WO2016103403A1 - Moteur en v - Google Patents

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Publication number
WO2016103403A1
WO2016103403A1 PCT/JP2014/084343 JP2014084343W WO2016103403A1 WO 2016103403 A1 WO2016103403 A1 WO 2016103403A1 JP 2014084343 W JP2014084343 W JP 2014084343W WO 2016103403 A1 WO2016103403 A1 WO 2016103403A1
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WO
WIPO (PCT)
Prior art keywords
bank
injection valve
cylinder
intake
intake port
Prior art date
Application number
PCT/JP2014/084343
Other languages
English (en)
Japanese (ja)
Inventor
武広 西殿
格 野口
淳次 高井
敏郎 横山
Original Assignee
三菱自動車工業株式会社
三菱自動車エンジニアリング株式会社
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, 三菱自動車エンジニアリング株式会社 filed Critical 三菱自動車工業株式会社
Priority to JP2016565761A priority Critical patent/JPWO2016103403A1/ja
Priority to PCT/JP2014/084343 priority patent/WO2016103403A1/fr
Publication of WO2016103403A1 publication Critical patent/WO2016103403A1/fr

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    • 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
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/32—Engines with pumps other than of reciprocating-piston type
    • F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
    • 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
    • F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
    • F02M35/10—Air intakes; Induction systems
    • F02M35/104—Intake manifolds
    • F02M35/116—Intake manifolds for engines with cylinders in V-arrangement or arranged oppositely relative to the main shaft

Definitions

  • the present disclosure relates to a V-type engine, and particularly to a V-type engine equipped with a supercharger.
  • V-type engines are provided with a supercharger for the purpose of improving engine output, and others are provided with a supercharger (mechanical supercharger) driven by the engine (Patent Literature). 1).
  • a supercharger mechanical supercharger driven by the engine
  • Patent Document 2 An engine including the in-cylinder injection valve and the intake port injection valve is employed not only in an in-line cylinder engine but also in a V-type engine.
  • Patent Document 2 shows an injection valve for dual fuel injection in a V-type engine, which is connected to an in-cylinder injector that is attached to a cylinder head and directly injects fuel into a combustion chamber, and an intake port.
  • An arrangement including an intake pipe injector attached to an intake manifold and injecting fuel into an intake port is shown.
  • Patent Document 1 in a V-type engine, when a structure in which superchargers are arranged between banks or between banks is employed, there arises a problem with an increase in overall height.
  • the cylinder injection injectors are arranged inside the V bank and inside the intake port as viewed from the crankshaft direction, and the left and right cylinder injection injectors are directed obliquely upward and inside to each other.
  • the intake pipe injector is located between the V banks and outside the intake passage (intake manifold) connected to the intake port formed in the cylinder head, and is directed substantially upward. Therefore, there is a problem that the bank angle of the V bank is required to be large, the entire width of the V-type engine is enlarged, and the size is increased.
  • an object of at least one embodiment of the present invention is to provide in-cylinder injection in a V bank below a supercharger in a V-type engine having a supercharger between banks or between banks.
  • the aim is to reduce the size of the V-type engine by arranging an injector and an intake port injection injector.
  • a V-type engine includes an intake port provided in a cylinder head so as to be connected to a combustion chamber of each cylinder inside a V bank, and the intake port as viewed in the crankshaft direction.
  • An intake port injection valve disposed so as to inject fuel into the intake port, and located closer to the combustion chamber than the intake port injection valve as viewed in the crankshaft direction, Inside the cylinder injection valve arranged to inject fuel directly into the combustion chamber, a supercharger provided above between the V banks, and the discharge air from the supercharger
  • An intake passage to be introduced into the intake port, and the intake port injection valve and the in-cylinder injection valve in each of the left and right banks are the supercharger, the intake passage, and the left and right banks. Characterized in that it is arranged so as be enclosed by.
  • both the intake port injection valve and the in-cylinder injection valve are disposed so as to be surrounded by the supercharger, the intake passage, and the left and right banks, that is, the intake passage. Since both injection valves are disposed inside the V bank, the bank angle of the V bank does not need to be set wider than the conventional structure in which the port injection valve is disposed outside the intake passage, and the entire width is suppressed. be able to. Furthermore, since both the intake port injection valve and the in-cylinder injection valve are disposed inside the supercharger, the intake passage, and the left and right banks, an increase in the overall height can be suppressed.
  • the intake passage that surrounds the intake port injection valve and the in-cylinder injection valve has a branch passage to the cylinders of each bank, and is adjacent to each other.
