JP6011501B2 - Valve device - Google Patents

Valve device Download PDF

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JP6011501B2
JP6011501B2 JP2013193783A JP2013193783A JP6011501B2 JP 6011501 B2 JP6011501 B2 JP 6011501B2 JP 2013193783 A JP2013193783 A JP 2013193783A JP 2013193783 A JP2013193783 A JP 2013193783A JP 6011501 B2 JP6011501 B2 JP 6011501B2
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intake
passage
pressure egr
valve
egr
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JP2015059506A (en
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岳大 菅原
岳大 菅原
徳幸 稲垣
徳幸 稲垣
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Denso Corp
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Denso Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/65—Constructional details of EGR valves
    • F02M26/71—Multi-way valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
    • F02M26/02—EGR systems specially adapted for supercharged engines
    • F02M26/09—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine
    • F02M26/10—Constructional details, e.g. structural combinations of EGR systems and supercharger systems; Arrangement of the EGR and supercharger systems with respect to the engine having means to increase the pressure difference between the exhaust and intake system, e.g. venturis, variable geometry turbines, check valves using pressure pulsations or throttles in the air intake or exhaust system

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust-Gas Circulating Devices (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Lift Valve (AREA)

Description

本発明は、吸気通路に接続する低圧ＥＧＲ通路を開閉する低圧ＥＧＲバルブと、吸気通路を開閉する吸気絞り弁とを備えるバルブ装置に関する。   The present invention relates to a valve device including a low pressure EGR valve that opens and closes a low pressure EGR passage connected to an intake passage, and an intake throttle valve that opens and closes the intake passage.

従来より、比較的低圧低温の排気の一部を低圧ＥＧＲガスとして吸気通路へ還流させる低圧ＥＧＲ装置が公知である（例えば、特許文献１、２参照）。
低圧ＥＧＲ装置は、低圧ＥＧＲ通路を流れる低圧ＥＧＲガスの流量を調整するバタフライ型の低圧ＥＧＲバルブと、低圧ＥＧＲバルブの開閉操作に連動して低圧ＥＧＲ通路よりも吸気上流において吸気通路の開度を調整するバタフライ型の吸気絞り弁とを有するバルブ装置を備える。そして、低圧ＥＧＲバルブが低圧ＥＧＲ通路の開度を最大とするときに、吸気絞り弁が吸気通路を最も絞り（この状態を吸気全閉と呼ぶ）、吸気通路へ還流されるＥＧＲガスの流量を増加させる。 2. Description of the Related Art Conventionally, a low pressure EGR device that recirculates a part of a relatively low pressure and low temperature exhaust gas as low pressure EGR gas to an intake passage is known (for example, see Patent Documents 1 and 2).
The low pressure EGR device is a butterfly type low pressure EGR valve that adjusts the flow rate of the low pressure EGR gas flowing through the low pressure EGR passage, and the opening degree of the intake passage upstream of the low pressure EGR passage in conjunction with the opening and closing operation of the low pressure EGR valve. A valve device having a butterfly type intake throttle valve to be adjusted; When the low-pressure EGR valve maximizes the opening of the low-pressure EGR passage, the intake throttle valve restricts the intake passage most (this state is called intake fully closed), and the flow rate of EGR gas recirculated to the intake passage is reduced. increase.

特許文献１、２には、バルブ装置の小型化等の要求から、吸気通路と低圧ＥＧＲ通路とが直角に接続された技術が開示されている。
そして、特許文献１のバルブ装置では、低圧ＥＧＲ通路の流路軸と吸気通路の流路軸との交点が回転中心となるように吸気絞り弁が配されている。 Patent Documents 1 and 2 disclose a technique in which an intake passage and a low-pressure EGR passage are connected at a right angle in response to a request for downsizing a valve device or the like.
In the valve device of Patent Document 1, the intake throttle valve is arranged so that the intersection of the flow path shaft of the low pressure EGR passage and the flow passage shaft of the intake passage is the center of rotation.

しかし、この構造の場合、吸気全閉時にＥＧＲガスを吸気通路へ流す流路が、吸気絞り弁の近傍で絞られてしまう。この現象を「ＥＧＲ絞り現象」と呼ぶ。この「ＥＧＲ絞り現象」が発生するとＥＧＲガスの流量が低下してしまうという問題が生じる。
一方で、特許文献１のバルブ装置では、吸気全閉時において、吸気絞り弁を吸気通路の流路軸に対して傾斜した状態で存在させることにより、低圧ＥＧＲ通路から吸気通路の下流側へ流れ込むようにＥＧＲガスの流れをガイドすることができる。この機能を、「ＥＧＲ流れガイド機能」と呼ぶ。 However, in this structure, the flow path for flowing EGR gas to the intake passage when the intake is fully closed is throttled in the vicinity of the intake throttle valve. This phenomenon is referred to as “EGR aperture phenomenon”. When this “EGR throttling phenomenon” occurs, there arises a problem that the flow rate of EGR gas decreases.
On the other hand, in the valve device of Patent Document 1, when the intake is fully closed, the intake throttle valve is present in an inclined state with respect to the flow axis of the intake passage, thereby flowing from the low pressure EGR passage to the downstream side of the intake passage. Thus, the flow of EGR gas can be guided. This function is called an “EGR flow guide function”.

