WO2016189566A1

WO2016189566A1 - Internal combustion engine

Info

Publication number: WO2016189566A1
Application number: PCT/JP2015/002625
Authority: WO
Inventors: 容康木村; 高生伊藤; 忠俊宮野
Original assignee: 日産自動車株式会社
Priority date: 2015-05-25
Filing date: 2015-05-25
Publication date: 2016-12-01

Abstract

In this internal combustion engine (1), a cylinder head (20) that forms a combustion chamber (22) along with a cylinder block (10) in which a cylinder (12) is formed has an intake channel (30), which connects the combustion chamber (22) with an intake pipe (2) having a supercharger (CH) connected thereto, and an exhaust channel (40), which connects an exhaust pipe (8) with the combustion chamber (22), wherein the opening area of an exhaust valve hole (42), which is an opening in the exhaust channel (40) that opens to the combustion chamber (22), is larger than the opening area of an intake valve hole (32), which is an opening in the intake channel (30) that opens to the combustion chamber (22).

Description

Internal combustion engine

The present invention relates to the structure of an internal combustion engine.

As an internal combustion engine, for example, as described in Patent Document 1, the opening area of an intake valve hole that is closed by contact with an intake valve is larger than the opening area of an exhaust valve hole that is closed by contact of an exhaust valve. There is something formed.

JP-A-5-187307

However, when the configuration of the intake device includes a supercharger, as in Patent Document 1 described above, if the opening area of the intake valve hole is equal to or larger than the opening area of the exhaust valve hole, the intake amount is increased by the supercharger. In this case, the ratio of the exhaust amount to the intake amount may be reduced. When the ratio of the exhaust amount to the intake amount is reduced, the exhaust efficiency is lowered, which may cause a problem that the combustion efficiency of the internal combustion engine is lowered.
The present invention has been made paying attention to the above problems, and an object of the present invention is to provide an internal combustion engine capable of suppressing a decrease in combustion efficiency.

In order to solve the above problems, according to one aspect of the present invention, a cylinder head portion that forms a combustion chamber together with a cylinder block portion has an exhaust valve hole having an opening area larger than that of the intake valve hole. The intake valve hole is an opening that opens to the combustion chamber in an intake passage that communicates the intake pipe connected to the supercharger and the combustion chamber. The exhaust valve hole is an opening that opens to the combustion chamber in an exhaust passage that allows the exhaust pipe and the combustion chamber to communicate with each other.

According to one aspect of the present invention, it is possible to exhaust air that has been sucked from an intake pipe connected to a supercharger and burned in a combustion chamber from an exhaust valve hole having an opening area larger than that of the intake valve hole. Become.
Accordingly, it is possible to provide an internal combustion engine that can suppress a decrease in exhaust efficiency and suppress a decrease in combustion efficiency.

1 is a block diagram illustrating a schematic configuration of a vehicle including an internal combustion engine according to a first embodiment of the present invention. 1 is a plan view showing a schematic configuration of an internal combustion engine according to a first embodiment of the present invention. It is the III-III sectional view taken on the line of FIG. It is the IV-IV sectional view taken on the line of FIG. It is a conceptual diagram which shows each positional relationship of the nozzle attachment hole, exhaust valve hole, intake valve hole, and plug attachment hole provided with respect to the same combustion chamber. It is a conceptual diagram which shows the state which divided the upper surface of the cylinder head part into the 1st area | region and the 2nd area | region. It is a figure which shows the modification of 1st embodiment of this invention. It is a figure which shows the modification of 1st embodiment of this invention. It is a figure which shows the modification of 1st embodiment of this invention. It is a figure which shows the modification of 1st embodiment of this invention.

In the following detailed description, specific details are set forth in order to provide a thorough understanding of the embodiments of the invention. However, it will be apparent that one or more embodiments may be practiced without such specific details. In other instances, well-known structures and devices are shown in schematic form in order to simplify the drawing.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to the drawings.
(Schematic configuration of the vehicle)
A schematic configuration of a vehicle including the internal combustion engine (engine) 1 according to the first embodiment will be described with reference to FIG.
As shown in FIG. 1, the internal combustion engine 1 includes an air-fuel mixture obtained by mixing air sucked from an intake pipe 2 connected to a supercharger CH and fuel supplied from within a fuel tank 4 into a combustion chamber. Burn in (not shown). Then, the energy generated by the combustion of the air-fuel mixture is transmitted to the drive device 6 including a transmission and the like. Further, the burned gas is discharged from the combustion chamber to the outside air through the exhaust pipe 8.
The supercharger CH pressurizes or accelerates the air sucked from outside air and supplies the air to the intake pipe 2.
Further, the supercharger CH includes an exhaust turbine drive supercharger (turbocharger) or a machine drive supercharger (supercharger).

