JP2006037765A - Exhaust gas recirculation control device - Google Patents

Exhaust gas recirculation control device Download PDF

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Publication number
JP2006037765A
JP2006037765A JP2004215714A JP2004215714A JP2006037765A JP 2006037765 A JP2006037765 A JP 2006037765A JP 2004215714 A JP2004215714 A JP 2004215714A JP 2004215714 A JP2004215714 A JP 2004215714A JP 2006037765 A JP2006037765 A JP 2006037765A
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Prior art keywords
exhaust gas
passage
swing
valve
cooling passage
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JP2004215714A
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JP4324967B2 (en
Inventor
Katsuhiro Kuroki
勝洋 黒木
Kazuto Maeda
一人 前田
Takashi Kobayashi
高史 小林
Osamu Shimane
修 島根
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Denso Corp
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Denso Corp
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Priority to JP2004215714A priority Critical patent/JP4324967B2/en
Priority to FR0507849A priority patent/FR2873412B1/en
Priority to DE102005034363A priority patent/DE102005034363A1/en
Publication of JP2006037765A publication Critical patent/JP2006037765A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • 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
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/25—Layout, e.g. schematics with coolers having bypasses
    • F02M26/26—Layout, e.g. schematics with coolers having bypasses characterised by details of the bypass valve
    • 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
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
    • F02M26/30—Connections of coolers to other devices, e.g. to valves, heaters, compressors or filters; Coolers characterised by their location on the engine
    • 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
    • F02M26/45—Sensors specially adapted for EGR systems
    • F02M26/46—Sensors specially adapted for EGR systems for determining the characteristics of gases, e.g. composition
    • F02M26/47—Sensors specially adapted for EGR systems for determining the characteristics of gases, e.g. composition the characteristics being temperatures, pressures or flow rates
    • 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
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/28—Layout, e.g. schematics with liquid-cooled heat exchangers
    • 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
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
    • F02M26/32—Liquid-cooled heat exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/06—Derivation channels, e.g. bypass

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Analytical Chemistry (AREA)
  • Thermal Sciences (AREA)
  • Exhaust-Gas Circulating Devices (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compact and inexpensive exhaust gas recirculation control device which achieves the prevention of a malfunction and the improvement of vibration resistance. <P>SOLUTION: The device is provided with a cooling passage 75 for circulating exhaust gas being cooled, a bypass passage 81 for circulating the exhaust gas by bypassing the cooling passage 75, a swing valve 56 for opening/closing respective outlets 72, 73 of the cooling passage 75 and the bypass passage 81, bearings 78, 79 for supporting a swing shaft 84 of the swing valve 56 and a lead-out port 83 for leading out exhaust gas to an intake system of an engine by communicating to one of the cooling passage 75 and the bypass passage 81 in which one of the outlets 72, 73 is opened. The swing shaft 84 is arranged so as to extend in the cooling passage 75. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、内燃機関（以下、「内燃機関」をエンジンという）の吸気系へ導いて再循環させる排気ガスの温度を制御する排気ガス再循環制御装置（以下、「排気ガス再循環」をＥＧＲという）に関する。   The present invention relates to an exhaust gas recirculation control device (hereinafter referred to as “exhaust gas recirculation”) that controls the temperature of exhaust gas to be recirculated by introducing it into the intake system of an internal combustion engine (hereinafter referred to as “the internal combustion engine”). About).

特許文献１には、排気ガスを冷却しつつ流通させる冷却通路と、冷却通路を迂回して排気ガスを流通させるバイパス通路と、バイパス通路を開閉するバタフライ弁とを備えたＥＧＲ制御装置が開示されている。このＥＧＲ制御装置では、バタフライ弁によりバイパス通路を開放することで、当該バイパス通路を通過した排気ガスと冷却通路を通過した排気ガスとを混合して吸気系へと導くことができる。したがって、バタフライ弁の開度を調整すれば、各通路からの排気ガスの混合率が変化して、吸気系へ導かれる排気ガスの温度も変化する。   Patent Document 1 discloses an EGR control device that includes a cooling passage that circulates exhaust gas while cooling, a bypass passage that bypasses the cooling passage and circulates exhaust gas, and a butterfly valve that opens and closes the bypass passage. ing. In this EGR control device, by opening the bypass passage by the butterfly valve, the exhaust gas that has passed through the bypass passage and the exhaust gas that has passed through the cooling passage can be mixed and guided to the intake system. Therefore, if the opening degree of the butterfly valve is adjusted, the mixing ratio of the exhaust gas from each passage changes, and the temperature of the exhaust gas guided to the intake system also changes.

欧州特許出願公開第０９８７４２７号明細書European Patent Application No. 0987427

しかし、上記特許文献１のＥＧＲ制御装置では、バタフライ弁の弁軸がバイパス通路内を延伸しているため、当該弁軸を支持する軸受は、バイパス通路を通過した高温の排気ガスに晒される。そのため、高温の排気ガスの熱が弁軸を通じて軸受へ伝達されると、軸受が温度上昇して溶融してしまい、弁ロック等の作動不良が生じる。また、温度上昇により軸受の熱膨張量が大きくなるため、弁軸と軸受との間のクリアランスを大きく設定しなければならず、それにより耐振性が低下する。
尚、こうした問題を解決する方法として、高温に晒された軸受を冷媒により冷却する方法が考えられるが、この方法では、冷媒の流通装置を追加しなければならないため、ＥＧＲ制御装置の大型化とコストアップとを招いてしまう。
本発明の目的は、作動不良の防止と耐振性の向上とを達成する小型且つ安価なＥＧＲ制御装置を提供することにある。 However, in the EGR control device of Patent Document 1, since the valve shaft of the butterfly valve extends in the bypass passage, the bearing that supports the valve shaft is exposed to high-temperature exhaust gas that has passed through the bypass passage. Therefore, when the heat of the high-temperature exhaust gas is transmitted to the bearing through the valve shaft, the bearing rises in temperature and melts, resulting in malfunction such as valve locking. Moreover, since the amount of thermal expansion of the bearing increases due to the temperature rise, the clearance between the valve shaft and the bearing must be set large, thereby reducing the vibration resistance.
As a method for solving such a problem, a method of cooling a bearing exposed to a high temperature with a refrigerant can be considered. However, in this method, since a refrigerant circulation device has to be added, the EGR control device is increased in size. Incurs an increase in cost.
An object of the present invention is to provide a small and inexpensive EGR control device that achieves prevention of malfunction and improvement of vibration resistance.

