JP2003090257A - Overhead valve type engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To allow a rocker arm to be positioned in parallel or nearly parallel with a virtual crossline 37 and shortened. SOLUTION: This overhead valve type engine is provided with intake valve ports 10a and 10b of its cylinder in front of the virtual crossline 37 and exhaust valve ports 32a and 32b of the cylinder rearwards respectively and push rods 36 and 36 of a valve system in the outlet side of an exhaust port 11. Out of the exhaust port 11, an intermediate part 38 is deflected to the front direction from an outlet beginning edge part 39 placed along a cylinder head lateral direction of a cylinder head 1 and an outlet end edge part 40 placed along the cylinder head lateral direction is biased to a position where it is fitted to the virtual crossline 37. Each of a pair of the push rods 36 and 36 of the cylinder is arranged to be distributed in front or in the rear of the outlet end edge part 40.

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to an overhead valve engine.

[0002]

2. Description of the Related Art Conventionally, as in the present invention, an overhead valve engine is assumed to have a virtual transverse line on the cylinder center axis which is orthogonal to the crankshaft center axis when viewed in a direction parallel to the cylinder center axis. With the longitudinal direction as the front-rear direction and one of them as the front, the intake valve port of the cylinder is arranged in front of the virtual crossing line, and the exhaust valve port of the cylinder is arranged in the rear, and the valve operating device is arranged on the outlet side of the exhaust port. There is a push rod arranged. In this type, the exhaust port is led out straight in a direction orthogonal to the arrangement direction of the intake valve port and the exhaust valve port, and a pair of push rods are arranged on both sides of the exhaust port.

[0003]

The above-mentioned conventional techniques have the following problems. << Problem 1 >> There are cases where the valve operation cannot be performed accurately. The direction of the rocker arm may be greatly tilted from the posture parallel to the virtual transverse line, and the rocker arm may become long.
In this case, the weight inertia of the rocker arm increases, and the operation followability of the rocker arm with respect to the push rod decreases. Therefore, the valve operation may not be performed accurately.

<Problem 2> The passage resistance of the exhaust port tends to increase. It may be necessary to narrow the outlet end of the exhaust port to avoid with the push rod,
In this case, the passage resistance of the exhaust port tends to increase.

An object of the present invention is to provide an overhead valve engine which can solve the above problems.

[0006]

(Invention of Claim 1) As shown in FIG. 2, when viewed in a direction parallel to the cylinder center axis (7), the crankshaft center axis ( 1
Assuming an imaginary transverse line (37) orthogonal to 7), seeing the longitudinal direction of the cylinder head (1) as the front-back direction and one of them as the front,
In front of the virtual crossing line (37), the intake valve port (10a) of that cylinder
(10b) to the rear of the exhaust valve port (32a) (32
b) are arranged respectively, and in the overhead valve engine in which the push rods (36) (36) of the valve gear are arranged on the outlet side of the exhaust port (11), the exhaust port (11) of the cylinder head (1) The leading end portion (39) along the head width direction is deflected forward from the middle portion (38) so that the leading end portion (40) along the head width direction is forwardly moved to a position overlapping the virtual transverse line (37). An overhead valve engine, characterized in that the pair of push rods (36) (36) of the cylinder are separately arranged before and after the leading end portion (40).

[0007]

(Invention of Claim 1) The invention of Claim 1 has the following effects. << Effect 1 >> The valve operation can be accurately performed. Figure 2
As shown in FIG.
6 is biased forward to a position where it overlaps with the virtual transverse line (37), and the push rods (36) (36) of the cylinder are arranged so as to be distributed before and after the leading end portion (40). As shown in, rocker arm (48) (48)
Can be placed in a posture parallel to the virtual transverse line (37) or a posture almost parallel thereto, and the rocker arms (48) (48) can be shortened. Therefore, the rocker arm (48) (4
Since the weight inertia of 8) becomes small and the operation followability of the rocker arms (48) (48) with respect to the push rod (36) is enhanced, the valve operation can be accurately performed.

<Effect 2> The passage resistance of the exhaust port can be reduced. 2, the exhaust port
Since the pair of push rods (36) (36) of the cylinder are arranged before and after the lead-out terminal portion (40) of (11), these can be arranged without difficulty, and the push rod (36)
Exhaust port end of exhaust port (11) to avoid (36)
It is not necessary to narrow (40) and the passage resistance of the exhaust port (11) can be reduced.

