JP3137384B2 - Intake device for engine with mechanical supercharger - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an intake device for an engine with a mechanical supercharger.

[0002]

2. Description of the Related Art In general, an intake device for an engine is provided with a collecting portion for collecting independent intake passages of respective cylinders on the upstream side in order to stabilize the flow of intake air. However, when the independent intake passages of the cylinders whose intake strokes are adjacent to each other are gathered in the gathering portion, there is a problem that intake interference occurs in the gathering portion and intake charging efficiency is reduced. Therefore, in a multi-cylinder engine, a plurality of collecting portions are provided for collecting the independent intake passages of the cylinders whose intake strokes are not adjacent to each other on the upstream side, and the intake passage upstream of the collecting portion is also separated for each collecting portion to some extent upstream. Thus, the intake interference is prevented (see Japanese Patent Application Laid-Open No. 2-227517). Therefore,
In a portion relatively close to the engine, two intake systems are provided.

[0003]

However, this has a problem that the intake device is bulky. In addition, when the passage lengths of the two intake systems are different, there is a problem that the responsiveness of the two intake systems is different, and the air-fuel ratio control is disturbed.

On the other hand, in a multi-cylinder engine equipped with a mechanical supercharger, air is adiabatically compressed by supercharging and becomes high in temperature. However, if this high temperature air is supplied to the combustion chamber, the charging efficiency is not sufficient. I can't. Therefore, in an engine with a supercharger, an intercooler for cooling air is usually provided in an intake passage downstream of the supercharger (for example, see Japanese Patent Application Laid-Open No. 2-227517). However, since air has a very small heat transfer coefficient (film heat transfer coefficient), an intercooler having a considerable heat transfer area is required to effectively cool such air. This makes the intercooler quite bulky. In addition, the intercooler is a considerably large source of intake resistance.

Therefore, in a multi-cylinder engine provided with a mechanical supercharger, a mechanical supercharger, an intercooler, a set of two systems, an intake passage upstream thereof, and the like must be arranged. There is a problem that the layout is difficult. Furthermore, since various members are provided downstream of the mechanical supercharger, there is a problem that the intake resistance increases and the supercharging effect is not sufficiently exerted. In particular, in recent years, there has been a demand for higher performance of vehicles, and while devices or members arranged in an engine room are increasing,
There is a tendency for the engine room to become narrower due to a lower bonnet. For this reason, in engines equipped with a mechanical supercharger, there is a strong demand for a compact intake device.
The present invention has been made in order to solve the above-mentioned conventional problems, and in a vehicle equipped with a mechanical supercharged engine, a compact intake device capable of effectively reducing intake resistance. The purpose is to provide.

[0006]

According to a first aspect of the present invention, there is provided a fuel cell system comprising: (i) a plurality of collecting portions for collecting, on an upstream side, independent intake passages of cylinders whose intake strokes are not adjacent to each other; And in the intake device of the engine provided with a mechanical supercharger that is rotationally driven by the engine output shaft,
(Ii) A discharge port of the mechanical supercharger is provided on an outer peripheral portion of a rotor casing of the mechanical supercharger, and two branch intakes branched from an intake passage downstream of the discharge port to an engine front side and an engine rear side. A passage is provided, each branch intake passage is connected to a corresponding collecting part such that the passage lengths are equal to each other, and an intercooler is provided in each branch intake passage, and (iii) the engine comprises: A V-type engine in which a cylinder row on one bank side and a cylinder row on the other bank side are arranged so as to be offset from each other in the axial direction of the engine output shaft, and a mechanical supercharger is arranged between both banks. The discharge port of the mechanical turbocharger is located on the rotor casing side of the bank (forward offset bank) on which the cylinder row is offset to the front of the engine, and branches to the front of the engine. The branch intake passage that extends is extended toward the bank (rear offset bank) that is offset toward the rear of the engine, and the branch intake passage that branches to the rear of the engine is extended toward the rear of the engine at the front offset bank, An intercooler of a branch intake passage extending rearward of the engine is disposed rearward of the engine on the side of the front offset bank, thereby providing an intake device for an engine with a mechanical supercharger.