  • the branched passages are connected by connecting walls to form an integrated wall surface.
  • the intake passage to be enclosed has a branch passage to the cylinder of each bank, and connects the adjacent branch passages with a connecting wall to form an integrated wall surface. Since the enclosed internal space is shaped like a tunnel, it also has the effect of guiding the flow of air from vehicle travel to make it easier to flow, so the flow of travel air is expected to improve the cooling effect of injection valves, delivery pipes, etc. it can.
  • each bank is offset in the same direction as the rotation direction of the crankshaft, and one bank ranks higher than the other bank due to the offset.
  • a high bank positioned higher in the axial direction view, the intake port injection valve and the in-cylinder injection valve on the high bank side than the intake port injection valve and the in-cylinder injection valve on the other low bank side It is characterized by being arranged at a high position.
  • the intake port injection valves and the in-cylinder injection valves in the left and right banks are alternately shifted in the vertical direction when viewed from the crankshaft direction. It becomes easy to dispose inside.
  • the high bank in the configuration of (1) or (2), is arranged with a position shifted from the other low bank in the crankshaft direction, and the high bank is more
  • the intake port injection valve and the in-cylinder injection valve on the high bank side are shifted from the low bank toward the one end side of the crankshaft, and the intake port injection valve on the other low bank side and the in-cylinder injection valve It is characterized by being shifted from the in-cylinder injection valve to the one end side.
  • the high bank and the low bank are shifted in the crankshaft direction when viewed in a direction perpendicular to the crankshaft. Further, the in-cylinder injection valves are alternately arranged in the front-rear direction so as to be alternately arranged, so that the arrangement between the V banks is further facilitated.
  • a low-pressure delivery pipe connected to the intake port injection valve of each cylinder to supply fuel, and the cylinder
  • a high-pressure delivery pipe connected to an in-cylinder injection valve for supplying fuel, and the low-pressure delivery pipe and the high-pressure delivery pipe are each arranged extending in the cylinder arrangement direction, and supply the fuel to the low-pressure delivery pipe
  • the inlet side and the fuel supply inlet side to the high-pressure delivery pipe are positioned on opposite sides in the arrangement direction of the cylinders.
  • the fuel supply inlet side to the low pressure delivery pipe and the fuel supply inlet side to the high pressure delivery pipe are located on opposite sides in the cylinder arrangement direction.
  • On the fuel supply inlet side of the high-pressure delivery pipe and the high-pressure delivery pipe it is possible to avoid complicated piping arrangement in order to avoid mutual interference. As a result, it is easy to dispose the intake port injection valve and the in-cylinder injection valve between the V banks.
  • a V-type bank angle of the V-type engine is set in a range of about 60 ° or less.
  • both the intake port injection valve and the in-cylinder injection valve are connected to the V bank below the supercharger. It is possible to provide a V-type engine having a supercharger with a reduced overall width and height.
  • the in-cylinder injector and the intake port injector are disposed in the V bank below the supercharger.
  • the V-type engine can be made compact.
  • FIG. 3 is a cross-sectional explanatory view taken along line AA in FIG. 2.
  • FIG. 3 is a side view and a partial cross-sectional explanatory view of the intake structure portion of FIG. 2.
  • It is a plane view schematic diagram of a fuel injection device.
  • an expression indicating that things such as “identical”, “equal”, and “homogeneous” are in an equal state not only represents an exactly equal state, but also has a tolerance or a difference that can provide the same function. It also represents the existing state.
  • expressions representing shapes such as quadrangular shapes and cylindrical shapes represent not only geometrically strict shapes such as quadrangular shapes and cylindrical shapes, but also irregularities and chamfers as long as the same effects can be obtained. A shape including a part or the like is also expressed.
  • the expressions “comprising”, “comprising”, “comprising”, “including”, or “having” one constituent element are not exclusive expressions for excluding the existence of other constituent elements.
  • FIG. 1 to 6 show a V-type engine according to an embodiment of the present invention.
  • the front-rear, left-right, and up-down directions are directions viewed from the driver's seat when the V-type engine 1 is mounted on the front of the vehicle with the crankshaft aligned with the front-rear direction of the vehicle.
  • FIG. 1 and FIG. 1 show a V-type engine according to an embodiment of the present invention.
  • the front-rear, left-right, and up-down directions are directions viewed from the driver's seat when the V-type engine 1 is mounted on the front of the vehicle with the crankshaft aligned with the front-rear direction of the vehicle.