請求項１に記載の発明によると、軸受に支持されて冷却通路及びバイパス通路の各出口部を開閉する揺動弁の揺動軸は冷却通路内を延伸しているので、当該揺動軸は、冷却通路により冷却された低温の排気ガスに晒されることとなる。これにより、揺動軸を通じて伝達される排気ガスの熱によって軸受の温度が上昇することを抑制できる。そのため、排気ガスからの受熱によっては軸受が溶融し難くなるので、弁ロック等の作動不良を防止できる。また、排気ガスからの受熱による軸受の熱膨張量が小さくなるので、揺動軸と軸受との間のクリアランスを小さく設定して、耐振性を向上することができる。そして、このような効果は、冷却装置等を用いなくても、冷却通路内を延伸するように揺動軸を配置するだけで得られるので、小型且つ安価なＥＧＲ制御装置を実現できる。   According to the first aspect of the present invention, the swing shaft of the swing valve supported by the bearing and opening and closing the outlets of the cooling passage and the bypass passage extends in the cooling passage. Then, it is exposed to the low-temperature exhaust gas cooled by the cooling passage. Thereby, it can suppress that the temperature of a bearing raises with the heat | fever of the exhaust gas transmitted through a rocking | fluctuation shaft. For this reason, the bearing becomes difficult to melt depending on the heat received from the exhaust gas, and malfunction such as valve locking can be prevented. In addition, since the amount of thermal expansion of the bearing due to heat received from the exhaust gas is reduced, the vibration resistance can be improved by setting the clearance between the swing shaft and the bearing small. Since such an effect can be obtained by merely arranging the swing shaft so as to extend in the cooling passage without using a cooling device or the like, a small and inexpensive EGR control device can be realized.

揺動軸と軸受との間をシールするシール部材を備えた請求項２に記載の発明によれば、揺動軸を通じて伝達される排気ガスの熱に起因して軸受並びに当該シール部材が溶融することを防止できる。このようにシール部材の溶融が防止されることによって、揺動軸と軸受との間のシール性が長期に亘って確保され得る。   According to the second aspect of the present invention, the seal member for sealing between the swing shaft and the bearing is melted due to the heat of the exhaust gas transmitted through the swing shaft. Can be prevented. By preventing the sealing member from melting as described above, the sealing performance between the swing shaft and the bearing can be ensured over a long period of time.

請求項３に記載の発明によると、揺動軸は、冷却通路の出口部とバイパス通路の出口部とを仕切る隔壁を挟んでバイパス通路の出口部とは反対側に設けられる。これにより、バイパス通路を流通する高温の排気ガスが隔壁に遮られて揺動軸の周囲に到達し難くなるので、当該高温の排気ガスによって軸受が温度上昇することを抑制できる。
請求項４に記載の発明によると、隔壁において排気ガス流れの下流側端部は揺動軸側へ曲げられているので、バイパス通路を流通する高温の排気ガスが揺動軸の周囲に一層到達し難くなり、軸受の温度上昇の抑制効果が促進される。 According to the invention described in claim 3, the swing shaft is provided on the opposite side of the outlet portion of the bypass passage across the partition wall that partitions the outlet portion of the cooling passage and the outlet portion of the bypass passage. As a result, the high-temperature exhaust gas flowing through the bypass passage is blocked by the partition wall and does not easily reach the periphery of the swing shaft. Therefore, it is possible to suppress the temperature rise of the bearing due to the high-temperature exhaust gas.
According to the fourth aspect of the invention, since the downstream end of the exhaust gas flow in the partition wall is bent toward the swing shaft, the high-temperature exhaust gas flowing through the bypass passage further reaches the periphery of the swing shaft. It becomes difficult to suppress the temperature rise of the bearing.

請求項５に記載の発明によると、揺動弁は、バイパス通路を開くとき揺動軸と隔壁との間の隙間を通じて冷却通路と導出口とを連通させる。これにより、バイパス通路が開かれても、冷却通路により冷却された低温の排気ガスが揺動軸と隔壁との間の隙間を流通するようになるため、バイパス通路から導出口へと流出した高温の排気ガスが揺動軸の周囲に到達し難くなる。したがって、高温の排気ガスにより軸受が温度上昇することを抑制できる。   According to the fifth aspect of the present invention, the swing valve communicates the cooling passage and the outlet through the gap between the swing shaft and the partition when the bypass passage is opened. As a result, even if the bypass passage is opened, the low-temperature exhaust gas cooled by the cooling passage flows through the gap between the swing shaft and the partition wall. This makes it difficult for the exhaust gas to reach the periphery of the swing shaft. Therefore, it is possible to suppress the temperature rise of the bearing due to the high temperature exhaust gas.

請求項６に記載の発明によると、揺動弁の連通遮断部は、揺動弁が冷却通路を閉じるとき隔壁に係止されて冷却通路と導出口との連通を遮断する。これにより、冷却通路及びバイパス通路の双方を開くときには、低温の排気ガスを揺動軸と隔壁との間の隙間に流して軸受の温度上昇を抑制することができ、また一方、バイパス通路のみを開くときには、冷却通路を閉塞して高温の排気ガスを確実に吸気系へ導くことができる。   According to the sixth aspect of the present invention, the communication blocking portion of the swing valve is locked to the partition wall when the swing valve closes the cooling passage to block communication between the cooling passage and the outlet. As a result, when both the cooling passage and the bypass passage are opened, a low-temperature exhaust gas can be passed through the gap between the swing shaft and the partition wall to suppress an increase in the temperature of the bearing. When opening, the cooling passage can be closed to reliably guide the hot exhaust gas to the intake system.

請求項７に記載の発明によると、揺動弁がバイパス通路を閉じるとき隔壁の下流側端部が揺動弁を係止するので、当該係止機能を発揮する部品を新たに設ける必要がない。したがって、部品点数の減少、ひいてはコストダウンに貢献できる。
請求項８に記載の発明によると、揺動弁がバイパス通路を閉じるとき隔壁の下流側端部は、揺動弁において揺動軸から径方向外側へ突出する弁本体を係止する。これにより、バイパス通路を流通する高温の排気ガスが弁本体に遮られて揺動軸の周囲に一層到達し難くなるため、軸受の温度上昇の抑制効果が促進される。 According to the seventh aspect of the invention, when the swing valve closes the bypass passage, the downstream end of the partition wall locks the swing valve, so there is no need to newly provide a part that exhibits the locking function. . Therefore, it is possible to contribute to a reduction in the number of parts and a cost reduction.
According to the eighth aspect of the present invention, when the swing valve closes the bypass passage, the downstream end of the partition wall locks the valve main body protruding radially outward from the swing shaft in the swing valve. As a result, the high-temperature exhaust gas flowing through the bypass passage is blocked by the valve main body and hardly reaches the periphery of the swing shaft, thereby promoting the effect of suppressing the temperature rise of the bearing.

請求項９に記載の発明によると、揺動弁が冷却通路を閉じるとき隔壁の下流側端部が揺動弁を係止するので、当該係止機能を発揮する部品を新たに設ける必要がない。したがって、部品点数の減少、ひいてはコストダウンに貢献できる。   According to the ninth aspect of the present invention, when the swing valve closes the cooling passage, the downstream end of the partition wall locks the swing valve, so there is no need to newly provide a part that exhibits the locking function. . Therefore, it is possible to contribute to a reduction in the number of parts and a cost reduction.

以下、本発明の複数の実施形態を図面に基づいて説明する。
図２は、本発明が適用された第一実施形態によるエンジンシステム１０を示している。車両に搭載されて用いられるエンジンシステム１０は、エンジン１２、吸気系２０、排気系３０、ＥＧＲ系４０等から構成されている。 Hereinafter, a plurality of embodiments of the present invention will be described with reference to the drawings.
FIG. 2 shows an engine system 10 according to a first embodiment to which the present invention is applied. An engine system 10 mounted and used in a vehicle includes an engine 12, an intake system 20, an exhaust system 30, an EGR system 40, and the like.

