WO2016121482A1 - Structure d'orifice d'admission pour moteur - Google Patents

Structure d'orifice d'admission pour moteur Download PDF

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Publication number
WO2016121482A1
WO2016121482A1 PCT/JP2016/050651 JP2016050651W WO2016121482A1 WO 2016121482 A1 WO2016121482 A1 WO 2016121482A1 JP 2016050651 W JP2016050651 W JP 2016050651W WO 2016121482 A1 WO2016121482 A1 WO 2016121482A1
Authority
WO
WIPO (PCT)
Prior art keywords
seat ring
intake port
end side
engine
rear end
Prior art date
Application number
PCT/JP2016/050651
Other languages
English (en)
Japanese (ja)
Inventor
遼 森岡
智 吉川
義幸 干場
Original Assignee
三菱自動車工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱自動車工業株式会社 filed Critical 三菱自動車工業株式会社
Priority to CN201680007804.1A priority Critical patent/CN107208569B/zh
Publication of WO2016121482A1 publication Critical patent/WO2016121482A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/06—Valve members or valve-seats with means for guiding or deflecting the medium controlled thereby, e.g. producing a rotary motion of the drawn-in cylinder charge
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B31/00—Modifying induction systems for imparting a rotation to the charge in the cylinder
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
    • 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 intake port structure of an engine that enables good combustion in a combustion chamber.
  • tumble flow (longitudinal vortex), which is a swirling flow flowing along the axial direction of the cylinder bore, or swirl flow, which is a swirling flow flowing along the circumferential direction of the inner peripheral surface of the cylinder bore, in the combustion chamber of the engine
  • swirl flow which is a swirling flow flowing along the circumferential direction of the inner peripheral surface of the cylinder bore
  • a technique for generating tumble flow for example, there is a technique for changing the degree of shielding in the intake port by an intake flow control valve provided in the intake port to generate tumble flow (for example, Patent Document 1 below) reference).
  • a nozzle that generates tumble flow by ejecting air downward along a wall surface of a valve throat from a nozzle provided in an intake port (for example, see Patent Document 2 below).
  • an object of the present invention is to strengthen tumble flow in the fuel chamber without complicating the structure.
  • the present invention comprises an intake port connected to a combustion chamber of an engine, and an annular seat ring provided in a region of the intake port facing the combustion chamber;
  • the inner surface of the intake port continuing to the upstream side of the inner surface is the inner surface of the seat ring at the rear end side far from the axial center of the cylinder bore in a plan view along the axial direction of the seat ring from the combustion chamber side.
  • a flared portion provided with a single inner surface matching portion and projecting to the inner side of the inner surface of the seat ring at any other portion, and the cross-sectional area of the flow path at the location where the flared portion is
  • the engine intake port structure was made smaller than the cross-sectional area of the engine.
  • the projecting portion is any one of side portions connecting the rear end side and the front end side close to the axial center of the cylinder bore among the inner surfaces of the intake port continuing to the upstream side of the inner surface of the seat ring A configuration provided on the side or both sides of the
  • the inner surface matching portion may adopt a configuration provided on the front end side of the inner surface of the intake port continuing on the upstream side of the inner surface of the seat ring.
  • a protrusion is provided on the front end side, and a maximum protrusion length of the protrusion of the side portion inward from the inner surface of the seat ring is the inner length from the inner surface of the seat ring in the protrusion on the front end side.
  • a configuration set larger than the maximum protrusion length can be adopted.
  • the inner surface of the intake port continuing on the upstream side of the inner surface of the seat ring has a maximum diameter in the front-rear direction connecting the front end side and the rear end side in the width direction orthogonal to that A configuration that is set larger than the maximum diameter can be adopted.