これに対して、特許文献２のバルブ装置では、低圧ＥＧＲ通路の接続口が開口する位置よりも十分上流の吸気通路に吸気絞り弁を配している。
しかし、この構造の場合には、「ＥＧＲ絞り現象」は発生しないものの、「ＥＧＲ流れガイド機能」が発揮されない。このため、接続口から流出するＥＧＲガスが低圧ＥＧＲ通路の流路軸に沿って真っ直ぐ進み、吸気通路の流路壁に衝突する等して圧力損失が生じ、結果的にＥＧＲガスの流量が低下してしまうという問題が生じる。 On the other hand, in the valve device of Patent Document 2, the intake throttle valve is arranged in the intake passage sufficiently upstream from the position where the connection port of the low pressure EGR passage opens.
However, in the case of this structure, although the “EGR throttling phenomenon” does not occur, the “EGR flow guide function” is not exhibited. For this reason, the EGR gas flowing out from the connection port advances straight along the flow path axis of the low pressure EGR passage and collides with the flow passage wall of the intake passage to cause pressure loss, resulting in a decrease in the flow rate of the EGR gas. The problem of end up occurs.

そこで、ＥＧＲガスの流量を増加させるために、低圧ＥＧＲ通路の通路径を大きくするという方法があるが、通路径を大きくするとバルブ装置の小型化を阻害することになる。   In order to increase the flow rate of EGR gas, there is a method of increasing the passage diameter of the low pressure EGR passage. However, increasing the passage diameter inhibits the miniaturization of the valve device.

特開２０１２−２３７３０６号公報JP 2012-237306 A 特開２０１２−１２７２０４号公報JP 2012-127204 A

本発明は、上記の問題点を解決するためになされたものであり、その目的は、低圧ＥＧＲ装置のバルブ装置において、バルブ装置の小型化を図りつつ、ＥＧＲガスの流量を増加させることを目的とする。   The present invention has been made to solve the above-described problems, and an object of the present invention is to increase the flow rate of EGR gas while reducing the size of the valve device in the valve device of the low pressure EGR device. And

本発明のバルブ装置は、排気通路に配される排気タービンと吸気通路に配されるコンプレッサとを有する過給機と、排気の一部を吸気通路へ還流する高圧ＥＧＲ装置及び低圧ＥＧＲ装置とを備える内燃機関の吸排気システムにおいて、低圧ＥＧＲ装置を構成するバルブ装置であって、自身の流路軸ｙを吸気通路内に延長したときに吸気通路の流路軸ｘと直交する低圧ＥＧＲ通路と、低圧ＥＧＲ通路を開閉するバタフライ型の低圧ＥＧＲバルブと、吸気通路に配されて、吸気通路を絞り、吸気通路に導入されるＥＧＲガスの流量を増加させるバタフライ型の吸気絞り弁と、低圧ＥＧＲバルブ及び吸気絞り弁の回動中心となるシャフト同士を連動駆動し、低圧ＥＧＲバルブが低圧ＥＧＲ通路の開度を最大とする時に、吸気絞り弁が吸気通路を最も絞った吸気全閉にする連動駆動機構と、吸気全閉時の吸気絞り弁の姿勢であって、回動中心よりも低圧ＥＧＲ通路の接続口に近い側に吸気絞り弁の上流端が位置し、回動中心よりも接続口から遠い側に吸気絞り弁の下流端が位置するように、吸気通下流端が位置するように、吸気通路の流路軸ｘに対して傾斜する吸気絞りの姿勢とを備える。 A valve device according to the present invention includes a supercharger having an exhaust turbine disposed in an exhaust passage and a compressor disposed in an intake passage, and a high-pressure EGR device and a low-pressure EGR device that recirculate part of the exhaust to the intake passage. In the intake / exhaust system for an internal combustion engine, a valve device that constitutes a low-pressure EGR device, and a low-pressure EGR passage that is orthogonal to the flow passage axis x of the intake passage when its own flow passage shaft y is extended into the intake passage; A butterfly-type low-pressure EGR valve that opens and closes the low-pressure EGR passage, a butterfly-type intake throttle valve that is disposed in the intake passage, restricts the intake passage, and increases the flow rate of EGR gas introduced into the intake passage, and low-pressure EGR interlocked driven shaft with each other serving as the rotation center of the valve and the intake throttle valve, when the low-pressure EGR valve to maximize the degree of opening of the low-pressure EGR passage, the intake throttle valve is most an intake passage And the intake throttle valve posture when the intake is fully closed, and the upstream end of the intake throttle valve is located closer to the connection port of the low pressure EGR passage than the center of rotation. The attitude of the intake throttle that is inclined with respect to the flow path axis x of the intake passage so that the downstream end of the intake throttle valve is positioned so that the downstream end of the intake throttle valve is positioned farther from the connection port than the rotation center With.

そして、吸気絞り弁の下流端は、吸気全閉時に、吸気通路の流路軸ｘと低圧ＥＧＲ通路の流路軸ｙとの交点ｏよりも吸気通路の下流側に位置する。
また、吸気全閉時に低圧ＥＧＲ通路を経て吸気絞り弁下流側の吸気通路へＥＧＲガスが流れる流路において、流路面積が最も小さい箇所が、低圧ＥＧＲ通路に設けられている。 The downstream end of the intake throttle valve is located downstream of the intersection point o between the flow path axis x of the intake passage and the flow path axis y of the low pressure EGR passage when intake is fully closed.
Further, in the flow path through which the EGR gas flows through the low pressure EGR passage to the intake passage downstream of the intake throttle valve when the intake is fully closed, a portion having the smallest flow path area is provided in the low pressure EGR passage.

