれぞれ規制するストッパ手段（３９ｂ，４０ｂ，４２，４４）を設けたことを特徴とする、請求項１または請求項２に記載の流体制御装置。
The stopper means (39b, 40b, 42, 44) for restricting the fully closed positions of the first and second control valves (19, 20), respectively, is provided. Fluid control device.
JP2005175526A 2005-06-15 2005-06-15 Fluid control device Expired - Fee Related JP4530920B2 (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010510425A (en) * 2006-11-20 2010-04-02 バレオ・システムズ・ドウ・コントロール・モトウール Intake device and charge air cooler unit in internal combustion engine

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58104323A (en) * 1981-12-01 1983-06-21 ア−・ベ−・ボルボ Apparatus for supplying air to over-charge internal combustion engine while charged air is cooled
JPS6057741U (en) * 1983-09-28 1985-04-22 いすゞ自動車株式会社 Intake system for turbocharged engine
JP2002332887A (en) * 2001-05-10 2002-11-22 Fuji Heavy Ind Ltd Combustion controller of compression ignition engine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS58104323A (en) * 1981-12-01 1983-06-21 ア−・ベ−・ボルボ Apparatus for supplying air to over-charge internal combustion engine while charged air is cooled
JPS6057741U (en) * 1983-09-28 1985-04-22 いすゞ自動車株式会社 Intake system for turbocharged engine
JP2002332887A (en) * 2001-05-10 2002-11-22 Fuji Heavy Ind Ltd Combustion controller of compression ignition engine

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010510425A (en) * 2006-11-20 2010-04-02 バレオ・システムズ・ドウ・コントロール・モトウール Intake device and charge air cooler unit in internal combustion engine
JP2010510424A (en) * 2006-11-20 2010-04-02 バレオ・システムズ・ドウ・コントロール・モトウール Gas intake device
KR101291482B1 (en) * 2006-11-20 2013-07-30 발레오 시스템므 드 꽁트롤르 모뙤르 Intake device and charge-air cooler unit in an internal combustion engine
KR101295403B1 (en) 2006-11-20 2013-08-09 발레오 시스템므 드 꽁트롤르 모뙤르 Gas intake device

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