WO2013073132A1 - 多気筒エンジンの排気装置 - Google Patents
多気筒エンジンの排気装置 Download PDFInfo
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- WO2013073132A1 WO2013073132A1 PCT/JP2012/007113 JP2012007113W WO2013073132A1 WO 2013073132 A1 WO2013073132 A1 WO 2013073132A1 JP 2012007113 W JP2012007113 W JP 2012007113W WO 2013073132 A1 WO2013073132 A1 WO 2013073132A1
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- Prior art keywords
- exhaust
- cylinder
- valve
- area
- downstream
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
- F01N13/08—Other arrangements or adaptations of exhaust conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
- F01N13/008—Mounting or arrangement of exhaust sensors in or on exhaust apparatus
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N13/00—Exhaust or silencing apparatus characterised by constructional features ; Exhaust or silencing apparatus, or parts thereof, having pertinent characteristics not provided for in, or of interest apart from, groups F01N1/00 - F01N5/00, F01N9/00, F01N11/00
- F01N13/08—Other arrangements or adaptations of exhaust conduits
- F01N13/10—Other arrangements or adaptations of exhaust conduits of exhaust manifolds
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
- F02D13/0261—Controlling the valve overlap
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D35/00—Controlling engines, dependent on conditions exterior or interior to engines, not otherwise provided for
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1438—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor
- F02D41/1439—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the position of the sensor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1438—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor
- F02D41/1444—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases
- F02D41/1454—Introducing closed-loop corrections using means for determining characteristics of the combustion gases; Sensors therefor characterised by the characteristics of the combustion gases the characteristics being an oxygen content or concentration or the air-fuel ratio
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2260/00—Exhaust treating devices having provisions not otherwise provided for
- F01N2260/16—Exhaust treating devices having provisions not otherwise provided for for reducing exhaust flow pulsations
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2470/00—Structure or shape of gas passages, pipes or tubes
- F01N2470/20—Dimensional characteristics of tubes, e.g. length, diameter
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N2470/00—Structure or shape of gas passages, pipes or tubes
- F01N2470/30—Tubes with restrictions, i.e. venturi or the like, e.g. for sucking air or measuring mass flow
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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
Definitions
- the present invention relates to an exhaust device for a multi-cylinder engine mounted on an automobile or the like.
- Patent Document 1 exhaust passages of cylinders whose exhaust order is not continuous are bundled and gathered as a tapered exhaust pipe, and the gathered throttle portion has an ejector effect, thereby preventing exhaust interference between cylinders. Techniques to do this are disclosed.
- an object of the present invention is to provide an exhaust device for a multi-cylinder engine that can suppress a decrease in ejector effect with a simple configuration.
- the present invention is an exhaust system for a multi-cylinder engine having a plurality of cylinders provided with an intake valve capable of opening and closing an intake port and an exhaust valve capable of opening and closing an exhaust port.
- a plurality of independent exhaust passages whose upstream ends are connected to the exhaust ports of cylinders or a plurality of cylinders whose exhaust order is not continuous, and a downstream side in the exhaust flow direction are gradually reduced in diameter, and exhaust gas that has passed through the independent exhaust passages flows in.
- a collecting section connected to the upstream end of the collecting section in a state in which the downstream ends of the independent exhaust passages are bundled, and an exhaust passage is partially formed in the collecting section or an exhaust passage downstream from the collecting section.
- An exhaust device for a multi-cylinder engine characterized in that an obstacle member that is closed up is provided.
- FIG. 1 is a schematic configuration diagram of an exhaust device for a multi-cylinder engine according to an embodiment of the present invention. It is a principal part enlarged view of FIG. It is a principal part side view of FIG. It is explanatory drawing in which the valve opening period of the exhaust valve of each cylinder of the said engine and the valve opening period of an intake valve overlap a predetermined overlap period. It is explanatory drawing of the valve opening period of the said intake valve and an exhaust valve.
- FIG. 6 is a sectional view taken along line VI-VI in FIG. 2.
- FIG. 7 is a sectional view taken along line VII-VII in FIG. 2.
- O 2 is a mixing tube and a longitudinal sectional view of the periphery thereof when provided in the straight portion of the mixing tube which is downstream of the exhaust passage from the collecting portion of the mixing tube sensors. It is explanatory drawing of the effect
- FIG. 6 is an explanatory diagram of an operation of the embodiment (reduction in vibration amplitude at a frequency of 1000 Hz to 2000 Hz).
- FIG. 6 is an explanatory diagram of the operation of the embodiment (decrease in the total value of the vibration amplitude when the engine speed is 1000 rpm to 6000 rpm).
- (A)-(d) is a figure for demonstrating the cause in which the self-excited oscillation of an exhaust jet arises in steps.
- FIG. 9 is a cross-sectional view taken along line XIII-XIII in FIG. 8 and illustrates a flow area at the downstream end of the independent exhaust passage and an area obtained by subtracting an area where an obstacle member blocks the exhaust flow path from the minimum flow area. is there.
- O 2 upstream pipe portion of the casing of the catalytic converter in the case of providing the upstream pipe portion of the casing of the catalytic converter which is the exhaust passage downstream of the collective portion of the mixing tube a sensor, a mixing tube and a longitudinal sectional view of the periphery thereof.
- FIG. 1 is a schematic configuration diagram of an exhaust device 100 for a multi-cylinder engine according to the present embodiment
- FIG. 2 is an enlarged view of a main part of FIG. 1
- FIG. 3 is a side view of the main part of FIG.
