JP6500434B2 - V-type engine - Google Patents

Description

  The present disclosure relates to a V-type engine provided with a direct injector.

  Patent Document 1 discloses a V-type engine provided with a direct injector. A V-type engine is attached to each bank by a V-type cylinder block in which a plurality of cylinders are alternately arranged to the left and right in banks arranged in a V-type, and each cylinder obliquely upward from the combustion chamber to the cylinder axis And a cylinder head having an intake port extending inside the bank. In addition, the cylinder head is provided with a direct injector that directly injects fuel into the combustion chamber inside the bank, which is the cylinder radial direction outer side of the intake port.

Patent No. 4495211

However, in the direct injector in which the electrical connector is attached to the body radially from the outside, the electrical connector interferes between the direct injector in one bank and the direct injector in the other bank, and the electrical connector is attached to the direct injector You may not be able to
In view of the above situation, the present invention avoids the interference of the electrical connector between the direct injector of one bank and the direct injector of the other bank in the limited space between the banks, thereby making the electrical connector to the direct injector It is an object of the present invention to provide a V-type engine that can be mounted.

  According to the present invention, a plurality of cylinders are alternately arranged on the left and right sides in a V-shaped bank, and the cylinders are attached to each bank, and each cylinder is inclined to the axis of the cylinder from the combustion chamber A cylinder head having an intake port extending to the inside of the upper bank, and a plurality of direct injectors disposed at positions radially outward of the intake port for each cylinder and directly injecting fuel into the combustion chamber; The plurality of direct injectors project radially outward from the body portion, and a first connector mounting portion on which a first electrical connector is mounted is arranged so that the heights of the banks are different among the banks. It features.

  According to the present invention, the plurality of direct injectors project radially outward from the body portion, and the first connector mounting portions on which the first electrical connectors are mounted are arranged to have different heights between the banks. Therefore, in the limited space between the banks, the interference of the first electrical connector is avoided between the direct injector of one bank and the direct injector of the other bank, and the first electrical connector is attached to the direct injector. be able to.

In one aspect of the present invention, in the first connector mounting portion, a mounting direction of the first electrical connector is a radial direction of the direct injector.
In this way, the first electrical connector can be attached to the first connector mounting portion from the radial outer side of the direct injector. Also, the first electrical connector can be attached to and detached from the first connector mounting portion radially outward of the direct injector.

In one aspect of the present invention, the banks are offset in the same direction as the rotational direction of the crankshaft, and direct injectors disposed in a second bank lower than the first bank are disposed in the first bank. It is located lower than the direct injector.
In this way, the direct injectors arranged in the second bank are arranged at a lower position than the direct injectors arranged in the first bank. Interference of the first electrical connector is avoided between the direct injector arranged in the bank and the direct injector arranged in the second bank, and the direct injector can be mounted with the first electrical connector.

In one aspect of the present invention, in the plurality of direct injectors, the first connector mounting portion of the first bank faces obliquely backward, and the first connector mounting portion of the second bank is obliquely forward Turn.
In this way, the first connector mounting portion faces obliquely backward in the first bank and the first connector mounting portion slants forward in the second bank lower than the first bank. First injector of the direct injector disposed in the first bank, avoiding interference of the first electrical connector between the direct injector disposed in the second bank and the direct injector disposed in the second bank The first electrical connector can be attached to the attachment portion, and the first electrical connector can be attached to the first connector attachment portion of the direct injector disposed in the second bank.

In one aspect of the present invention, each of the cylinders is provided with a plurality of port injectors that are disposed on the same side as the direct injector with respect to the intake port and inject fuel into the intake port, and the plurality of ports The injector protrudes radially outward from the body portion, and a second mounting portion to which a second electrical connector is mounted is disposed toward the outside of the bank.
According to this configuration, the plurality of port injectors project radially outward from the body portion, and the second connector mounting portion on which the second electrical connector is mounted is disposed toward the outside of the bank. Interference of the second electrical connector is avoided between the port injectors of the bank and the port injectors of the other bank, and a second electrical connector can be attached to the port injector.

In one aspect of the present invention, in the second connector mounting portion, a mounting direction of the second electrical connector is a diagonally upward direction of the port injector.
In this way, the second electrical connector can be mounted on the second connector mounting portion from the diagonally upward direction of the port injector. In addition, the second connector can be detached from the second connector mounting portion obliquely upward of the port injector.

  As described above, according to the present invention, the interference of the first electrical connector is avoided between the direct injector of one bank and the direct injector of the other bank, and the first electrical connector is attached to the direct injector. can do.

It is the front view seen from the front direction of the crankshaft direction which shows the whole structure of V-type engine which is this embodiment, Comprising: It is the figure which represented a part in cross section. It is a top view which shows the whole structure of the V-type engine shown in FIG. It is sectional drawing which shows the combustion chamber provided in the cylinder head shown in FIG. It is the conceptual diagram which looked at the combustion chamber shown in FIG. 3 from the IV-IV direction. It is sectional drawing which shows the intake port provided in the cylinder head shown in FIG. It is the conceptual diagram which looked at the intake port shown in FIG. 5 from the VI-VI direction. It is a front view which shows the intake system shown in FIG.1 and FIG.2. It is a side view which shows the intake system shown in FIG.1 and FIG.2, Comprising: It is the figure which represented a part in the cross section. It is an enlarged front view which shows the fuel supply system shown in FIG. It is a top view which shows the state which attached the electrical connector to the connector mounting part shown in FIG. It is a front view which shows the direct injector and port injector which were shown in FIG. It is a top view which shows the direct injector and port injector which were shown in FIG.

Hereinafter, preferred embodiments of the engine according to the present invention will be described in detail with reference to the attached drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of the components described as the embodiments or shown in the drawings are not intended to limit the scope of the present invention to this, but are merely illustrative. Absent.
For example, a representation representing a relative or absolute arrangement such as “in a direction”, “along a direction”, “parallel”, “orthogonal”, “center”, “concentric” or “coaxial” is strictly Not only does it represent such an arrangement, but also represents a state of relative displacement with an angle or distance that allows the same function to be obtained.
Further, for example, the expression expressing a shape such as a quadrangular shape or a cylindrical shape not only represents a shape such as a rectangular shape or a cylindrical shape in a geometrically strict sense, but also an uneven portion within the range where the same effect can be obtained The shape including a chamfer and a chamfer etc shall also be expressed.
On the other hand, the expressions "comprising", "having", "having", "including" or "having" one component are not exclusive expressions excluding the presence of other components.

  Further, the direction of the engine described in the present embodiment is based on the driver's seat of an automobile equipped with the engine at the front of the vehicle body. Therefore, in the drawings based on the front in the direction of the crankshaft, the right and left sides are reversed, the left side is referred to as the right side, and the right side is referred to as the left side.

FIG. 1 is a front view seen from the front in the crankshaft direction showing the overall configuration of a V-type engine 1 according to this embodiment, a part of which is shown in cross section, and FIG. 2 is shown in FIG. FIG. 1 is a plan view showing the overall configuration of a V-type engine 1;
As shown in FIG. 1, a V-type engine 1 according to an embodiment of the present invention is configured to include respective devices of an intake system 3 and a fuel supply system 7 in addition to an engine body 10.