これによれば、「ＥＧＲ絞り現象」が発生させず、かつ、「ＥＧＲ流れガイド機能」を維持することができるため、低圧ＥＧＲ通路の通路径を大きくすることなく、ＥＧＲガスの流量を増加させることができる。すなわち、バルブ装置の小型化を図りつつ、ＥＧＲガスの流量を増加させることができる。   According to this, since the “EGR throttling phenomenon” does not occur and the “EGR flow guide function” can be maintained, the flow rate of the EGR gas is increased without increasing the diameter of the low pressure EGR passage. be able to. That is, the flow rate of the EGR gas can be increased while downsizing the valve device.

内燃機関の吸排気システムの概略図である。It is the schematic of the intake / exhaust system of an internal combustion engine. バルブ装置の基本構成を説明する断面図である。It is sectional drawing explaining the basic composition of a valve apparatus. 実施例のバルブ装置の模式図である。It is a schematic diagram of the valve apparatus of an Example. 従来例のバルブ装置の模式図である。It is a schematic diagram of the valve apparatus of a prior art example. 従来例のバルブ装置の模式図である。It is a schematic diagram of the valve apparatus of a prior art example. 距離Ｃと流量の関係を示した相関図である。It is the correlation figure which showed the relationship between the distance C and flow volume.

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

〔実施例〕
実施例を図１〜６を用いて説明する。
まず、本実施例のバルブ装置が適用される内燃機関の吸排気システムを図１を用いて説明する。
吸排気システムは、エンジン１に吸気を導く吸気通路２と、エンジン１から排気を排出するための排気通路３と、排気通路３に配される排気タービン４と吸気通路２に配されるコンプレッサ５とを有する過給機と、排気の一部を吸気通路２へ還流する高圧ＥＧＲ装置及び低圧ＥＧＲ装置とを備える。 〔Example〕
Examples will be described with reference to FIGS.
First, an intake / exhaust system of an internal combustion engine to which the valve device of this embodiment is applied will be described with reference to FIG.
The intake / exhaust system includes an intake passage 2 that guides intake air to the engine 1, an exhaust passage 3 that discharges exhaust from the engine 1, an exhaust turbine 4 that is disposed in the exhaust passage 3, and a compressor 5 that is disposed in the intake passage 2. And a high pressure EGR device and a low pressure EGR device that recirculate a part of the exhaust gas to the intake passage 2.

吸気通路２には、吸気上流側から、吸気の異物を取り除くエアクリーナ８、過給機のコンプレッサ５、コンプレッサ５で圧縮された吸気を冷却するインタークーラ９、吸気量を調整するスロットルバルブ１０、所定の容積室を形成するサージタンク１１等が配置されている。   In the intake passage 2, an air cleaner 8 that removes foreign matter from intake air from the upstream side of intake air, a compressor 5 of a supercharger, an intercooler 9 that cools intake air compressed by the compressor 5, a throttle valve 10 that adjusts the intake air amount, A surge tank 11 and the like that form a volume chamber are arranged.

排気通路３には、排気上流側から、過給機の排気タービン４、排気に含まれる粒子状物質（ＰＭ）を捕集するＤＰＦ１２等が配されている。   In the exhaust passage 3, an exhaust turbine 4 of a supercharger, a DPF 12 that collects particulate matter (PM) contained in the exhaust, and the like are arranged from the exhaust upstream side.

排気タービン４は、排気のエネルギを回転力に変換するもので、コンプレッサ５は、排気タービン４と同軸に連結され排気タービン４の回転力によって回転して吸気を圧縮するものである。   The exhaust turbine 4 converts exhaust energy into rotational force, and the compressor 5 is coaxially connected to the exhaust turbine 4 and rotates by the rotational force of the exhaust turbine 4 to compress intake air.

高圧ＥＧＲ装置は、エンジン１から排出された直後の比較的高圧高温の排気の一部を高圧ＥＧＲガスとして吸気通路２へ還流させる装置である。
高圧ＥＧＲ装置は、排気タービン４より排気上流側の排気通路３と、スロットルバルブ１０よりも吸気下流側の吸気通路２とを接続する高圧ＥＧＲ通路１３と、高圧ＥＧＲ通路１３を流れる高圧ＥＧＲガスの流量を調整する高圧ＥＧＲバルブ１４と、高圧ＥＧＲガスを冷却する高圧ＥＧＲクーラ１５と、高圧ＥＧＲクーラ１５を通過する経路と高圧ＥＧＲクーラ１５をバイパスする経路との間を切り替える切替弁１６とを有する。 The high-pressure EGR device is a device that recirculates a portion of the relatively high-pressure and high-temperature exhaust immediately after being discharged from the engine 1 to the intake passage 2 as high-pressure EGR gas.
The high-pressure EGR device includes a high-pressure EGR passage 13 that connects the exhaust passage 3 upstream of the exhaust turbine 4, the intake passage 2 downstream of the throttle valve 10, and high-pressure EGR gas that flows through the high-pressure EGR passage 13. A high-pressure EGR valve that adjusts the flow rate; a high-pressure EGR cooler that cools the high-pressure EGR gas; and a switching valve that switches between a path that passes through the high-pressure EGR cooler and a path that bypasses the high-pressure EGR cooler. .