吸気系２０は、吸気管２１、吸気マニホールド２２、エアクリーナ２３及びスロットル装置２４を有している。吸気管２１及び吸気マニホールド２２は、車外から吸入された空気が流通する吸気通路を形成している。吸気管２１の中途部には、エアクリーナ２３及びスロットル装置２４が上流側からこの順で介装されている。エアクリーナ２３は、吸気通路を流れる吸入空気中の異物を除去する。スロットル装置２４は、吸気通路における吸入空気の流量を調整する。吸気管２１とエンジン１２との間を接続している吸気マニホールド２２は、サージタンク２６及び複数の分枝管２７を備えている。スロットル装置２４により流量調整された吸入空気は、サージタンク２６により脈動を吸収された後、各分枝管２７によってエンジン１２の各シリンダへと分配される。   The intake system 20 includes an intake pipe 21, an intake manifold 22, an air cleaner 23, and a throttle device 24. The intake pipe 21 and the intake manifold 22 form an intake passage through which air sucked from outside the vehicle flows. In the middle of the intake pipe 21, an air cleaner 23 and a throttle device 24 are interposed in this order from the upstream side. The air cleaner 23 removes foreign matter in the intake air flowing through the intake passage. The throttle device 24 adjusts the flow rate of intake air in the intake passage. The intake manifold 22 that connects the intake pipe 21 and the engine 12 includes a surge tank 26 and a plurality of branch pipes 27. The intake air whose flow rate is adjusted by the throttle device 24 is pulsated by the surge tank 26 and then distributed to each cylinder of the engine 12 by each branch pipe 27.

排気系３０は、排気マニホールド３１及び排気管３２を有している。排気マニホールド３１及び排気管３２は、エンジン１２から排出された排気ガスが流通する排気通路を形成している。排気マニホールド３１は、複数の分枝管３４及び合流部３５を備えている。エンジン１２の各シリンダから各分枝管３４へ排出された排気ガスは合流部３５において合流する。排気管３２は合流部３５に接続されており、合流部３５から流れ込む排気ガスを車両のマフラーを通じて車外へ放出する。   The exhaust system 30 has an exhaust manifold 31 and an exhaust pipe 32. The exhaust manifold 31 and the exhaust pipe 32 form an exhaust passage through which exhaust gas discharged from the engine 12 flows. The exhaust manifold 31 includes a plurality of branch pipes 34 and a merging portion 35. Exhaust gases discharged from the cylinders of the engine 12 to the branch pipes 34 merge at the merge portion 35. The exhaust pipe 32 is connected to the junction 35 and discharges exhaust gas flowing from the junction 35 to the outside of the vehicle through the muffler of the vehicle.

ＥＧＲ系４０は、環流管４１、温度調整装置４２、流量調整装置４３、温度センサ４４及びコントローラ４５を有している。環流管４１は排気マニホールド３１の合流部３５と吸気マニホールド２２のサージタンク２６との間を接続しており、合流部３５から流れ込む排気ガスの一部をサージタンク２６へと導いてエンジン１２に再循環させるＥＧＲ通路を形成している。環流管４１の中途部には、温度調整装置４２及び流量調整装置４３が上流側からこの順で介装されている。即ち環流管４１は、合流部３５と温度調整装置４２との間の第一管部４７、温度調整装置４２と流量調整装置４３との間の第二管部４８、並びに流量調整装置４３とサージタンク２６との間の第三管部４９とからなる。温度調整装置４２はコントローラ４５に電気的に接続されており、コントローラ４５の指令に従ってサージタンク２６へ導く排気ガスの温度を調整する。流量調整装置４３はコントローラ４５に電気的に接続されており、コントローラ４５の指令に従ってＥＧＲ弁の開度を変化させることで、サージタンク２６へ導く排気ガスの流量を調整する。温度センサ４４は第三管部４９に付設されており、サージタンク２６へ導く排気ガスの温度を検出する。温度センサ４４はコントローラ４５に電気的に接続されており、排気ガス温度の検出結果をコントローラ４５へ出力する。コントローラ４５はマイクロコンピュータを主体に構成されており、温度調整装置４２、流量調整装置４３等を制御する。   The EGR system 40 includes a reflux pipe 41, a temperature adjustment device 42, a flow rate adjustment device 43, a temperature sensor 44, and a controller 45. The recirculation pipe 41 is connected between the merging portion 35 of the exhaust manifold 31 and the surge tank 26 of the intake manifold 22, and a part of the exhaust gas flowing from the merging portion 35 is led to the surge tank 26 and recirculated to the engine 12. An EGR passage to be circulated is formed. A temperature adjusting device 42 and a flow rate adjusting device 43 are interposed in this order from the upstream side in the middle of the reflux pipe 41. That is, the reflux pipe 41 includes a first pipe part 47 between the merging part 35 and the temperature adjustment apparatus 42, a second pipe part 48 between the temperature adjustment apparatus 42 and the flow rate adjustment apparatus 43, and a flow rate adjustment apparatus 43 and a surge. A third pipe portion 49 between the tank 26 and the tank 26 is provided. The temperature adjusting device 42 is electrically connected to the controller 45, and adjusts the temperature of the exhaust gas led to the surge tank 26 in accordance with a command from the controller 45. The flow rate adjusting device 43 is electrically connected to the controller 45, and adjusts the flow rate of the exhaust gas led to the surge tank 26 by changing the opening of the EGR valve in accordance with a command from the controller 45. The temperature sensor 44 is attached to the third pipe portion 49 and detects the temperature of the exhaust gas led to the surge tank 26. The temperature sensor 44 is electrically connected to the controller 45, and outputs the detection result of the exhaust gas temperature to the controller 45. The controller 45 is mainly composed of a microcomputer and controls the temperature adjusting device 42, the flow rate adjusting device 43, and the like.

次に、温度調整装置４２及びコントローラ４５について詳細に説明する。図１及び図４に示すように温度調整装置４２は、導入部５１、冷却部５２、バイパス部５３、弁支持部５４、導出部５５、隔壁５８、揺動弁５６及び弁駆動部５７を備えている。
導入部５１はＳＵＳ等の金属で筒状に形成されている。第一管部４７に接続される導入部５１は、排気マニホールド３１からの排気ガスが導入される導入口６０を内側に形成している。 Next, the temperature adjustment device 42 and the controller 45 will be described in detail. As shown in FIGS. 1 and 4, the temperature adjustment device 42 includes an introduction part 51, a cooling part 52, a bypass part 53, a valve support part 54, a lead-out part 55, a partition wall 58, a swing valve 56, and a valve drive part 57. ing.
The introduction part 51 is formed in a cylindrical shape with a metal such as SUS. The introduction part 51 connected to the first pipe part 47 has an introduction port 60 into which exhaust gas from the exhaust manifold 31 is introduced on the inner side.