(Invention of Claim 2) The invention of Claim 2 has the following effect in addition to the effect of the invention of Claim 1. << Effect 3 >> Exhaust efficiency is high. As shown in FIG. 2, since the bypass passage (41) for exhaust gas from the first exhaust valve opening (32a) is formed in the rear of the second exhaust valve opening (32b), the bypass passage (41) from the first exhaust valve opening (32a) is formed. The exhaust gas does not interfere with the outflow of the exhaust gas from the second exhaust valve port (32b), and the exhaust efficiency is high.

<Effect 4> Overheating of the peripheral portion of the second exhaust valve opening is suppressed. As shown in FIG. 2, the first exhaust valve port (3
Since the exhaust gas from 2a passes through the bypass passage (41) at the rear of the second exhaust valve opening (32b), overheating of the peripheral portion of the second exhaust valve opening (32b) is suppressed.

(Invention of Claim 3) The invention of claim 3 has the following effect in addition to the effect of the invention of claim 1 or claim 2. << Effect 5 >> It is possible to secure a sufficient amount of exhaust gas reduction. As shown in FIG. 2, since the EGR gas outlet passage (42) is led out from the exhaust blow-in portion guided by the intermediate portion (38) of the curved exhaust port (11), in addition to the differential pressure between the supply and exhaust, Exhaust gas can be reduced by utilizing the pushing force of the exhaust gas, and a sufficient amount of exhaust gas reduction can be secured.

(Invention of Claim 4) The invention of claim 4 has the following effect in addition to the effect of the invention of any one of claims 1 to 3. << Effect 6 >> A dedicated EGR gas radiator is not required. As shown in FIG. 2, since the EGR gas outlet passage (42) passes through the inside of the head jacket (43), a dedicated E
The GR gas radiator becomes unnecessary.

<Effect 7> The arrangement of parts of the cylinder head becomes easy. Since it is not necessary to attach a dedicated EGR gas radiator to the cylinder head (1), the parts arrangement of the cylinder head (1) becomes easy.

(Invention of Claim 5) The invention of claim 5 has the following effect in addition to the effect of the invention of any one of claims 1 to 4. <Effect 8> The parts of the cylinder head can be arranged easily. As shown in FIG. 2, the EG continuing to the EGR gas outlet passage (42)
Since the R gas supply passage (44) is formed in the wall of the intake distribution means (13), the EGR gas supply passage (44) does not greatly extend from the cylinder head (1), and the R head of the cylinder head (1) is prevented. Parts placement becomes easy.

(Invention of Claim 6) The invention of claim 6 has the following effect in addition to the effect of the invention of any one of claims 1 to 5. << Effect 9 >> Thermal deterioration of the valve actuator is suppressed.
As shown in FIG. 2, since the flange portion (45) is led out from the intake distribution means (13) and the valve actuator (35) is attached to the flange portion (45), the valve actuator (35) is attached.
Thermal deterioration of the valve actuator (35) is suppressed as compared with the case where (35) is directly attached to the cylinder head (1).

(Invention of Claim 7) The invention of claim 7 has the following effect in addition to the effect of any one of claims 1 to 6. << Effect 10 >> The valve seat can be easily maintained. As shown in FIG. 2, the valve actuator (3
Since the valve seat (47) of the EGR valve (46) driven by 5) is formed on the side surface (23) of the cylinder head (1), the valve seat (47) can be easily maintained.

[0017]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described with reference to the drawings. 1 to 6 are diagrams for explaining an embodiment of the present invention. In this embodiment, a vertical overhead valve type multi-cylinder diesel engine will be described.

The structure of this engine is as follows.
As shown in FIG. 1, the cylinder head (1) is attached to the upper part of the cylinder block (49), and the head cover is attached to the upper part.
(15) is assembled. A fuel injection nozzle (2) and a glow plug (3) are attached to the cylinder head (1).

The mounting structure of the fuel injection nozzle (2) and the glow plug (3) is as follows. As shown in FIG. 1, the tip of the fuel injection nozzle (2) faces the center part (4) of the cylinder,
The glow plug (3) is penetrated through the intake port wall portion (6) between the fuel injection nozzle (2) and the intake port (5), and the glow plug (3) is predetermined for the fuel injection nozzle (2). angle
The tip part is inserted into the cylinder center part (4) by inclining by (Θ1).