  • the V-type engine 1 is a four-cycle V-type six-cylinder gasoline engine, and the bank angle (bank angle) of the V bank is, for example, about 60 °. Three cylinders are juxtaposed in the right bank 12a and the left bank 12b, both of which are V-shaped.
  • pistons 16a and 16b are slidably fitted in the cylinders 14a and 14b.
  • the pistons 16a and 16b are connected to the crankshaft 20 rotatably accommodated in the crankcase 18 via connecting rods 22a and 22b.
  • Each of the left and right banks 12a and 12b has cylinder heads 26a and 26b coupled to the cylinder blocks 24a and 24b and upper portions thereof, and a rocker cover 28a so as to cover a valve mechanism such as a camshaft. 28b are attached.
  • the cylinder heads 26a and 26b are provided with intake ports 38a and 38b and exhaust ports (not shown) that are controlled to be opened and closed by an intake valve and an exhaust valve (not shown) for each cylinder.
  • the intake ports 38a and 38b and intake port openings 39a and 39b are provided in the cylinder heads 26a and 26b.
  • openings 39a and 39b of the intake ports 38a and 38b are provided on the upper surfaces of the cylinder heads 26a and 26b of the banks 12a and 12b.
  • the intake valve and the exhaust valve are each driven at a predetermined timing via a cam shaft.
  • the V-type engine 1 has an offset crank structure. As shown in FIG. 1, this offset crank structure maintains a height from the center P of the crankshaft to the upper surface of the cylinder head with respect to a normal engine (V-type engine in which each bang is not offset).
  • V-type engine in which each bang is not offset.
  • the length of the intake air inlets 64a and 64b that support the supercharger 30 to be described later can be made shorter on the right bank (high bank) 12a side than on the left bank (low bank) 12b side. Specifically, the length of the lower intake introduction portion 68a described later can be shortened. By shortening the length, the support rigidity on the right bank 12a side can be improved as compared with the left bank 12b side.
  • the driving force for driving the supercharger 30 is transmitted from the crankshaft 20 by a power transmission means 48 such as a belt or a chain.
  • a supercharger pulley 50 for transmitting the driving force is as shown in FIG. Since it is positioned closer to the right bank 12a, the vibration of the supercharger 30 can be suppressed by strengthening the rigidity by being positioned on the higher support rigidity side.
  • the cylinders arranged in the banks 12a and 12b are arranged with their positions shifted in the front-rear direction of the crankshaft 20. As will be described later, when the injectors and the like of the fuel injection device are opposed to each other inside the V bank, it is difficult to arrange the injectors due to the arrangement space.
  • the right bank (high bank) 12a has one end side of the crankshaft 20, that is, the input rotation of the supercharger 30, with respect to the other left bank (low bank) 12b in the crankshaft 20 direction. It is shifted (offset) by L on one end side (front side) connected by the shaft 31 and the power transmission means (belt) 48. Therefore, among the intake passages 29 that support the supercharger 30 above the V banks, the intake passage 29 of the right bank 12a on the side close to the input rotation shaft 31 is positioned close to one end (front side), so that the input rotation The support rigidity of the shaft 31 can be further increased, and the vibration reduction effect of the supercharger can be further improved.
  • the main body of the V-type engine 1 is configured such that the right bank 12a is higher than the left bank 12b and is shifted forward (offset). Thereby, the support rigidity of the supercharger 30 can be increased, and the vibration reduction of the supercharger 30 can be improved.
  • a supercharger 30 driven by the crankshaft 20 is provided between the right bank 12a and the left bank 12b (between bank angles) and above the cylinder heads 26a and 26b of each bank.
  • the supercharger 30 is driven by the driving force transmitted from the crankshaft 20 to the input rotary shaft 31 by a power transmission means (belt) 48 such as a belt or a chain, and the intake port 38a formed in the cylinder heads 26a and 26b. , 38b.
  • a power transmission means such as a belt or a chain
  • FIG. 1 it is located above the shaft center P of the crankshaft 20, and is provided so that the lower surface of the supercharger 30 is positioned above the upper surfaces of the rocker covers 28a, 28b (H in FIG. 1). .
  • position the lower intake introduction parts 68a and 68b in the space between the lower surface of a supercharger and the upper surface of the rocker cover provided in the cylinder head is securable.
  • a cooling effect is obtained by ventilation passing through the lower surface side of the supercharger 30.
  • the supercharger 30 is attached to the upper portion of the supercharger 30 and is supported in a state of being hung at a substantially central portion of an outlet passage portion 32 formed to extend in the direction of the left and right banks 12a and 12b.