  • the inner surface of the intake port continuing on the upstream side of the inner surface of the seat ring has an arc-shaped portion around the axial center of the seat ring on the rear end side and the front end side, It is possible to adopt a configuration in which the radius of the arc-shaped portion on the rear end side is set larger than the radius of the arc-shaped portion on the front end side.
  • the present invention is characterized in that the inner surface of the intake port continued to the upstream side of the inner surface of the seat ring, and the seat ring on the rear end side far from the axial center of the cylinder bore in plan view along the axial direction of the seat ring from the combustion chamber side. Since the inner surface matching portion flush with the inner surface and the projecting portion protruding inward of the inner surface of the seat ring is provided at any other portion, the tumble ratio, that is, The rotational speed of the tumble flow can be improved while the piston reciprocates one time. As a result, the tumble flow in the fuel chamber can be enhanced without complicating the structure.
  • FIG. 1A is a main part enlarged view showing the vicinity of the intake port of the engine of this embodiment.
  • FIG. 1B is a modification thereof.
  • the arrangement of the combustion chamber 3 of the engine and the shape of the intake port 5 are shown in FIGS. 5A to 5C.
  • the engine of this embodiment is a diesel engine for automobiles.
  • a piston 2 is accommodated in a cylinder 1 of the engine.
  • a combustion chamber 3 is formed by the inner peripheral surface of the cylinder 1, the upper surface of the piston 2, and the like.
  • An intake passage 5 for feeding intake air into the combustion chamber 3 of each cylinder, an exhaust port 7 drawn from the combustion chamber 3, and a fuel injection device 9 for injecting fuel into the combustion chamber 3 are provided.
  • cylinder 1 In these drawings, members and means directly related to the present invention are mainly shown, and other members and the like are not shown. Further, although only one cylinder 1 is shown in the drawings, the engine may be a single cylinder or may be a multi-cylinder having a plurality of cylinders.
  • the intake port 5 branches into two passages in front of the combustion chamber 3.
  • the exhaust port 7 also branches into two passages in front of the combustion chamber 3.
  • An intake valve hole 5 a which is an opening of each intake port 5 to the combustion chamber 3, is opened and closed by the intake valve 6. Further, exhaust valve holes 7 a, which are openings of the exhaust ports 7 to the combustion chamber 3, are opened and closed by the exhaust valve 8. At this time, the intake valve 6 and the exhaust valve 8 contact with and separate from an annular seat ring 20 provided in a region facing the combustion chamber 3 of the intake port 5 and the exhaust port 7, respectively.
  • the intake valve 6 and the exhaust valve 8 open and close the intake valve hole 5a and the exhaust valve hole 7a at a predetermined timing by the rotation of a camshaft provided on the cylinder head 4 side.
  • the shaft portions of the intake valve 6 and the exhaust valve 8 are drawn out to the camshaft side in the cylinder head 4 from a shaft insertion portion 5 b opened to the inner surface of the intake port 5 and the exhaust port 7.
  • the shaft insertion portion 5b of the intake port 5 opens at a bent portion 5c located on the upstream side of the intake valve hole 5a in the intake port 5, or immediately upstream of the bent portion 5c. .
  • the downstream side of the shaft insertion portion 5b supporting the shaft portion of the intake valve 6 and immediately above the seat ring 20 The portion (hereinafter referred to as the seat ring upstream portion 30) located on the side of the cylinder bore has a cylinder bore in a bottom view from the combustion chamber 3 side, that is, a plan view along the axial center direction of the seat ring 20 from the combustion chamber 3 side.
  • an inner surface matching portion 32 flush with the inner surface of the seat ring 20 is provided at the rear end side far from the axial center x.
  • the rear end portion 31 d of FIG. 1A corresponds to the inner surface matching portion 32.
  • the seat ring is provided on the other portion of the seat ring upstream portion 30, that is, on the front end side close to the axial center x of the cylinder bore in the plan view, and on both side portions connecting the front end side and the rear end side.