- An exhaust system 100 for a multi-cylinder engine is connected to an engine body 1 having a cylinder head 9 and a cylinder block (not shown), an engine control ECU (Engine Control Unit) 2, and the engine body 1. And an exhaust manifold 5 and a catalyst device 6 connected to the exhaust manifold 5.
- an engine body 1 having a cylinder head 9 and a cylinder block (not shown), an engine control ECU (Engine Control Unit) 2, and the engine body 1.
- an exhaust manifold 5 and a catalyst device 6 connected to the exhaust manifold 5.
- the engine body 1 is an inline 4-cylinder engine.
- a plurality (four in the illustrated example) of cylinders 12 each having a piston fitted therein are formed in series in the engine body 1.
- a first cylinder 12a, a second cylinder 12b, a third cylinder 12c, and a fourth cylinder 12d are formed in order from the right with respect to FIGS.
- the cylinder head 9 is provided with a spark plug 15 for each cylinder 12 so as to face a combustion chamber defined above the piston.
- Each cylinder 12 is provided with a fuel injection valve (not shown) that directly injects fuel into the combustion chamber.
- Engine body 1 is a 4-cycle engine. As shown in FIG. 4, in each cylinder 12a to 12d, ignition by the spark plug 15 is performed at a timing shifted by 180 ° CA (crank angle). As a result, the intake stroke, the compression stroke, the expansion stroke, and the exhaust stroke are performed. Each stroke is performed at a timing shifted by 180 ° CA. In the present embodiment, ignition is performed in the order of the first cylinder 12a ⁇ the third cylinder 12c ⁇ the fourth cylinder 12d ⁇ the second cylinder 12b, and each stroke is performed in this order.
- the cylinder head 9 is provided with two intake ports 17 and two exhaust ports 18 that open toward the combustion chamber for each cylinder 12.
- the intake port 17 is for introducing intake air into each cylinder 12.
- the exhaust port 18 is for exhausting exhaust from each cylinder 12.
- Each intake port 17 is provided with an intake valve 19 for opening and closing the intake port 17 to communicate or block the intake port 17 and the inside of the cylinder 12.
- Each exhaust port 18 is provided with an exhaust valve 20 for opening and closing the exhaust port 18 to communicate or block the exhaust port 18 and the inside of the cylinder 12.
- the intake valve 19 opens and closes the intake port 17 at a predetermined timing by being driven by an intake valve drive mechanism 30 serving as valve drive means.
- the exhaust valve 20 opens and closes the exhaust port 18 at a predetermined timing by being driven by an exhaust valve drive mechanism 40 that is a valve drive means.
- the intake valve drive mechanism 30 has an intake camshaft 31 and an intake VVT 32 connected to the intake valve 19.
- the intake camshaft 31 is connected to a crankshaft (not shown) via a known power transmission mechanism such as a chain and sprocket mechanism, and rotates with the rotation of the crankshaft to open and close the intake valve 19.
- the intake VVT 32 is for changing the valve timing of the intake valve 19.
- the intake VVT 32 has a predetermined driven shaft that is arranged coaxially with the intake camshaft 31 and is directly driven by the crankshaft, and changes the phase difference between the driven shaft and the intake camshaft 31. As a result, the phase difference between the crankshaft and the intake camshaft 31 is changed, and the valve timing of the intake valve 19 is changed.
- the configuration of the intake VVT 32 include a hydraulic mechanism and an electromagnetic mechanism.
- the hydraulic mechanism has a plurality of liquid chambers arranged in the circumferential direction between the driven shaft and the intake camshaft 31, and the driven shaft and the intake cam are adjusted by adjusting a pressure difference between the liquid chambers.
- the phase difference between the shaft 31 and the shaft 31 is changed.
- an electromagnet is disposed between the driven shaft and the intake camshaft 31, and a phase difference between the driven shaft and the intake camshaft 31 is adjusted by adjusting electric power applied to the electromagnet. Is to change.
- the intake VVT 32 changes the phase difference based on the target valve timing of the intake valve 19 calculated by the ECU 2.
- the intake camshaft 31 rotates with the rotation of the crankshaft under the phase difference, and opens and closes the intake valve 19 at the target valve timing.
- the downstream end of the intake passage 3 is connected to the intake port 17 of each cylinder 12.
- the upstream end of each intake passage 3 is connected to a surge tank 3a.
- the exhaust valve drive mechanism 40 has the same structure as the intake valve drive mechanism 30. That is, the exhaust valve drive mechanism 40 changes the phase difference between the exhaust camshaft 41 and the crankshaft by changing the phase difference between the exhaust camshaft 41 and the crankshaft. And an exhaust VVT 42 for changing.
- the exhaust VVT 42 changes the phase difference based on the target valve timing of the exhaust valve 20 calculated by the ECU 2.
- the exhaust camshaft 41 rotates with the rotation of the crankshaft under the phase difference, and opens and closes the exhaust valve 20 at the target valve timing.
- the intake VVT 32 and the exhaust VVT 42 are arranged such that the intake valve 19 and the exhaust valve 20 are opened and closed while the valve opening period and the lift amount, ie, the valve profile, of the intake valve 19 and the exhaust valve 20 are kept constant. Change the valve timing.
- the opening timing and closing timing of the intake valve 19 and the exhaust valve 20 are portions where the gradient of the valve lift is gentle near the opening and closing of the valve, respectively, as shown in FIG.
- the timing when the valve lift increases or decreases to 0.4 mm becomes the valve opening timing and the valve closing timing, respectively.
- the exhaust manifold 5 is connected to the three independent exhaust passages 52 and the downstream ends of the independent exhaust passages 52 in order from the upstream side, and the mixture into which exhaust gas that has passed through the independent exhaust passages 52 flows.