冷却部５２の冷却ケース６１はＳＵＳ等の金属で筒状に形成されている。冷却ケース６１には、エンジン１２の冷却水系に冷却水管６２、６３（図２参照）を介して接続される二つの開口部６４、６５が形成されており、一方の冷却水管６２により冷却ケース６１内へ引水し、他方の冷却水管６３により冷却水系へ戻水する循環路が形成されている。冷却部５２のガス管６６はＳＵＳ等の金属で直管状に形成され、冷却ケース６１内を互いに平行に延伸する形態で複数設けられている。各ガス管６６の両端部は、冷却ケース６１の両端部を覆うリテーナ６７、６８を貫通する形態で当該リテーナ６７、６８に保持されている。これにより、各ガス管６６がそれぞれ内側に形成する複数の第一通路６９が、冷却ケース６１内における冷却水の流通部分との連通を遮断されている。冷却ケース６１の一端部を覆うリテーナ６７は導入部５１に接続されており、当該リテーナ６７に保持される各ガス管６６内の第一通路６９の一端部が導入口６０に連通している。各第一通路６９は、導入口６０から一端部側へ流入する排気ガスを他端部側へ向かって流通させる。このとき各第一通路６９を通過する排気ガスは、冷却ケース６１内に引き込まれた冷却水によって冷却される。   The cooling case 61 of the cooling unit 52 is formed in a cylindrical shape with a metal such as SUS. The cooling case 61 is formed with two openings 64 and 65 connected to the cooling water system of the engine 12 via cooling water pipes 62 and 63 (see FIG. 2). A circulation path is formed for drawing water inward and returning water to the cooling water system by the other cooling water pipe 63. The gas pipe 66 of the cooling unit 52 is formed in a straight tube shape with a metal such as SUS, and a plurality of gas pipes 66 are provided in a form extending in parallel with each other in the cooling case 61. Both end portions of each gas pipe 66 are held by the retainers 67 and 68 so as to penetrate the retainers 67 and 68 that cover both end portions of the cooling case 61. As a result, the plurality of first passages 69 formed on the inner sides of the gas pipes 66 are blocked from communicating with the circulation portion of the cooling water in the cooling case 61. A retainer 67 that covers one end portion of the cooling case 61 is connected to the introduction portion 51, and one end portion of the first passage 69 in each gas pipe 66 held by the retainer 67 communicates with the introduction port 60. Each first passage 69 circulates the exhaust gas flowing from the inlet 60 to the one end side toward the other end side. At this time, the exhaust gas passing through each first passage 69 is cooled by the cooling water drawn into the cooling case 61.

バイパス部５３はＳＵＳ等の金属で形成されており、冷却部５２の各ガス管６６に対して略平行の筒状を呈している。バイパス部５３の一端部はリテーナ６７を介して導入部５１に接続されており、当該バイパス部５３が内側に形成する第二通路７０の一端部が導入口６０に連通している。第二通路７０は、導入口６０から一端部側へ流入する排気ガスを他端部側へ向かって流通させる。   The bypass part 53 is formed of a metal such as SUS and has a cylindrical shape substantially parallel to each gas pipe 66 of the cooling part 52. One end portion of the bypass portion 53 is connected to the introduction portion 51 via the retainer 67, and one end portion of the second passage 70 formed inside by the bypass portion 53 communicates with the introduction port 60. The second passage 70 allows the exhaust gas flowing from the introduction port 60 to the one end side to flow toward the other end side.

図１、図３及び図４に示すように弁支持部５４は、ＳＵＳ等の金属で筒状に形成されており、隔壁５８により内側を二つに仕切られている。弁支持部５４は、隔壁５８を挟む両側に第三通路７２と第四通路７３とを形成している。   As shown in FIGS. 1, 3, and 4, the valve support 54 is formed in a cylindrical shape with a metal such as SUS, and the inside is partitioned into two by a partition wall 58. The valve support 54 forms a third passage 72 and a fourth passage 73 on both sides of the partition wall 58.

弁支持部５４の一端部の第三通路７２側は、冷却ケース６１の導入部５１とは反対側の端部を覆うリテーナ６８に接続されており、当該リテーナ６８に保持される各ガス管６６内の第一通路６９の下流側端部が第三通路７２に連通している。これにより、排気ガスを冷却しつつ流通させる冷却通路７５が複数の第一通路６９と第三通路７２とから構成されており、第三通路７２が当該冷却通路７５の出口部７２を形成している。弁支持部５４の側壁７６、７７にそれぞれ埋設された軸受７８、７９は揺動弁５６の揺動軸８４の両端部を揺動可能に支持しており、当該揺動軸８４の中間部８４ａが冷却通路７５の出口部７２内を当該出口部７２の幅方向へ延伸している。尚、軸受７９と揺動軸８４との間には、冷却通路７５から弁駆動部５７内への排気ガス漏れを防ぐシール部材８０が介装されている。   The third passage 72 side of one end portion of the valve support portion 54 is connected to a retainer 68 that covers an end portion of the cooling case 61 opposite to the introduction portion 51, and each gas pipe 66 held by the retainer 68. A downstream end portion of the first passage 69 communicates with the third passage 72. As a result, the cooling passage 75 through which the exhaust gas is circulated is composed of a plurality of first passages 69 and third passages 72, and the third passage 72 forms the outlet portion 72 of the cooling passage 75. Yes. Bearings 78 and 79 embedded in the side walls 76 and 77 of the valve support portion 54 respectively support both end portions of the swing shaft 84 of the swing valve 56 so as to be swingable, and an intermediate portion 84 a of the swing shaft 84. Extends in the width direction of the outlet portion 72 in the outlet portion 72 of the cooling passage 75. A seal member 80 is interposed between the bearing 79 and the swing shaft 84 to prevent exhaust gas leakage from the cooling passage 75 into the valve drive unit 57.

また、弁支持部５４の上記一端部の第四通路７３側は、バイパス部５３の導入部５１とは反対側の端部にリテーナ６８を介して接続されており、当該バイパス部５３内の第二通路７０の下流側端部が第四通路７３に連通している。これにより、上記冷却通路７５を迂回して排気ガスを流通させるバイパス通路８１が第二通路７０と第四通路７３とから構成されており、第四通路７３が当該バイパス通路８１の出口部７３を形成している。   Further, the fourth passage 73 side of the one end portion of the valve support portion 54 is connected to an end portion of the bypass portion 53 opposite to the introduction portion 51 via a retainer 68, and the first end portion in the bypass portion 53 is connected. The downstream end of the second passage 70 communicates with the fourth passage 73. Thus, a bypass passage 81 that bypasses the cooling passage 75 and distributes the exhaust gas is constituted by the second passage 70 and the fourth passage 73, and the fourth passage 73 passes through the outlet 73 of the bypass passage 81. Forming.

導出部５５は、ＳＵＳ等の金属で弁支持部５４と一体に形成されている。円筒状の導出部５５は、揺動軸８４に対して中心軸線が略垂直である導出口８３を内側に形成している。一端部が第二管部４８に接続される導出部５５の他端部は、弁支持部５４における冷却部５２及びバイパス部５３とは反対側の端部に接続されている。導出部５５内の導出口８３は、冷却通路７５及びバイパス通路８１のうち出口部７２、７３が開かれた通路に連通し、連通した通路から流入する排気ガスを第二管部４８内のＥＧＲ通路へ導出する。   The lead-out part 55 is formed integrally with the valve support part 54 from a metal such as SUS. The cylindrical lead-out portion 55 has a lead-out port 83 having a central axis substantially perpendicular to the swing shaft 84 formed inside. The other end portion of the lead-out portion 55 whose one end portion is connected to the second pipe portion 48 is connected to an end portion of the valve support portion 54 opposite to the cooling portion 52 and the bypass portion 53. The outlet 83 in the outlet 55 communicates with the passage in which the outlets 72 and 73 are opened in the cooling passage 75 and the bypass passage 81, and exhaust gas flowing in from the connected passage passes through the EGR in the second pipe portion 48. Derived to the passage.