  • the supercharger 30 is, for example, a four-leaf root type, and a pair of rotors 54, 54 mesh with each other in a cylindrical casing 52, and reversely rotate to push out intake air downstream. By doing so, increase the intake pressure.
  • the rotating shaft of one rotor 54 protrudes from the cylindrical casing 52, a supercharger pulley 50 is provided at the front end portion, and the other rotor is configured to be rotatable by gears or the like in the casing.
  • Both ends of the cylindrical casing 52 are shielded by end plates 51 and 53, and a conical bearing body 51 a that rotatably supports the supercharger pulley 50 is bolted to the end plate 51.
  • a suction port 56 for introducing the intake air into the supercharger 30 is formed at the rear end portion of the cylindrical casing 52, and a discharge port 58 for discharging the intake air from the supercharger 30 is formed in the cylindrical casing. 52 is formed in the upper part of the front portion.
  • the intake air discharged by the rotation of the rotors 54 is discharged upward through the discharge port 58 (discharge air A2).
  • An outlet housing 34 constituting the outlet passage portion 32 is provided above the cylindrical casing 52, and an intake outlet passage q is formed inside the outlet housing 34.
  • a bypass casing 60 that forms a bypass passage b is connected to the cylindrical casing 52 and the outlet housing 34 on the vehicle body rear side by bolts 61.
  • the bypass passage b is arranged in the vertical direction, and a bypass valve 62 is provided.
  • the bypass passage b communicates with the opening duct 40 and the suction port 56 for sucking outside air on the downstream side of the bypass valve 62.
  • a part of the intake air discharged from the supercharger 30 to the outlet passage q by the bypass passage b is returned to the suction port 56 by the bypass passage b.
  • the return intake air amount is adjusted by the bypass valve 62.
  • the opening duct 40 is formed in the inlet passage casing 43, and the inlet passage casing 43 is attached to the bypass casing 60 by bolting.
  • a throttle valve 41 is provided in the opening duct 40, and the intake amount is adjusted via the throttle valve 41 and introduced from the intake port 56 (intake air A1).
  • the intake passage 29 for guiding the intake air discharged from the discharge port 58 of the supercharger 30 to the intake ports 38a and 38b of the engine is roughly divided into an outlet passage portion 32 and intake air introduction portions 64a and 64b. .
  • the exit passage portion 32 is attached to the upper portion of the supercharger 30 and is formed to extend in the direction of the left and right banks 12a and 12b.
  • the intake air discharged upward from the supercharger 30 is distributed in the direction of the left and right banks 12a and 12b.
  • the intake air introduction portions 64a and 64b extend downward from the left and right ends of the outlet passage portion 32 and pass through the left and right sides of the supercharger 30 to lead to the intake ports 38a and 38b of the cylinders of the banks 12a and 12b. It is.
  • the supercharger 30 is suspended and supported at a substantially central portion of the outlet passage portion 32 by the intake air introduction portions 64 a and 64 b and the outlet passage portion 32.
  • the intake air introduction portions 64a and 64b are constituted by upper intake air introduction portions 66a and 66b to which the intercoolers 70a and 70b are mounted, and lower intake air introduction portions 68a and 68b provided below the upper intake air introduction portions 66a and 66b.
  • the lower intake introduction portions 68a and 68b are configured to have branch passages 69a, 71a, 73a and 69b, 71b, 73b branched toward the respective cylinders, and are curved inward along the outer shape of the rocker covers 28a and 28b. Then, it is connected to the intake ports 38a and 38b of the cylinders 14a and 14b of the banks 12a and 12b.
  • the outlet housing 34 is a flat, substantially rectangular parallelepiped shape having a longitudinal shape in the left and right bank directions and a short shape in the direction perpendicular to the left and right banks (in the direction of the crankshaft 20). It is made up of.
  • the outlet housing 34 flat, the height of the outlet housing 34 can be suppressed, and the overall height of the V-type engine 10 can be suppressed.
  • it is easy to secure the required intake air amount by securing the length in the short direction even if it is flat.
  • a central opening 59 is formed in the central portion of the bottom wall of the outlet housing 34 in the left-right direction so as to overlap the upper position of the discharge port 58 of the supercharger 30, and is formed around the discharge port 58 of the supercharger 30.
  • a central opening flange portion 34a to be joined to the flange portion 52a is formed.
  • a right opening 63 and a left opening 67 connected to the upper end portions of the upper intake introduction portions 66a and 66b are formed at the left and right end portions of the bottom wall of the outlet housing 34, and a fastening flange is formed around each opening.