According to a second aspect of the present invention, in the intake device for an engine with a mechanical supercharger according to the first aspect, the intake port of the mechanical supercharger is arranged on the rear side of the engine while the discharge port is arranged on the front side of the engine. And the intercooler is
An intake device for an engine with a mechanical supercharger, which is disposed behind the engine on the front offset bank side and on the side of the rear offset bank on the vehicle front side.

According to a third aspect of the present invention, there is provided an intake device for an engine with a mechanical supercharger according to the first aspect, wherein the engine is mounted horizontally on a vehicle. To provide an air intake device.

According to a fourth aspect of the present invention, there is provided (i) a mechanical supercharger in which a plurality of collecting portions are provided on an upstream side for collecting independent intake passages of cylinders whose intake strokes are not adjacent to each other, and are rotationally driven by an engine output shaft. (Ii) a discharge port of a mechanical supercharger is provided on an outer peripheral portion of a rotor casing of the mechanical supercharger, and an intake port downstream of the discharge port is connected to a front side of the engine. Two branch intake passages branching to the rear side of the engine are provided, each branch intake passage is connected to a corresponding collecting part so that the passage lengths are equal to each other, and an intercooler is interposed in each branch intake passage. (Iii) the engine is
A horizontally mounted V-type engine having two banks, the engine being inclined with its upper part inclined forward of the vehicle, a mechanical supercharger disposed between both banks, The discharge port of the engine is arranged on the front side of the engine, one branch intake passage extends to one side in the engine width direction, the intercooler of the branch intake passage is arranged above the corresponding bank, and the other branch intake passage is arranged. An intake device for an engine with a mechanical supercharger, wherein an intake passage extends to the other side in the engine width direction, and an intercooler of the branch intake passage is disposed above a corresponding bank. .

[0010]

[0011]

[0012]

【Example】

<First Embodiment> Hereinafter, a first embodiment of the present invention will be specifically described. As shown in FIGS. 1 to 4, an engine room 3 is defined by a vehicle body inner wall 2 in a vehicle body front portion 1 of the vehicle WD. Note that suspension towers 4 are disposed at both ends in the vehicle width direction of the engine room 3, and the upper part of the engine room 3 is closed by a bonnet 5. Here, in the vehicle WD, the hood is reduced, the height of the engine room 3 is relatively low, and the engine room 3 is relatively narrow.

In the engine room 3, a 6-cylinder V-type engine E, a transmission T, and an intake device Q for supplying air to the engine E are arranged in a predetermined positional relationship as described later. . Here, the engine E is arranged such that the engine output axis is oriented in the axle axis direction, that is, in the vehicle width direction (the left-right direction in FIG. 1). That is, the engine E is mounted horizontally on the vehicle WD. The transmission T is arranged on the rear side of the engine E, that is, on the left side of the engine E with reference to the vehicle WD (the right side in FIG. 1) so that its input axis coincides with the engine output axis. That is, the power train PT in which the engine E and the transmission T are connected in series is mounted horizontally on the vehicle WD.

[0014] In the following, in order to clearly indicate the direction in the horizontal plane with respect to the vehicle WD, as also shown by arrows in FIGS. 1 to 11, refers to the vehicle front direction "X ₁ direction",
The direction after the vehicle is referred to as "X ₂ direction", the engine front direction, that the vehicle rightward direction (in FIG. 1 to the left) is referred to as "Y ₁ direction", the engine-rear direction i.e. the vehicle leftward direction (in Fig. 1 right) It will be referred to as "Y ₂ direction". Note that the up and down direction of the vehicle WD is simply referred to as an upward direction or a downward direction. For example, the axle axis direction or the engine output shaft axial direction, are displayed as Y ₁ -Y ₂ direction.