[Engine body]
The engine body 10 according to the present embodiment is a 4-cycle V-type six-cylinder SOHC (Single Over Head Camshaft) gasoline engine, and has a bank angle (bank narrow angle) of 60 degrees.
As shown in FIG. 1, the engine body 10 includes a cylinder block 11 in which cylinder rows (banks) 12A and 12B are formed in a V-shape, and cylinder heads 2A and 2B joined on the left and right banks 12A and 12B. And a crankcase 13 joined below the cylinder block 11.

  As shown in FIG. 2, in the cylinder block 11 formed in a V-shape, the left and right banks 12A and 12B are offset in the front-rear direction (crankshaft direction), and the bank 12A on the right (left in FIG. 2) is on the front side. The left side (right side in FIG. 2) bank 12B is located on the rear side. Further, as shown in FIG. 1, three cylinders 14A and 14B are arranged in parallel in each of the left and right banks 12A and 12B (see FIG. 12), and one crankshaft common to the lower regions of these Reference numeral 15 is rotatably supported by the crankcase 13. The three cylinders 14A and 14B juxtaposed to the left and right banks 12A and 12B are such that the cylinder 14A on the foremost side is the most cylinder # 1 in the right bank 12A, and thereafter, on the rear side of the cylinder block 11 Directly to the left and right alternately, the second cylinder # 2, the third cylinder # 3, the fourth cylinder # 4, the fifth cylinder # 5, the sixth cylinder # 6 (see FIG. 12), and the spark plug 22 described later (see FIG. 3) ) Are fired in this order.

  As shown in FIG. 1, the cylinders 14A and 14B are formed in a cylindrical shape, and the pistons 16 reciprocating in the directions of the axis lines L3 and L4 are accommodated in the cylinders 14A and 14B. The piston 16 is formed in a cylindrical shape whose head is closed, and a pin hole penetrating in the radial direction is provided in the body of the piston 16. Further, one end (small end (not shown)) of the connecting rod 17 is accommodated in the body of the piston 16, and the small end of the connecting rod 17 is connected to the piston 16 by the piston pin 162 inserted into the pin hole. .

  The crankshaft 15, together with the connecting rod 17, converts the reciprocating motion (downward motion) of the piston 16 into rotational motion, and a crank pin (not shown) parallel to an axis passing through the rotation center of the crankshaft 15 have. The other end (large end (not shown)) of the connecting rod 17 is connected to the crank pin. Thereby, the reciprocating motion of the piston 16 is converted to the rotational motion of the crankshaft 15.

  FIG. 3 is a cross-sectional view showing a combustion chamber provided in the cylinder head shown in FIG. 1, and FIG. 4 is a conceptual view of the combustion chamber shown in FIG. 3 viewed from the IV-IV direction. 5 is a cross-sectional view showing an intake port provided in the cylinder head shown in FIG. 1, and FIG. 6 is a conceptual view of the intake port shown in FIG. 5 as viewed from the VI-VI direction.

  As shown in FIGS. 3 and 5, each cylinder head 2A, 2B is provided with a combustion chamber 21 at a position corresponding to the cylinders 14A, 14B formed in the cylinder block 11, and as shown in FIG. A spark plug 22 is attached to the combustion chamber 21. The spark plug 22 ignites and burns the air-fuel mixture supplied to the combustion chamber 21 and the air-fuel mixture mixed in the combustion chamber 21 or the cylinders (cylinders 14A and 14B), and each cylinder head 2A according to the present embodiment. , 2B are disposed at positions inside the left and right banks 12A, 12B.

  Further, as shown in FIG. 5, each combustion chamber 21 is provided with two intake ports 23 and two exhaust ports 24. The two intake ports 23 provided in each combustion chamber 21 are aligned in a row along the arrangement direction of the cylinders 14A and 14B inside the banks 12A and 12B, and open to the combustion chambers 21. Similarly, the two exhaust ports 24 provided in each combustion chamber 21 are aligned in a row along the arrangement direction of the cylinders 14A and 14B outside the left and right banks 12A and 12B, and open to each combustion chamber 21. .

  A valve seat (seating surface) 231 is provided in each of the two intake ports 23 provided in each combustion chamber 21 and is opened and closed by an intake valve 25 provided for each intake port 23. Similarly, valve seats (seating surfaces) 241 are respectively provided in the two exhaust ports 24 provided in each combustion chamber 21 and are opened and closed by exhaust valves 26 provided for each of the exhaust ports 24.

Further, an intake port 27 and an exhaust port 28 are provided in each of the combustion chambers 21 in the cylinder heads 2A and 2B.
The intake port 27 passes through the axis lines L3 and L4 of the cylinders 14A and 14B, is provided along a direction (hereinafter referred to as "intake and exhaust direction") orthogonal to the arrangement direction of the cylinders 14A and 14B, and opens in the combustion chamber 21. It communicates with the two intake ports 23. The intake port 27 has an upstream port 271 and a downstream port 272.

  As shown in FIG. 6, the upstream port 271 is a flow path provided one for two intake ports 23 provided in each combustion chamber 21, and is provided on the upstream side of the intake port 27, and its cross section An axis N passing through the center is disposed in a plane passing through the axes L3 and L4 of the cylinders 14A and 14B. Then, the upstream port 271 opens in the horizontal plane inside the cylinder heads 2A and 2B (see FIG. 5). The upstream port openings 273 of the cylinder heads 2A and 2B are long ovals in the front-rear direction, and a flange (port injector mounting seat) 275 having a flat joint surface 274 is provided around it (FIG. 5) reference).

  As shown in FIG. 6, one downstream port 272 is a flow path provided for one intake port 23, and is provided to branch from the upstream port 271 on the downstream side of the upstream port 271. There is. Therefore, the inlets of the two downstream ports 272 are provided at the outlet of the upstream port 271, and the outlet of the downstream port 272 is provided at the inlet of the valve seat 231 provided at the inlet 23.

  Further, as shown in FIG. 5, the intake port 27 has an arc-shaped portion 276 which is downwardly convex in a central region of the intake port 27 which is upstream of the valve seat 231. The arc-shaped portion 276 is for curving the axis N passing through the cross-sectional center of the intake port 27, thereby lengthening the intake passage, and the air injected from the port injector 91 described later flows through the intake port 27. Well mixed into.

  The exhaust port 28 is provided along the intake and exhaust directions on the opposite side of the intake port 27 and the combustion chamber 21, and communicates with two exhaust ports 24 opened to the combustion chamber 21. The exhaust port 28 has an upstream port 281 and a downstream port (not shown). The upstream port 281 is a flow path provided one for each of the two exhaust ports 24 provided in each combustion chamber 21, and is provided on the upstream side of the exhaust port 28. The downstream port is a channel provided one for the two exhaust ports 24 provided in each combustion chamber 21 so that the two upstream ports 281 merge on the downstream side of the two upstream ports 281. , And the axis passing through the center thereof is disposed in a plane passing through the axes of the cylinders 14A, 14B. Thus, the inlets of the two upstream ports 281 are provided at the outlet of the valve seat 241 provided at the exhaust port 24, and the outlets of the two upstream ports 281 are provided at the inlet of the downstream port.