- the mixing pipe 50 has, on its axis, in order from the upstream side, the collecting portion 56 whose flow area decreases toward the downstream side, and the flow area of the downstream end of the collecting portion 56 (the minimum flow path of the mixing pipe 50). (Straight area) and a diffuser portion 58 having a flow passage area that increases toward the downstream side.
- each independent exhaust passage 52 is connected to the exhaust port 18 of each cylinder 12. Specifically, of the four cylinders 12, the upstream end of one independent exhaust passage (first independent exhaust passage) 52 a is connected to the exhaust port 18 of the first cylinder 12 a, and another exhaust port 18 of the fourth cylinder 12 d is connected to another exhaust port 18. The upstream end of one independent exhaust passage (third independent exhaust passage) 52d is connected. On the other hand, with respect to the second cylinder 12b and the third cylinder 12c in which the exhaust strokes are not adjacent to each other and the exhaust order is not continuous, from the viewpoint of simplifying the structure, one common independent exhaust passage (second independent exhaust passage) 52b is provided. The upstream end is connected to the exhaust port 18.
- the second independent exhaust passage 52b whose upstream end is connected to the exhaust port 18 of the second cylinder 12b and the exhaust port 18 of the third cylinder 12c is branched into two passages on the upstream side.
- the upstream end of the one passage is connected to the exhaust port 18 of the second cylinder 12b, and the upstream end of the other passage is connected to the exhaust port 18 of the third cylinder 12c.
- the second independent exhaust passage 52b corresponding to the second cylinder 12b and the third cylinder 12c is between the second cylinder 12b and the third cylinder 12c, that is, the central portion of the engine body 1 in the cylinder row direction. Is extended toward the collecting portion 56 of the mixing tube 50.
- the first independent exhaust passage 52a corresponding to the first cylinder 12a and the third independent exhaust passage 52d corresponding to the fourth cylinder 12d are curved from positions facing the first cylinder 12a and the fourth cylinder 12d, respectively. , Extending toward the collecting portion 56 of the mixing tube 50.
- the first, second, and third independent exhaust passages 52a, 52b, and 52d are independent of each other. Therefore, the exhaust discharged from the first cylinder 12a, the exhaust discharged from the second cylinder 12b or the third cylinder 12c, and the exhaust discharged from the fourth cylinder 12d are independent of each other, and each independent exhaust passage 52a. , 52b, 52d and discharged downstream. Exhaust gas that has passed through the independent exhaust passages 52 a, 52 b, 52 d flows into the collecting portion 56 of the mixing pipe 50.
- Each independent exhaust passage 52 and the collecting portion 56 have the following shapes. That is, as the exhaust gas is ejected from each independent exhaust passage 52 at a high speed and flows into the collecting portion 56 at a high speed, a negative pressure is generated around the high-speed exhaust gas, and the generated negative pressure in the mixing pipe 50 is reduced. It acts on the other adjacent independent exhaust passage 52 and the exhaust port 18 communicating with this other independent exhaust passage 52, and the exhaust pressure in the exhaust port 18 is sucked out downstream by the action of this negative pressure (ie, ejector effect). Is obtained).
- the collecting portion 56 flows toward the downstream side so that the exhaust discharged from each independent exhaust passage 52 flows downstream while maintaining a high speed and the backward flow from the downstream side is prevented.
- the road area is reduced.
- the flow area at the downstream end of the collecting portion 56 is smaller than the total flow area at the downstream end of each independent exhaust passage 52 so that the exhaust speed is maintained at a higher level. Is set.
- the collecting portion 56 has an inverted truncated cone shape (funnel shape) whose diameter decreases toward the downstream side.
- the gathering portion 56 and the straight portion 57 of the mixing tube 50 have a downstream channel area smaller than the upstream channel area. Therefore, the exhaust gas passes through the collecting portion 56 and the straight portion 57 at a high speed. During this passage, the exhaust pressure and temperature decrease. Therefore, in the gathering portion 56 and the straight portion 57, the amount of heat released to the outside of the exhaust gas can be kept small.
- the exhaust gas that has passed through the straight portion 57 flows into the diffuser portion 58 whose flow path area increases toward the downstream side. Thereby, the pressure and temperature of the exhaust gas are recovered, and the exhaust gas that has passed through the diffuser portion 58 while maintaining a high temperature is discharged to the downstream catalytic device 6.
- each independent exhaust passage 52 has a shape in which the flow passage area becomes smaller toward the downstream side so that the exhaust is ejected from each independent exhaust passage 52 to the collecting portion 56 at a high speed.
- the upstream side portions (indicated by phantom lines) of the independent exhaust passages 52a, 52b, 52d have a substantially elliptical cross-sectional shape, and the downstream ends (indicated by solid lines) are It has a fan-shaped cross-sectional shape.
- the cross-sectional area that is, the flow passage area is reduced from the upstream portion toward the downstream side, and the flow passage area at the downstream end of each independent exhaust passage 52a, 52b, 52d is approximately 1 / of the flow passage area of the upstream portion.
- the independent exhaust passages 52 a, 52 b, 52 d are aggregated so that the downstream ends forming a fan shape are adjacent to each other and form a substantially circular cross section as a whole, and are connected to the upstream end of the aggregation portion 56.
- FIGS. 1 and 2 See FIGS. 1 and 2. That is, the cross-sectional shapes of the downstream ends of the independent exhaust passages 52 in the direction orthogonal to the axis of the mixing pipe 50 are formed in the same sector shape (see FIGS. 6 and 7), and the sectors are gathered to form a substantially circle.