First, the engine E will be described. FIG. 5 is an enlarged view around the engine E in FIG. As described above, the engine E is such that the engine output shaft axis is oriented Y ₁ -Y ₂ direction, that is arranged to be transversely with respect to the vehicle WD. The engine E is provided with a cylinder head 6 and a cylinder block 7. Here, the cylinder heads 6 are Y
First made long in ₁ -Y ₂ direction and the second bank 6a, consist 6b, the first bank 6a is disposed on X ₁ side (vehicle front side), the second
Bank 6b is disposed on the X ₂ side (vehicle rear side). A substantially V-shaped trough-shaped V space portion 8 is formed between the banks 6a and 6b. In addition, both banks 6a and 6b have
Three cylinders at which the intake stroke is not Tonariawa are arranged in a row in the Y ₁ -Y ₂ directions. Here, the cylinder row of the first bank 6a side is arranged offset relatively Y ₂ direction with respect to the cylinder row of the second bank 6b side. The offset is performed in order to make the width of the engine E as small as possible. By the offset of such cylinder bank, the engine E, and the vicinity of the end portion of the Y ₁ side of the first bank 6a, in the vicinity of the end portion of the Y ₂ side of the second bank 6b,
A slight space (dead space) is formed in each case.

An oil pan 9 is mounted below the cylinder block 7, and a cylinder head cover 10a, 1 is provided above the cylinder head 6 (first and second banks 6a, 6b).
0b is attached. Further, the radiator 12 in X ₁ side of the engine E through the transmission T, the inside of the engine room 3, comprises two fans 11
Is arranged. Note that the X ₁ side of the side portion of the engine E, an exhaust manifold 51, O ₂ sensor 52, the catalyst 5
3, a water temperature sensor 54, a thermostat case 55, a water pipe 56 and the like are arranged. Further, the starter 58 is disposed on the side of the X ₂ side.

As described above, the transmission T
It is connected in series to an end portion of the Y ₂ side of the engine E. For this reason, the power train PT including the engine E and the transmission T extends in the Y ₁ -Y ₂ direction. However, since the height of the transmission T is considerably lower than the height of the engine E, the transmission T A relatively large space (dead space) is formed above the space. Since the power train PT are arranged horizontally, the X ₁ side of the space portion of the transmission T upper (vehicle front side), in particular a large apparatus is not disposed. Therefore, when the vehicle is traveling, the traveling wind hits the space above the transmission relatively well.

Hereinafter, the intake device Q will be described. First, the overall configuration of the intake device Q will be described. The fender 1 is provided in the intake device Q in order from the upstream side when viewed in the intake flow direction.
An air inlet 15 toward the inside of the engine room 3 (Y ₁ direction) opening at 4 near the fresh air duct 16, an air cleaner 17 for removing floating dust in the air
A connection passage 18 having a bellows portion, a resonator 19 for attenuating air column vibration at a predetermined frequency to reduce noise in the intake system, a throttle body 20 having a built-in throttle valve, and a resholm type mechanical filter. A feeder 21 is provided. The mechanical supercharger 21 includes a rotor (not shown in FIG. 9).
Are driven to rotate by the engine E via the pulley 22. The intake system up to this point is a common part for all cylinders or banks 6a and 6b,
Only one system is provided. Incidentally, the intake system from the fresh air duct 15 to the resonator 19 is basically formed of resin is disposed on the Y ₂ side of the engine E.

Slightly downstream of the discharge port 25 of the mechanical supercharger 21, the intake system includes a first upstream branch intake passage 26 for supplying air to each cylinder on the first bank 6a side, and a second bank 6
Second upstream branch intake passage 2 for supplying air to each cylinder on the b side
Branching to 7 Downstream of the first upstream branch intake passage 26, an air-cooled first intercooler 28, a first downstream branch intake passage 29, and a first surge tank 30 (collecting portion) are sequentially connected. Here, outside air for cooling the intake air is introduced into the first intercooler 28 through the first air duct 31. The first surge tank 30 is connected to an independent intake passage 32 of each cylinder on the first bank 6a side. The first upstream branch intake passage 2
6 and the first downstream branch intake passage 29 constitute a branch intake passage according to claims 1 to 8.

On the other hand, on the downstream side of the second upstream branch intake passage 27, an air-cooled second intercooler 36, a second downstream branch intake passage 37, and a second surge tank 38 are sequentially connected. Here, outside air for intake air cooling is introduced into the second intercooler 36 through the second air duct 39. And the second surge tank 38
Is connected to the independent intake passage 32 of each cylinder on the second bank 6b side. The second upstream branch intake passage 27 and the second downstream branch intake passage 37 constitute a branch intake passage according to claims 1 to 8.