低圧ＥＧＲ装置は、比較的低圧低温の排気の一部を低圧ＥＧＲガスとして吸気通路２へ還流させる装置である。
低圧ＥＧＲ装置は、排気タービン４より排気下流側（本実施例では、ＤＰＦ１２の下流側）の排気通路３と、コンプレッサ５より吸気上流側の吸気通路２とを接続する低圧ＥＧＲ通路２０と、低圧ＥＧＲ通路２０を流れる低圧ＥＧＲガスの流量を調整する低圧ＥＧＲバルブ２１と、低圧ＥＧＲガスを冷却する低圧ＥＧＲクーラ２２と、低圧ＥＧＲバルブ２１の開閉操作に連動して低圧ＥＧＲ通路２０よりも吸気上流において吸気通路２の開度を調整する吸気絞り弁２３とを有する。 The low pressure EGR device is a device that recirculates a part of the relatively low pressure and low temperature exhaust gas to the intake passage 2 as low pressure EGR gas.
The low-pressure EGR device includes a low-pressure EGR passage 20 that connects an exhaust passage 3 downstream of the exhaust turbine 4 (in the present embodiment, downstream of the DPF 12) and an intake passage 2 upstream of the compressor 5; A low-pressure EGR valve 21 that adjusts the flow rate of the low-pressure EGR gas that flows through the EGR passage 20, a low-pressure EGR cooler 22 that cools the low-pressure EGR gas, and an intake upstream of the low-pressure EGR passage 20 in conjunction with the opening and closing operation of the low-pressure EGR valve 21 And an intake throttle valve 23 for adjusting the opening of the intake passage 2.

低圧ＥＧＲバルブ２１と吸気絞り弁２３とは１つのアクチュエータによって駆動する１つのバルブ装置２４としてユニット化されている。
次にバルブ装置２４の基本構成を図２を用いて説明する。 The low pressure EGR valve 21 and the intake throttle valve 23 are unitized as one valve device 24 driven by one actuator.
Next, the basic configuration of the valve device 24 will be described with reference to FIG.

バルブ装置２４は、低圧ＥＧＲ通路２０の一部をなすＥＧＲ配管２０ａと、ＥＧＲ配管２０ａに配される低圧ＥＧＲバルブ２１と、吸気通路２の一部をなす吸気配管２ａと、吸気配管２ａに配される吸気絞り弁２３と、低圧ＥＧＲバルブ２１と吸気絞り弁２３とを連動駆動させる連動駆動機構等を備える。   The valve device 24 includes an EGR pipe 20a that forms part of the low-pressure EGR passage 20, a low-pressure EGR valve 21 that is arranged in the EGR pipe 20a, an intake pipe 2a that forms part of the intake passage 2, and an intake pipe 2a. And an interlocking drive mechanism for interlockingly driving the low-pressure EGR valve 21 and the intake throttle valve 23.

ＥＧＲ配管２０ａと吸気配管２ａとは直角に接続されている。すなわち、図３に示すように、ＥＧＲ配管２０ａの流路軸ｙは、吸気通路内に延長したときに吸気配管２ａの流路軸ｘと直交する。   The EGR pipe 20a and the intake pipe 2a are connected at a right angle. That is, as shown in FIG. 3, the flow path axis y of the EGR pipe 20a is orthogonal to the flow path axis x of the intake pipe 2a when extended into the intake passage.

低圧ＥＧＲバルブ２１は、バタフライバルブであり、回転中心となるシャフト２６はＥＧＲ配管２０ａに回転自在に支持されている。   The low pressure EGR valve 21 is a butterfly valve, and a shaft 26 serving as a rotation center is rotatably supported by the EGR pipe 20a.

吸気絞り弁２３は、吸気通路２を絞り、吸気通路２に導入されるＥＧＲガスの流量を増加させるバタフライバルブであり、回転中心となるシャフト２７は吸気配管２ａに回転自在に支持されている。吸気絞り弁２３の構造は後に詳述する。   The intake throttle valve 23 is a butterfly valve that throttles the intake passage 2 and increases the flow rate of EGR gas introduced into the intake passage 2, and a shaft 27 serving as a rotation center is rotatably supported by the intake pipe 2a. The structure of the intake throttle valve 23 will be described in detail later.

連動駆動機構は、回転駆動力を発生するアクチュエータ２９と、シャフト２６とシャフト２７とを連結するリンク機構３０とを備える。
アクチュエータ２９は、例えば電動モータであり、動力伝達機構を介してシャフト２６に回転駆動力を与える。 The interlocking drive mechanism includes an actuator 29 that generates a rotational driving force, and a link mechanism 30 that connects the shaft 26 and the shaft 27.
The actuator 29 is an electric motor, for example, and applies a rotational driving force to the shaft 26 via a power transmission mechanism.