(Configuration of internal combustion engine 1)
The configuration of the internal combustion engine 1 according to the first embodiment will be described with reference to FIG. 1 and FIGS. 2 to 6.
As shown in FIGS. 2 to 4, the internal combustion engine 1 includes a cylinder block portion 10 and a cylinder head portion 20.
The cylinder block portion 10 and the cylinder head portion 20 are made of a metal material such as an aluminum alloy, and are integrally formed by casting, for example. That is, the internal combustion engine 1 of the first embodiment has a structure (head block integrated structure) formed by integrally casting the cylinder head portion 20 and the cylinder block portion 10.
Therefore, in the internal combustion engine 1 of the first embodiment, the cylinder block portion 10 forms a lower portion of the internal combustion engine 1. Further, in the internal combustion engine 1 of the first embodiment, the cylinder head portion 20 forms an upper portion of the internal combustion engine 1.

A plurality of cylinders 12 are formed in the cylinder block portion 10.
In the first embodiment, a case where three cylinders 12 are formed in the cylinder block portion 10 will be described.
Each cylinder 12 is arranged with the stroke direction of the piston 14 in each cylinder 12 oriented in parallel. 3 and 4, the piston 14 is not shown in cross section for the sake of explanation.
The piston 14 reciprocates in the axial direction of the cylinder 12 in the cylinder 12 in accordance with the combustion of the air-fuel mixture in the combustion chamber 22.

Each cylinder 12 forms a stroke of the piston 14 with a bore diameter of the cylinder 12 or more together with a connecting rod (not shown) and a crankshaft (not shown). In FIG. 4, the stroke of the piston 14 is indicated by “St”, and the bore diameter of the cylinder 12 is indicated by “BID”. Accordingly, each cylinder 12 is formed in a shape that satisfies the following conditional expression (1).
St ≧ BID (1)

In particular, in the first embodiment, each cylinder 12 is formed in a shape that satisfies the following conditional expression (2).
St> (BID × 1.2) (2)
That is, in the first embodiment, the stroke St of the piston 14 exceeds 1.2 times the bore diameter BID of the cylinder 12.
The shape of the cylinder head portion 20 is a shape that covers the upper end of each cylinder 12. Thus, the cylinder head portion 20 forms a plurality of combustion chambers 22 together with the cylinder block portion 10.
The plurality of combustion chambers 22 are arranged with the stroke direction of the piston 14 in each cylinder 12 parallel.

In the first embodiment, as described above, the three cylinders 12 are formed in the cylinder block portion 10. For this reason, the case where the cylinder head part 20 forms the three combustion chambers 22 with the cylinder block part 10 is demonstrated.
That is, in the first embodiment, a case will be described in which the internal combustion engine 1 is an in-line 3-cylinder internal combustion engine (in-line 3-cylinder engine).
In addition, the cylinder head portion 20 includes an intake passage 30, an exhaust passage 40, a nozzle attachment hole 24, and a plug attachment hole 26.
In addition, an out frame portion 50, an intake side cam frame portion 52, and an exhaust side cam frame portion 54 are formed in the cylinder head portion 20.

The intake passage 30 is a passage that allows the intake pipe 2 and the combustion chamber 22 to communicate with each other. The intake passage 30 is formed in the internal space of the cylinder head portion 20.
In the first embodiment, a case where one combustion chamber 22 and the intake pipe 2 are communicated with each other by two intake passages 30 will be described. Therefore, in the first embodiment, the cylinder head portion 20 has six intake passages 30.
The two intake passages 30 for communicating one combustion chamber 22 with the intake pipe 2 are arranged along the direction in which the three cylinders 12 are arranged (the vertical direction in FIG. 2). Further, the two intake passages 30 for communicating one combustion chamber 22 and the intake pipe 2 are formed with the length direction parallel to the radial direction of the cylinder 12 when viewed from the axial direction of the cylinder 12.

One opening end of the intake passage 30 opens to the outer surface of the internal combustion engine 1 and communicates with the intake pipe 2. The other opening end of the intake passage 30 opens into the combustion chamber 22 and communicates with the combustion chamber 22.
An intake valve 34 contacts the opening of the intake passage 30 that opens to the combustion chamber 22. Accordingly, the opening of the intake passage 30 that opens to the combustion chamber 22 forms an intake valve hole 32 that is opened and closed by the intake valve 34.
The intake valve hole 32 opens in a portion of the intake passage 30 that forms the upper surface of the combustion chamber 22.