- the downstream end of each independent exhaust passage 52 is connected to the upstream end of the collecting portion 56 of the mixing pipe 50 in a state where the downstream ends of the independent exhaust passages 52 are bundled.
- the opening period of the exhaust valve 20 and the opening period of the intake valve 19 of each cylinder 12 sandwich the intake top dead center (TDC).
- TDC intake top dead center
- the exhaust valve 20 of the third cylinder 12c is opened during the overlap period T_O / L between the exhaust valve 20 of the first cylinder 12a and the intake valve 19, and the third cylinder 12c.
- the exhaust valve 20 of the fourth cylinder 12d opens during the overlap period T_O / L between the exhaust valve 20 and the intake valve 19 and the overlap period T_O / between the exhaust valve 20 and the intake valve 19 of the fourth cylinder 12d.
- the exhaust valve 20 of the second cylinder 12b opens, and during the overlap period T_O / L between the exhaust valve 20 of the second cylinder 12b and the intake valve 19, the exhaust valve 20 of the first cylinder 12a opens. Is set to
- the intake valve drive mechanism 30 and the exhaust valve drive mechanism 40 receive a control signal from the ECU 2 and at least in the low speed and high load region, the valve opening period of the exhaust valve 20 and the valve opening period of the intake valve 19 in each cylinder 12.
- the exhaust valve 20 of the succeeding cylinder 12 is opened during the overlap period T_O / L of the preceding cylinder 12 between the cylinders 12 and 12 in which the exhaust order is continuous.
- the intake valve 19 and the exhaust valve 20 of each cylinder 12 are driven.
- the exhaust valve 20 of the cylinder 12 in the exhaust stroke is opened, and as the blowdown gas is ejected from the cylinder 12 in the exhaust stroke through the independent exhaust passage 52 to the collecting portion 56 at high speed, the ejector effect
- a negative pressure is generated in the exhaust port 18 of the cylinder 12 in the intake stroke during the overlap period T_O / L. Therefore, the ejector effect extends not only from the exhaust port 18 of the cylinder 12 in the intake stroke during the overlap period T_O / L but also from the cylinder 12 to the intake port 17 and from the cylinder in the intake stroke during the overlap period T_O / L. Twelve scavenging is further promoted.
- the catalyst device 6 is a device for purifying the exhaust discharged from the engine body 1.
- the catalyst device 6 includes a catalyst body 64 and a casing 62 that houses the catalyst body 64.
- the casing 62 has a substantially cylindrical shape extending in parallel with the exhaust circulation direction.
- the catalyst main body 64 is for purifying harmful components in the exhaust gas.
- the catalyst main body 64 contains a three-way catalyst and exhibits a three-way catalyst function in a stoichiometric air-fuel ratio atmosphere.
- the catalyst body 64 is accommodated in the diameter-enlarged portion in the center of the casing 62 in the exhaust flow direction.
- a predetermined space (upstream pipe portion of the casing 62) is formed at the upstream end of the casing 62.
- the downstream end of the diffuser portion 58 of the mixing pipe 50 is connected to the upstream pipe portion of the casing 62.
- the exhaust discharged from the diffuser portion 58 flows into the upstream pipe portion and then proceeds to the catalyst body 64 side.
- the entire exhaust system passage including the independent exhaust passage 52, the mixing pipe 50, the casing 62 of the catalyst device 6 and the like through which exhaust exhausted from the cylinder 12 flows is defined as an exhaust passage. 4 is shown.
- an O 2 sensor 59 is disposed in the exhaust passage 4 downstream of the collecting portion 56 of the mixing pipe 50. More specifically, the O 2 sensor 59 is disposed at the upstream end portion of the straight portion 57 downstream of the collecting portion 56 (see also FIGS. 2 and 3). That is, the O 2 sensor 59 is disposed at a position where the flow channel area of the mixing tube 50 is the smallest.
- the O 2 sensor 59 has a rod-shaped sensor portion that protrudes from the tube wall of the mixing tube 50 into the internal space, that is, the exhaust passage.
- the O 2 sensor 59 functions as an obstacle member that partially blocks the exhaust flow path of the mixing pipe 50, more specifically, the exhaust flow path of the straight portion 57 (see also FIGS. 6 and 7).
- the O 2 sensor 59 will be referred to as an obstacle member 59 and described.
- the reason why the obstacle member 59 that partially blocks the exhaust passage is disposed in the exhaust passage 4 downstream from the gathering portion 56 of the mixing pipe 50 is as follows.
- FIG. 9 shows an independent exhaust passage 52a (fourth) of the first cylinder 12a among the three independent exhaust passages 52a, 52b, 52d of the exhaust manifold 5 according to the crank angle (CA) in the engine according to the present embodiment. It is explanatory drawing (engine speed is 2500 rpm) which shows how the internal pressure of the independent exhaust passage 52d of the cylinder 12d changes similarly).
- the high pressure near 360 ° CA is a positive pressure generated in the independent exhaust passage 52a by blowdown gas from the own cylinder (first cylinder 12a).
- the negative pressure near 540 ° CA is the negative pressure generated in the independent exhaust passage 52a by the ejector effect based on the blowdown gas flowing out from the third cylinder 12c to the collecting portion 56
- the negative pressure near 0 ° CA is The negative pressure generated in the independent exhaust passage 52a by the ejector effect based on the blowdown gas flowing out from the four cylinders 12d to the collecting portion 56, that is, the negative pressure near 180 ° CA, flows out from the second cylinder 12b to the collecting portion 56. This is a negative pressure generated in the independent exhaust passage 52a by the ejector effect based on the gas.