Here, the intake path length on the first bank 6a side from the first upstream branch intake passage 26 to the first surge tank 30 and the second bank from the second upstream branch intake passage 27 to the second surge tank 38 The intake path length on the 6b side is set substantially equal. As a result, there is no discrepancy in the responsiveness of the intake flow between the first bank 6a and the second bank 6b during acceleration or the like, and the accuracy of air-fuel ratio control and the like is improved.

As described above, each bank 6a, 6b
On the side, since the intake strokes of the cylinders belonging to the cylinders are not adjacent to each other, no intake interference occurs in each of the surge tanks 30, 38, and the charging efficiency is increased. In addition, the mechanical supercharger 2
The first and second bypass intake passages 41 and 42 connected to the first and second surge tanks 30 and 38 by bypassing the first and second intercoolers 28 and 36 are provided for cooling air. When unnecessary, air is supplied to each cylinder through the first and second bypass intake passages 41 and 42. This switching is performed by a switching valve 45 driven to be opened and closed by an actuator 43.
Further, a supercharging pressure control valve 44 for controlling the supercharging pressure is provided.
(ABV) is provided.

Hereinafter, the specific configuration, arrangement, and the like of each part of the intake device Q will be described with reference to FIGS. (1) Mechanical supercharger The reshroom type mechanical supercharger 21 that is driven to rotate by the engine E is formed in an elongated shape that is long in the axial direction of the rotor, and is provided between the banks 6a and 6b. In the V space portion 8, they are arranged so as to be long in the Y ₁ -Y ₂ direction. Since the mechanical supercharger 21 is arranged by effectively using the V space 8 as described above, the intake device Q is made compact.

[0024] In such arrangement, the suction port 74 (see FIG. 8), in the rotor axis, the ends of the Y ₂ side of the rotor casing of the mechanical supercharger 21,
It is formed so as to open toward the substantially Y ₂ direction.
The suction port 74 is connected to the throttle body 20. With the formation and arrangement of the suction port 74, the mechanical supercharger 21
The air flow to the air is smoothed, and the intake resistance is reduced.

The discharge port 25 is connected to the mechanical supercharger 2.
Near the edge of the Y ₁ side of the first rotor casing, X ₂ direction, i.e. toward the second bank 6b side are formed so as to open from the rotor casing outer peripheral portion. That is, the discharge port 25 is opened in the direction in which the air is sent out by the rotor at the position where the air pressure is the highest. For this reason, the ejection performance is improved. As shown in FIG. 8, the mechanical supercharger 21 is attached to the engine body E using a bracket 73. Since the resholm-type mechanical supercharger 21 rotates at high speed, vibration is likely to occur. In order to suppress such vibration, the bracket 73 has a particularly rigid structure. In addition,
A lever 75 is provided on the throttle body 20.

As shown in FIG. 9, the mechanical supercharger 21
At a branch portion 77 to the first and second bypass intake passages 41 and 42, a partition wall 78 is provided to partition the opening of the first bypass intake passage 41 and the opening of the second bypass intake passage 42 so as not to communicate with each other. Have been. That is, when air is supplied from the first and second bypass intake passages 41 and 42, if the partition wall 78 is not provided, intake interference occurs at the branch portion 77 and the charging efficiency is reduced.

[0027] (2) first, second branch intake passage first upstream branch intake passage 26 is branched from the discharge port 25 in the Y ₁ direction, and curved in the vicinity of the end portion of the Y ₁ side of the rear second bank 6b extended by changing the direction in the X ₁ direction Te, the first bank 6a
It is connected to the first intercooler 28 disposed X ₁ side of the. As described above, by offsetting the cylinder row,
The vicinity of the end portion of the Y ₁ side of the first bank 6a but dead space is formed, are arranged first upstream branch intake passage 26 by effectively utilizing the dead space. Thereby, the intake device Q is made compact.