By the way, as shown in FIG. 1, the engine body 10 according to the present embodiment adopts an offset crank structure.
In a general V-type engine (engines in which the left and right banks are not offset in the same direction as the rotation direction of the crankshaft), the axes L1 and L2 of the cylinders 14A and 14B in the left and right banks 12A and 12B are the crankshaft 15 , And the left and right banks are at positions shown by two-dot chain lines in FIG.
On the other hand, the engine main body 10 (V-type engine 1) according to the present embodiment adopting the offset crank structure has left and right banks while maintaining the distance from the center P of the crankshaft 15 to the upper surfaces of the cylinder heads 2A and 2B. The axis lines L1 and L2 of the cylinders 14A and 14B in 12A and 12B are moved in parallel with the center P of the crankshaft 15 in the same direction as the rotational direction of the crankshaft 15 (the arrow E direction). Thereby, the axis lines L1 and L2 of the cylinders 14A and 14B are offset to L3 and L4 while maintaining the bank angles of the left and right banks 12A and 12B, and the axis lines L1 and L2 of the cylinders 14A and 14B are δ (offset amount Move only).

Therefore, the height of the right bank (left bank in FIG. 1) 2A is higher than that of the left bank (right bank in FIG. 1) 2B, causing a difference in height, and the right bank 12A The same height difference (H2-H1) is also generated at the inlet opening of the intake port 27 in the left bank 12B.
Thus, the engine body 10 according to the present embodiment is arranged in a relationship in which the right bank 12A is before the left bank 12B and the right bank 12A is higher than the left bank 12B.

  In the upper region of each cylinder head 2A, 2B, a valve operating mechanism such as a cam shaft (not shown) or a rocker arm (not shown) is disposed, and a rocker cover 29 is attached to cover them. ing. And the intake valve 25 and the exhaust valve 26 which were mentioned above are each opened and closed at a predetermined timing via a camshaft and a rocker arm.

[Intake system]
FIG. 7 is a front view showing the intake system 3 shown in FIG. 1 and FIG. FIG. 8 is a side view showing the intake system 3 shown in FIG. 1 and FIG. 2, and is a view showing a part in cross section.
The intake system 3 according to the present embodiment supercharges air to an intake port 27 provided for each combustion chamber 21 in the cylinder heads 2A and 2B of the left and right banks 12A and 12B.

  As shown in FIG. 7, the intake system 3 is joined onto intake manifolds 4A and 4B joined to the cylinder heads 2A and 2B of the left and right banks 12A and 12B and on the left and right intake manifolds 4A and 4B. It comprises the intercoolers 5A, 5B, the outlet housing 31 bridged to the left and right intercoolers 5A, 5B, and the supercharger 6 suspended to the outlet housing 31.

  The supercharger 6 is driven by power transmitted from the crankshaft 15 (see FIG. 1) to deliver air (intake air), and is between the left and right banks 12A and 12B and on the left and right. It is attached above locker cover 29. Thus, the supercharger 6 is located above the crankshaft 15, and the lower surface of the supercharger 6 is positioned above the upper surface of the rocker cover 29.

The supercharger 6 boosts the air pressure (intake pressure) supplied to the engine body 10 by extruding and discharging the supplied air (intake air) downstream, and the supercharger 6 according to the present embodiment It consists of a single leaf roots supercharger.
The supercharger 6 is rotatably supported by the housing 61 and the housing 61, and is housed in the input rotary shaft 62 (see FIG. 8) projecting forward of the housing 61, and housed in the housing 61. And a pair of rotors 63A and 63B that rotate in opposite directions.

  As shown in FIG. 8, the housing 61 includes a housing body 61A, an inlet housing 61B joined to the rear surface of the housing body 61A, and a bearing housing 61C joined to the front surface of the housing body 61A. There is.

  As shown in FIG. 7, the housing main body 61A has a housing space in which the pair of rotors 63A and 63B are housed in a mutually meshed state. The housing space is opened in the rear surface and the upper surface front area of the housing main body 61A, and the air sucked from the rear surface opening passes between the pair of rotors 63A and 63B housed in the housing space, and the upper surface front area opening 61A1 8). Further, the housing main body 61A is provided with a recess in the upper surface thereof in which the upper surface front area opening 61A1 is formed. The recess is formed in a rectangular shape whose lateral direction is the lateral direction and whose longitudinal direction is the longitudinal direction, and has a flat bonding surface around it.

  As shown in FIG. 8, the inlet housing 61 </ b> B has an intake passage through which the air sucked into the housing body 61 </ b> A passes. The intake passage opens to the left side surface and the front surface of the inlet housing 61B, and the air taken in from the side opening passes through the intake passage and is taken into the housing main body 61A from the front opening.

  Further, as shown in FIG. 2, a throttle body 64 is provided on the right side surface (left side surface in FIG. 2) of the inlet housing 61B. The throttle body 64 has a cylindrical suction port 64A on the side surface, and a throttle valve (not shown) is provided in the inside thereof. Thus, the amount of intake of air is adjusted through the throttle valve, and air (intake air) is introduced from the intake port 64A.

  As shown in FIG. 2, the bearing housing 61C has a cylindrical bearing portion on the front right side (left side in FIG. 2) of the housing body 61A, and the input rotary shaft 62 is rotatably supported. Thus, the input rotary shaft 62 is disposed on the right side of the bank 12A.

  The input rotary shaft 62 is an input shaft that receives power from the crankshaft 15 and is rotated. As shown in FIG. 1, the input rotary shaft 62 is provided at the front end of the pulley 67 with the pulley 67 provided at its front end. A belt 68 is wound around a pulley (not shown). Thus, the rotation of the crankshaft 15 is transmitted from the crankshaft 15 to the input rotary shaft 62 via the belt 68, and power is transmitted from the crankshaft 15 to the input rotary shaft 62. The transmission of power from the crankshaft 15 to the input rotary shaft 62 is not limited to the power transmission means in which the pulley 67 and the belt 68 are combined. For example, even if a power transmission means in which a sprocket and a chain are combined is adopted. Good.

  As shown in FIG. 7, the pair of rotors 63A and 63B are accommodated in the housing main body 61A, and are engaged with each other in the housing main body 61A. The rotation axis of one rotor 63A (hereinafter referred to as "drive rotor 63A") of the pair of rotors 63A and 63B is constituted by the input rotation shaft 62, and the rotation of the input rotation shaft 62 causes the drive rotor 63A to become the input rotation shaft 62. It rotates in the same direction as the rotation direction. Then, the other rotor 63B (hereinafter referred to as "followed rotor 63B") meshed with the drive rotor 63A follows the drive rotor 63A and rotates in the opposite direction to the rotation direction of the drive rotor 63A. As a result, the air in the space closed by the drive rotor 63A, the driven rotor 63B, and the housing main body 61A is pushed out and discharged from the upper surface front area opening 61A1 of the housing main body 61A.

  The outlet housing 31 distributes the air discharged from the supercharger 6 to the left and right banks 12A and 12B, and is formed of a light metal such as aluminum or a synthetic resin such as FRP or a prepreg. As a result, the weight of the outlet housing 31 can be reduced, and further, the outlet housing 31 can be easily manufactured by casting or integrally molding the light metal with synthetic resin.

  The outlet housing 31 is provided to straddle the left and right banks 12A and 12B at the center in the front-rear direction of the left and right banks 12A and 12B. The outlet housing 31 is formed in a rectangular shape in a rectangular shape in which the horizontal direction is the longitudinal direction and the longitudinal direction is the lateral direction and the height direction is lowered in a rectangular shape in plan view, and the upper surface is gradually lowered from the rear toward the front. (See Figure 8).