- FIG. 10 is a frequency analysis of the vibration at the time of negative pressure generation shown in FIG. 9 (engine speed is 2500 rpm). As shown in the figure, the vibration amplitude is the largest in the range of 1000 Hz to 2000 Hz among the frequencies of 500 Hz to 8000 Hz (broken line).
- FIG. 11 shows a total value (overall) of vibration amplitudes in the range of the engine speed of 1000 rpm to 6000 rpm and the frequency of 1000 Hz to 2000 Hz.
- the obstruction member that partially blocks the exhaust passage is not provided in the exhaust passage 4 downstream from the gathering portion 56 of the mixing pipe 50 (broken line), compared to the case (solid line) provided.
- the total value of the amplitudes of vibrations in the engine speed range of 1000 rpm to 6000 rpm and the frequency range of 1000 Hz to 2000 Hz is large.
- FIG. 7 shows a part of FIG. 7 extracted and redrawn.
- reference numeral 256 denotes a converging part of the mixing pipe (corresponding to the collecting part 56 of the mixing pipe 50 of the present embodiment)
- reference numeral 252b denotes a nozzle from which compressed air from the compressor is ejected (independent exhaust passage of other cylinders of the present embodiment).
- reference numerals 252a and 252d are passages (corresponding to the independent exhaust passages 52a and 52d of the self-cylinder of this embodiment) which are adjacent to the nozzle 252b and communicate with a collecting cylinder (chamber) (not shown).
- the jet E When the dry air is ejected from the nozzle 252b to the converging portion 256 of the mixing tube at a super-high speed of Mach 3.05, the jet E is ejected on either side in the mixing tube due to negative pressure imbalance in the mixing tube. And is in contact with the inner wall surface of the mixing tube (the state shown in FIG. 12A). Then, the speed of the jet E decreases on the contact side, and the negative pressure becomes weak, whereby the jet E moves to another location on the inner wall surface of the mixing tube (see FIG. 12 (b) through the state of FIG. 12 (b). c)). This time, the speed of the jet E decreases on the other side in contact with it, and the negative pressure becomes weaker.
- the jet E moves to another location on the inner wall surface of the mixing tube (the state shown in FIG. 12 (d)). After that, the state of FIG.
- the jet E of compressed air ejected from the nozzle 252b causes self-excited vibration.
- This self-excited vibration is considered to appear as pressure vibration when negative pressure is generated (when compressed air is ejected) in the passages 252a and 252d adjacent to the nozzle 252b.
- the obstacle member 59 that partially blocks the exhaust passage is disposed in the exhaust passage 4 downstream from the gathering portion 56 of the mixing pipe 50.
- the obstruction member 59 prevents the self-excited vibration by preventing the exhaust jet jetted at a high speed from each independent exhaust passage 52 to the gathering portion 56 of the mixing pipe 50 from moving to another location on the inner wall surface of the mixing pipe 50. It is thought that it has the effect
- the exhaust jet moves to another location on the inner wall surface of the mixing tube 50, the exhaust jet flows along the inner wall surface of the mixing tube 50, that is, while in contact with the inner wall surface of the mixing tube 50. It is thought that it moves to the place of.
- FIGS. 9 to 11 also show the operation in the case where the obstacle member 59 that partially blocks the exhaust flow path is disposed in the exhaust passage 4 downstream from the gathering portion 56 of the mixing pipe 50 (solid line).
- the self-excited vibration is suppressed.
- the vibration amplitude is reduced in the frequency range of 1000 Hz to 2000 Hz.
- the total value of the amplitudes of vibrations in the range of the engine speed from 1000 rpm to 6000 rpm and the frequency from 1000 Hz to 2000 Hz is relatively reduced.
- the obstacle member 59 is disposed in the exhaust passage 4 downstream from the collecting portion 56
- the obstacle member 59 is disposed in the diffuser portion 58 of the mixing pipe 50 as indicated by a virtual line in FIG. May be.
- it may be disposed in the upstream pipe portion of the casing 62 of the catalyst device 6 downstream of the mixing pipe 50.
- the obstacle member 59 may be arranged in the collecting portion 56.
- FIG. 13 is a cross-sectional view taken along line XIII-XIII in FIG.
- reference numeral S ⁇ b> 1 indicates a flow path area at the downstream end of the independent exhaust passage 52 indicated by a virtual line.
- the hatched portion indicates an area (effective flow area) obtained by subtracting the area where the obstacle member 59 blocks the exhaust flow path from the minimum flow path area of the mixing pipe 50.
- the minimum channel area is the channel area at the downstream end of the collecting portion 56 of the mixing tube 50 or the channel area of the straight portion 57 of the mixing tube 50.
- the obstacle member 59 is disposed on the straight portion 57 (that is, disposed at the position where the flow path area is minimum).
- the area obtained by subtracting the area where the obstruction member 59 blocks the exhaust flow path (the area of the white area) from the area of the circle 57) is hatched.
- the diameter of a perfect circle having the same area as the flow path area S1 at the downstream end of the independent exhaust passage 52 is a, and the area where the obstruction member 59 blocks the exhaust flow path from the flow area of the straight portion 57.
- a / D is 0.5 to 0.85, where D is the diameter of a perfect circle having the same area as the effective channel area (hatched portion in FIG. 13).
- the present embodiment has a plurality of cylinders 12a, 12b, 12c, and 12d provided with an intake valve 19 that can open and close the intake port 17 and an exhaust valve 20 that can open and close the exhaust port 18.
- An exhaust device 100 for a multi-cylinder engine is provided.
- the exhaust device 100 includes a plurality of independent exhaust passages 52a, 52b, 52d whose upstream ends are connected to the exhaust ports 18 of one cylinder 12a or 12d or a plurality of cylinders 12b, 12c whose exhaust order is not continuous, and each independent exhaust passage.