In the first embodiment, one combustion chamber 22 and the intake pipe 2 are communicated with each other through two intake passages 30. For this reason, in the first embodiment, two intake valve holes 32 are opened in a portion of the intake passage 30 that forms the upper surface of the combustion chamber 22. Therefore, in the first embodiment, the cylinder head portion 20 has six intake valve holes 32.
In the first embodiment, all the intake valve holes 32 are formed in the same shape.
Two intake valve holes 32 opened to one combustion chamber 22 are arranged along the direction in which the three cylinders 12 are arranged.
The intake valve 34 includes an intake valve stem 34a and an intake valve head 34b. In FIG. 3, the intake valve stem 34a and the intake valve head 34b are not shown in cross section for the sake of explanation.

The intake valve stem 34a is formed in a rod shape. Further, the intake valve stem 34 a projects one end from the intake valve guide hole 36.
The intake valve stem 34a is supported by the cylinder head portion 20 via an intake valve spring 34c. In FIG. 3, the intake valve spring 34 c is not shown in cross section for explanation.
The intake valve spring 34c can be expanded and contracted in the axial direction of the intake valve stem 34a in accordance with the rotation of an intake side camshaft 38 to be described later. Further, the intake valve spring 34c is extended by an elastic force to bring the intake valve head 34b into contact with the intake valve hole 32 from the combustion chamber 22 side.
The intake valve guide hole 36 is a through hole formed in the upper surface (upper deck) 20 a of the cylinder head portion 20.

The intake valve head 34b is formed in a shape (circular shape) capable of closing the intake valve hole 32. The intake valve head 34 b is attached to the other end of the intake valve stem 34 a and disposed in the combustion chamber 22.
As a result, when the intake valve spring 34 c is extended and the intake valve head 34 b is brought into contact with the intake valve hole 32 from the combustion chamber 22 side, the intake valve head 34 b closes the intake passage 30.
The intake side camshaft 38 includes an intake side shaft portion 38a and a plurality of intake side cams 38b.
The intake side shaft portion 38a is a columnar member. The intake-side shaft portion 38a is disposed at a position where the axial direction is orthogonal to the direction in which the three cylinders 12 are arranged and overlaps with all the intake valve holes 32 in plan view. Further, both end portions of the intake side shaft portion 38 a are inserted into through holes (not shown) formed in the out frame portion 50.

Each intake side cam 38b is disposed on the outer peripheral surface of the intake side shaft portion 38a. Each intake side cam 38b is disposed at a position overlapping the intake valve hole 32 in plan view. Each intake side cam 38b is formed in an egg shape having a major axis and a minor axis as seen from the axial direction of the intake side shaft portion 38a.
In the first embodiment, the cylinder block portion 10 and the cylinder head portion 20 form three combustion chambers 22, and each combustion chamber 22 and the intake pipe 2 are communicated with each other through two intake passages 30. For this reason, in the first embodiment, the intake side camshaft 38 includes six intake side cams 38b.

When one end of the intake valve stem 34a is pressed by the long diameter portion of the intake side cam 38b, the intake valve spring 34c contracts. When the intake valve spring 34 c contracts, the intake valve head 34 b moves away from the intake valve hole 32 and opens the intake passage 30.
Thus, the intake valve 34 is displaced according to the rotation of the intake side camshaft 38 to open and close the intake passage 30.
In the first embodiment, one combustion chamber 22 and the intake pipe 2 are communicated with each other through two intake passages 30. For this reason, two intake valve holes 32 are provided for one combustion chamber 22. Therefore, in the first embodiment, two intake valve guide holes 36 are provided for one combustion chamber 22. The two intake valve guide holes 36 are arranged along the direction in which the three cylinders 12 are arranged.
The exhaust passage 40 is a passage that allows the exhaust pipe 8 and the combustion chamber 22 to communicate with each other. Each exhaust passage 40 is formed in a space different from the intake passage 30 in the internal space of the cylinder head portion 20.

In the first embodiment, a case where one combustion chamber 22 and the exhaust pipe 8 are communicated with each other through two exhaust passages 40 will be described. Therefore, in the first embodiment, the cylinder head portion 20 has six exhaust passages 40.
Two exhaust passages 40 for communicating one combustion chamber 22 and the exhaust pipe 8 are arranged along the direction in which the three cylinders 12 are arranged. Further, the two exhaust passages 40 for communicating one combustion chamber 22 and the exhaust pipe 8 are formed such that the length direction is parallel to the radial direction of the cylinder 12 when viewed from the axial direction of the cylinder 12.