  The outlet housing 31 also has a distribution passage 32 for distributing the air discharged from the supercharger 6 to the left and right banks 12A and 12B. The distribution passage 32 is formed along the outer shape of the outlet housing 31, and its ceiling surface 32A is inclined so as to gradually lower from the rear to the front, similarly to the upper surface of the outlet housing 31. Thereby, the air (intake air) discharged from the supercharger 6 obliquely collides with the ceiling surface 32A of the distribution passage 32, so the area where the intake air hits the ceiling surface 32A becomes large, and the right angle with the ceiling surface 32A The collision noise can be reduced more than in the case of collision. That is, the radiation noise due to the discharge pressure from the supercharger 6 can be reduced.

  Further, the distribution passage 32 is opened at the center of the lower surface of the outlet housing 31 in the left-right direction. The central opening 33 of the outlet housing 31 is formed the same as the recess provided in the housing main body 61A (a rectangular shape whose lateral direction is the lateral direction and whose longitudinal direction is the longitudinal direction), and has a flat joint surface around it. doing. The joint surface of the housing body 61A is joined to this joint surface, and the supercharger 6 is attached to the outlet housing 31 by six bolts. Thus, the supercharger 6 is suspended at the center of the outlet housing 31 in the left-right direction.

  Further, the distribution passage 32 is opened on the lower surface of the outlet housing 31 on both sides in the left-right direction. The left and right openings 34A, 34B of the outlet housing 31 are formed in a rectangular shape smaller than the central opening 33, and a flange having a flat joint surface is provided around it.

  Further, the distribution passage 32 has a weir 32A1 that protrudes downward on a ceiling surface that is the center in the left-right direction. The weir 32A1 is provided along the front-rear direction, and divides the distribution passage 32 into left and right. Therefore, the air introduced from the central opening 33 is distributed to the right passage and the left passage at the weir 32A1, the air distributed to the right is discharged from the right opening 34A, and the air distributed to the left is the left opening 34B. It is discharged from. As a result, the distribution of the air (intake air) discharged from the supercharger 6 to the left and right banks 12A and 12B is improved, and the intake air is uniformly supplied to the left and right banks 12A and 12B.

  The distribution passage 32 is opened at the rear surface of the outlet housing 31 at the center in the left-right direction. As shown in FIG. 8, the rear surface opening of the outlet housing 31 is an opening communicating with a bypass passage 691 described later, is formed in a circular shape, and has a flat joint surface around it. Then, the bypass housing 69 is joined to this joint surface, and the bypass housing 69 is attached to the outlet housing 31 by two bolts.

  The bypass housing 69 has a bypass passage 691 that bypasses the air discharged from the supercharger 6 to the inlet housing 61B. The bypass passage 691 is open to the front and lower surfaces of the bypass housing 69. The front opening of the bypass housing 69 is formed substantially the same as the rear opening of the outlet housing 31 and is in communication with the rear opening of the outlet housing 31 as described above.

  A bypass valve 66 is provided on the lower surface of the bypass housing 69. The lower surface of the bypass valve 66 is connected to the inlet housing 61 B, and the bypass passage 691 and the intake passage are in communication via the bypass valve 66. As a result, part of the air (intake air) discharged from the supercharger 6 to the outlet housing 31 is returned to the intake passage via the bypass passage 691, and the discharge air pressure (discharge intake pressure) is adjusted. The return air pressure (return intake pressure) is adjusted by the bypass valve 66.

  As shown in FIG. 7, the left and right intercoolers 5A and 5B are for discharging the air discharged from the supercharger 6 and distributed to the left and right, respectively, and are both left and right sides of the supercharger 6 and Above the left and right locker covers 29, the left and right banks 12A and 12B are separately provided.

  The left and right intercoolers 5A and 5B have the same structure on the left and right, and include a case 51, an intercooler core 52 accommodated in the case 51, and a plurality of collars 55 disposed around the case 51. Is configured.

  The case 51 accommodates the intercooler core 52, and is formed of a synthetic resin such as FRP or a prepreg, or a light metal such as aluminum. As a result, the weight of the case 51 can be reduced, and further, the case 51 can be easily manufactured by integrally molding the case 51 with a synthetic resin or casting it with a light metal.

  The case 51 has a rectangular shape in a plan view rectangular shape with the left-right direction as the lateral direction and the front-rear direction as the longitudinal direction, and the intake passage through which the air supplied from the outlet housing 31 to the intake manifolds 4A and 4B passes therethrough. Have. The intake passage opens in the upper surface and the lower surface of the case 51.

  The upper surface opening of the case 51 is formed to be the same as the left and right openings 34A and 34B of the outlet housing 31 (a rectangular shape having the horizontal direction as the short direction and the front and rear direction as the longitudinal direction) Have. And the joint surface of the flange provided in the outlet housing 31 is joined to this joint surface. Further, the lower surface opening of the case 51 is formed to be the same as the upper surface opening (a rectangular shape having the lateral direction as the short direction and the longitudinal direction as the longitudinal direction), around which a flange having a flat bonding surface is provided .

  The intercooler core 52 is for cooling air flowing through the intake passage, and is provided so that a pipe through which cooling water supplied from the outside of the case 51 and discharged to the outside of the case 51 passes is penetrated. ing. The inlet side 54A (see FIG. 1) of the pipe is disposed on the upper side in the front of the case 51, and the outlet side 54B (see FIG. 1) is disposed on the lower side in the front of the case 51. Thus, air bubbles contained in the cooling water are discharged upward.

  The plurality of collars 55 transmit load from the outlet housing 31 to the intake manifolds 4A and 4B to protect the case 51, and the plurality of collars 55 according to the present embodiment are configured of six pieces. The flange 51 and the outlet housing 31 are disposed at substantially the same intervals.

  Each of the six collars 55 is a cylindrical cylinder through which a bolt is inserted, and has disk-shaped flanges on both sides thereof. The height of the collar 55 is set to be the same as the height from the upper surface of the flange of the case 51 to the lower surface of the outlet housing 31 or higher by the amount of the gasket (not shown).

  Each of the six bolts penetrates the flange of the outlet housing 31, the collar 55, and the flange of the case 51, and is screwed into a female screw provided on a flange of the intake manifold 4A, 4B described later. , Intercoolers 5A, 5B and intake manifolds 4A, 4B are integrated. Thus, the load is transmitted from the outlet housing 31 to the intake manifolds 4A and 4B, and the case 51 is protected.

  The left and right intake manifolds 4A and 4B are for distributing air (intake air) to a plurality of cylinders (three cylinders 14A and 14B) provided in the left and right banks 12A and 12B, and are made of a light metal such as aluminum Or it is formed by synthetic resins, such as FRP and a prepreg. Thereby, weight reduction of each intake manifold 4A, 4B on either side is attained, and also manufacture can be made easy by integrally molding each intake manifold 4A, 4B on either side with a light metal, or synthetic resin. .

  The left and right intake manifolds 4A and 4B according to the present embodiment further support the supercharger 6, the outlet housing 31, and the left and right intercoolers 5A and 5B, and the left and right intake manifolds 4A, 4B is integrally formed, and provided between the lower surfaces of the intercoolers 5A, 5B and the joint surfaces of the cylinder heads 2A, 2B, respectively.

By the way, as described above, the engine body 10 according to this embodiment adopts the offset crank structure, and the height of the right bank 12A (the left bank in FIG. 2) is the left bank 12B (the right in FIG. 2). The height difference between the right bank 12A and the left bank 12B is the same, and the difference in height is also generated at the inlet opening of the intake port 27.
Therefore, in each of the left and right intake manifolds 4A and 4B according to the present embodiment, the mounting height (inlet opening of the intake port 27) is the same height difference (H2-H2) between the right bank 12A and the left bank 12B. ) Has occurred.