  • a projecting portion 31 is provided which protrudes inward from the inner surface of 20.
  • the front end portion 31 c and the side portions 31 a and 31 b of FIG. 1A correspond to the overhanging portion 31.
  • the entire sectional shape of the seat ring upstream portion 30 has a so-called oval shape in which the maximum diameter in the front-rear direction connecting the front end side and the rear end side is set larger than the maximum diameter in the width direction orthogonal thereto. It has become.
  • each of the rear end portion 31 d and the front end portion 31 c is provided with an arc-shaped portion around the axial center of the seat ring 20.
  • the side portions 31a and 31b are linear inner surfaces connecting the rear end 31d and the front end 31c.
  • the side portions 31a and 31b may be in the shape of a gentle arc.
  • the cross-sectional area of the flow passage of the seat ring upstream portion 30 is smaller than the cross-sectional area of the flow passage of the seat ring 20 by the projecting portion 31. Thereby, the flow velocity of the intake air into the combustion chamber 3 can be increased.
  • the overhanging portion 31 is not provided at the rear end portion 31 d of the seat ring upstream portion 30 which is far from the axial center x of the cylinder bore.
  • the overhanging portion 31 is provided at a location excluding the rear end 31 d.
  • the flow rate of intake can be increased by narrowing the flow path at the other portion, that is, the side provided with the overhang portion 31 while securing the flow rate of intake at the side close to the inner circumferential surface of the cylinder 1 . It has been confirmed by experiments that the tumble ratio can be improved by securing the flow rate at the rear end 31 d and improving the flow velocity on the other side.
  • the seat ring upstream portion 30, that is, the inner surface of the intake port 5 continuing on the upstream side of the inner surface of the seat ring 20 is the inner surface of the seat ring 20 among the inner surfaces of the It means the part located immediately above.
  • the projecting portion 31 is provided to reduce the cross-sectional area of the flow passage in the intake port 5. For this reason, even if the shaft insertion portion 5 b supporting the shaft portion of the intake valve 6 has a portion that protrudes to the inner surface of the intake port 5, it does not correspond to the overhang portion 31.
  • the seat ring upstream portion 30 is located immediately above the seat ring 20, and usually is also a portion where the cross-sectional area of the flow path of the intake port 5 gradually spreads toward the combustion chamber 3.
  • FIG. 1B A modification is shown in FIG. 1B.
  • the seat ring upstream portion 30 is the same as the above-described example in that the inner side matching portion 32 is provided at the rear end 31d and the projecting portion 31 is provided at the front end 31c and the side portions 31a and 31b.
  • the point which equips each of the back end part 31d and the front end part 31c with the arc-shaped part of the circumference of the axial center of the seat ring 20 is also the same.
  • the side portions 31a and 31b are linear inner surfaces connecting the rear end 31d and the front end 31c.
  • the radius rd of the circular arc portion of the rear end portion 31 d is set larger than the radius rc of the circular arc portion of the front end portion 31 c.
  • the maximum projecting lengths a and b of the projecting portions 31 of the side portions 31a and 31b from the inner surface of the seat ring 20 are the same as those of the front end portion 31c. It is desirable to set the projection length 31 to be larger than the maximum inward projection length c from the inner surface of the seat ring 20. The amount of reduction of the flow passage cross-sectional area for improving the flow velocity can be secured larger at the side portions 31a and 31b than at the front end 31c.
  • FIG. 1 The effect of the tumble ratio improvement of this invention is shown in FIG.
  • the flow rate and the tumble ratio are in a trade-off relationship, and there is a problem that when the flow rate is increased, the tumble ratio is decreased.
  • the tumble ratio can be increased while the flow rate is increased, the trade-off relationship between the conventional flow rate and the tumble ratio can be improved.
  • FIG. 3A Another embodiment is shown in FIG. 3A.