動力伝達機構は、電動モータ３０の出力軸に設けられたピニオン３１と、ピニオン３１に噛み合う減速ギヤ３２と、減速ギヤ３２と一体に設けられて共通の中心軸周りに回転する小径ギヤ３３と、小径ギヤ３３と噛み合うバルブギヤ３４とで構成される。バルブギヤ３４はシャフト２６に固定されており、電動モータの回転がシャフト２６に伝達される。   The power transmission mechanism includes a pinion 31 provided on the output shaft of the electric motor 30, a reduction gear 32 that meshes with the pinion 31, a small-diameter gear 33 that is provided integrally with the reduction gear 32 and rotates around a common central axis, The valve gear 34 meshes with the small diameter gear 33. The valve gear 34 is fixed to the shaft 26, and the rotation of the electric motor is transmitted to the shaft 26.

低圧ＥＧＲバルブ２１のシャフト２６は、吸気絞り弁２３のシャフト２７と平行に設けられている。
シャフト２６とシャフト２７とはリンク機構を介して連結しており、電動モータによってシャフト２６が回動するのに伴ってシャフト２７が回動するように構成されている。 The shaft 26 of the low pressure EGR valve 21 is provided in parallel with the shaft 27 of the intake throttle valve 23.
The shaft 26 and the shaft 27 are connected via a link mechanism, and the shaft 27 is configured to rotate as the shaft 26 is rotated by the electric motor.

リンク機構３０は、シャフト２６と一体に回転する駆動プレート３８と、シャフト２７と一体的に回転する従動プレート３９とを有し、駆動プレート３８に形成されたカム溝３８ａと、従動プレート３９に形成されたピン３９ａとの係合によって構成されている。   The link mechanism 30 includes a drive plate 38 that rotates integrally with the shaft 26, and a driven plate 39 that rotates integrally with the shaft 27, and is formed on the cam plate 38 a formed in the drive plate 38 and the driven plate 39. It is comprised by engagement with the pin 39a made.

以上に説明した連動駆動機構によって、低圧ＥＧＲバルブ２１と吸気絞り弁２３とは１つのアクチュエータにより駆動される。そして、低圧ＥＧＲバルブ２１がＥＧＲ配管２０ａの開度を最大とする時に、吸気絞り弁２３が吸気配管２ａを最も絞った吸気全閉にする。   The low-pressure EGR valve 21 and the intake throttle valve 23 are driven by a single actuator by the interlock driving mechanism described above. When the low pressure EGR valve 21 maximizes the opening of the EGR pipe 20a, the intake throttle valve 23 fully closes the intake pipe 2a.

低圧ＥＧＲバルブ２１が低圧ＥＧＲ通路２０を開くと、ＥＧＲ配管２０ａの接続口４０の位置よりも吸気上流側から流れ込む空気に、ＥＧＲガスが合流して、吸気下流へと流れる。   When the low-pressure EGR valve 21 opens the low-pressure EGR passage 20, the EGR gas merges with the air flowing from the intake upstream side of the position of the connection port 40 of the EGR pipe 20a, and flows to the intake downstream.

吸気絞り弁２３は、楕円形の板状を呈しており、シャフト２７と一体的に回動する。
そして、吸気全閉時において吸気絞り弁２３は、流路軸ｘに対して傾斜した姿勢をとる。すなわち、板厚方向が流路軸ｘに平行とはなっていない。
図３に示すように、吸気全閉時において吸気絞り弁２３は、吸気配管２ａの下流に向かって横たわるように傾斜している。すなわち、流路軸ｙに沿う方向において、回動中心（シャフト２７）よりもＥＧＲ配管２０ａの接続口４０に近い側に吸気絞り弁２３の上流端２３ａが位置し、回動中心よりも接続口４０から遠い側に吸気絞り弁２３の下流端２３ｂが位置するように、傾斜している。 The intake throttle valve 23 has an elliptical plate shape and rotates integrally with the shaft 27.
When the intake is fully closed, the intake throttle valve 23 is inclined with respect to the flow path axis x. That is, the plate thickness direction is not parallel to the flow path axis x.
As shown in FIG. 3, when the intake is fully closed, the intake throttle valve 23 is inclined so as to lie toward the downstream side of the intake pipe 2a. That is, in the direction along the flow path axis y, the upstream end 23a of the intake throttle valve 23 is located closer to the connection port 40 of the EGR pipe 20a than the rotation center (shaft 27), and the connection port is located more than the rotation center. It is inclined so that the downstream end 23b of the intake throttle valve 23 is located on the side far from 40.

〔本実施例の特徴及び作用効果〕
本実施例の特徴を図３を用いて説明する。
本実施例の吸気絞り弁２３は、吸気全閉時に、下流端２３ｂが流路軸ｘと流路軸ｙとの交点ｏよりも吸気下流側に位置するように配されている。 [Features and effects of this embodiment]
The features of this embodiment will be described with reference to FIG.
The intake throttle valve 23 of this embodiment is arranged so that the downstream end 23b is located on the intake downstream side of the intersection point o between the flow path axis x and the flow path axis y when the intake is fully closed.

ここで、吸気全閉時にＥＧＲ配管２０ａと吸気絞り弁下流の吸気配管２ａとにより形成される流路であって、ＥＧＲ配管２０ａを経て吸気絞り弁２３下流側の吸気配管２ａへＥＧＲガス流通可能な流路をＥＧＲ合流流路５０と呼ぶ。   Here, it is a flow path formed by the EGR pipe 20a and the intake pipe 2a downstream of the intake throttle valve when the intake is fully closed, and the EGR gas can flow through the EGR pipe 20a to the intake pipe 2a downstream of the intake throttle valve 23. Such a flow path is called an EGR merge flow path 50.