  Thus, in the left and right intake manifolds 4A and 4B according to the present embodiment, the intake manifold 4A (hereinafter referred to as "right intake manifold 4A") on the right bank 12A (left bank in FIG. 7) is the left bank. The supercharger 6 which is set shorter than the intake manifold 4B (hereinafter referred to as "left intake manifold 4B") on the side of 12B (the right bank in FIG. 7) and which is suspended by the outlet housing 31 and the outlet housing 31 takes a horizontal posture. . As a result, the support rigidity of the right intake manifold 4A becomes higher than the support rigidity of the left intake manifold 4B.

  In addition, since the input rotary shaft 62 (see FIG. 2) is disposed on the right side of the bank 12A, the side with high support rigidity (right intake manifold 4A side) located on the front side of the engine body 10 (bank on the right) 12A), and the vibration of the supercharger 6 can be suppressed.

  The left and right intake manifolds 4A and 4B are curved along the outer shape of the rocker cover 29 from the left and right intercoolers 5A and 5B toward the left and right banks 12A and 12B, respectively. And each intercooler 5A, 5B on either side is supported. Further, each of left and right intake manifolds 4A, 4B has a surge portion facing the joint surface of intercoolers 5A, 5B, and is branched from the surge portion toward each intake port provided in each of left and right cylinder heads 2B. It has a branch passage.

  The surge portion opens to the joint surface of the intercoolers 5A and 5B, and each branch passage opens to each joint surface joined to each intake port 27. The surge portion openings of the left and right intake manifolds 4A and 4B are formed in the same manner as the lower surface opening of the case 51 (rectangular shape having the horizontal direction as the lateral direction and the front and rear direction as the longitudinal direction) A flange is provided.

  Then, the joint surfaces of the flanges provided to the intercoolers 5A and 5B are joined to the joint surfaces, and as described above, each of the six bolts corresponds to the flange of the outlet housing 31, the collar 55, and the flange of the case 51. The outlet housing 31, the intercoolers 5A and 5B, and the intake manifolds 4A and 4B are integrated with a female screw provided through a flange of the intake manifolds 4A and 4B.

  The intake port joint surface openings of the left and right intake manifolds 4A and 4B are formed identical to the upstream port openings of the cylinder heads 2A and 2B (long oval in the front-rear direction), and have flat joint surfaces around them A flange is provided. The joint surface is joined to the joint surface provided in the cylinder heads 2A and 2B, and four bolts pass through the flanges of the intake manifolds 4A and 4B for each of the left and right banks 12A and 12B, and the cylinder head The left and right intake manifolds 4A and 4B, in which the outlet housing 31 and the intercoolers 5A and 5B are integrated with each other by being screwed into female screws provided on the flanges 2A and 2B, are attached to the cylinder heads 2A and 2B. .

  Further, each of the left and right intake manifolds 4A and 4B has a connecting wall between the adjacent branch passages. The connecting wall mutually connects adjacent branch passages, closes between the adjacent branch passages, and forms a tunnel-like space between the left and right banks 12A and 12B. Further, a reinforcing rib is formed on the wall surface of the connection wall. As a result, the insides of the left and right intake manifolds 4A, 4B are protected by the connecting walls of the left and right intake manifolds 4A, 4B, and the pipes of the fuel injection devices 8, 9 arranged inside the intake manifolds 4A, 4B (high pressure The safety of the delivery pipes 82A, 82B, low pressure delivery pipes 92A, 92B, etc. and parts (direct injectors 81, port injectors 91, etc.) is secured. Furthermore, since the connection wall forms a tunnel-like space between the left and right banks 12A and 12B, both side walls of the connection wall also have a function of guiding the air flowing in the tunnel-like space. The cooling effect of the pipes and parts of the fuel injection devices 8 and 9 disposed inside the respective intake manifolds 4A and 4B can also be expected.

  Further, each of the left and right intake manifolds 4A, 4B has a left and right connecting part at the lower end. The left and right connecting parts connect the lower ends of the left and right intake manifolds 4A and 4B so as to bridge each other. The left and right connecting portions may be provided at a plurality of places at intervals in the front-rear direction on both sides or in the front-rear direction, and may be provided on the front so as to constitute a bottom wall. Thereby, the rigidity of each intake manifold 4A, 4B on either side can be raised further.

  As described above, in the intake system 3 according to this embodiment, the supercharger 6 includes the outlet housing 31, the left and right intercoolers 5A and 5B, and the left and right intake manifolds 4A, It is disposed inside the closed cross-sectional structure surrounded by 4B. As a result, the rigidity of the suspension support structure of the supercharger 6 is further improved, and stable support is possible.

  Further, since the outlet housing 31, the left and right intercoolers 5A and 5B, and the left and right intake manifolds 4A and 4B can be assembled separately as a separate structure, the fuel injection can be performed inside the left and right banks. Even if it is a structure which accommodates piping and parts of the apparatuses 8 and 9, it can assemble easily.

  Further, since the outlet housing 31, the left and right intercoolers 5A and 5B, and the left and right intake manifolds 4A and 4B are separately configured, the right bank (high bank) 12A side and the left bank (low bank) 12B The difference in height on the side can be easily coped with by simply changing the heights of the left and right intake manifolds 4A and 4B, and the left and right intercoolers 5A and 5B can be accommodated in the left and right banks 12A and 12B. Can be shared.

  Further, since the outlet housing 31 and the case 51 of the left and right intercoolers 5A and 5B are formed of rigid resin or light metal, weight reduction is possible, and the weight load on the left and right intake manifolds 4A and 4B is reduced. . Thus, the durability of each of the left and right intake manifolds 4A and 4B is improved. Furthermore, the weight reduction of the intake system 3 lowers the center of gravity of the V-type engine 1, which contributes to the improvement of the motion performance of the vehicle (prevention of understeer).

  A sound absorbing material may be disposed between the supercharger 6 and the components (outlet housing 31, left and right intercoolers 5A, 5B, and left and right intake manifolds 4A, 4B) constituting the closed cross-sectional structure. . In this way, the noise emitted from the supercharger 6 is reduced, and the load of the supercharger 6 on the fuel system component in the event of a collision can be reduced.

  In the above-described intake system, the supercharger 6 is described as being suspended from the flat rectangular parallelepiped outlet housing 31 extending in the left and right bank directions. However, the supercharger 6 may not necessarily be suspended. For example, they may be mounted on and fixed to the left and right intercoolers 5A and 5B.

[Fuel supply system]
FIG. 9 is a front view showing the in-cylinder injection device and the port injection device shown in FIG. 1, and FIG. 10 is a plan view showing a state in which the electrical connector is attached to the connector attachment portion shown in FIG. FIG. 11 is a front view showing the direct injector and the port injector shown in FIG. FIG. 12 is a plan view showing the direct injector and the port injector shown in FIG.
The fuel supply system according to the present embodiment injects fuel into an in-cylinder injection system that directly injects fuel into the combustion chamber 21 provided for each of the cylinders 14A and 14B and an intake port 27 provided for each of the combustion chambers 21. It has two fuel injection devices 8 and 9 of a port injection system.

  As shown in FIG. 9, the fuel injection device 8 of the in-cylinder injection system (hereinafter referred to as "in-cylinder injection device 8") is a direct injector 81 provided for each cylinder 14A, 14B in each of the left and right banks 12A, 12B. , High-pressure delivery pipes 82A, 82B provided commonly to the plurality of direct injectors 81 in the left and right banks 12A, 12B, and a high-pressure fuel pump (not shown) for supplying fuel to the high-pressure delivery pipes 82A, 82B. , Is configured.