隔壁５８はＳＵＳ等の金属で板状に形成され、弁支持部５４の側壁７６、７７に固定されている。隔壁５８において、冷却通路７５及びバイパス通路８１を通過する排気ガス流れの下流側に位置した端部８７は揺動軸８４側へ曲げられており、当該下流側端部８７を除く部分は導出口８３の中心軸線に対して略平行となっている。   The partition wall 58 is formed in a plate shape with a metal such as SUS and is fixed to the side walls 76 and 77 of the valve support portion 54. In the partition wall 58, an end portion 87 located on the downstream side of the exhaust gas flow passing through the cooling passage 75 and the bypass passage 81 is bent toward the swing shaft 84, and a portion excluding the downstream end portion 87 is a lead-out port. It is substantially parallel to the 83 central axis.

揺動弁５６はＳＵＳ等の金属で形成されている。揺動弁５６の揺動軸８４は、上述の如く軸受７８、７９に支持されて冷却通路７５内を延伸している。これにより揺動軸８４は、隔壁５８を挟んでバイパス通路８１の出口部７３とは反対側に位置している。揺動弁５６の弁本体８５は、揺動軸８４の外周面から径方向外側へ突出する板状に形成されている。揺動弁５６の突起部８６は、弁本体８５とＶ字をなす形態で揺動軸８４の外周面から径方向外側へ突出する板状に形成されている。   The swing valve 56 is made of a metal such as SUS. As described above, the swing shaft 84 of the swing valve 56 is supported by the bearings 78 and 79 and extends in the cooling passage 75. Thus, the swing shaft 84 is located on the opposite side of the outlet portion 73 of the bypass passage 81 with the partition wall 58 interposed therebetween. The valve body 85 of the swing valve 56 is formed in a plate shape that protrudes radially outward from the outer peripheral surface of the swing shaft 84. The protrusion 86 of the swing valve 56 is formed in a plate shape that protrudes radially outward from the outer peripheral surface of the swing shaft 84 in a V-shape with the valve body 85.

揺動弁５６は、弁支持部５４及び導出部５５内において揺動することで、冷却通路７５及びバイパス通路８１の各出口部７２、７３を開閉する。
具体的には、いずれの揺動位置においても、弁本体８５及び突起部８６は弁支持部５４の側壁７６、７７に当接する。 The swing valve 56 swings in the valve support portion 54 and the lead-out portion 55 to open and close the outlet portions 72 and 73 of the cooling passage 75 and the bypass passage 81.
Specifically, the valve main body 85 and the protrusion 86 abut against the side walls 76 and 77 of the valve support 54 at any swing position.

そして、図４に示す第一揺動位置では、弁本体８５が弁支持部５４の第一係止壁８８に係止される。これにより、冷却通路７５の出口部７２が閉じられると共にバイパス通路８１の出口部７３が開かれ、当該バイパス通路８１を通過した高温の排気ガスが導出口８３を介して第二管部４８へと導かれる。尚、このとき、突起部８６と隔壁５８とが僅かに離間するため、揺動軸８４と隔壁５８の下流側端部８７との間の隙間９０を通じて冷却通路７５と導出口８３とが連通し、当該隙間９０を冷却通路７５の排気ガスが流れる。   4, the valve main body 85 is locked to the first locking wall 88 of the valve support 54. As a result, the outlet portion 72 of the cooling passage 75 is closed and the outlet portion 73 of the bypass passage 81 is opened, and the high-temperature exhaust gas that has passed through the bypass passage 81 passes through the outlet 83 to the second pipe portion 48. Led. At this time, since the protruding portion 86 and the partition wall 58 are slightly separated from each other, the cooling passage 75 and the outlet port 83 communicate with each other through the gap 90 between the swing shaft 84 and the downstream end portion 87 of the partition wall 58. The exhaust gas in the cooling passage 75 flows through the gap 90.

また、図５に示す第二揺動位置では、弁本体８５が弁支持部５４の第二係止壁８９及び隔壁５８の下流側端部８７に係止される。これにより、バイパス通路８１の出口部７３が閉じられると共に冷却通路７５の出口部７２が開かれ、当該冷却通路７５により冷却された低温の排気ガスが導出口８３を介して第二管部４８へと導かれる。   5, the valve main body 85 is locked to the second locking wall 89 of the valve support 54 and the downstream end 87 of the partition wall 58. As a result, the outlet portion 73 of the bypass passage 81 is closed and the outlet portion 72 of the cooling passage 75 is opened, and the low-temperature exhaust gas cooled by the cooling passage 75 passes to the second pipe portion 48 via the outlet port 83. It is guided.

またさらに、図６に示すように第一揺動位置と第二揺動位置の間となる揺動位置では、弁本体８５が第一及び第二係止壁８８、８９並びに隔壁５８のいずれにも係止されない。これにより、冷却通路７５及びバイパス通路８１の双方の出口部７２、７３が開放され、導出口８３では、各通路７５、８１からの排気ガスが合流して混ざり合い、当該混合ガスが導出口８３から第二管部４８へと導出される。したがって、第一揺動位置と第二揺動位置の間において揺動弁５６の揺動位置が変化することで、各通路７５、８１からの排気ガスの混合率が変化し、第二管部４８への導出ガスの温度が変化する。尚、このとき、突起部８６と隔壁５８とが離間するため、揺動軸８４と隔壁５８の下流側端部８７との間の隙間９０を通じて冷却通路７５と導出口８３とが連通し、当該隙間９０を冷却通路７５の排気ガスが流れる。   Furthermore, as shown in FIG. 6, the valve main body 85 is in any of the first and second locking walls 88 and 89 and the partition wall 58 at the swing position between the first swing position and the second swing position. Is not locked. As a result, the outlet portions 72 and 73 of both the cooling passage 75 and the bypass passage 81 are opened, and the exhaust gas from the passages 75 and 81 merges and mixes at the outlet 83, and the mixed gas flows into the outlet 83. To the second pipe 48. Therefore, when the rocking position of the rocking valve 56 changes between the first rocking position and the second rocking position, the mixing ratio of the exhaust gas from the passages 75 and 81 changes, and the second pipe portion The temperature of the derived gas to 48 changes. At this time, since the protruding portion 86 and the partition wall 58 are separated from each other, the cooling passage 75 and the outlet 83 are communicated with each other through the gap 90 between the swing shaft 84 and the downstream end portion 87 of the partition wall 58. Exhaust gas in the cooling passage 75 flows through the gap 90.

図１に示す弁駆動部５７は、図２に示すコントローラ４５と電気的に接続されており、コントローラ４５の指令に従って揺動弁５６の揺動位置を調整する。
コントローラ４５は、温度センサ４４から出力された排気ガス温度の検出結果等に基づいて、所望の排気ガス温度を実現するのに必要な揺動弁５６の揺動位置を弁駆動部５７に指令する。したがって、エンジンシステム１０では、排気ガス温度がフィードバック制御されることとなる。このように、温度調整装置４２、温度センサ４４及びコントローラ４５が共同して、特許請求の範囲に記載の「ＥＧＲ制御装置」を構成している。 The valve drive unit 57 shown in FIG. 1 is electrically connected to the controller 45 shown in FIG. 2 and adjusts the swing position of the swing valve 56 in accordance with a command from the controller 45.
Based on the detection result of the exhaust gas temperature output from the temperature sensor 44, the controller 45 instructs the valve drive unit 57 about the swing position of the swing valve 56 necessary to achieve the desired exhaust gas temperature. . Therefore, in the engine system 10, the exhaust gas temperature is feedback-controlled. Thus, the temperature adjusting device 42, the temperature sensor 44, and the controller 45 jointly constitute an “EGR control device” described in the claims.