The advantages of the above structure are as follows.
Since the glow plug (3) penetrates through the intake port wall portion (6) between the fuel injection nozzle (2) and the intake port (5), the heat of the exhaust gas passing through the exhaust port (11) is transferred to the glow plug (3). )
Hard to reach. Therefore, overheating of the glow plug (3) can be suppressed. Further, since the tip of the glow plug (3) is inserted in the cylinder center (4), the entire combustion chamber can be heated uniformly. Also, glow plug (3)
Is inclined with respect to the fuel injection nozzle (2), the tip of the glow plug (3) can be inserted into the cylinder central portion (4) without interfering with the fuel injection nozzle (2).
Therefore, the glow plug (3) can be easily inserted.

The structure of the intake port (5) is as follows. As shown in FIG. 1, a swirl intake port is used as the intake port (5). The inner wall surface (8) of the intake port wall portion (6) near the intake valve openings (10a) (10b) is inclined so that it approaches the cylinder center axis (7) as it approaches the cylinder (21). Glow plug on the wall (8)
According to the inclination of (3), the facing wall surface (8a) of this inner peripheral wall (8)
Are raised along a direction parallel to the cylinder center axis (7), and the intake valve ports (10a) (1
The wedge-shaped port portion (5a) is widened toward 0b). Therefore, the intake air passing through the intake port (5) is strongly pressed into the intake valve ports (10a) (10b) while being pressed against the opposing wall (5a) by the wedge-shaped port portion (5a). Therefore, high-speed intake air flows into the cylinder (21) toward the inner peripheral surface thereof, and the swirl in the cylinder (21) is strengthened.

The mounting structure of the fuel injection nozzle (2) is as follows. As shown in FIG. 2, the intake port wall portion
The fuel injection nozzle is attached to the nozzle boss (6a) bulging from (6).
(2) is inserted. Therefore, the heat of the exhaust gas passing through the exhaust port (11) is less likely to be transferred to the fuel injection nozzle (2), and the overheating of the fuel injection nozzle (2) can be suppressed.

Glow plug (3) and head jacket (4
The relationship with 3) is as follows. As shown in Figure 1,
A port wall portion (6) in which an inter-port crossing channel (12) is formed between the intake port (5) and the exhaust port (11) and the glow plug (3) is passed through the inter-port crossing channel (12). Is facing. Therefore, overheating of the glow plug (3) is suppressed. Further, the cooling water passing through the inter-port crossing water passage (12) is directed from the intake distribution means (13) side toward the exhaust merging means (14) side. Therefore, exhaust heat is less likely to be transferred to the intake distribution means side, the rise in intake air temperature can be suppressed, and intake efficiency is high.

The relationship between the glow plug (3) and the head cover (15) is as follows. As shown in FIG. 1, the outer wall (1) of the head cover (15) attached to the cylinder head (1) is
The end of the glow plug (3) is penetrated through 6), and the terminal of the glow plug (3) is projected outside the head cover (15). Therefore, there is no possibility that condensed water, oil mist, etc. in the head cover (15) will adhere to this terminal, and the leakage of the glow plug (3) can be suppressed.

The relationship between the glow plug (3) and the breather chamber (20) is as follows. As shown in FIG. 5, when viewed in a direction parallel to the cylinder center axis (7), the head cover (15)
Install the breather chamber (20) on the ceiling of the
(17) is biased toward one side, and as shown in FIG. 6, two intake valve openings (10a) (10b) are provided for each intake port (5), and the intake valve openings (10a) (10b) are provided. In order to penetrate the glow plug (3) through the intake port wall portion (6), the following is done. As shown in FIG. 6, when viewed in a direction parallel to the cylinder center axis (7), the two intake valve openings (10a)
By rotating the virtual connecting line (18) connecting each center point of (10b) from the posture orthogonal to the crankshaft central axis (17) by a predetermined angle (Θ2) about the cylinder central axis (7). The glow plug (3) is displaced in the direction opposite to the biasing direction of the breather chamber (20). Therefore, the breather chamber (15) can be expanded in the direction opposite to the bias direction without being obstructed by the glow plug (3) penetrating the head cover (15), and the volume of the breather chamber (15) can be increased. Can be secured.