  • Portions 88a and 88b are formed and coupled to the upper ends of the upper intake introduction portions 66a and 66b.
  • the outlet housing 34 has a short distribution rib 36 on the inner wall surface facing the discharge port 58 of the supercharger 30 for distributing the intake air discharged upward from the supercharger 30 in the left and right banks 12a and 12b.
  • the shape protrudes in the hand direction and inward, and is formed over the entire region in the short direction.
  • a bypass opening 65 communicating with the bypass passage b is provided on the rear wall of the outlet housing 34 located at the rear end of the distribution rib 36.
  • the distribution ribs 36 improve the distribution of the intake air discharged from the supercharger 30 to the left and right banks 12a, 12b, so that the intake air can be evenly supplied to the cylinders of the left and right banks.
  • the outlet housing 34 is formed such that the height of the inner wall surface of the upper wall facing the discharge port 58 of the supercharger 30 increases from the front to the rear in the short direction. That is, as shown in FIG. 5, the inner wall surface of the outlet housing 34 is inclined with respect to the rotation axis direction of the rotors 54, 54 of the supercharger 30. Therefore, the intake air discharged from the discharge port 58 of the supercharger 30 collides with the inner wall surface of the upper wall of the outlet housing 34 in an inclined state, not in a perpendicular direction. For this reason, the area where the intake air hits the inner wall surface becomes large, and the effect of reducing the collision noise generated at the time of the collision can be obtained. That is, the radiated sound due to the discharge pressure from the supercharger can be reduced.
  • the supercharger 30 is attached to the lower surface of the bottom wall of the outlet housing 34 by fastening bolts 80 inserted from above the upper surface of the upper wall of the outlet housing 34. Thereby, the supercharger 30 can be fixed in a suspended state.
  • the outlet housing 34 is made of a light metal such as resin or aluminum. As a result, the outlet housing 34 can be reduced in weight, and the outlet housing 34 is integrally formed of resin or light metal, thereby facilitating manufacture. Further, since the outlet housing 34 can be reduced in weight, the upper part of the engine can be reduced in weight, the weight load can be reduced, and the durability reliability can be improved. In addition, since the upper part of the engine can be reduced in weight, the center of gravity of the engine is lowered, which contributes to improving the vehicle performance (preventing understeer).
  • the upper intake introduction portions 66a and 66b are configured by intercoolers 70a and 70b.
  • the intercoolers 70a and 70b are provided separately for the left and right banks 12a and 12b on the left and right sides of the supercharger 30 and above the rocker covers 28a and 28b. Since the intake air is cooled for each bank, cooling can be obtained more effectively than cooling the entire intake air collectively. Further, since the intercoolers 70a and 70b are arranged on both sides of the supercharger 30, the upper space portions of the rocker covers 28a and 28b of the V-type engine 1 can be used effectively.
  • the intercoolers 70a and 70b have the same structure on both the left and right sides, and water-cooled intercooler cores 74a and 74b are accommodated in the cylindrical bodies 72a and 72b having a square cross section.
  • the intercooler cores 74a and 74b The cooling water W is supplied and discharged from the outside.
  • the cooling water supply ports 76a and 76b are disposed on the upper side, and the discharge ports 78a and 78b are disposed on the lower side, so that the bubbles in the cooling water are easily discharged upward (see FIGS. 1 and 5).
  • lower end flange portions 82a and 82b are formed around the lower end portions of the cylindrical bodies 72a and 72b, and the lower end flange portions 82a and 82b extend around the cylindrical bodies 72a and 72b.
  • a plurality of reinforcing column portions (made of metal or resin) 84a and 84b are provided upright.
  • pillar portions 84a and 84b have a hollow shape, and fastening bolts 86a and 86b pass through the inside. If the upper ends of the pillar portions 84a and 84b are the right intercooler 70a, they contact the flange portion 88a of the right opening of the outlet housing 34, and if they are the left intercooler 70b, the flange portion 88b of the left opening of the outlet housing 34 Abut.
  • the lower end flange portions 82a and 82b of the cylindrical bodies 72a and 72b are joined to the upper end flange portions 90a and 90b of the lower intake air introduction portion 68a. Then, the fastening bolts 86a and 86b are inserted from the upper surfaces of the flange portions 88a and 88b, and screwed into the female screw portions formed in the upper end flange portions 90a and 90b of the lower intake air introduction portions 68a and 68b, thereby the cylindrical body 72a. And 72b are fixed so as to be sandwiched between the outlet housing 34 and the lower intake introduction portions 68a and 68b. In addition, the cylindrical bodies 72a and 72b are integrally molded, for example with resin.