The second upstream branch intake passage 27 is connected to the discharge port 2
Is connected to the second intercooler 36 extend to almost X ₂ direction and somewhat Y ₂ side of the position from the end portion of the Y ₂ side of the Y ₂ direction branches into intermediate direction anyway second bank 6b from 5.
And, as described above, by offsetting the cylinder row,
The vicinity of the end portion of the Y ₂ side of the second bank 6a but dead space is formed, are arranged a second downstream branch intake passage 37 by effectively utilizing the dead space. Since this position is also above the transmission T, there is considerable spatial clearance in this part. Therefore, the second
The layout of the downstream branch intake passage 37 can be set quite freely. Therefore, by slightly meandering the second downstream branch intake passage 37 and increasing the length of the passage, the first
The passage lengths of the branch intake passages 26 and 29 are made equal to the passage lengths of the second branch intake passages 27 and 37. Therefore, it is extremely easy to equalize the intake path length on the first bank 6a side and the intake path length on the second bank 6b side.

(3) First and second intercoolers First, the intercoolers are first and second intercoolers 28 and 36.
, The volume per intercooler is reduced, and these can be arranged by using a relatively small space in the engine room 3 in detail.
The layout of the intercooler is easy. And the first
Intercooler 28, the side of the X ₁ side of the engine E, the spreading face is disposed so as to face the X ₁ direction, i.e. the front of the vehicle. When the vehicle is running, the traveling wind is applied to the space, so that the cooling performance is very high. The first
Since the traveling wind is guided to the first intercooler 28 by the air duct 31, the cooling performance is further enhanced.

The second intercooler 36 is connected to the second bank 6b.
In the Y ₂ side of the end portion of the Y ₂ side of the position, it is disposed in the space above the transmission T (dead space). The second intercooler 36, X ₁ side becomes high X ₂ side is inclined arranged vertically so as to be lower. For this reason, the ventilation to the second intercooler 36 is enhanced, and a compact configuration is obtained. As described above, since a dead space due to the offset of the cylinder row is also formed in this portion, the layout of the second intercooler 36 becomes very easy. Further, as described above, this portion has good ventilation and the second air duct 39 is provided, so that the cooling performance of the second intercooler 36 is enhanced.

(4) Air Cleaner As shown in FIG. 6, the air cleaner 17 is formed of a resin, and a sound absorbing material is disposed inside the air cleaner. The air cleaner 17 is attached to the vehicle body frame 62 using a plurality of attachment members 61. A resin-made fresh air duct 16 is connected to a lower portion of the air cleaner 17, and an air inlet 15 of the fresh air duct 16 is provided.
Is fixed to the apron 13 connected to the fender 14. A connection passage 18 made of resin is connected to an upper portion of the air cleaner 17.
The downstream end of 8 is connected to a resonator 19. An air flow meter 63 is provided in the connection passage 18, and a bellows portion made of rubber is provided in an intermediate portion of the connection passage 18.

(5) Resonator The resonator 19 is formed of a resin and has a plurality of fastening portions 65.
And is attached to the transmission T using a predetermined fastening member 64. This resonator 19 is provided with an expansion chamber 19a and a resonance chamber 19b, and both chambers 19a, 19b
Are communicated via a neck (not shown). here,
A sound absorbing material is arranged in both chambers 19a and 19b. This resonator 19 attenuates air column vibration of a predetermined frequency in the intake system, and reduces intake noise. As shown in FIG. 7, the resonator 19 is provided with a substantially cylindrical fitting portion 71, and the fitting portion 71 is fitted to a substantially cylindrical connecting portion 72 of the throttle body 20 to thereby form the resonator 19. And the throttle body 20 are connected.

(6) Throttle body The throttle body 20 is formed of an aluminum alloy, and as described above, is connected to the resonator 19 on the upstream side by the connecting portion 72.
Are connected to the fitting portion 71 of the resonator 19. The throttle body 20 has
Throttle valve (not shown) attached to valve shaft 67
And the throttle valve is provided with a link mechanism 66.
Through an accelerator pedal (not shown).