The structure of the intake device is as follows. Figure 2
As shown in FIG. 3, the intake distribution means (13) is arranged on the side surface (23) of the cylinder head (1), and the intake distribution means (13) is provided in a longitudinal case along the side surface (23) of the cylinder head (1). With the structure, the side surface of the intake distribution means (13) facing the side surface (23) of the cylinder head (1) is entirely opened, and the opening edge is formed.
(24) is attached to the side surface (23) of the cylinder head (1). In addition, a mounting edge is provided on the side surface (23) of the cylinder head (1).
(25) is provided, and the intake distribution means (13) is provided on the mounting edge (25).
Attach the opening edge (24) of the cylinder head (1) to the side
Of (23), the part surrounded by the mounting edge (25) is the mounting edge
It is retracted more toward the inside of the head than (25). For this reason,
Even if the width dimension of the intake distribution means (13) is shortened, the intake passage cross-sectional area can be sufficiently secured, and the cylinder head (1)
The overhanging dimension of the intake distribution means (13) from the side surface (23) can be shortened.

Further, as shown in FIG. 2, an outward surface located between the intake port inlets (26) (26) of the adjacent cylinders.
(27) and the inner peripheral surface (2) of each intake port inlet (26) (26)
Boundaries (26b) and (26b) with 6a) and (26a) are rounded. Therefore, when the intake air is introduced from the intake distribution means (13) into the intake ports (5) and (5), the boundary portion (26b)
There is no risk of turbulence at (26b),
(5) The intake to (5) is done smoothly. Furthermore, the mounting edge
During the polishing process of (25), a part of the radius is scraped off and there is no defect that an edge is formed, and a smooth radius can be reliably formed. Further, since the mounting edge (25) can be rounded before being polished, this round can be formed by the casting die of the cylinder head (1) and the rounding can be easily performed.

The structure for mounting parts on the cylinder head (1) is as follows.
It is as follows. As shown in FIG. 2, the cylinder head
The intake distribution means (13), the exhaust merging means (14), and the cooling water circulation thermostat case (31) are provided in (1), and the intake valve openings (10a) (10b) and the exhaust valve openings (32a) (32b) are provided. The intake port (5) and the exhaust port (11) in opposite directions along the head width direction of the cylinder head (1),
The intake distribution means (13) is provided on one side of the cylinder head (1).
(23) and the exhaust merging means (14) on the other side (3
It is attached to 4).

As shown in FIG. 2, at one end of the cylinder head (1) in the longitudinal direction of the head, a thermostat case (31) is attached to the side surface (34) of the cylinder head (1) to which the exhaust merging means (14) is attached. In arranging, the longitudinal direction of the head is the front-rear direction, and the one end of the cylinder head (1) in which the thermostat case (31) is arranged is viewed as the front, and the exhaust valve openings (32a) (32b) of each cylinder are Cylinder intake valve port (10
a) (10b), the exhaust merging means (1
4) is arranged rearward of the intake distribution means (13), and in front of the exhaust merging means (14), the side surface of the cylinder head (1).
The thermostat case (31) is attached to (34).

The advantages of the above structure are as follows.
Install a large thermostat case (31) into the cylinder head
Since it can be arranged on the side surface (34) of (1), the total length of the engine can be shortened. Exhaust merging means
Place (14) behind the cylinder head in front of it.
Since the large thermostat case (31) can be mounted on the large mounting surface formed on the side surface (34) of (1), the side surface (34) of the cylinder head (1) can be used as a component mounting surface without waste. it can.

Further, as shown in FIG. 2, intake distribution means
E in front of (13) on the side surface (23) of the cylinder head (1).
The valve actuator (35) of the GR device (30) is arranged. In this way, a large thermostat case (31) is arranged in a wide space in front of the exhaust merging means (14), and a small valve actuator (35) is arranged in a narrow space in front of the intake distribution means (13). Therefore, it is easy to fit the parts into the cylinder head (1), and the cylinder head (1)
Can be compactly assembled.

Exhaust port (11) and push rod (36)
The relationship with is as follows. As shown in FIG. 2, on the outlet side of the exhaust port (11), the push rod (3
6) When arranging (36), the cylinder center axis (7)
Assuming an imaginary transverse line (37) orthogonal to the crankshaft central axis (17) on the cylinder central axis (7) when viewed in a direction parallel to, the intake air of the cylinder is in front of this imaginary transverse line (37). Valve
(10a) and (10b) to the rear of the exhaust valve port (32
a) and (32b) are respectively arranged, and in the exhaust port (11), the leading end portion (39) along the head width direction to the intermediate portion (38) are deflected in the forward direction to lead out along the head width direction. The portion (40) is biased forward to a position where it overlaps with the virtual transverse line (37), and each of the pair of push rods (36) (36) of the cylinder is arranged in front of and behind the lead-out terminal portion (40). is doing.