  • the inner surface matching portion 32 is provided on the rear end portion 31d side in the plan view.
  • an overhanging portion 31 is provided on the front end portion 31c and the side portions 31a and 31b on both sides.
  • the overhanging portions 31 of the side portions 31a and 31b are not linear but are continuous with the arc-like overhanging portions 31 of the front end 31c only in the portion closer to the front end than the axial center o of the seat ring 20
  • An arcuate overhang 31 is provided.
  • the arc-shaped overhanging portion 31 of the side portions 31a and 31b and the arc-shaped overhanging portion 31 of the front end portion 31c are continuous circles having the same radius rc concentrically, these arcs having different radii. It may be Further, the area rc of the overhanging portion 31 may be increased by making the radius rc of the overhanging portion 31 smaller than the radius rd of the arc-shaped inner surface on the rear end portion 31d side.
  • the inner surface matching portion 32 is provided at the rear end portion 31 d and the front end portion 31 c.
  • the overhanging portions 31 are provided on the side portions 31a and 31b on both sides.
  • the cross-sectional shape of the seat ring upstream portion 30 is a so-called oval in which the maximum diameter in the front-rear direction connecting the front end side and the rear end side is set larger than the maximum diameter in the width direction orthogonal thereto. It is a shape.
  • the overhanging portion 31 is provided on both side portions 31a and 31b, but the overhanging portion 31 is provided only on one of the side portions and the other side portion is also used as the inner surface matching portion 32. Good.
  • the intake port 5 including the seat ring upstream portion 30 is manufactured together with the cylinder head 4 by casting. Since the cross-sectional shape of the seat ring upstream portion 30 is not a perfect circle due to the existence of the projecting portion 31 and the inner surface matching portion 32, the mold of the casting at the time of casting is made to have such a shape or The member is cut by a three-dimensional machining center or the like.
  • the seat ring 20 before processing is press-fit into a portion of the intake port 5 facing the combustion chamber 3 in advance, and is fixed to the intake port 5.
  • the throat portion 22 which is gradually expanded toward the combustion chamber 3 is processed on the inner surface of the deep portion of the intake valve hole 5a.
  • the throat cutter A is caused to approach a predetermined amount into the intake port 5 along an axial center coinciding with the center line of the intake valve 6.
  • the inner surface of the seat ring 20 and the upstream portion 30 of the seat ring are shaved.
  • a throat portion 22 formed of a conical surface, a spherical surface or the like is formed continuously from the inner surface of the seat ring 20 to the inner surface of the seat ring upstream portion 30. Therefore, at this time, a part of the overhanging portion 31 and the inner surface matching portion 32 is also cut.
  • the valve abutment portion 21 is processed.
  • the sheet cutter B is advanced into the seat ring 20 along the axial center coincident with the center line of the intake valve 6 by a predetermined amount.
  • the inner surface of the seat ring 20 is cut by rotating the sheet cutter B around the axis.
  • the valve contact portion 21 formed of a conical surface or a spherical surface is formed on the inner surface of the seat ring 20.
  • the throat portion 22 and the valve contact portion 21 are smoothly continuous, so that a smooth inner surface is formed from the projecting portion 31 and the inner surface matching portion 32 to the inner surface of the seat ring 20. Be done.
  • the throat portion 22 may be processed earlier than the valve contact portion 21, and the valve contact portion 21 may be processed earlier than the throat portion 22.
  • the configuration of the present invention has been described by taking a diesel engine for a car as an example.
  • the present invention can be applied to a four-cycle gasoline engine for a car, other various applications, and various engines.
  • Reference Signs List 1 cylinder 2 piston 3 combustion chamber 4 cylinder head 5 intake port 6 intake valve 7 exhaust port 8 exhaust valve 9 fuel injection device 20 seat ring 21 valve contact portion 22 throat portion 30 seat ring upstream portion 31 overhang portion 32 inner surface matching portion