  The direct injector 81 is for injecting fuel directly into the combustion chamber 21 provided for each of the cylinders 14A and 14B, and as shown in FIG. It is arranged along the exhaust direction. Specifically, in the lower region of the downstream port 272 where the intake port 27 is branched into two, the central axis of the direct injector 81 is disposed in a plane passing through the axis L3 (L4) of the cylinder 14A (14B) Be done. Thus, the direct injectors 81 are disposed orthogonal to the arrangement direction of the cylinders 14A (14B), and are disposed so as to be staggered in plan view inside the respective banks 12A and 12B on the left and right.

  As shown in FIG. 11, the direct injector 81 has a small diameter nozzle portion 81a, a trunk portion 81b larger in diameter than the nozzle portion 81a, and a delivery pipe connection larger in diameter than the nozzle portion 81a and smaller in diameter than the trunk portion 81b. It has a portion (not shown) and a connector mounting portion 81d (first connector mounting portion) provided in the radially outward direction of the trunk portion 81b. At the tip of the nozzle portion 81a, an injection hole (not shown) for injecting the fuel supplied from the high pressure fuel pump so as to spread in a conical shape is provided. A control unit (not shown) for controlling the injection amount and injection timing of the fuel is accommodated in the body portion 81b, the high pressure delivery pipes 82A and 82B are connected to the delivery pipe connection portion, and the high pressure fuel pipe is connected to the high pressure delivery pipe. Fuel is supplied through 82A and 82B.

  Further, an electrical connector 83 (first electrical connector) is attached to the connector attachment portion 81 d. In the connector mounting portion 81d, the mounting direction of the electrical connector 83 is the radial direction of the direct injector 81 (body 81b), the electrical connector 83 is mounted on the connector mounting portion 81d from the radial outside, and the radial direction from the connector mounting portion 81d The electrical connector 83 is attached and detached to the outside.

  As shown in FIG. 10, the direct injectors 81 are arranged such that the connector mounting portions 81d are alternately diagonally parallel in plan view between the left and right banks 12A and 12B. Thus, in the right bank 12A (the left bank in FIG. 10), the connector mounting portion 81d faces obliquely backward, and the left bank 12B (the right bank in FIG. 10) is offset rearward with respect to the right bank 12A. The connector mounting portion 81 d faces diagonally forward in FIG. The central axis of the direct injector 81 inclines the space between the left and right banks 12A and 12B obliquely upward, and the fuel (injection axis S) injected from the direct injector 81 is directed into the cylinder As attached.

  As shown in FIG. 11, the high pressure delivery pipes 82A and 82B are for supplying fuel to the direct injector 81, and as described above, the direct injector 81 is orthogonal to the arrangement direction of the cylinders 14A (14B) As it is disposed, the high pressure delivery pipe 82A (82B) is disposed along the direction in which the cylinders 14A (14B) are arranged. As a result, the high pressure delivery pipes 82A and 82B are disposed inside the left and right banks 12A and 12B, and the delivery pipe connection portion of the direct injector 81 is connected (see FIG. 9).

  The fuel supplied to the high pressure delivery pipes 82A and 82B is supplied to the direct injector 81 from the high pressure delivery pipes 82A and 82B. Then, the control device accommodated in the body 81b is controlled by the electric signal supplied from the electrical connector 83 attached to the connector attachment 81d, and an arbitrary fuel injection amount is supplied to the nozzle 81a at an arbitrary injection timing. Ru. As a result, the fuel supplied to the nozzle portion 81a is injected so as to spread conically from the nozzle holes into the cylinders (cylinders 14A and 14B).

  Further, as shown in FIG. 12, the high pressure delivery pipes 82A and 82B provided in each of the left and right banks 12A and 12B have high pressure delivery pipes 82A (hereinafter referred to as “high pressure delivery pipes” provided in the right bank 12A. The rear end 82A1 of the right side high pressure delivery pipe 82A) is connected to the high pressure fuel pump by the fuel pipe 84a, and the high pressure delivery pipe 82B provided in the rear end 82A1 of the right high pressure delivery pipe 82A and the left bank 12B. A fuel pipe 84b is connected to the rear end 82B1 of the main body (hereinafter referred to as "the high-pressure delivery pipe 82B on the left side"). Thus, the fuel supplied from the high pressure fuel pump to the right high pressure delivery pipe 82A is distributed to the left high pressure delivery pipe 82B. The fuel supplied to the right high pressure delivery pipe 82A is supplied to the direct injector 81 provided in the right bank 12A, and the fuel supplied to the left high pressure delivery pipe 82B is provided in the left bank 12B. It is supplied to the direct injector 81.

By the way, as described above, the engine body 10 according to the present embodiment adopts the offset crank structure, and as shown in FIG. 9, the height of the right bank 12A (the left bank in FIG. 9) is the left bank. 12B (the bank on the right in FIG. 9) is located at a higher position, causing a difference in height, and the same difference in height between the inlet opening of the intake port 27 and the bank 12A on the right and the bank 12B on the left It is happening.
Therefore, in the direct injector 81 according to the present embodiment, the same difference in height occurs in the mounting height between the right bank 12A and the left bank 12B, and the same difference in height occurs in the connector mounting portion 81d. There is.
Similarly, in the high pressure delivery pipes 82A and 82B according to the present embodiment, the same height difference occurs in the mounting height between the right bank 12A and the left bank 12B.

  As shown in FIG. 9, a port injection type fuel injection device 9 (hereinafter referred to as "port injection device 9") is provided at an intake port 27 provided for each combustion chamber 21 in each of the left and right banks 12A and 12B. Low-pressure fuel pump for supplying fuel to the port injectors 91, low-pressure delivery pipes 92A and 92B provided commonly to the plurality of port injectors 91 in the left and right banks 12A and 12B, and low-pressure delivery pipes 92A and 92B Not shown), and is comprised.

  The port injector 91 is for injecting fuel to the intake port 27 provided for each combustion chamber 21. As shown in FIG. 5, the port injector 91 is on the same side as the direct injector 81 with respect to the intake port 27. It is arranged along the intake and exhaust direction. Specifically, the central axis of port injector 91 is disposed in a plane passing through axis L3 (L4) of cylinder 14A (14B) at a position where intake port 27 most protrudes inside the bank of cylinder block 11 Ru. Therefore, the central axis of the port injector 91 is disposed on the same plane as the central axis of the direct injector 81, and the port injector 91 is disposed orthogonal to the arrangement direction of the cylinders 14A (14B). Thus, the port injectors 91 are arranged so as to be staggered in plan view inside the left and right banks 12A and 12B. Then, the fuel (injection axis T) injected from the port injector 91 is distributed to the downstream port 272 branched into two on the downstream side of the intake port 27, and the axis L3 (L4) of the cylinder 14A (14B) and the direct It is equally distributed on both sides of the plane passing through the central axis of the injector 81.

  Further, as shown in FIG. 5, the injection axis T indicating the injection direction of the port injector 91 points in the direction in which the fuel injected from the port injector passes the lower region of the arc-shaped portion 276. Therefore, the angle formed by injection axis T indicating the injection direction of port injector 91 with respect to the lower surface of cylinder head 2A (2B) is the straight line contacting the lowermost surface of arc-shaped portion 276 through the injection position of port injector 91 It is larger than the angle formed with respect to the lower surface of (2B).