As shown in FIG. 8, the throttle body 20
Is connected to the suction port 74 of the mechanical supercharger 21 on the downstream side. The throttle body 20 is only connected to the resonator 19 and the mechanical supercharger 21 (suction port 74), and is not supported by the power train PT or the like. That is, the throttle body 20
A mechanical supercharger 21 attached to the engine body E;
It is only supported on both sides by the resonator 19 attached to the transmission case T.
Therefore, the vibration of the engine body E is not transmitted to the mechanical supercharger 21 via the throttle body 20, and the durability or reliability of the mechanical supercharger 21 is improved.

(7) ISC Mechanism In general, the engine is provided with an ISC mechanism for supplying air required for idling when the throttle valve is fully closed. Such an ISC mechanism is usually arranged in a throttle body. You. However, in the present embodiment, as described above, the throttle body 20 is
The throttle body 20 is preferably as lightweight as possible because it is supported only by the two ends of the mechanical supercharger 21 and the resonator 19 without being fixed to the throttle body 20. Therefore, in this embodiment, the ISC mechanism is provided outside the throttle body 20 in order to reduce the weight of the throttle body 20.

That is, as shown in FIGS. 10 and 11, when the throttle valve is fully closed, the air in the resonator 19 is connected to the connecting portion 82a provided outside the throttle body 20 and connected to the resonator 19. The throttle body 20 is provided via an upstream ISC hose 82, an ISC valve 83, and a downstream ISC hose 84 provided.
The air is supplied to the air pipe 81 on the downstream side.

Here, the ISC valve 83 performs idle control such as controlling the idle speed by adjusting the idle air amount. In such idle control, the idle air amount is adjusted according to the engine temperature. I need to change. Therefore, engine cooling water is introduced into the ISC valve 83. That is, the engine cooling water in the water jacket 87 of the cylinder head 6 is
The cooling water is introduced into the water jacket 88 of the valve 83, and then flows into the thermo case 92 in this order through the upstream heater hose 89, the inside of the throttle body 20, and the downstream heater hose 90. The reason why the engine cooling water is introduced into the throttle body 20 in this way is to prevent the throttle valve from freezing in cold weather.

<Second Embodiment> A second embodiment according to claims 1 and 6 will be described below with reference to FIGS. 12 and 13. In order to avoid redundant description, FIGS. First shown
Portions common to the first embodiment are denoted by the same reference numerals, and the description thereof is omitted. Only different points from the first embodiment will be described. As shown in FIGS. 12 and 13, in the second embodiment,
The engine E is inclined forward of the vehicle by a predetermined angle. In Figure 13, the straight line L ₁ in the horizontal direction, L ₂ is a vertical direction,
L ₃ represents a vertical direction of the engine E. That is, the engine E is tilted disposed before an angle sandwiched by the straight line L ₂ and the straight line L _3. Thus the total height or length of the vertical direction (L ₂ direction) of the engine E is reduced, a relatively large space (dead space) is formed between the engine E and the bonnet 5. Therefore, the first intercooler 28 is arranged above the first bank 6a, and the second intercooler 36 is arranged above the second bank 6b.

Since a sufficient space is formed between the engine E and the bonnet 5, the mechanical supercharger 21
Is provided above the rotor casing. The intake passage downstream of the discharge port 25 extends from the connection with the discharge port 25 to the front of the engine, then branches right and left, and is connected to the corresponding intercoolers 28 and 36. With this configuration, the dead space can be effectively used, the space in the engine room 3 can be effectively used, and the length of the branch intake system can be made equal.

Third Embodiment A third embodiment according to the first and fourth aspects of the present invention will be described below. As shown in FIG.
In the third embodiment, the engine SE is connected to the first to sixth cylinders # 1
To # 6. The left side in FIG. 14 is the front of the vehicle. Hereinafter, for convenience, the front of the vehicle (left direction in FIG. 14) is referred to as “front”, and the opposite direction is referred to as “rear”. The first cylinder # 1 direction is referred to as “left” when viewed in the engine longitudinal direction, and the sixth cylinder # 6
The direction is called "right".