  • the lower intake introduction portions 68a and 68b are provided below the upper intake introduction portions 66a and 66b, and have branch passages 69a, 71a, 73a and 69b, 71b, 73b branched toward the respective cylinders. That is, the lower intake introduction portions 68a and 68b are portions corresponding to intake manifolds, and the lower intake introduction portions 68a and 68b having a branch passage are integrally formed by casting or resin.
  • the upper part of the engine can be further reduced in weight by making the cylindrical bodies 72a and 72b resinous or light metallized and the lower intake introduction parts 68a and 68b resinous or light metallized.
  • the upper end flange portions 90a and 90b of the lower intake introduction portions 68a and 68b are fastened to the lower end portions of the upper intake introduction portions 66a and 66b by the fastening bolts 86a and 86b as described above, and the lower end flanges of the lower intake introduction portions 68a and 68b.
  • the portions 92a and 92b are bolted to the openings 39a and 39b of the intake ports 38a and 38b of the cylinder heads 26a and 26b.
  • the upper portions of the lower intake introduction portions 68a and 68b are formed with collecting portions 75a and 75b that collect the intake air after passing through the intercoolers 70a and 70b and direct the flow direction to the inside of the bank.
  • Branching passages 69a, 71a, 73a and 69b, 71b, 73b are formed by branching from the collecting portions 75a, 75b by the number of cylinders downstream. As shown in FIGS.
  • the branch passages 69a, 71a, 73a and 69b, 71b, 73b are curved inward along the outer shapes of the upper and side surfaces of the rocker covers 28a, 28b, so that the rocker covers 28a, 28b Passing between the upper surface and the lower surface of the supercharger 30, it is connected to the intake ports 38a, 38b of the cylinders of the banks 12a, 12b.
  • the branch passages 69 a, 71 a, 73 a and 69 b, 71 b, 73 b branched toward each cylinder have a structure that is provided in the lower region from near the lower portion of the supercharger 30. For this reason, the branch passage improves the rigidity of the portion corresponding to the leg portion that suspends the supercharger 30 and can contribute to stable support of the supercharger.
  • a plurality of adjacent branch passages 69a, 71a, 73a and a connecting wall 94 are connected between the plurality of adjacent branch passages 69a, 71a, 73b from the collecting portions 75a, 75b of the lower intake introduction portions 68a, 68b to the lower end flange portions 92a, 92b.
  • a wall surface K1 is integrated to form a wall surface K1.
  • reinforcing ribs 96 are formed on the integrated wall surface K1 and the wall surfaces K2 of the collecting portions 75a and 75b.
  • left and right banks 12a and 12b are connected by a left and right connecting portion 98 so as to bridge the lower end flange portions 92a and 92b of the lower intake introduction portions 68a and 68b.
  • the left and right connecting portions 98 may be provided at both end portions in the front-rear direction, or at a plurality of locations at intervals in the front-rear direction, and may be provided entirely as a bottom wall. This further increases the rigidity of the lower intake air introduction portions 68a and 68b.
  • the intake air is evenly distributed to the left and right banks 12a, 12b by the distribution ribs 36. Thereafter, the intake air directed toward the banks 12a and 12b changes in the downward direction at both end portions of the outlet housing 34 and is introduced into the left and right intercoolers 70a and 70b to be cooled.
  • the cooled intake air changes the flow direction to the inside of the bank at the collecting portions 75a and 75b, and the branched passages 69a, 71a, 73a and 69b, which are curved along the outer shape of the rocker covers 28a and 28b, 71b and 73b, are led from the openings 39a and 39b formed on the upper surfaces of the cylinder heads 26a and 26b to the intake ports 38a and 38b, and are supplied to the combustion chambers 103a and 103b.
  • the overall height is not increased.
  • a supercharger 30 can be installed.
  • the supercharger 30 is described as being suspended from the outlet housing 34 having a flat rectangular parallelepiped shape extending in the left and right bank directions.
  • the supercharger 30 is not necessarily suspended. For example, you may make it mount and fix to the lower intake introduction parts 68a and 68b.
  • low pressure delivery pipes 107 a and 107 b for port injection are attached to the lower portion of the supercharger 30 in the cylinder row direction, and intake port injection valves are respectively provided in the low pressure delivery pipes 107 a and 107 b.
  • 101a and 101b are connected for three cylinders.