  Further, the injection axis S of the port injector 91 and the injection axis T of the direct injector 81 intersect in parallel or in the front in the fuel injection direction (see FIG. 3). In this case, the angle formed by the injection axis S of the port injector 91 with respect to the lower surface of the cylinder head 2A (2B) is equal to or greater than the angle formed by the injection axis T of the direct injector 81 with the lower surface of the cylinder head 2A (2B). . Accordingly, the fuel injected from the direct injector 81 is diffused against the tumble flow generated in the cylinder 14A (14B).

  As shown in FIG. 11, the port injector 91 has a nozzle portion 91a having a smaller diameter, a body portion 91b having a larger diameter than the nozzle portion 91a, and a delivery pipe connecting portion (not shown) having substantially the same diameter as the body portion 91b. And a connector mounting portion 91d (second connector mounting portion) provided in an outer radial direction of the body portion 91b. At the tip of the nozzle portion 91a, an injection hole (not shown) for injecting fuel supplied from the low pressure fuel pump so as to spread conically toward the two downstream ports is provided. A control unit (not shown) for controlling the injection amount and injection timing of the fuel is accommodated in the body portion 91b, the low pressure delivery pipes 92A and 92B are connected to the delivery pipe connection portion, and the low pressure fuel pipe is connected to the low pressure delivery pipe. Fuel is supplied through 92A and 92B.

  Further, an electrical connector 93 (second electrical connector) is attached to the connector attachment portion 91d. In the connector mounting portion 91d, the mounting direction of the electrical connector 93 is a diagonally upward direction of the port injector 91 (body portion 91b), the electrical connector 93 is mounted on the connector mounting portion 91d from a diagonally upper direction. The electrical connector 93 is detached in the direction.

  In the port injector 91, a connector mounting portion 91d is disposed toward the outside of the bank. Specifically, the nozzle portion 81a of the port injector 91 is disposed so as to project toward the intake port 27 (the cylinder head 2A) than the joint surface of the cylinder head 2A and the intake manifolds 4A and 4B. The tip of the nozzle portion 91a of the port injector 91 is located in the intake port 27, and the central axis of the port injector 91 is inclined obliquely upward in the space between the left and right banks 12A and 12B. The fuel (injection axis T) injected from 91 is attached to point to the umbrella center of the intake valve 25.

  As shown in FIGS. 11 and 12, the low pressure delivery pipes 92A and 92B are for supplying fuel to the port injector 91, and are provided inside the left and right banks 12A and 12B, as shown in FIG. And the high pressure delivery pipes 82A and 82B. The low pressure delivery pipes 92A and 92B are connected to a delivery pipe connecting portion of the port injector 91. As a result, the fuel supplied from the low pressure fuel pump to the low pressure delivery pipes 92A and 92B is supplied from the low pressure delivery pipe 92A to the port injector 91. Then, the control device housed in the body portion 91b is controlled by the electric signal supplied from the electric connector 93 mounted to the connector mounting portion 91d, and an arbitrary fuel injection amount is supplied to the nozzle portion 91a at an arbitrary injection timing. Ru. As a result, the fuel supplied to the nozzle portion 91a is injected so as to spread conically from the nozzle holes toward the two downstream ports.

  Further, as shown in FIG. 12, the low pressure delivery pipes 92A and 92B provided in the left and right banks 12A and 12B have low pressure delivery pipes 92A (hereinafter referred to as " The front end 92A1 of the right low-pressure delivery pipe 92A ′ ′ is connected to a fuel pipe (branch pipe) 94b branched from the fuel pipe (main pipe) 94a, and is a low-pressure delivery pipe 92B (hereinafter referred to as The front end 94B1 of the “right side low-pressure delivery pipe 92B” is connected to a fuel pipe (main pipe) 94a. Thus, the fuel discharged from the low pressure fuel pump is supplied to the low pressure delivery pipe 92A on the right side and the low pressure delivery pipe on the left side through the fuel pipes 94a and 94b. The fuel supplied to the right low pressure delivery pipe 92A is supplied to the port injector 91 provided in the right bank 12A, and the fuel supplied to the left low pressure delivery pipe 92B is provided in the left bank 12B. The port injector 91 is supplied.

By the way, as described above, the engine body 10 according to the present embodiment adopts the offset crank structure, and the height of the right bank 12A (the left bank in FIG. 9) is the left bank 12B (the right in FIG. 9). The height difference between the right bank 12A and the left bank 12B is the same, and the difference in height is also generated at the inlet opening of the intake port 27.
Therefore, even in the port injector 91 according to the present embodiment, the same difference in height occurs in the mounting height in the right bank 12A and the left bank 12B, and the same difference in height occurs in the connector mounting portion 91d. There is.
Similarly, in the low pressure delivery pipe 92A according to the present embodiment, the same height difference occurs in the mounting height between the right bank 12A and the left bank 12B.

  As described above, the V-type engine 1 according to the embodiment of the present invention has the valve seat 231 at the intake port 23 opened to the combustion chamber 21 and the central region of the intake port 27 on the upstream side of the valve seat 231 The injection axis T indicating the injection direction of the port injector 91 is directed from the port injector 91 to the direction in which the fuel passes through the lower region of the arc portion 276. And the port injector 91 can be arranged efficiently, and the fuel injected from the port injector 91 is well mixed with the air flowing through the intake port 27.

  Further, since the direct injector 81 can be disposed in the lower area of the downstream side port 272 branched into two, the direct injector 81 can be disposed efficiently.

  Further, the fuel injected from the direct injector 81 is diffused against the tumble flow generated in the cylinders 14A and 14B. This promotes the mixing of fuel and air in the cylinders 14A, 14B.

  Further, since the direct injector 81 and the port injector 91 are orthogonal to the arrangement direction of the cylinders 14A, 14B, the high pressure delivery pipes 82A, 82B for supplying fuel to the direct injector 81 may be piped in the arrangement direction of the cylinders 14A, 14B. The low pressure delivery pipes 92A and 92B for supplying fuel to the port injector 91 can be piped in the direction in which the cylinders 14A and 14B are arranged.

  Further, the intake manifolds 4A and 4B can be fixed to the cylinder heads 2A and 2B in a state where the port injector 91 is fixed to the intake manifolds 4A and 4B. Further, compared to the case where the nozzle portion 91a of the port injector 91 is positioned closer to the intake manifold 4A, 4B than the joint surface 274, the thickness of the port injector mounting seat can be thinner.

  In addition, the fuel (injection axis T) injected from the port injector 91 flows toward the umbrella center of the intake valve 25, and the adhesion of the fuel to the inner wall surface of the intake port 27 can be suppressed.

  Further, the direct injectors 81 and the port injectors 91 can be integrated and arranged inside the bank of the cylinder block 11.

  In addition, since the plurality of direct injectors 81 project radially outward from the body 81b, and the connector mounting portions 81d to which the electrical connectors 83 are mounted are arranged to have different heights between the banks, the boundaries between the banks are limited. Interference in the electrical connector 83 is avoided between the direct injector 81 of one bank 12A (12B) and the direct injector 81 of the other bank 12B (12A) in the closed space, and the direct injector 81 is mounted with the electrical connector 83 can do.

  Further, the electrical connector 83 can be attached to the connector attachment portion 81 d from the outside in the radial direction of the direct injector 81. Further, the electrical connector 83 can be attached to and detached from the connector mounting portion 81 d radially outward of the direct injector 81.