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Abstract

Selon l'invention, un écoulement tourbillonnaire dans une chambre de carburant est renforcé sans compliquer la structure. Une structure d'orifice d'admission, pour un moteur, présente un orifice d'admission (5) d'un moteur qui est continu avec le côté amont de la surface interne d'une bague de siège annulaire (20) dans l'orifice d'admission (5), la surface interne de l'orifice d'admission est pourvue d'une partie de mise en correspondance de surface interne (32) qui, dans une vue en plan dans la direction axiale de la bague de siège (20) à partir d'un côté chambre de combustion (3), est alignée sur la surface interne de la bague de siège (20) sur le côté extrémité arrière le plus éloigné du centre axial d'un alésage de cylindre, et toute autre partie est pourvue d'une partie saillante (31) qui fait saillie plus loin vers l'intérieur que la surface interne de la bague de siège (20).
PCT/JP2016/050651 2015-01-29 2016-01-12 Structure d'orifice d'admission pour moteur WO2016121482A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201680007804.1A CN107208569B (zh) 2015-01-29 2016-01-12 发动机的进气口结构

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015-015376 2015-01-29
JP2015015376A JP6561480B2 (ja) 2015-01-29 2015-01-29 エンジンの吸気ポート構造

Publications (1)

Publication Number Publication Date
WO2016121482A1 true WO2016121482A1 (fr) 2016-08-04

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CN (1) CN107208569B (fr)
WO (1) WO2016121482A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7040977B2 (ja) * 2018-03-29 2022-03-23 本田技研工業株式会社 吸気ポート構造
JP7173166B2 (ja) * 2019-01-07 2022-11-16 三菱自動車工業株式会社 シリンダヘッド

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS55102028U (fr) * 1979-01-09 1980-07-16
EP0281015A2 (fr) * 1987-02-26 1988-09-07 Motoren-Werke Mannheim Aktiengesellschaft Faucille de tourbillonnement dans un conduit d'admission d'un moteur à combustion interne
JPH02125916A (ja) * 1988-11-07 1990-05-14 Toyota Motor Corp ２サイクル内燃機関
JPH0352338U (fr) * 1989-09-29 1991-05-21
JPH08100702A (ja) * 1994-09-30 1996-04-16 Yanmar Diesel Engine Co Ltd ディーゼル機関
JPH0979040A (ja) * 1995-09-11 1997-03-25 Mitsubishi Motors Corp 筒内噴射型内燃機関
JPH1150852A (ja) * 1997-08-04 1999-02-23 Honda Motor Co Ltd 内燃機関の吸気装置
JP2007032560A (ja) * 2005-06-20 2007-02-08 Toyota Motor Corp 気流制御装置
JP2007046457A (ja) * 2003-09-22 2007-02-22 Toyota Motor Corp 内燃機関の吸気ポートおよびその製造方法
JP2013122188A (ja) * 2011-12-09 2013-06-20 Mitsubishi Motors Corp 内燃機関

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4022006B2 (ja) * 1998-06-09 2007-12-12 ヤンマー株式会社 内燃機関の吸気ポート形状
JP3676967B2 (ja) * 2000-08-14 2005-07-27 新潟原動機株式会社 シリンダヘッド
AT5484U1 (de) * 2001-08-02 2002-07-25 Avl List Gmbh Zylinderkopf für eine brennkraftmaschine
JP2013072390A (ja) * 2011-09-28 2013-04-22 Nippon Soken Inc 内燃機関

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS55102028U (fr) * 1979-01-09 1980-07-16
EP0281015A2 (fr) * 1987-02-26 1988-09-07 Motoren-Werke Mannheim Aktiengesellschaft Faucille de tourbillonnement dans un conduit d'admission d'un moteur à combustion interne
JPH02125916A (ja) * 1988-11-07 1990-05-14 Toyota Motor Corp ２サイクル内燃機関
JPH0352338U (fr) * 1989-09-29 1991-05-21
JPH08100702A (ja) * 1994-09-30 1996-04-16 Yanmar Diesel Engine Co Ltd ディーゼル機関
JPH0979040A (ja) * 1995-09-11 1997-03-25 Mitsubishi Motors Corp 筒内噴射型内燃機関
JPH1150852A (ja) * 1997-08-04 1999-02-23 Honda Motor Co Ltd 内燃機関の吸気装置
JP2007046457A (ja) * 2003-09-22 2007-02-22 Toyota Motor Corp 内燃機関の吸気ポートおよびその製造方法
JP2007032560A (ja) * 2005-06-20 2007-02-08 Toyota Motor Corp 気流制御装置
JP2013122188A (ja) * 2011-12-09 2013-06-20 Mitsubishi Motors Corp 内燃機関

Also Published As

Publication number Publication date
JP6561480B2 (ja) 2019-08-21
CN107208569A (zh) 2017-09-26
CN107208569B (zh) 2019-10-01
JP2016138534A (ja) 2016-08-04

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