The advantages of the above structure are as follows.
As shown in FIG. 6, the rocker arms (48) (48) can be in a posture parallel to the virtual transverse line (37), or can be in a posture close to parallel, and the rocker arms (48) (48) can be shortened. . For this reason, the weight inertia of the rocker arms (48) (48) is reduced, and the followability of the rocker arms (48) (48) with respect to the push rod (36) is improved, so that the valve operation can be accurately performed. Also, the exhaust port (1
1) the terminating end portion (40) and a pair of push rods (3
6) and (36) can be arranged comfortably, and it is not necessary to narrow the outlet end portion (40) of the exhaust port (11) in order to avoid the push rods (36) (36).
The passage resistance of (11) can be reduced.

The structure of the exhaust port (11) is as follows. As shown in FIG. 2, a pair of exhaust valve openings (32a) (32b) are arranged in the exhaust port (11) along the head width direction, and the first exhaust valve opening (32a) is connected to the exhaust port (11). The second exhaust valve port (32
When opening b) at the intermediate portion (38) of the exhaust port (11), the intermediate portion (38) of the exhaust port (11) is led forward from the lead-out starting end portion (39) along the head width direction. The second exhaust valve opening (32b) is opened at the center position of the curved arc of the intermediate portion (38), and the first exhaust valve opening (32b) is provided behind the second exhaust valve opening (32b). It forms a bypass passage (41) for the exhaust from 32a). For this reason,
Exhaust from the first exhaust valve opening (32a) is transferred to the second exhaust valve opening (32a).
Exhaust efficiency is high without blocking the outflow of exhaust from b). Further, since the exhaust gas from the first exhaust valve port (32a) passes through the bypass passage (41) at the rear of the second exhaust valve port (32b), overheating of the peripheral portion of the second exhaust valve port (32b) is prevented. Suppressed.

The relationship between the exhaust device and the EGR device (30) is as follows.
It is as follows. As shown in Fig. 2, the exhaust port (11)
The EGR gas lead-out passageway (42) is led out from the exhaust blow-in portion guided by the curved intermediate portion (38). In addition to the pressure difference between the supply and exhaust gas, the exhaust gas pushing force can be used to perform exhaust gas reduction, and a sufficient amount of exhaust gas reduction can be secured. Further, the EGR gas lead-out passage (42) passes through the inside of the head jacket (43). For this reason, a dedicated EGR gas radiator is not needed, and the parts arrangement of the cylinder head (1) is facilitated. An EGR gas supply passage (44) following the EGR gas outlet passage (42) is formed in the wall of the intake distribution means (13). For this reason, the EGR gas supply passage (44) does not greatly extend from the cylinder head (1), and the parts arrangement of the cylinder head (1) is facilitated.

The valve actuator (3 of the EGR device (30)
The mounting structure of 5) is as follows. As shown in FIG. 2, the flange portion (45) is led out from the intake distribution means (13), and the valve actuator (35) of the EGR device (30) is attached to the flange portion (45). Thermal deterioration of the valve actuator (35) is suppressed as compared with the case where the valve actuator (35) is directly attached to the cylinder head (1). In addition, the EG driven by the valve actuator (35)
The valve seat (47) of the R valve (46) is formed on the side surface (23) of the cylinder head (1) to which the intake distribution means (13) is attached.
Therefore, the valve seat (47) can be easily maintained.

[Brief description of drawings]

FIG. 1 is a vertical sectional side view around a front end portion of a cylinder head of an engine according to an embodiment of the present invention.

2 is a cross-sectional plan view of a front end portion of a cylinder head of the engine of FIG.

3 (A) is a sectional view taken along line III-III of FIG. 2, FIG. 3 (B).
2 is a side view of a cylinder head of the engine of FIG. 1. FIG.

4 is a sectional view taken along line IV-IV in FIG.

5A and 5B are diagrams illustrating a head cover of the engine of FIG. 1, FIG. 5A being a plan view and FIG. 5B being a side view.