One open end of the exhaust passage 40 opens to the outer surface of the internal combustion engine 1 and communicates with the exhaust pipe 8. The other opening end of the exhaust passage 40 opens to the combustion chamber 22 and communicates with the combustion chamber 22.
An exhaust valve 44 contacts the opening of the exhaust passage 40 that opens to the combustion chamber 22. Accordingly, the opening of the exhaust passage 40 opened to the combustion chamber 22 forms an exhaust valve hole 42 that is opened and closed by the exhaust valve 44.
The exhaust valve hole 42 opens in a portion of the exhaust passage 40 that is different from each intake valve hole 32 in a portion that forms the upper surface of the combustion chamber 22.
In the first embodiment, one combustion chamber 22 and the exhaust pipe 8 are communicated with each other through two exhaust passages 40. For this reason, two exhaust valve holes 42 are opened in a portion of the exhaust passage 40 that forms the upper surface of the combustion chamber 22. Therefore, in the first embodiment, the cylinder head portion 20 has six exhaust valve holes 42.

In the first embodiment, all the exhaust valve holes 42 are formed in the same shape.
In the first embodiment, the exhaust valve hole 42 and the intake valve hole 32 are formed in a shape that satisfies the following conditional expression (3).
EXHvdi> INTvdi (3)
In conditional expression (3), “EXHvdi” is the inner diameter of the exhaust valve hole 42, and “INTvdi” is the inner diameter of the intake valve hole 32. Therefore, in the first embodiment, the opening area of the exhaust valve hole 42 is made larger than the opening area of the intake valve hole 32.
In FIG. 5, only four holes (exhaust valve hole 42, intake valve hole 32, nozzle mounting hole 24, plug mounting hole 26) provided for one combustion chamber 22 are shown for explanation. To do.

As described above, in the first embodiment, the cylinder head portion 20 has the six intake valve holes 32 and the six exhaust valve holes 42. Furthermore, in the first embodiment, all intake valve holes 32 are formed in the same shape. In addition, in the first embodiment, all the exhaust valve holes 42 are formed in the same shape.
Therefore, in the first embodiment, the total value of the opening areas of the two exhaust valve holes 42 opened to one combustion chamber 22 is the total value of the opening areas of the two intake valve holes 32 opened to one combustion chamber 22. Is bigger than.

In the first embodiment, since the total value of the opening areas of all the exhaust valve holes 42 is larger than the total value of the opening areas of all the intake valve holes 32, the following conditional expression (4) is satisfied. ing.
(EXHvdi × 6)> (INTvdi × 6) (4)
Two exhaust valve holes 42 opened in a portion of the exhaust passage 40 forming the roof of the combustion chamber 22 are arranged along the direction in which the three cylinders 12 are arranged.
The exhaust valve 44 includes an exhaust valve stem 44a and an exhaust valve head 44b. In FIG. 3, the exhaust valve stem 44a and the exhaust valve head 44b are not shown in cross section for the sake of explanation.

The exhaust valve stem 44a is formed in a rod shape. Further, the exhaust valve stem 44 a projects one end from the exhaust valve guide hole 46.
The exhaust valve stem 44a is supported on the cylinder head portion 20 via an exhaust valve spring 44c. In FIG. 3, the exhaust valve spring 44 c is not shown in cross section for explanation.
The exhaust valve spring 44c can be expanded and contracted in the axial direction of the exhaust valve stem 44a in accordance with the rotation of an exhaust camshaft 48 described later. Further, the exhaust valve spring 44c is extended by an elastic force to bring the exhaust valve head 44b into contact with the exhaust valve hole 42 from the combustion chamber 22 side.
The exhaust valve guide hole 46 is a through hole formed in the upper surface 20 a of the cylinder head portion 20.

The exhaust valve head 44b is formed in a shape (circular shape) capable of closing the exhaust valve hole 42. Further, the exhaust valve head 44 b is attached to the other end of the exhaust valve stem 44 a and disposed in the combustion chamber 22. Thereby, when the exhaust valve spring 44c is extended and the exhaust valve head 44b is brought into contact with the exhaust valve hole 42 from the combustion chamber 22 side, the exhaust valve head 44b closes the exhaust passage 40.
As described above, in the first embodiment, the inner diameter EXHvdi of the exhaust valve hole 42 is made larger than the inner diameter INTvdi of the intake valve hole 32. Therefore, in the first embodiment, the outer diameter of the exhaust valve head 44b (the outer diameter of the portion in contact with the exhaust valve hole 42) is the outer diameter of the intake valve head 34b (the outer diameter of the portion in contact with the intake valve hole 32). Larger than. That is, the mass of the exhaust valve head 44b is made larger than the mass of the intake valve head 34b.