  • the injection ports 102a and 102b of the intake port injection valves 101a and 101b are installed so as to be positioned in the openings 39a and 39b of the intake ports 38a and 38b of the cylinder heads 26a and 26b, and the axes of the intake port injection valves 101a and 101b are
  • the left and right banks 12a and 12b are inclined so as to face the center and obliquely upward, and are attached so that the injection direction from the intake port injection valves 101a and 101b is directed to the valve body of the intake valve.
  • high pressure delivery pipes 109a and 109b for in-cylinder injection are mounted in the cylinder row direction inside the banks 12a and 12b of the cylinder heads 26a and 26b, and in-cylinder injection is respectively provided to the high pressure delivery pipes 109a and 109b.
  • Valves 105a and 105b are connected for three cylinders.
  • the in-cylinder injection valves 105a and 105b are inclined in the same way as the intake port injection valves 101a and 101b toward the center in the banks 12a and 12b and obliquely upward, and the in-cylinder injection valves 105a and 105b. Are attached so as to direct the injection direction from the combustion chambers 103a and 103b.
  • the intake port injection valves 101a and 101b and the in-cylinder injection valves 105a and 105b are inclined so as to be inclined obliquely upward inside the banks 12a and 12b, respectively, and are located above and below in the crankshaft direction view.
  • the axis of the injector is arranged substantially parallel.
  • the left and right banks 12a and 12b have different heights, and the right bank 12a is higher than the left bank 12b. Therefore, the intake port injection valves 101a and 101b and the in-cylinder injection valves 105a, Since 105b is offset vertically between the banks, the intake port injection valves 101a and 101b and the in-cylinder injection valves 105a and 105b can be arranged in the space in the left and right banks 12a and 12b without interference. Furthermore, since it also shifts in the front-rear direction, the arrangement can be facilitated without further interference.
  • both the intake port injection valves 101a and 101b and the in-cylinder injection valves 105a and 105b are arranged in the V bank and at the center between the banks of the lower intake introduction portions 68a and 68b.
  • it can be arranged so as to be surrounded by the supercharger 30, the lower intake introduction portions 68a and 68b, and the left and right banks 12a and 12b.
  • the bank angle of the V bank is not set wider, and the full width of the V-type engine can be suppressed.
  • a V-type engine with a reduced overall width can be obtained.
  • both the intake port injection valve and the in-cylinder injection valve are disposed inside the supercharger 30, the lower intake introduction portions 68a and 68b, and the left and right banks 12a and 12b. Even if it is provided, the increase in the total height can be suppressed as much as possible.
  • the left and right banks 12a and 12b are provided with low-pressure delivery pipes 107a and 107b for intake port injection and high-pressure delivery pipes 109a and 109b for in-cylinder injection. Attached to each bank.
  • FIG. 6 shows a plan view of the delivery pipe and the injection valve.
  • High-pressure fuel from a high-pressure fuel pump (not shown) is supplied to one (right side) high-pressure delivery pipe 109a through a high-pressure fuel supply pipe 111, and the other (through a branch pipe 113 branched from the one high-pressure delivery pipe 109a ( To the high pressure delivery pipe 109b on the left side).
  • low-pressure fuel from a low-pressure fuel pump (not shown) is distributed in the middle of the low-pressure fuel supply pipe 115 and supplied to one (right side) low-pressure delivery pipe 107a and the other (left side) delivery pipe 107b.
  • the high-pressure fuel from the high-pressure fuel pump is supplied from the rear end side of the engine 1 as indicated by an arrow E in FIG. Further, the low-pressure fuel from the low-pressure fuel pump is supplied from the front end side of the engine 1 as indicated by an arrow F in FIG. Therefore, since fuel is supplied to the delivery pipe from the opposite side in the front-rear direction, the piping of the fuel supply pipe to the delivery pipe is complicated in order to avoid mutual interference at the fuel supply inlet side. Can be avoided. As a result, it is easy to dispose the intake port injection valve and the in-cylinder injection valve between the V banks.
  • the branch passages 69a, 71a, 73a and 69b, 71b, 73b provided adjacent to each other are connected and integrated by a connecting wall 94 to form a wall surface K1.
  • the enclosed internal space has a tunnel shape, so that it is possible to guide the flow of traveling air by traveling the vehicle, thereby cooling the injector, delivery pipe, etc. of the fuel injection device by the traveling air flow. The improvement of the effect can be expected.
  • the V-type engine can be made compact by arranging the in-cylinder injector and the intake port injector in the V bank below the supercharger. It is effective for application to.