本実施例では、このＥＧＲ合流流路５０において、流路面積が最も小さい箇所が、ＥＧＲ配管２０ａに設けられている。すなわち、シャフト２７が交点ｏよりも吸気上流側に位置しており、吸気配管２ａのＥＧＲ配管２０ａとの交差部での最小流路面積Ａよりも、ＥＧＲ配管２０ａの流路面積Ｂが小さくなっている。   In the present embodiment, in the EGR merging flow channel 50, a portion having the smallest flow channel area is provided in the EGR pipe 20a. That is, the shaft 27 is positioned upstream of the intersection point o, and the flow path area B of the EGR pipe 20a is smaller than the minimum flow path area A at the intersection of the intake pipe 2a and the EGR pipe 20a. ing.

本実施例の作用効果を説明するために、従来のバルブ装置について説明する。
図４で従来例１を、図５で従来例２を説明する。 In order to explain the function and effect of this embodiment, a conventional valve device will be described.
Conventional Example 1 will be described with reference to FIG. 4, and Conventional Example 2 will be described with reference to FIG.

従来例１は、下流端２３ｂが交点ｏよりも吸気下流側に位置している。このため、「ＥＧＲ流れガイド機能」が発揮される。すなわち、接続口４０から流出するＥＧＲガスが傾斜した吸気絞り弁２３にガイドされて、吸気絞り弁２３の下流側へスムーズにＥＧＲガスが流れる。   In Conventional Example 1, the downstream end 23b is located on the intake downstream side of the intersection o. For this reason, the “EGR flow guide function” is exhibited. In other words, the EGR gas flowing out from the connection port 40 is guided by the inclined intake throttle valve 23, and the EGR gas flows smoothly downstream of the intake throttle valve 23.

しかし、従来例１では、交差部での最小流路面積Ａが、ＥＧＲ配管２０ａの流路面積よりも小さい。このため、「ＥＧＲ絞り現象」が発生する。すなわち、ＥＧＲ合流流路５０が、吸気絞り弁２３の存在によって最小流路面積Ａの箇所で絞られて、ＥＧＲガスの流量が低下する。   However, in Conventional Example 1, the minimum flow path area A at the intersection is smaller than the flow path area of the EGR pipe 20a. For this reason, the “EGR aperture phenomenon” occurs. That is, the EGR merge flow path 50 is throttled at the position of the minimum flow path area A due to the presence of the intake throttle valve 23, and the flow rate of EGR gas is reduced.

一方、従来例２は、吸気絞り弁２３の回転中心が交点ｏよりも吸気上流に位置しており、交差部での最小流路面積がＥＧＲ配管２０ａの流路面積よりも大きく、「ＥＧＲ絞り現象」は発生しない。   On the other hand, in the prior art example 2, the rotation center of the intake throttle valve 23 is located upstream of the intersection point o, and the minimum flow path area at the intersection is larger than the flow path area of the EGR pipe 20a. The phenomenon does not occur.

しかし、従来例２では、下流端２３ｂが交点ｏよりも吸気上流側に位置しているため、「ＥＧＲ流れガイド機能」を奏さない。すなわち、ＥＧＲ配管２０ａからのＥＧＲガスは、流路軸ｙに沿って直進し、接続口４０に対向する吸気配管２ａの壁面に衝突しやすくなる。このため、圧力損失が大きくなり、結果的にＥＧＲガスの流量が低減してしまう。   However, in the conventional example 2, since the downstream end 23b is located on the intake upstream side with respect to the intersection point o, the “EGR flow guide function” is not achieved. That is, the EGR gas from the EGR pipe 20 a goes straight along the flow path axis y and easily collides with the wall surface of the intake pipe 2 a facing the connection port 40. For this reason, a pressure loss becomes large and the flow volume of EGR gas will reduce as a result.

以上のように、従来例では、「ＥＧＲ絞り現象」の発生もしくは「ＥＧＲ流れガイド機能」の消失によって、ＥＧＲガスの流量が低減してしまっていた。   As described above, in the conventional example, the flow rate of EGR gas is reduced due to the occurrence of the “EGR throttling phenomenon” or the disappearance of the “EGR flow guide function”.

これに対して、本実施例では、「ＥＧＲ絞り現象」を発生させず、かつ、「ＥＧＲ流れガイド機能」を維持できる。
すなわち、本実施例では、吸気絞り弁２３の下流端２３ｂが、吸気全閉時に交点ｏよりも吸気下流側に位置する。このため、接続口４０から流出するＥＧＲガスを吸気絞り弁２３によって吸気絞り弁２３の下流側へガイドすることができる。 In contrast, in this embodiment, the “EGR throttling phenomenon” does not occur and the “EGR flow guide function” can be maintained.
That is, in the present embodiment, the downstream end 23b of the intake throttle valve 23 is located on the intake downstream side of the intersection point o when the intake is fully closed. For this reason, the EGR gas flowing out from the connection port 40 can be guided to the downstream side of the intake throttle valve 23 by the intake throttle valve 23.