The exhaust side camshaft 48 includes an exhaust side shaft portion 48a and a plurality of exhaust side cams 48b.
The exhaust-side shaft portion 48a is a columnar member. The exhaust-side shaft portion 48a is disposed at a position where the axial direction is orthogonal to the direction in which the three cylinders 12 are arranged and overlaps with all the exhaust valve holes 42 in plan view. Further, both end portions of the exhaust side shaft portion 48 a are inserted into through holes (not shown) formed in the out frame portion 50.
Each exhaust side cam 48b is disposed on the outer peripheral surface of the exhaust side shaft portion 48a. Further, each exhaust side cam 48b is arranged at a position overlapping the exhaust valve hole 42 in plan view. Each exhaust side cam 48b is formed in an egg shape having a major axis and a minor axis when viewed from the axial direction of the exhaust side shaft portion 48a.

In the first embodiment, three combustion chambers 22 are formed by the cylinder block portion 10 and the cylinder head portion 20, and each combustion chamber 22 and the exhaust pipe 8 are communicated by two exhaust passages 40. For this reason, in the first embodiment, the exhaust side camshaft 48 includes six exhaust side cams 48b.
When one end of the exhaust valve stem 44a is pressed by the long diameter portion of the exhaust side cam 48b, the exhaust valve spring 44c contracts. When the exhaust valve spring 44 c contracts, the exhaust valve head 44 b moves away from the exhaust valve hole 42 and opens the exhaust passage 40.
As described above, the exhaust valve 44 is displaced according to the rotation of the exhaust camshaft 48 to open and close the exhaust passage 40.

In the first embodiment, two exhaust valve holes 42 are provided for one combustion chamber 22 in order to allow one combustion chamber 22 and the exhaust pipe 8 to communicate with each other through two exhaust passages 40. Therefore, in the first embodiment, two exhaust valve guide holes 46 are provided for one combustion chamber 22. The two exhaust valve guide holes 46 are arranged along the direction in which the three cylinders 12 are arranged.
The nozzle mounting hole 24 is a hole for inserting the fuel injection nozzle 16 into the combustion chamber 22. The nozzle mounting hole 24 is formed as a through hole that penetrates the upper surface 20 a of the cylinder head portion 20. In FIG. 4, the fuel injection nozzle 16 is not shown in cross section for the sake of explanation.

In the first embodiment, the cylinder head portion 20 forms three combustion chambers 22 together with the cylinder block portion 10. For this reason, the cylinder head portion 20 has three nozzle mounting holes 24.
The nozzle mounting hole 24 is formed at a position where the following conditional expression (5) is satisfied.
INJ-EXTr> INJ-INTr (5)
In conditional expression (5), “INJ-EXTr” is the distance between the center of the nozzle mounting hole 24 and the center of the exhaust valve hole 42 provided for the same combustion chamber 22. In conditional expression (5), “INJ-INTr” is the distance between the center of the nozzle mounting hole 24 and the center of the intake valve hole 32 provided for the same combustion chamber 22.
Therefore, in the first embodiment, the distance between the nozzle mounting hole 24 and the exhaust valve hole 42 is longer than the distance between the nozzle mounting hole 24 and the intake valve hole 32.

The fuel injection nozzle 16 is connected to the fuel tank 4.
The fuel injection nozzle 16 injects fuel (gasoline etc.) in the fuel tank 4 into the combustion chamber 22 by control using an ECU (Engine Control Unit) or the like.
The plug attachment hole 26 is a hole for inserting the spark plug 18 into the combustion chamber 22. The plug attachment hole 26 is formed so as to penetrate the upper surface 20a of the cylinder head portion 20. In FIG. 4, the spark plug 18 is not shown in cross section for the sake of explanation.
In the first embodiment, the cylinder head portion 20 forms three combustion chambers 22 together with the cylinder block portion 10. For this reason, the cylinder head portion 20 has three plug attachment holes 26.

The plug attachment hole 26 is formed at a position where the following conditional expression (6) is satisfied.
SP-EXTr ≧ SP-INTr (6)
In conditional expression (6), “SP-EXTr” is the distance between the center of the plug mounting hole 26 and the center of the exhaust valve hole 42 provided for the same combustion chamber 22. In the conditional expression (6), “SP-INTr” is a distance between the center of the plug attachment hole 26 and the center of the intake valve hole 32 provided for the same combustion chamber 22.
Therefore, in the first embodiment, the distance between the plug attachment hole 26 and the exhaust valve hole 42 is set to a length equal to or longer than the distance between the plug attachment hole 26 and the intake valve hole 32.