The ignition sequence of the engine SE is # 1 → # 5 →
The order is # 3 → # 4 → # 2 → # 6. Then, the upstream ends of the independent intake passages 101 of the first to third cylinders # 1 to # 3 whose intake strokes are not adjacent are connected to the first surge tank 102, and the fourth to sixth cylinders # whose intake strokes are not adjacent to each other. The upstream ends of the independent intake passages 101 to 104 of the second surge tank 103
It is connected to the. Here, the first surge tank 102 is arranged in front of the first to third cylinders # 1 to # 3, and the second surge tank 103 is arranged in front of the fourth to sixth cylinders # 4 to # 6. . Then, the first surge tank 102 and the second surge tank 102
The surge tank 103 is disposed at a position substantially symmetrical with respect to the center of the engine SE.

A pulley 1 is located at the rear left position of the engine.
A mechanical supercharger 107 rotatably driven by the engine SE through the engine 06 is provided. An intake passage 108 downstream of the mechanical supercharger 107 branches right and left at a branch portion 109 located forward of the center position of the engine SE. Thus, first and second branch intake passages 104 and 105 are formed. In the first and second branch intake passages 104 and 105, first and second intercoolers 110 and 111 are provided at positions symmetrical with respect to the center of the engine. Here, the first branch intake passage 104 downstream of the first intercooler 110 is the first branch intake passage 104 from the left side.
The second surge tank 11 is connected to the surge tank 102.
The second branch intake passage 105 at one downstream is connected to the second surge tank 103 from the right side.

According to such a configuration, since both branch intake systems downstream of the branch portion 109 are symmetrical, the intake passage lengths are equal and the intake system is compact. Also,
Since both the intercoolers 110 and 111 are arranged on the front side of the engine SE, the traveling wind sufficiently hits the intercoolers 110 and 111 and the cooling performance is enhanced.

[0044]

According to the first aspect of the present invention, since the discharge port of the mechanical supercharger is provided on the outer periphery of the rotor casing, the discharge port is oriented in the direction in which air is sent from the rotor, and the discharge performance is improved. Enhanced. Further, since the two branch intake systems are made equal in length, the responsiveness during acceleration or the like is improved, and the intake system is made compact. Further, the mechanical supercharger is arranged between the banks, and the branch intake passage is arranged by utilizing the dead space generated by the offset of the cylinder row, so that the space in the engine room is effectively utilized, and the intake device is used. It is compact.

According to the second aspect, basically the same operation and effect as those of the first aspect can be obtained. Furthermore, since the intercooler is arranged in the dead space caused by the offset of the cylinder row, the space in the engine room is effectively used, and the intake device is made compact.

According to the third invention, basically the same operation and effect as those of the first invention can be obtained. Further, since the engine is mounted horizontally on the vehicle, ventilation to the intercooler is enhanced, and cooling performance is enhanced.

According to the fourth aspect, the discharge port of the mechanical supercharger is provided on the outer peripheral portion of the rotor casing, so that the discharge port is oriented in a direction in which air is sent out from the rotor, thereby improving discharge performance. In addition, since the two branch intake systems are made equal in length, the responsiveness during acceleration and the like becomes good,
And the intake system is made compact. In addition, since the engine is V-shaped and is inclined forward, a dead space occurs between the engine and the hood. Since the intercooler is arranged in the dead space, the space in the engine room is effectively used, and the intake device is made compact.

[0048]

[0049]

[Brief description of the drawings]

FIG. 1 is an explanatory plan view of a power train according to a first embodiment of the present invention.

FIG. 2 is a side elevational view of the power train shown in FIG. 1;

FIG. 3 is an explanatory front elevational view of the power train shown in FIG. 1;

FIG. 4 is a rear elevational view of the power train shown in FIG. 1;

FIG. 5 is an enlarged plan view of the power train shown in FIG. 1;

FIG. 6 is an elevation explanatory view around an air cleaner of the intake device.

FIG. 7 is an explanatory elevational view around a resonator of the intake device.

FIG. 8 is an elevational view of the intake device around the mechanical supercharger.

FIG. 9 is a partially sectional plan view of the mechanical supercharger.

FIG. 10 is an explanatory plan view of an ISC mechanism provided in the intake device.

11 is a rear elevational view of the ISC mechanism shown in FIG. 10;

FIG. 12 is an explanatory plan view of a powertrain including a forward-inclined engine, showing a second embodiment of the present invention.