また、本実施例では、このＥＧＲ合流流路５０において、流路面積が最も小さい箇所が、ＥＧＲ配管２０ａに設けられている。すなわち、シャフト２７が交点ｏよりも吸気上流側に位置しており、吸気配管２ａのＥＧＲ配管２０ａとの交差部での最小流路面積ＡがＥＧＲ配管２０ａの流路面積Ｂよりも大きくなっている。
このため、従来例１とは異なって、ＥＧＲ合流流路５０が吸気絞り弁２３の存在によって絞られることがない。 In the present embodiment, in the EGR merging flow channel 50, a portion having the smallest flow channel area is provided in the EGR pipe 20a. That is, the shaft 27 is positioned upstream of the intersection point o, and the minimum flow area A at the intersection of the intake pipe 2a with the EGR pipe 20a is larger than the flow area B of the EGR pipe 20a. Yes.
For this reason, unlike the conventional example 1, the EGR merging flow path 50 is not throttled by the presence of the intake throttle valve 23.

ここで、流路軸ｘに平行な方向での交点ｏから下流端２３ｂの距離をＣとする。交点ｏをゼロ点として、下流端２３ｂが交点ｏよりも下流側にある場合はプラス、上流側にある場合はマイナスとする。
図６に距離Ｃと流量の関係を示す。 Here, C is the distance from the intersection point o in the direction parallel to the flow path axis x to the downstream end 23b. Assume that the intersection point o is a zero point, and that the downstream end 23b is on the downstream side of the intersection point o, it is positive.
FIG. 6 shows the relationship between the distance C and the flow rate.

距離Ｃがマイナスの領域では、従来例２のように「ＥＧＲ流れガイド機能」が消失している。このため、圧力損失が大きく、小さい流量しか得られない。
距離Ｃをプラスにすると、「ＥＧＲ流れガイド機能」が発揮されるので、圧力損失が小さくなり、流量は増加する。しかし、距離Ｃが大きすぎると、従来例１のように、吸気絞り弁２３によってＥＧＲ合流流路５０が絞られてしまい、「ＥＧＲ絞り現象」が生じる。
本実施例の吸気絞り弁２３の配置は、「ＥＧＲ絞り現象」が発生せず、かつ、「ＥＧＲ流れガイド機能」を維持できる配置であり、ＥＧＲガスの流量を大きくすることができる。 In the region where the distance C is negative, the “EGR flow guide function” is lost as in the second conventional example. For this reason, pressure loss is large and only a small flow rate can be obtained.
When the distance C is increased, the “EGR flow guide function” is exhibited, so that the pressure loss is reduced and the flow rate is increased. However, if the distance C is too large, the EGR merging flow path 50 is throttled by the intake throttle valve 23 as in Conventional Example 1, and the “EGR throttle phenomenon” occurs.
The arrangement of the intake throttle valve 23 of the present embodiment is an arrangement in which the “EGR throttle phenomenon” does not occur and the “EGR flow guide function” can be maintained, and the flow rate of the EGR gas can be increased.

以上のように、本実施例によれば、「ＥＧＲ絞り現象」が発生せず、かつ、「ＥＧＲ流れガイド機能」を維持することができるため、ＥＧＲ配管２０ａの径を大きくすることなく、ＥＧＲガスの流量を増加させることができる。すなわち、バルブ装置の小型化を図りつつ、ＥＧＲガスの流量を増加させることができる。 As described above, according to the present embodiment, the “EGR throttling phenomenon” does not occur and the “EGR flow guide function” can be maintained, so that the EGR pipe 20a does not have to be increased in diameter without increasing the EGR diameter. The gas flow rate can be increased. That is, the flow rate of the EGR gas can be increased while downsizing the valve device.

２ 吸気通路、２ａ 吸気配管、２０ 低圧ＥＧＲ通路、２０ａ ＥＧＲ配管、２１ 低圧ＥＧＲバルブ、２３ 吸気絞り弁、２３ａ 吸気絞り弁の上流端、２３ｂ 吸気絞り弁の下流端、２４ バルブ装置、２７ シャフト、２９ アクチュエータ、３０ リンク機構、４０ 接続口   2 intake passage, 2a intake piping, 20 low pressure EGR passage, 20a EGR piping, 21 low pressure EGR valve, 23 intake throttle valve, 23a upstream end of intake throttle valve, 23b downstream end of intake throttle valve, 24 valve device, 27 shaft, 29 Actuator, 30 Link mechanism, 40 Connection port

Claims (2)