- a mixing pipe 50 into which exhaust gas that has passed through 52a, 52b, and 52d flows.
- the downstream ends of the independent exhaust passages 52a, 52b, and 52d are connected to the upstream end of the mixing pipe 50 in a bundled state.
- the mixing pipe 50 includes a collecting portion 56 whose diameter is gradually reduced on the downstream side in the exhaust flow direction.
- An obstruction member 59 that partially closes the exhaust passage is provided in the gathering portion 56 or the exhaust passage 4 downstream from the gathering portion 56.
- the exhaust gas that has passed through each independent exhaust passage 52 flows into the mixing pipe 50, thereby generating a negative pressure in the mixing pipe 50.
- An ejector effect is obtained in which the exhaust in the exhaust port 18 of the other cylinder 12 that communicates is sucked downstream.
- the mixing pipe 50 includes a collecting portion 56 whose diameter gradually decreases on the downstream side in the exhaust flow direction, in other words, a collecting portion 56 whose flow path area decreases toward the downstream side.
- An obstruction member 59 that partially blocks the exhaust flow path in the collecting portion 56 or in the exhaust passage 4 downstream of the collecting portion 56 (which may be the exhaust passage 4 included in the mixing pipe 50 or not). Is provided.
- the obstacle member 59 prevents the exhaust jet ejected from the downstream end of each independent exhaust passage 52 from moving to another location on the inner wall surface of the mixing pipe 50, thereby suppressing the self-excited oscillation of the exhaust jet. Is done.
- the opening period of the exhaust valve 20 and the opening period of the intake valve 19 of each cylinder 12 overlap each other by a predetermined overlap period T_O / L and the exhaust order is continuous.
- Intake air that drives the intake valve 19 and the exhaust valve 20 of each cylinder 12 so that the exhaust valve 20 of the subsequent cylinder 12 opens during the overlap period T_O / L of the preceding cylinder 12 between the cylinders 12 and 12 A valve drive mechanism 30 and an exhaust valve drive mechanism 40 are provided.
- an overlap period T_O / L is provided in which the exhaust valve 20 and the intake valve 19 of each cylinder 12 are both open, and between the cylinders 12 and 12 in which the exhaust order is continuous. Since the exhaust valve 20 of the subsequent cylinder 12 opens during the overlap period T_O / L of the preceding cylinder 12, the ejector effect extends to the intake port 17 of the preceding cylinder 12 during the overlap period T_O / L. As a result, scavenging of the preceding cylinder 12 is further promoted, and the volumetric efficiency ( ⁇ V) is further improved, and further, the torque is further improved.
- the O 2 sensor is also used as the obstruction member 59, it is not necessary to prepare a dedicated member as the obstruction member 59. By using the O 2 sensor as the obstruction member 59, the number of parts can be reduced. Figured. Further, since the O 2 sensor is provided at the position where the flow path area is the minimum (straight portion 57), the oxygen concentration of the exhaust discharged from all the cylinders 12 can be detected evenly. Therefore, the operating state of the engine can be detected with high accuracy, and for example, control for each cylinder 12 during execution of AWS can be performed with high accuracy.
- the obstruction member 59 is provided at a position where the flow passage area is the smallest (straight portion 57), and the diameter of a perfect circle having the same area as the flow passage area S1 at the downstream end of each independent exhaust passage 52 is a.
- a / D is 0.5 to 0.85.
- the effective flow path area is too large, which means that the area where the obstruction member 59 blocks the exhaust flow path is too small. As a result, the exhaust jet flow The self-excited vibration suppression effect may be insufficient.
- the a / D exceeds 0.85, the effective flow path area is too small, which means that the area where the obstruction member 59 blocks the exhaust flow path is too large.
- the flow of the exhaust jet ejected from the downstream end of the independent exhaust passage 52 becomes stagnant, the negative pressure in the mixing pipe 50 becomes weak, and the ejector effect may be insufficient.
- the a / D to 0.5 to 0.85, the ejector effect and the suppression effect of the self-excited vibration of the exhaust jet flow are balanced.
- the present embodiment is an exhaust device of a multi-cylinder engine having a plurality of cylinders provided with an intake valve capable of opening and closing an intake port and an exhaust valve capable of opening and closing an exhaust port, and one cylinder or the exhaust order is not continuous
- a plurality of independent exhaust passages whose upstream ends are connected to the exhaust ports of a plurality of cylinders, and a collecting portion into which exhaust gas flowing through the independent exhaust passages flows into the downstream side in the exhaust flow direction, and the exhaust gas passes through the independent exhaust passages.
- An obstruction member for partially blocking the exhaust flow path is provided in the exhaust passage downstream of the collective portion or the collective portion connected to the upstream end of the collective portion in a state where the downstream ends of the independent exhaust passages are bundled.
- each independent exhaust passage flows into the collecting portion, thereby generating a negative pressure in the collecting portion. Due to this negative pressure, other independent exhaust passages or other cylinders that communicate with the other exhaust passages are generated. An ejector effect is obtained in which the exhaust gas in the exhaust port is sucked out downstream.
- the collecting portion has a shape in which the downstream side in the exhaust flow direction is gradually reduced in diameter, in other words, a shape in which the flow path area becomes smaller on the downstream side, and the collecting portion is downstream of the collecting portion.
- this exhaust passage for example, an exhaust passage included in the mixing pipe including the collecting portion or an exhaust passage that is not included
- an obstruction member that partially blocks the exhaust passage.