以上説明した温度調整装置４２では、揺動弁５６の揺動軸８４が冷却通路７５内を延伸しているので、当該揺動軸８４は、冷却通路７５により冷却された低温の排気ガスに晒されることとなる。これにより、揺動軸８４を通じて伝達される排気ガスの熱によって軸受７８、７９及びシール部材８０の温度が上昇することを抑制できる。   In the temperature adjusting device 42 described above, the swing shaft 84 of the swing valve 56 extends in the cooling passage 75, so that the swing shaft 84 is exposed to the low-temperature exhaust gas cooled by the cooling passage 75. Will be. Thereby, it is possible to suppress the temperature of the bearings 78 and 79 and the seal member 80 from rising due to the heat of the exhaust gas transmitted through the swing shaft 84.

また、温度調整装置４２では、冷却通路７５の出口部７２とバイパス通路８１の出口部７３とを仕切る隔壁５８を挟んでバイパス通路８１の出口部７３とは反対側に揺動軸８４が設けられ、当該揺動軸８４側へ隔壁５８の下流側端部８７が曲げられている。そのため、バイパス通路８１を流通する高温の排気ガスが隔壁５８に十分に遮られて揺動軸８４の周囲に到達し難くなり、軸受７８、７９及びシール部材８０の温度上昇の抑制効果が高められる。   Further, in the temperature adjusting device 42, a swing shaft 84 is provided on the opposite side of the outlet portion 73 of the bypass passage 81 across the partition wall 58 that partitions the outlet portion 72 of the cooling passage 75 and the outlet portion 73 of the bypass passage 81. The downstream end portion 87 of the partition wall 58 is bent toward the swing shaft 84 side. Therefore, the high-temperature exhaust gas flowing through the bypass passage 81 is sufficiently blocked by the partition wall 58 and hardly reaches the periphery of the swing shaft 84, and the effect of suppressing the temperature rise of the bearings 78 and 79 and the seal member 80 is enhanced. .

さらに温度調整装置４２では、揺動弁５６がバイパス通路８１を開くとき、揺動軸８４と隔壁５８との間の隙間９０を通じて冷却通路７５と導出口８３とが連通する。そのため、バイパス通路８１が開かれても、冷却通路７５により冷却された低温の排気ガスが隙間９０を流れるようになるので、バイパス通路８１から導出口８３へと流出した高温の排気ガスが揺動軸８４の周囲に到達し難くなる。したがって、軸受７８、７９及びシール部材８０の温度上昇の抑制効果が高められる。   Further, in the temperature adjusting device 42, when the swing valve 56 opens the bypass passage 81, the cooling passage 75 and the outlet 83 communicate with each other through the gap 90 between the swing shaft 84 and the partition wall 58. Therefore, even if the bypass passage 81 is opened, the low-temperature exhaust gas cooled by the cooling passage 75 flows through the gap 90, so that the high-temperature exhaust gas flowing out from the bypass passage 81 to the outlet 83 swings. It becomes difficult to reach the periphery of the shaft 84. Therefore, the effect of suppressing the temperature rise of the bearings 78 and 79 and the seal member 80 is enhanced.

またさらに、温度調整装置４２では、揺動弁５６がバイパス通路８１を閉じるとき、揺動軸８４の径方向外側へ突出する弁本体８５が隔壁５８の下流側端部８７により係止される。これにより、バイパス通路８１を流通する高温の排気ガスは弁本体８５に遮られて揺動軸８４の周囲に到達し難くなる。したがって、軸受７８、７９及びシール部材８０の温度上昇の抑制効果が高められる。   Furthermore, in the temperature adjusting device 42, when the swing valve 56 closes the bypass passage 81, the valve main body 85 protruding outward in the radial direction of the swing shaft 84 is locked by the downstream end 87 of the partition wall 58. As a result, the high-temperature exhaust gas flowing through the bypass passage 81 is blocked by the valve body 85 and hardly reaches the periphery of the swing shaft 84. Therefore, the effect of suppressing the temperature rise of the bearings 78 and 79 and the seal member 80 is enhanced.

このように軸受７８、７９及びシール部材８０の温度上昇が効果的に抑制され得る温度調整装置４２では、それらの要素７８、７９、８０が排気ガスからの受熱によっては溶融し難くなるので、弁ロック等の作動不良並びにシール性の低下を防止できる。また、軸受７８、７９において排気ガスからの受熱による熱膨張量が小さくなるので、揺動軸８４と軸受７８、７９との間のクリアランスを小さく設定して耐振性を向上することができる。   Thus, in the temperature adjusting device 42 in which the temperature rise of the bearings 78 and 79 and the seal member 80 can be effectively suppressed, the elements 78, 79, and 80 are hardly melted by heat received from the exhaust gas. It is possible to prevent malfunctions such as locking and deterioration of sealing performance. Further, since the amount of thermal expansion due to heat received from the exhaust gas is reduced in the bearings 78 and 79, the clearance between the swing shaft 84 and the bearings 78 and 79 can be set small to improve vibration resistance.

そして、こうした作動不良及びシール性低下の防止効果や耐振性の向上効果は、冷却装置等を用いなくても、冷却通路７５内を延伸するように揺動軸８４を配置するだけで得られるので、小型化とコストダウンとを図ることができる。
しかも温度調整装置４２では、バイパス通路８１を閉じるときに隔壁５８の下流側端部８７が揺動弁５６を係止する機能を発揮するので、当該係止機能を発揮する新たな部品を追加する必要がない。したがって、部品点数の減少、ひいてはコストダウンをもたらすことができる。 Such an operation failure and the effect of preventing the deterioration of sealing performance and the effect of improving the vibration resistance can be obtained only by arranging the swing shaft 84 so as to extend in the cooling passage 75 without using a cooling device or the like. Therefore, it is possible to reduce the size and the cost.
In addition, in the temperature adjusting device 42, the downstream end 87 of the partition wall 58 functions to lock the swing valve 56 when the bypass passage 81 is closed, so a new part that exhibits the locking function is added. There is no need. Therefore, it is possible to reduce the number of parts and thus reduce the cost.

（第二実施形態）
図７は、本発明の第二実施形態による温度調整装置１００の要部を示している。第一実施形態と実質的に同一の構成部分には同一の符号を付すことで、説明を省略する。
温度調整装置１００では、第一揺動位置において揺動弁１１０が冷却通路７５を閉じるとき、隔壁１２０の下流側端部１２１が揺動弁１１０の突起部１１１を係止するように、それら要素１２１、１１１が形成されている。 (Second embodiment)
FIG. 7 shows a main part of the temperature adjusting device 100 according to the second embodiment of the present invention. Components that are substantially the same as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
In the temperature adjusting device 100, when the swing valve 110 closes the cooling passage 75 in the first swing position, these elements are arranged such that the downstream end 121 of the partition wall 120 locks the protrusion 111 of the swing valve 110. 121 and 111 are formed.