内燃機関（１）に吸気を導く吸気通路（２）と、前記内燃機関（１）から排気を排出するための排気通路（３）と、前記排気通路（３）に配される排気タービン（４）と前記吸気通路（２）に配されるコンプレッサ（５）とを有する過給機と、排気の一部を前記吸気通路（２）へ還流する高圧ＥＧＲ装置及び低圧ＥＧＲ装置とを備え、前記低圧ＥＧＲ装置が、前記排気タービン（４）より排気下流側の前記排気通路（３）と前記コンプレッサ（５）の吸気上流側の吸気通路（２、２ａ）とを接続してＥＧＲガスを前記吸気通路（２、２ａ）へ還流させる構成になっている内燃機関（１）の吸排気システムにおいて、
前記低圧ＥＧＲ装置を構成するバルブ装置であって、
自身の流路軸ｙを前記吸気通路（２、２ａ）内に延長したときに前記吸気通路（２、２ａ）の流路軸ｘと直交する低圧ＥＧＲ通路（２０、２０ａ）と、
前記低圧ＥＧＲ通路（２０、２０ａ）を開閉するバタフライ型の低圧ＥＧＲバルブ（２１）と、
前記吸気通路（２、２ａ）に配されて、前記吸気通路（２、２ａ）を絞り、前記吸気通路（２、２ａ）に導入されるＥＧＲガスの流量を増加させるバタフライ型の吸気絞り弁（２３）と、
前記低圧ＥＧＲバルブ（２１）及び前記吸気絞り弁（２３）の回動中心となるシャフト（２６、２７）同士を連動駆動し、前記低圧ＥＧＲバルブ（２１）が前記低圧ＥＧＲ通路（２０、２０ａ）の開度を最大とする時に、前記吸気絞り弁（２３）が前記吸気通路（２、２ａ）を最も絞った吸気全閉にする連動駆動機構（２９、３０）と、
吸気全閉時の前記吸気絞り弁（２３）の姿勢であって、前記回動中心（２７）よりも前記低圧ＥＧＲ通路（２０、２０ａ）の接続口（４０）に近い側に前記吸気絞り弁（２３）の上流端（２３ａ）が位置し、前記回動中心（２７）よりも前記接続口（４０）から遠い側に前記吸気絞り弁（２３）の下流端（２３ｂ）が位置するように、前記吸気通路（２、２ａ）の流路軸ｘに対して傾斜する前記吸気絞り弁（２３）の姿勢とを備え、
前記吸気絞り弁（２３）の下流端（２３ｂ）が、前記吸気全閉時に、前記吸気通路（２、２ａ）の流路軸ｘと前記低圧ＥＧＲ通路（２０、２０ａ）の流路軸ｙとの交点ｏよりも前記吸気通路（２、２ａ）の下流側に位置し、
前記吸気全閉時にＥＧＲガスが前記低圧ＥＧＲ通路（２０、２０ａ）を経て前記吸気絞り弁下流側の前記吸気通路（２、２ａ）へ流れる流路において、流路面積が最も小さい箇所が、前記低圧ＥＧＲ通路（２０、２０ａ）に設けられていることを特徴とするバルブ装置。 An intake passage (2) for guiding intake air to the internal combustion engine (1), an exhaust passage (3) for exhausting exhaust gas from the internal combustion engine (1), and an exhaust turbine (4) disposed in the exhaust passage (3) ) And a compressor (5) disposed in the intake passage (2), and a high-pressure EGR device and a low-pressure EGR device that recirculate a part of the exhaust to the intake passage (2), A low-pressure EGR device connects the exhaust passage (3) on the exhaust downstream side of the exhaust turbine (4) and the intake passage (2, 2a) on the intake upstream side of the compressor (5) to supply EGR gas to the intake air. In the intake and exhaust system of the internal combustion engine (1) configured to recirculate to the passage (2, 2a),
A valve device constituting the low-pressure EGR device ,
A low pressure EGR passage (20, 20a) orthogonal to the flow passage axis x of the intake passage (2, 2a) when its own flow passage axis y is extended into the intake passage (2, 2a);
A butterfly-type low-pressure EGR valve (21) for opening and closing the low-pressure EGR passage (20, 20a);
A butterfly type intake throttle valve (2) disposed in the intake passage (2, 2a) to restrict the intake passage (2, 2a) and increase the flow rate of EGR gas introduced into the intake passage (2, 2a). 23)
The low pressure EGR valve (21) and the shaft (26, 27), which are the rotation centers of the intake throttle valve (23), are driven together, and the low pressure EGR valve (21) is in the low pressure EGR passage (20, 20a). An interlocking drive mechanism (29, 30) that causes the intake throttle valve (23) to fully close the intake passage (2, 2a) when the opening of the intake valve is maximized,
A posture of the intake fully closed the intake throttle valve (23), said rotation center (27) the intake throttle valve on the side closer to the connection port (40) of the low-pressure EGR passage (20, 20a) than The upstream end (23a) of (23) is located, and the downstream end (23b) of the intake throttle valve (23) is located on the side farther from the connection port (40) than the rotation center (27). The posture of the intake throttle valve (23) inclined with respect to the flow path axis x of the intake passage (2, 2a) ,
The downstream end (23b) of the intake throttle valve (23) has a flow path axis x of the intake passage (2, 2a) and a flow path axis y of the low pressure EGR passage (20, 20a) when the intake is fully closed. Is located on the downstream side of the intake passage (2, 2a) from the intersection o of
In the flow path where EGR gas flows through the low pressure EGR passage (20, 20a) to the intake passage (2, 2a) on the downstream side of the intake throttle valve when the intake air is fully closed, the portion with the smallest flow area is the A valve device provided in the low pressure EGR passage (20, 20a). 請求項１に記載のバルブ装置において、
前記回動中心（２７）が、前記交点ｏよりも前記吸気通路（２、２ａ）の上流側に位置することを特徴とするバルブ装置。 The valve device according to claim 1,
The valve device, wherein the rotation center (27) is located upstream of the intersection point o in the intake passage (2, 2a).
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