FIG. 13 is a side elevational view of the power train shown in FIG. 12;

FIG. 14 is a schematic plan view of an in-line six-cylinder engine and an intake device thereof according to a third embodiment of the present invention.

[Explanation of symbols]

 WD: Vehicle PT: Powertrain E: Engine Q: Intake device T: Transmission 6a, 6b: First and second banks 25: Discharge ports 26, 27 ... First and second upstream branch intake passages 28, 36 ... First , Second intercooler 29, 37 ... first and second downstream branch intake passages 30, 38 ... first and second surge tanks 32 ... independent intake passages

──────────────────────────────────────────────────の Continued on the front page (51) Int.Cl. ⁷ Identification code FI F02B 75/22 F02B 75/22 C F02M 35/10 F02M 35/10 102F 35/104 301C (58) Investigation field (Int.Cl. . ^7, DB name) B60K 5/04 F02B 29/04 F02B 67/00 F02B 75/22 F02M 35/10

Claims (4)

(57) [Claims] An engine provided with a mechanical supercharger provided with a plurality of collecting portions for collecting independent upstream intake passages of cylinders whose intake strokes are not adjacent to each other at an upstream side and having a mechanical supercharger rotationally driven by an engine output shaft. In the intake device, a discharge port of a mechanical supercharger is provided on an outer peripheral portion of a rotor casing of the mechanical supercharger, and two branches branching from an intake passage downstream of the discharge port to an engine front side and an engine rear side. An intake passage is provided, each branch intake passage is connected to a corresponding collecting portion so that the passage length is equal to each other, and an intercooler is provided in each branch intake passage, and the engine is provided with one of A V-type engine in which a cylinder row on the bank side and a cylinder row on the other bank side are offset from each other in the axial direction of the engine output shaft, and the mechanical supercharger is The discharge port of the mechanical supercharger is arranged between the banks, and the discharge port of the mechanical supercharger is arranged on the side of the rotor casing on the bank (forward offset bank) side where the cylinder row is offset to the front of the engine, and branches to the front of the engine. The branch intake passage that extends is extended toward the bank (rear offset bank) that is offset toward the rear of the engine, and the branch intake passage that branches to the rear of the engine is extended toward the rear of the engine at the front offset bank, An intake device for an engine with a mechanical supercharger, wherein an intercooler of a branch intake passage extending rearward of the engine is disposed rearward of the engine on the front offset bank side. 2. The intake device for an engine with a mechanical supercharger according to claim 1, wherein an intake port of the mechanical supercharger is disposed on a rear side of the engine, and a discharge port is disposed on a front side of the engine. And an intercooler is arranged behind the engine on the front offset bank side and on the side of the rear offset bank on the vehicle front side, wherein the intake device of the engine with a mechanical supercharger is provided. 3. The intake device for an engine with a mechanical supercharger according to claim 1, wherein the engine is mounted horizontally on a vehicle. . 4. An engine provided with a mechanical supercharger provided with a plurality of gathering portions for gathering, at an upstream side, independent intake passages of cylinders whose intake strokes are not adjacent to each other, and having a mechanical supercharger rotationally driven by an engine output shaft. In the intake device, a discharge port of a mechanical supercharger is provided on an outer peripheral portion of a rotor casing of the mechanical supercharger, and two branches branching from an intake passage downstream of the discharge port to an engine front side and an engine rear side. An intake passage is provided, each branch intake passage is connected to a corresponding collecting portion so that the passage lengths are equal to each other, and an intercooler is provided in each branch intake passage. A horizontally mounted V-type engine having a bank, wherein the engine is inclined with its upper part inclined forward of the vehicle, and a mechanical supercharger is arranged between both banks. A discharge port of the feeder is arranged on the front side of the engine, and one branch intake passage extends to one side in the engine width direction, and an intercooler of the branch intake passage is arranged above a corresponding bank, and the other branch intake passage is arranged above the corresponding bank. An intake device for an engine with a mechanical supercharger, wherein a branch intake passage extends to the other side in the engine width direction, and an intercooler of the branch intake passage is disposed above a corresponding bank.