- the speed of the exhaust jet decreases on the contact side, and the negative pressure becomes weak, whereby the exhaust jet moves to another place on the inner wall surface of the mixing tube, and is caused by the repetition of the operation.
- the said obstruction member is considered to have the effect
- the exhaust jet undergoes self-excited vibration
- the negative pressure in the collecting portion (in the mixing tube) becomes weak, and the ejector effect decreases. Therefore, by suppressing the self-excited vibration of the exhaust jet, it is possible to suppress a decrease in the ejector effect with a simple configuration.
- NV noise (noise) and vibration (vibration)) in NVH is improved by suppressing self-excited vibration.
- valve drive means for driving the intake valve and the exhaust valve of each cylinder is provided so that the exhaust valve of the subsequent cylinder opens during the overlap period of the cylinder.
- an overlap period in which the exhaust valve and the intake valve of each cylinder are both open is provided, and the overlap of the preceding cylinder is made between the cylinders in which the exhaust order is continuous. Since the exhaust valve of the succeeding cylinder opens during the period, the ejector effect extends to the intake port of the preceding cylinder during the overlap period, thereby further promoting scavenging of the preceding cylinder and volume efficiency ( ⁇ V ), And in turn, torque can be further improved.
- This embodiment discloses that the obstruction member is provided in an exhaust passage immediately downstream of the gathering portion.
- the obstacle member is provided at a position where the flow path area is minimum. As the flow path area is smaller, the speed of the exhaust jet increases, the negative pressure becomes stronger, and the self-excited vibration of the exhaust jet tends to occur. Therefore, according to this configuration, the self-excited vibration of the exhaust jet is effectively suppressed by the obstacle member.
- the present embodiment discloses that the obstacle member is an O 2 sensor.
- the O 2 sensor is provided at a position where the flow path area is the minimum (for example, when provided immediately downstream of the gathering portion of the mixing pipe), the oxygen concentration of the exhaust discharged from all the cylinders is equalized. It can be detected. Therefore, the operating state of the engine can be detected with high accuracy, and for example, control for each cylinder at the time of execution of AWS (Accelerated Warm Up System) can be performed with high accuracy.
- AWS Accelerated Warm Up System
- the obstruction member is provided at a position where the flow passage area of the exhaust passage is the smallest, and the diameter of a perfect circle having the same area as the flow passage area at the downstream end of each independent exhaust passage is a, It is disclosed that a / D is 0.5 to 0.85, where D is the diameter of a perfect circle having the same area as the area obtained by subtracting the area where the obstacle member blocks the exhaust flow path from the road area. .
- the ejector effect and the suppression effect of the self-excited vibration of the exhaust jet are balanced. If the a / D is less than 0.5, the area obtained by subtracting the area where the obstruction member blocks the exhaust passage from the minimum passage area is too large. This means that the area blocking the road is too small, and as a result, the effect of suppressing the self-excited vibration of the exhaust jet can be insufficient. When the a / D exceeds 0.85, an area obtained by subtracting an area where the obstacle member blocks the exhaust passage from the minimum passage area is too small. As a result, the flow of the exhaust jet ejected from the downstream end of each independent exhaust passage is stagnated, the negative pressure in the gathering section (in the mixing tube) becomes weak, and the ejector effect is insufficient. obtain.
- the mixing tube 50 may include only the collecting portion 56 (the straight portion 57 and the diffuser portion 58 are not provided) in which the flow passage area is reduced. A thing including only the diffuser part 58 to expand (those without the straight part 57) may be used. The ejector effect can be obtained even when the mixing tube having such a configuration is used. For example, when the mixing tube 50 is shortened due to layout restrictions during mass production design, the mixing tube including only the collecting portion 56 or the straight portion is omitted and the collecting portion 56 and the diffuser portion 58 are directly and smoothly curved. It does not matter as a mixing tube or the like having a shape to be connected.
- the obstacle member (O 2 sensor in the illustrated example) 59 is located immediately downstream of the mixing tube 50, that is, immediately downstream of the collecting portion 56. It is preferable to arrange in the exhaust passage 4.
- the obstacle member 59 is disposed in the upstream pipe portion of the casing 62 of the catalyst device 6 downstream of the mixing pipe 50.
- the length of the mixing pipe 50 in the exhaust circulation direction can be reduced, and the length of the entire exhaust system in the exhaust circulation direction can be reduced.
- the obstruction member 59 is disposed at a position where the flow path area is minimum (immediately downstream of the gathering portion 56). As the flow path area is smaller, the speed of the exhaust jet increases, the negative pressure becomes stronger, and the self-excited vibration of the exhaust jet tends to occur. Therefore, according to this configuration, the obstacle member 59 effectively suppresses the self-excited vibration of the exhaust jet.
- the shape, number, arrangement mode, and the like of the obstacle member 59 are not particularly limited as long as they partially block the exhaust flow path, and may be appropriately determined according to the situation.
- Examples of shapes that can be adopted include rod shapes, plate shapes, and mesh shapes.
- a plurality may be arranged in the exhaust circulation direction, or a plurality may be arranged so as to surround the exhaust passage.
- the present invention has wide industrial applicability in the technical field of exhaust systems for multi-cylinder engines mounted on automobiles and the like.