  Further, since the direct injectors 81 disposed in the left bank 12B are disposed at a lower position than the direct injectors 81 disposed in the right bank 12A, the right bank 12A is disposed in the limited space between the banks. Interference of the electrical connector 83 is avoided between the direct injector 81 disposed and the direct injector 81 disposed in the left bank, and the electrical connector 83 can be attached to the direct injector 81.

  Further, since the connector mounting portion 81d faces obliquely backward in the right bank 12A and the connector mounting portion 81d faces diagonally forward in the left bank 12B lower than the right bank 12A, the direct injectors disposed in the right bank 12A Attach the electrical connector 83 to the connector mounting portion 81 d of the direct injector 81 disposed in the right bank 12A while avoiding interference between the electrical connector 83 and the direct injector 81 disposed in the left bank 12B. The electrical connector 83 can be attached to the connector attachment portion 81 d of the direct injector 81 disposed in the left bank 12B.

  Further, since the plurality of port injectors 91 project radially outward from the trunk portion 91b, and the connector mounting portion 91d to which the electrical connector 93 is mounted is disposed toward the outside of the bank, one of the banks 12A (12B) Interference of the electrical connector 93 is avoided between the port injector 91 and the port injector 91 of the other bank 12B (12A), and the electrical connector 93 can be attached to the port injector.

  Further, the electrical connector 93 can be attached to the connector attachment portion 91 d from the diagonally upward direction of the port injector 91. In addition, the electrical connector 93 can be detached from the connector mounting portion 91 d obliquely upward of the port injector 91.

  Further, since the low pressure delivery pipes 92A and 92B overlap the high pressure delivery pipes 82A and 82B in a plan view, the low pressure delivery pipes 92A and 92B do not protrude much more outward than the high pressure delivery pipes 82A and 82B. As a result, the high pressure delivery pipes 82A, 82B and the low pressure delivery pipes 92A, 92B are disposed close to each other, and efficient piping work of the high pressure delivery pipes 82A, 82B and the low pressure delivery pipes 92A, 92B becomes possible.

  Further, the high pressure delivery pipes 82A, 82B and the low pressure delivery pipes 92A, 92B are collectively disposed inside the bank of the cylinder block 11. This enables efficient piping work of the high pressure delivery pipes 82A, 82B and the low pressure delivery pipes 92A, 92B.

  Further, as viewed in the direction of the crankshaft 15, the high pressure delivery pipes 82A and 82B and the low pressure delivery pipes 92A and 92B in the left and right banks 12A and 12B are alternately shifted in the vertical direction and arranged alternately. It becomes possible to arrange in

  Further, in plan view, the high bank (right bank 12A) and the low bank (left bank 12B) are arranged offset in the direction of the crankshaft 15, so the high pressure delivery pipes 82A in the left and right banks 12A, 12B. , 82B and the low-pressure delivery pipes 92A, 92B are further staggered in the front-rear direction, which further facilitates the installation in the V-bank.

  In addition, since the inlet side to high pressure delivery pipes 82A and 82B and the inlet side to low pressure delivery pipes 92A and 92B are positioned opposite to each other in the arrangement direction of cylinders 14A and 14B, high pressure delivery pipes 82A and 82B and On the fuel supply inlet side to the low pressure delivery pipes 92A and 92B, it is possible to avoid the complication of the piping arrangement in order to avoid interference with each other.

  Further, the intake manifolds 4A, 4B can be fixed to the cylinder heads 2A, 2B in a state where the low pressure delivery pipes 92A, 92B are fixed to the intake manifolds 4A, 4B.

  Further, in the front view in the crankshaft direction, the direct injector 81, the port injector 91, and the fuel supply piping to these injectors are surrounded by the outlet housing 31, the supercharger 6, and the left and right banks 12A and 12B. Since the vehicle is disposed as described above, a cooling effect can also be expected as safety in the event of a vehicle collision can be obtained, and furthermore, the enclosed internal space can also have an effect of guiding the flow of air due to traveling of the vehicle.

  As described above, according to the present invention, interference of the electrical connector is avoided between the direct injector of one bank and the direct injector of the other bank, and the electrical connector can be attached to the direct injector. A V-type engine having a narrow bank angle is preferable.

1 V-type engine 10 engine main body 11 cylinder block 12A, 12B bank 13 crankcase 14A, 14B cylinder (cylinder)
Reference Signs List 15 crankshaft 16 piston 162 piston pin 17 connecting rod 2A, 2B cylinder head 21 combustion chamber 22 spark plug 23 intake port 231 valve seat (seating surface)
24 exhaust port 241 valve seat 25 intake valve 26 exhaust valve 27 intake port 271 upstream port 272 downstream port 273 upstream port opening 274 joint surface 275 flange (port injector mounting seat)
276 arc 28 exhaust port 281 upstream port 29 rocker cover 3 intake system 31 outlet housing 32 distribution passage 32A ceiling surface 32A1 A 33 central opening 34A opening (right opening)
34B opening (left opening)
4A, 4B Intake manifold 5A, 5B Intercooler 51 Case 52 Intercooler core 53 Collar 54A Inlet side (tube)
54B outlet side (tube)
55 collar 6 supercharger 61 housing 61A housing main body 61A1 upper front area opening 61B inlet housing 61C bearing housing 62 input rotary shaft 63A drive rotor (rotor)
63B driven rotor (rotor)
64 throttle body 64A suction port 66 bypass valve 67 pulley 68 belt 69 bypass housing 691 bypass passage 7 fuel supply system 8 in-cylinder injection device 81 direct injector 81a nozzle portion 81b body 81d connector mounting portion 82A, 82B high pressure delivery pipe 82A1, 82B1 Rear end 83 Electrical connector 84a, 84b Fuel piping 9 port injector 91 Port injector 91a Nozzle 91b Body 91d Connector mounting portion 92A1, 94B1 Front end 92A, 92B Low pressure delivery pipe 93 Electrical connector 94a, 94b Fuel piping

Claims (4)

V-type cylinder blocks in which a plurality of cylinders are alternately arranged to the left and right in banks arranged in V-type;
A cylinder head attached to each of the banks, the cylinder head having an intake port extending inward from the combustion chamber and obliquely upward with respect to the axis of the cylinder for each of the cylinders;
A plurality of direct injectors disposed at positions radially outward of the intake port for each of the cylinders and directly injecting fuel into the combustion chamber;
Equipped with
The banks are offset in the same direction as the direction of rotation of the crankshaft,
The direct injectors located in the second bank lower than the first bank are located lower than the direct injectors located in the first bank,
The plurality of direct injectors project radially outward from the body portion, and a first connector mounting portion on which a first electrical connector is mounted is arranged such that the heights of the banks are different from each other , and The V-type engine according to claim 1, wherein the first connector mounting portion is directed obliquely backward in one bank, and the first connector mounting portion is obliquely directed forward in the second bank .   The V-type engine according to claim 1, wherein a mounting direction of the first electrical connector of the first connector mounting portion is a radial direction of the direct injector. Each cylinder includes a plurality of port injectors disposed at the same side as the direct injector with respect to the intake port and injecting fuel into the intake port.
Wherein the plurality of ports injector protrudes from the barrel portion radially outwardly, according to claim 1 or the second connector mounting portion in which the second electrical connector is mounted is characterized in that it is disposed toward the bank outside V-type engine described in 2 . The V-type engine according to claim 3 , wherein a mounting direction of the second electrical connector of the second connector mounting portion is an obliquely upward direction of the port injector.

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