FIG. 6 is a plan view of the engine of FIG. 1 with a head cover removed.

[Explanation of symbols]

(10a) (10b) ... intake valve port, (11) ... exhaust port,
(32a) (32b) ... Exhaust valve port, (35) ... Valve actuator, (36) ... Push rod, (37) ... Virtual transverse line,
(38) ... Intermediate part, (39) ... Derivation start end part, (40) ... Derivation end part, (41) ... Detour passage, (42) ... EGR gas derivation passage, (43) ... Head jacket, (44) ... EGR gas supply passage, (45) ... Flange portion, (46) ... EGR valve,
(47) ... valve seat, (48) ... rocker arm.

─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. ⁷ Identification code FI theme code (reference) F02M 25/07 F02M 25/07 580F (72) Inventor Atsushi Yamaguchi 3-8 No. 8 Tsukiko Shinmachi, Sakai City, Osaka Stock Company Kubota Sakai Seaside Factory (72) Inventor Masahiko Sugimoto 3-8, Chikko Shinmachi, Sakai City, Osaka Prefecture F-term inside Kubota Sakai Seaside Factory (reference) 3G016 AA05 AA17 AA19 BA03 BA06 BB08 CA08 CA12 CA36 CA37 GA00 GA01 GA05 3G024 AA01 AA11 AA16 BA25 CA02 CA05 CA26 DA02 DA03 DA06 DA08 DA18 FA00 FA11 FA14 GA02 3G062 ED02 ED10

Claims (7)

[Claims] 1. A crankshaft center axis (1) on the cylinder center axis (7) when viewed in a direction parallel to the cylinder center axis (7).
Assuming an imaginary transverse line (37) orthogonal to 7), seeing the longitudinal direction of the cylinder head (1) as the front-back direction and one of them as the front,
In front of the virtual crossing line (37), the intake valve port (10a) of that cylinder
(10b) to the rear of the exhaust valve port (32a) (32
b), respectively, and an overhead valve engine in which the push rods (36) (36) of the valve gear are arranged on the outlet side of the exhaust port (11), in the exhaust port (11) of the cylinder head (1) The leading end portion (39) along the head width direction is deflected in the forward direction from the leading end portion (39) to the leading end portion along the head width direction.
(40) is biased forward to a position where it overlaps with the imaginary transverse line (37), and the pair of push rods (36) (36) of the cylinder are arranged so as to be distributed in front of and behind this lead-out end portion (40). An overhead valve engine characterized by the following. 2. The overhead valve engine according to claim 1, wherein a pair of exhaust valve openings (32a) (32b) are provided in the exhaust port (11).
Are arranged along the head width direction, and the first exhaust valve opening (32a)
Of the exhaust port (11) while opening the exhaust port (11) at the derivation start end part (39) and opening the second exhaust valve port (32b) at the intermediate part (38) of the exhaust port (11). The intermediate portion (38) is curved while being led out in the forward direction from the lead-out start end portion (39) along the head width direction, and the second exhaust valve port (32b) is located at the center position of the curved arc of the intermediate portion (38). Open this second exhaust valve opening
An overhead valve engine, characterized in that a bypass passage (41) for exhaust gas from the first exhaust valve opening (32a) is formed in the rear of (32b). 3. The overhead valve engine according to claim 1 or 2, wherein an intermediate portion (38) of the exhaust port (11) is led forward from a lead-out starting end portion (39) along the head width direction. While being curved, the EGR gas outlet passage (42) was led out from the exhaust hitting portion guided by the intermediate portion (38).
An overhead valve engine characterized by 4. The overhead valve engine according to any one of claims 1 to 3, wherein the EGR gas outlet passage (42) passes through the inside of the head jacket (43). Valve engine. 5. The overhead valve engine according to claim 1, wherein the EGR gas supply passage is connected to the EGR gas outlet passage (42).
An overhead valve engine characterized in that (44) is formed in a wall of the intake distribution means (13). 6. The overhead valve engine according to any one of claims 1 to 5, wherein a flange portion (45) is led forward from the intake distribution means (13), and an EGR device is provided in this flange portion (45). An overhead valve engine, to which a valve actuator (35) of (30) is attached. 7. The overhead valve engine according to claim 1, wherein an EGR valve (46) driven by the valve actuator (35).
The valve seat (47) of (1) is formed on the side surface (23) of the cylinder head (1) to which the intake distribution means (13) is attached.