そして温度調整装置１００では、第一揺動位置と第二揺動位置との間の揺動位置において揺動弁１１０が冷却通路７５及びバイパス通路８１の双方を開くとき、第一実施形態の場合と同様に冷却通路７５と導出口８３とが隙間９０を通じて連通し、揺動軸８４の温度上昇が抑えられる。   In the temperature adjusting device 100, when the swing valve 110 opens both the cooling passage 75 and the bypass passage 81 at the swing position between the first swing position and the second swing position, Similarly, the cooling passage 75 and the outlet 83 communicate with each other through the gap 90, and the temperature rise of the swing shaft 84 is suppressed.

一方、図７に示す第一揺動位置において揺動弁５６が冷却通路７５を閉じるときには、隔壁１２０の下流側端部１２１が揺動弁１１０の突起部１１１を係止することにより、隙間９０を通じた冷却通路７５と導出口８３との連通が遮断される。そのため、高温の排気ガスを吸気系２０へ導くためにバイパス通路８１のみを開くとき、冷却通路７５を閉塞して吸気系２０へ導く排気ガスの温度低下を防ぐことができる。以上、突起部１１１が特許請求の範囲に記載の「連通遮断部」に相当する。   On the other hand, when the oscillating valve 56 closes the cooling passage 75 at the first oscillating position shown in FIG. 7, the downstream end 121 of the partition wall 120 engages the protrusion 111 of the oscillating valve 110 so that the gap 90 The communication between the cooling passage 75 and the outlet 83 is cut off. Therefore, when only the bypass passage 81 is opened to guide the hot exhaust gas to the intake system 20, it is possible to prevent the temperature reduction of the exhaust gas that closes the cooling passage 75 and leads to the intake system 20. As described above, the protrusion 111 corresponds to a “communication blocking unit” recited in the claims.

さらに温度調整装置１００では、冷却通路７５を閉じるときに隔壁５８の下流側端部８７が揺動弁５６を係止する機能を発揮するので、当該係止機能を発揮する新たな部品を追加する必要がない。したがって、部品点数の減少、ひいてはコストダウンをもたらすことができる。   Further, in the temperature adjusting device 100, when the cooling passage 75 is closed, the downstream side end portion 87 of the partition wall 58 exhibits a function of locking the swing valve 56. Therefore, a new part that exhibits the locking function is added. There is no need. Therefore, it is possible to reduce the number of parts and thus reduce the cost.

（第三実施形態）
図８は、本発明の第三実施形態による温度調整装置１５０の要部を示している。第一実施形態と実質的に同一の構成部分には同一の符号を付すことで、説明を省略する。
温度調整装置１５０では、冷却通路７５内において隔壁１６０の下流側端部１６１より下流側を揺動弁１７０の揺動軸１７１が延伸している。そのため、隔壁１６０を挟んでバイパス通路８１の出口部７３とは反対側には揺動軸１７１が位置しておらず、隔壁１６０の長さが排気流れ方向において短くなっている。したがって、隔壁１６０の材料費が低減されるので、コストダウン効果が促進される。 (Third embodiment)
FIG. 8 shows a main part of the temperature adjusting device 150 according to the third embodiment of the present invention. Components that are substantially the same as those in the first embodiment are denoted by the same reference numerals, and description thereof is omitted.
In the temperature adjustment device 150, the swing shaft 171 of the swing valve 170 extends downstream from the downstream end 161 of the partition wall 160 in the cooling passage 75. Therefore, the swing shaft 171 is not located on the opposite side of the bypass passage 81 from the outlet portion 73 across the partition wall 160, and the length of the partition wall 160 is shortened in the exhaust flow direction. Therefore, since the material cost of the partition 160 is reduced, the cost reduction effect is promoted.

以上、本発明の複数の実施形態について説明したが、本発明は、それらの実施形態に限定して解釈されるべきではない。
例えば上記第一〜第三実施形態では、軸受と揺動弁の揺動軸との間をシールするシール部材を設けているが、そのようなシール部材を設けないようにしてもよい。 Although a plurality of embodiments of the present invention have been described above, the present invention should not be construed as being limited to those embodiments.
For example, in the first to third embodiments, the seal member that seals between the bearing and the swing shaft of the swing valve is provided. However, such a seal member may not be provided.

第一実施形態による温度調整装置の要部を示す一部切り欠き側面図である。It is a partially cutaway side view which shows the principal part of the temperature control apparatus by 1st embodiment. 第一実施形態によるエンジンシステムを示す模式図である。It is a mimetic diagram showing an engine system by a first embodiment. 第一実施形態による温度調整装置を示す一部切り欠き正面図である。It is a partially notched front view which shows the temperature control apparatus by 1st embodiment. 第一実施形態による温度調整装置の要部を示す断面図である。It is sectional drawing which shows the principal part of the temperature control apparatus by 1st embodiment. 第一実施形態による温度調整装置の作動を説明するための断面図である。It is sectional drawing for demonstrating the action | operation of the temperature control apparatus by 1st embodiment. 第一実施形態による温度調整装置の作動を説明するための断面図である。It is sectional drawing for demonstrating the action | operation of the temperature control apparatus by 1st embodiment. 第二実施形態による温度調整装置の要部を示す断面図である。It is sectional drawing which shows the principal part of the temperature control apparatus by 2nd embodiment. 第三実施形態による温度調整装置の要部を示す断面図である。It is sectional drawing which shows the principal part of the temperature control apparatus by 3rd embodiment.

符号の説明Explanation of symbols

１０ エンジンシステム、１２ エンジン、２０ 吸気系、３０ 排気系、４０ ＥＧＲ系、４２、１００、１５０ 温度調整装置（ＥＧＲ制御装置）、４４ 温度センサ（ＥＧＲ制御装置）、４５ コントローラ（ＥＧＲ制御装置）、５１ 導入部、５２ 冷却部、５３ バイパス部、５４ 弁支持部、５５ 導出部、５６、１１０、１７０ 揺動弁、５７ 弁駆動部、５８、１２０、１６０ 隔壁、６０ 導入口、６１ 冷却ケース、６６ ガス管、６９ 第一通路（冷却通路）、７０ 第二通路（バイパス通路）、７２ 第三通路、出口部（冷却通路）、７３ 第四通路、出口部（バイパス通路）、７５ 冷却通路、７８、７９ 軸受、８０ シール部材、８１ バイパス通路、８３ 導出口、８４、１７１ 揺動軸、８５ 弁本体、８６ 突起部、８７、１２１、１６１ 下流側端部、９０ 隙間、１１１ 突起部（連通遮断部）
10 engine system, 12 engine, 20 intake system, 30 exhaust system, 40 EGR system, 42, 100, 150 temperature adjustment device (EGR control device), 44 temperature sensor (EGR control device), 45 controller (EGR control device), 51 Introducing section, 52 Cooling section, 53 Bypass section, 54 Valve support section, 55 Deriving section, 56, 110, 170 Oscillating valve, 57 Valve driving section, 58, 120, 160 Partition, 60 Inlet, 61 Cooling case, 66 gas pipe, 69 first passage (cooling passage), 70 second passage (bypass passage), 72 third passage, outlet portion (cooling passage), 73 fourth passage, outlet portion (bypass passage), 75 cooling passage, 78, 79 Bearing, 80 Seal member, 81 Bypass passage, 83 Outlet, 84, 171 Oscillating shaft, 85 Valve body, 86 Projection, 87, 121, 161 Downstream side Parts, 90 gaps, 111 projections (connection cutoff unit)