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Abstract
Description
図1は本実施形態に係る多気筒エンジンの排気装置100の概略構成図、図2は図1の要部拡大図、図3は図2の要部側面図である。
排気マニホールド5は、上流側から順に、3つの独立排気通路52と、各独立排気通路52の下流端に接続されて各独立排気通路52を通過した排気が流入する混合管50とを有する。前記混合管50は、その軸芯上に、上流側から順に、下流側ほど流路面積が小さくなる集合部56と、前記集合部56の下流端の流路面積(混合管50の最小流路面積)を維持して下流側に延びるストレート部57と、下流側ほど流路面積が大きくなるディフューザー部58とを備えている。
図8に示すように、混合管50の集合部56より下流の排気通路4に、O2センサ59が配設されている。より具体的に、このO2センサ59は、集合部56より下流のストレート部57の上流端部に配設されている(図2、図3も参照)。すなわち、このO2センサ59は、混合管50の流路面積が最小の位置に配設されている。そして、このO2センサ59は、混合管50の管壁から内部空間、すなわち排気流路に突出する棒状のセンサ部を有している。これにより、O2センサ59は、混合管50の排気流路、より詳しくはストレート部57の排気流路を部分的に塞ぐ障害部材として機能する(図6、図7も参照)。以下、O2センサ59のことを障害部材59と称して説明する。
本実施形態では、吸気ポート17を開閉可能な吸気弁19及び排気ポート18を開閉可能な排気弁20が備えられた複数の気筒12a,12b,12c,12dを有する多気筒エンジンの排気装置100が提供される。排気装置100は、1つの気筒12a若しくは12d又は排気順序が連続しない複数の気筒12b,12cの排気ポート18に上流端が接続された複数の独立排気通路52a,52b,52dと、各独立排気通路52a,52b,52dを通過した排気が流入する混合管50とを有している。各独立排気通路52a,52b,52dの下流端は束ねられた状態で混合管50の上流端に接続されている。混合管50は、排気流通方向の下流側が次第に縮径する集合部56を含んでいる。集合部56又は集合部56より下流の排気通路4に、排気流路を部分的に塞ぐ障害部材59が設けられている。
混合管50は、流路面積が縮小する集合部56のみを含むもの(ストレート部57及びディフューザー部58がないもの)でもよく、集合部56と流路面積が拡大するディフューザー部58とだけを含むもの(ストレート部57がないもの)でもよい。このような構成の混合管を用いてもエゼクタ効果は得られる。例えば、量産設計時にレイアウト上の制約等から混合管50を短くする場合に、集合部56のみを含む混合管や、ストレート部を省略して集合部56とディフューザー部58とを直接滑らかに曲面でつなぐような形状の混合管等としても構わない。
Claims (5)
- 吸気ポートを開閉可能な吸気弁及び排気ポートを開閉可能な排気弁が備えられた複数の気筒を有する多気筒エンジンの排気装置であって、
1つの気筒又は排気順序が連続しない複数の気筒の排気ポートに上流端が接続された複数の独立排気通路と、排気流通方向の下流側が次第に縮径し、前記各独立排気通路を通過した排気が流入する集合部とを有し、
前記各独立排気通路の下流端が束ねられた状態で前記集合部の上流端に接続され、
前記集合部又は前記集合部より下流の排気通路に、排気流路を部分的に塞ぐ障害部材が設けられていることを特徴とする多気筒エンジンの排気装置。 - 請求項1に記載の多気筒エンジンの排気装置において、
少なくとも低速高負荷域において、前記各気筒の排気弁の開弁期間と吸気弁の開弁期間とが所定のオーバーラップ期間オーバーラップすると共に、排気順序が連続する気筒間において先行の気筒の前記オーバーラップ期間中に後続の気筒の排気弁が開弁するように、各気筒の吸気弁及び排気弁を駆動する弁駆動手段が設けられていることを特徴とする多気筒エンジンの排気装置。 - 請求項1又は2に記載の多気筒エンジンの排気装置において、
前記障害部材は、前記集合部の直下流の排気通路に設けられていることを特徴とする多気筒エンジンの排気装置。 - 請求項1から3のいずれか1項に記載の多気筒エンジンの排気装置において、
前記障害部材は、O2センサであることを特徴とする多気筒エンジンの排気装置。 - 請求項1から4のいずれか1項に記載の多気筒エンジンの排気装置において、
前記集合部を備える混合管を設け、
前記障害部材を前記混合管の流路面積が最小の位置に設け、
各独立排気通路の下流端の流路面積と同じ面積を有する真円の直径をaとし、前記最小の流路面積から前記障害部材が排気流路を塞ぐ面積を減算した面積と同じ面積を有する真円の直径をDとしたときに、a/Dが0.5~0.85であることを特徴とする多気筒エンジンの排気装置。
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US14/345,926 US9140173B2 (en) | 2011-11-14 | 2012-11-06 | Exhaust apparatus for multi-cylinder engine |
CN201280053082.5A CN103906907B (zh) | 2011-11-14 | 2012-11-06 | 多气缸发动机的排气装置 |
DE201211004737 DE112012004737T5 (de) | 2011-11-14 | 2012-11-06 | Abgasvorrichtung für Mehrzylindermotor |
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JP2011248723A JP5915104B2 (ja) | 2011-11-14 | 2011-11-14 | 多気筒エンジンの排気装置 |
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JP6102874B2 (ja) * | 2014-09-26 | 2017-03-29 | マツダ株式会社 | 多気筒エンジンの排気装置 |
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JP2009197758A (ja) * | 2008-02-25 | 2009-09-03 | Mazda Motor Corp | 過給機付エンジンシステム |
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CN103906907B (zh) | 2016-11-16 |
JP5915104B2 (ja) | 2016-05-11 |
US9140173B2 (en) | 2015-09-22 |
JP2013104355A (ja) | 2013-05-30 |
DE112012004737T5 (de) | 2014-07-31 |
CN103906907A (zh) | 2014-07-02 |
US20140237991A1 (en) | 2014-08-28 |
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