Further, the plug mounting hole 26 is disposed at the center of the combustion chamber 22 into which the ignition plug 18 is inserted as viewed from the axial direction of the cylinder 12.
The spark plug 18 generates a spark in the combustion chamber 22 by control using an ECU or the like.
The out frame part 50 is formed by combining four plate-like members into a frame shape, and is arranged on the upper surface 20 a of the cylinder head part 20. Further, the out frame part 50 is formed in a shape surrounding the periphery of the cylinder head part 20 in plan view, and forms an outer frame of the cylinder head part 20.
Here, the upper surface 20a of the cylinder head portion 20 is divided into a first region E1 and a second region E2, as shown in FIG.

The first region E1 is a region that overlaps with the combustion chamber 22 when viewed from the axial direction of the cylinder 12 along the direction in which the plurality of cylinders 12 are arranged.
The second region E2 is a region between two adjacent first regions E1.
In the first embodiment, the cylinder head portion 20 forms three combustion chambers 22 together with the cylinder block portion 10. For this reason, the upper surface 20a of the cylinder head part 20 is divided into three first regions E1 and two second regions E2.
The intake side cam frame portion 52 is formed of a plate-like member, and the side surface thereof is opposed to the upper surface 20 a of the cylinder head portion 20 and the inner side surface of the out frame portion 50.

In the first embodiment, a case where two intake side cam frame portions 52 are formed on the upper surface 20a of the cylinder head portion 20 will be described.
In addition, an intake side frame through hole 52 a is formed in the intake side cam frame portion 52.
The intake side frame through hole 52a is a through hole that penetrates the intake side cam frame portion 52 in the thickness direction.
Further, the intake side frame through hole 52a is formed in a shape in which a portion of the intake side shaft portion 38a where the intake side cam 38b is not disposed can be inserted rotatably. Thus, the inner wall surface of the intake side frame through hole 52a forms an intake side cam journal portion 56 that rotatably supports the intake side camshaft 38.

In the first embodiment, a case where two intake side cam frame portions 52 are formed on the upper surface 20a of the cylinder head portion 20 will be described. Therefore, in the first embodiment, the cylinder head portion 20 has the two intake side cam journal portions 56.
In the first embodiment, the two intake side cam frame portions 52 are respectively arranged in the second region E2 of the upper surface 20a of the cylinder head portion 20.
Therefore, in the first embodiment, the two intake side cam journal portions 56 are arranged in the second region E2 on the upper surface 20a of the cylinder head portion 20, respectively.
The exhaust side cam frame portion 54 is formed of a plate-like member, and the side surface is opposed to the upper surface 20 a of the cylinder head portion 20 and the inner side surface of the out frame portion 50.

The exhaust side cam frame portion 54 is formed in the same shape as the intake side cam frame portion 52.
In the first embodiment, a case where three exhaust side cam frame portions 54 are formed on the upper surface 20a of the cylinder head portion 20 will be described.
Further, an exhaust side frame through hole 54 a is formed in the exhaust side cam frame portion 54.
The exhaust side frame through hole 54a is a through hole that penetrates the exhaust side cam frame portion 54 in the thickness direction.
Further, the exhaust side frame through hole 54a is formed in a shape in which a portion of the exhaust side shaft portion 48a where the exhaust side cam 48b is not disposed can be rotatably inserted. Thereby, the inner wall surface of the exhaust-side frame through hole 54a forms an exhaust-side cam journal portion 58 that rotatably supports the exhaust-side camshaft 48.

In the first embodiment, a case where three exhaust side cam frame portions 54 are formed on the upper surface 20a of the cylinder head portion 20 will be described. That is, in the first embodiment, the cylinder head portion 20 has three exhaust side cam journal portions 58.
Therefore, in the first embodiment, the intake-side cam frame portion 52 and the exhaust-side cam frame portion 54 are formed in the same shape, and the exhaust-side cam frame portion 54 is further provided on the upper surface 20a of the cylinder head portion 20. One more than the frame part 52 is formed.
In the first embodiment, the three exhaust-side cam frame portions 54 are arranged in the first region E1 on the upper surface 20a of the cylinder head portion 20, respectively.
Therefore, in the first embodiment, the three exhaust side cam journal portions 58 are arranged in the first region E1 on the upper surface 20a of the cylinder head portion 20, respectively.