Claims (9)

内燃機関の吸気系へ導いて再循環させる排気ガスの温度を制御する排気ガス再循環制御装置であって、
排気ガスを冷却しつつ流通させる冷却通路と、
前記冷却通路を迂回して排気ガスを流通させるバイパス通路と、
第一揺動位置において前記冷却通路の出口部を閉じると共に前記バイパス通路の出口部を開き、第二揺動位置において前記冷却通路の出口部を開くと共に前記バイパス通路の出口部を閉じ、前記第一揺動位置と前記第二揺動位置との間において前記冷却通路及び前記バイパス通路の双方の出口部を開く揺動弁と、
前記揺動弁の揺動軸を支持する軸受と、
前記冷却通路及び前記バイパス通路のうち出口部が開いた通路に連通し、前記吸気系へ排気ガスを導出する導出口とを備え、
前記揺動軸は、前記冷却通路内を延伸していることを特徴とする排気ガス再循環制御装置。 An exhaust gas recirculation control device that controls the temperature of exhaust gas that is recirculated by being led to an intake system of an internal combustion engine,
A cooling passage for circulating the exhaust gas while cooling,
A bypass passage that bypasses the cooling passage and distributes exhaust gas;
In the first swing position, the outlet portion of the cooling passage is closed and the outlet portion of the bypass passage is opened. In the second swing position, the outlet portion of the cooling passage is opened and the outlet portion of the bypass passage is closed. A swing valve that opens both outlets of the cooling passage and the bypass passage between a swing position and the second swing position;
A bearing for supporting a swing shaft of the swing valve;
An outlet for communicating exhaust gas to the intake system, communicating with a passage having an outlet portion open among the cooling passage and the bypass passage;
The exhaust gas recirculation control device, wherein the swing shaft extends in the cooling passage. 前記揺動軸と前記軸受との間をシールするシール部材をさらに備えることを特徴とする請求項１に記載の排気ガス再循環制御装置。   The exhaust gas recirculation control device according to claim 1, further comprising a seal member that seals between the swing shaft and the bearing. 前記冷却通路の出口部と前記バイパス通路の出口部とを仕切る隔壁をさらに備え、
前記揺動軸は、前記隔壁を挟んで前記バイパス通路の出口部とは反対側に設けられることを特徴とする請求項１又は２に記載の排気ガス再循環制御装置。 A partition that partitions the outlet portion of the cooling passage and the outlet portion of the bypass passage;
3. The exhaust gas recirculation control device according to claim 1, wherein the swing shaft is provided on a side opposite to an outlet portion of the bypass passage with the partition wall interposed therebetween. 前記隔壁において排気ガス流れの下流側端部は前記揺動軸側へ曲げられていることを特徴とする請求項３に記載の排気ガス再循環制御装置。   The exhaust gas recirculation control device according to claim 3, wherein a downstream end portion of the exhaust gas flow in the partition wall is bent toward the swing shaft. 前記揺動弁は、前記バイパス通路を開くとき前記揺動軸と前記隔壁との間の隙間を通じて前記冷却通路と前記導出口とを連通させることを特徴とする請求項３又は４に記載の排気ガス再循環制御装置。   5. The exhaust according to claim 3, wherein the swing valve communicates the cooling passage with the outlet through a gap between the swing shaft and the partition when the bypass passage is opened. Gas recirculation control device. 前記揺動弁は、前記冷却通路を閉じるとき前記隔壁に係止されて前記冷却通路と前記導出口との連通を遮断する連通遮断部を有することを特徴とする請求項５に記載の排気ガス再循環制御装置。   6. The exhaust gas according to claim 5, wherein the oscillating valve has a communication blocking portion that is locked to the partition wall to close communication between the cooling passage and the outlet when the cooling passage is closed. Recirculation control device. 前記隔壁において排気ガス流れの下流側端部は、前記揺動弁が前記バイパス通路を閉じるとき前記揺動弁を係止することを特徴とする請求項３〜６のいずれか一項に記載の排気ガス再循環制御装置。   The downstream end of the exhaust gas flow in the partition wall locks the swing valve when the swing valve closes the bypass passage. Exhaust gas recirculation control device. 前記揺動弁は、前記揺動軸から径方向外側へ突出する弁本体を有し、
前記揺動弁が前記バイパス通路を閉じるとき前記隔壁の前記下流側端部は前記弁本体を係止することを特徴とする請求項７に記載の排気ガス再循環制御装置。 The swing valve has a valve body that protrudes radially outward from the swing shaft,
The exhaust gas recirculation control device according to claim 7, wherein the downstream end portion of the partition wall engages the valve body when the swing valve closes the bypass passage. 前記隔壁において排気ガス流れの下流側端部は、前記揺動弁が前記冷却通路を閉じるとき前記揺動弁を係止することを特徴とする請求項３〜８のいずれか一項に記載の排気ガス再循環制御装置。
The downstream end of the exhaust gas flow in the partition wall locks the swing valve when the swing valve closes the cooling passage. Exhaust gas recirculation control device.
JP2004215714A 2004-07-23 2004-07-23 Exhaust gas recirculation control device Expired - Fee Related JP4324967B2 (en)

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JP2004215714A JP4324967B2 (en) 2004-07-23 2004-07-23 Exhaust gas recirculation control device
FR0507849A FR2873412B1 (en) 2004-07-23 2005-07-22 DEVICE FOR CONTROLLING GAS TEMPERATURE
DE102005034363A DE102005034363A1 (en) 2004-07-23 2005-07-22 Gas temperature control device

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JP2009036077A (en) * 2007-08-01 2009-02-19 Denso Corp Exhaust gas change-over valve
JP2010169056A (en) * 2009-01-26 2010-08-05 Nissan Motor Co Ltd Control device for egr device
US8132407B2 (en) * 2008-04-03 2012-03-13 GM Global Technology Operations LLC Modular exhaust gas recirculation cooling for internal combustion engines

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DE102007048824B4 (en) * 2007-10-10 2018-02-22 Mahle International Gmbh Heat exchanger, in particular for exhaust gas cooling

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US6330910B1 (en) * 1999-03-03 2001-12-18 Easton Bennett Heat exchanger for a motor vehicle exhaust
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US6330910B1 (en) * 1999-03-03 2001-12-18 Easton Bennett Heat exchanger for a motor vehicle exhaust
JP2004169613A (en) * 2002-11-20 2004-06-17 Denso Corp Exhaust gas recirculation control apparatus
JP2004190693A (en) * 2002-12-06 2004-07-08 Aisan Ind Co Ltd Flow passage switching valve

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JP2009036077A (en) * 2007-08-01 2009-02-19 Denso Corp Exhaust gas change-over valve
US8132407B2 (en) * 2008-04-03 2012-03-13 GM Global Technology Operations LLC Modular exhaust gas recirculation cooling for internal combustion engines
JP2010169056A (en) * 2009-01-26 2010-08-05 Nissan Motor Co Ltd Control device for egr device

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