Landscapes

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

Abstract

Un objet de la présente invention est de réduire la taille d'un moteur en V équipé d'un compresseur de suralimentation dans une position située entre les rangées en V et au-dessus de celles-ci, par agencement des injecteurs de cylindre et des injecteurs d'orifice d'admission dans les rangées en V au-dessous du compresseur de suralimentation. Pour ce faire, la présente invention est caractérisée : en ce que des soupapes d'injection d'orifice d'admission (101a) et des soupapes d'injection de cylindre (105a) sont agencées à l'intérieur, tel qu'observé depuis la direction d'un vilebrequin (20), des rangées en V (12a, 12b); en ce qu'elle est pourvue d'un compresseur de suralimentation (30) agencé dans une position située entre les rangées en V et au-dessus de celles-ci, et d'un trajet d'admission (29) qui introduit l'air évacué depuis le compresseur de suralimentation (30) dans les rangées gauche et droite; et en ce que les soupapes d'injection d'orifice d'admission (101a) et les soupapes d'injection de cylindre (105a) des rangées gauche et droite sont agencées de sorte à être enserrées par le compresseur de suralimentation (30), le trajet d'admission (29) et les rangées gauche et droite, (12a, 12b).
PCT/JP2014/084343 2014-12-25 2014-12-25 Moteur en v WO2016103403A1 (fr)

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JP2016565761A JPWO2016103403A1 (ja) 2014-12-25 2014-12-25 Ｖ型エンジン
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JP2002295343A (ja) * 2001-03-30 2002-10-09 Honda Motor Co Ltd 多気筒内燃機関の吸気装置
JP2005009380A (ja) * 2003-06-18 2005-01-13 Mitsubishi Motors Corp Ｖ型エンジン
JP2005054655A (ja) * 2003-08-04 2005-03-03 Mitsubishi Motors Corp Ｖ型エンジン
JP2006329151A (ja) * 2005-05-30 2006-12-07 Toyota Motor Corp 内燃機関の燃料系統の異常判定装置
JP2007315286A (ja) * 2006-05-25 2007-12-06 Toyota Motor Corp 内燃機関
JP2008075509A (ja) * 2006-09-20 2008-04-03 Yamaha Motor Co Ltd エンジンの吸気制御装置
JP2008537053A (ja) * 2005-04-19 2008-09-11 アウディー アーゲー 内燃機関用過給装置モジュール
JP2011043105A (ja) * 2009-08-21 2011-03-03 Daikyonishikawa Corp 樹脂製インテークマニホールド
JP2012097566A (ja) * 2010-10-29 2012-05-24 Daihatsu Motor Co Ltd 樹脂製インテークマニホールド
JP2014214627A (ja) * 2013-04-23 2014-11-17 トヨタ自動車株式会社 内燃機関の制御装置

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DE19840616C1 (de) * 1998-09-05 1999-12-02 Daimler Chrysler Ag Brennkraftmaschine in V-Bauweise mit einem mechanisch angetriebenen Lader
EP1860319B1 (fr) * 2005-03-18 2019-04-24 Toyota Jidosha Kabushiki Kaisha Moteur à injection de carburant bivalente
GB0520415D0 (en) * 2005-10-07 2005-11-16 Ford Global Tech Llc A v type internal combustion engine
US9103304B2 (en) * 2012-05-30 2015-08-11 GM Global Technology Operations LLC Integrated intake manifold and compressor

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002295343A (ja) * 2001-03-30 2002-10-09 Honda Motor Co Ltd 多気筒内燃機関の吸気装置
JP2005009380A (ja) * 2003-06-18 2005-01-13 Mitsubishi Motors Corp Ｖ型エンジン
JP2005054655A (ja) * 2003-08-04 2005-03-03 Mitsubishi Motors Corp Ｖ型エンジン
JP2008537053A (ja) * 2005-04-19 2008-09-11 アウディー アーゲー 内燃機関用過給装置モジュール
JP2006329151A (ja) * 2005-05-30 2006-12-07 Toyota Motor Corp 内燃機関の燃料系統の異常判定装置
JP2007315286A (ja) * 2006-05-25 2007-12-06 Toyota Motor Corp 内燃機関
JP2008075509A (ja) * 2006-09-20 2008-04-03 Yamaha Motor Co Ltd エンジンの吸気制御装置
JP2011043105A (ja) * 2009-08-21 2011-03-03 Daikyonishikawa Corp 樹脂製インテークマニホールド
JP2012097566A (ja) * 2010-10-29 2012-05-24 Daihatsu Motor Co Ltd 樹脂製インテークマニホールド
JP2014214627A (ja) * 2013-04-23 2014-11-17 トヨタ自動車株式会社 内燃機関の制御装置

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