(Regarding the position of the intake side cam frame portion 52)
The reason why the intake side cam frame portion 52 is arranged in the second region E2 in the upper surface 20a of the cylinder head portion 20 will be described with reference to FIGS.
In the internal combustion engine having a separate head block structure, the intake-side cam frame portion 52 has two upper surfaces 20 a of the cylinder head portion 20 that are provided for one combustion chamber 22 when viewed from the axial direction of the cylinder 12. Arranged between the intake valve holes 32. That is, in the internal combustion engine having a separate head block structure, the intake side cam frame portion 52 is disposed in the first region E1 in the upper surface 20a of the cylinder head portion 20.

In the separate head block structure, the cylinder head part 20 and the cylinder block part 10 are individually cast. And it is the structure which mutually fastened the cylinder head part 20 and the cylinder block part 10 with the cylinder head bolt. Further, in FIG. 2, for the purpose of explanation, a virtual attachment position of a cylinder head bolt in an internal combustion engine having a separate head block structure is indicated by a reference numeral “VSP”.
The reason why the intake-side cam frame portion 52 is arranged in the first region E1 in the upper surface 20a of the cylinder head portion 20 in the internal combustion engine having a separate head block structure is as follows.

In the internal combustion engine having a separate head block structure, the cylinder head bolt is attached to the adjacent combustion chambers 22 on the upper surface 20a of the cylinder head 20 according to the strength required for the internal combustion engine. Between the provided intake valve holes 32.
The internal combustion engine 1 of the first embodiment has a head block integrated structure and does not require a cylinder head bolt. Therefore, in 1st embodiment, the opening part and space which insert a cylinder head bolt in the cylinder head part 20 and the cylinder block part 10 are not formed.
For this reason, in the first embodiment, the intake-side cam frame portion 52 can be disposed at a position where the cylinder head bolt is disposed in the internal combustion engine having a separate head block structure.

(Regarding the position of the nozzle mounting hole 24)
The reason why the nozzle mounting hole 24 is formed at a position where the conditional expression (5) is satisfied will be described with reference to FIGS.
As described above, in the internal combustion engine having the separate head block structure, the intake side cam frame portion 52 is located on the upper surface 20a of the cylinder head portion 20 with respect to one combustion chamber 22 when viewed from the axial direction of the cylinder 12. Between the two intake valve holes 32 provided. For this reason, in the internal combustion engine having a separate head block structure, the nozzle mounting hole 24 is formed immediately above the combustion chamber 22 (direct injection structure).

This is because the intake-side cam frame portion 52 is disposed closer to the intake pipe 2 than the combustion chamber 22, and it is difficult to secure a space in which the fuel injection nozzle 16 is disposed. Similarly, the exhaust side cam frame portion 54 is disposed closer to the exhaust pipe 8 than the combustion chamber 22, and it is difficult to secure a space in which the fuel injection nozzle 16 is disposed.
As described above, in the internal combustion engine 1 of the first embodiment, in the internal combustion engine having a separate head block structure, the intake-side cam frame portion 52 can be disposed at a position where the cylinder head bolt is disposed.
Thereby, the internal combustion engine 1 of the first embodiment can secure a space for disposing the fuel injection nozzle 16 on the intake pipe 2 side of the combustion chamber 22. Therefore, in the first embodiment, the nozzle mounting hole 24 can be formed at a position where the conditional expression (5) is satisfied.

(About the position of the plug mounting hole 26)
The reason why the plug attachment hole 26 is formed at a position where the conditional expression (6) is satisfied will be described with reference to FIGS.
As described above, in the internal combustion engine having a separate head block structure, the nozzle mounting hole 24 is formed immediately above the combustion chamber 22. For this reason, in the internal combustion engine having a separate head block structure, the plug mounting hole 26 is formed closer to the exhaust pipe 8 than the combustion chamber 22. This is to avoid interference between the spark plug 18 and the fuel injection nozzle 16.
As described above, the internal combustion engine 1 according to the first embodiment can secure a space for disposing the fuel injection nozzle 16 on the intake pipe 2 side of the combustion chamber 22. Therefore, in the first embodiment, the plug attachment hole 26 can be formed at a position where the conditional expression (6) is satisfied.

(About the opening area of the exhaust valve hole 42 and the opening area of the intake valve hole 32)
The reason why the opening area of the exhaust valve hole 42 is larger than the opening area of the intake valve hole 32 will be described with reference to FIGS.
As described above, in the internal combustion engine having the separate head block structure, the intake side cam frame portion 52 is located on the upper surface 20a of the cylinder head portion 20 with respect to one combustion chamber 22 when viewed from the axial direction of the cylinder 12. Between the two intake valve holes 32 provided. In addition, in the internal combustion engine having a separate head block structure, the exhaust-side cam frame portion 54 is located on the upper surface 20 a of the cylinder head portion 20 with respect to one combustion chamber 22 when viewed from the axial direction of the cylinder 12. Arranged between the two exhaust valve holes 42 provided.

This is because the position where the cylinder head bolt is attached on the upper surface 20a of the cylinder head portion 20 of the pair of exhaust valve holes 42 provided for one combustion chamber 22 according to the required strength or the like. It is because it becomes between.
As described above, the internal combustion engine 1 according to the first embodiment can secure a space for disposing the fuel injection nozzle 16 on the intake pipe 2 side of the combustion chamber 22. In addition, the plug attachment hole 26 can be formed at a position where the conditional expression (5) is satisfied. As a result, in the first embodiment, it is possible to ensure a sufficient space on the exhaust pipe 8 side of the combustion chamber 22 than on the intake pipe 2 side of the combustion chamber 22.
Therefore, in the first embodiment, the opening area of the exhaust valve hole 42 can be made larger than the opening area of the intake valve hole 32.

(Operation)
An example of an operation performed using the internal combustion engine 1 of the first embodiment will be described with reference to FIGS.
When the internal combustion engine 1 is operated, such as when the vehicle is used, the air sucked from the intake pipe 2 and the fuel injected from the nozzle mounting hole 24 into the combustion chamber 22 are mixed in the combustion chamber 22. Then, a spark generated by the spark plug 18 is ignited to the air-fuel mixture mixed in the combustion chamber 22, and the air-fuel mixture is combusted in the combustion chamber 22. Thereby, the energy generated by the combustion of the air-fuel mixture is transmitted to the driving device 6, and the burned gas is discharged to the outside air through the exhaust pipe 8.
In the first embodiment, the supercharger CH is connected to the intake pipe 2. For this reason, when the amount of air (intake amount) sucked into the combustion chamber 22 from the intake pipe 2 is increased when the vehicle is accelerated, the intake amount is forcibly increased by the supercharger CH. Thereby, the charging efficiency of the air supplied into the combustion chamber 22 is increased.

In the internal combustion engine 1 of the first embodiment, the opening area of the exhaust valve hole 42 is larger than the opening area of the intake valve hole 32.
Therefore, the amount of air (exhaust gas) that can pass through the exhaust valve hole 42 per unit time can be made larger than the amount of air (intake air) that can pass through the intake valve hole 32.
Thus, even when the intake air amount is increased by the supercharger CH, the decrease in the ratio of the exhaust amount to the intake air amount is suppressed, and the increase in the intake air amount by the supercharger CH is absorbed. Is possible.
Therefore, in the first embodiment, it is possible to suppress a decrease in exhaust efficiency and suppress a decrease in combustion efficiency with respect to the internal combustion engine 1.
The above-described first embodiment is an example of the present invention, and the present invention is not limited to the above-described first embodiment, and the present invention may be applied to other forms than this embodiment. Various modifications can be made according to the design or the like as long as they do not depart from the technical idea.

(Effects of the first embodiment)
If it is the internal combustion engine 1 of 1st embodiment, it will become possible to show the effect described below.
(1) The opening area of the exhaust valve hole 42 is made larger than the opening area of the intake valve hole 32.
For this reason, it is possible to make the exhaust amount per unit time larger than the intake amount per unit time.
As a result, even when the intake air amount is increased by the supercharger CH, the increase in the intake air amount by the supercharger CH is absorbed by suppressing a decrease in the ratio of the exhaust amount to the intake air amount. Is possible.
Thereby, with respect to the internal combustion engine 1, it is possible to suppress a decrease in exhaust efficiency and suppress a decrease in combustion efficiency. For this reason, it is possible to improve the torque and output generated by the internal combustion engine 1.

(2) The stroke St of the piston 14 is not less than the bore diameter BID of the cylinder 12.
As a result, the piston 14 can be kept at a higher speed and the exhaust efficiency can be improved as compared with the internal combustion engine 1 having the cylinder 12 having the same displacement and the stroke St less than the bore diameter BID. It becomes possible to make it.
(3) The distance INJ-EXTr between the nozzle mounting hole 24 and the exhaust valve hole 42 is made longer than the distance INJ-INTr between the nozzle mounting hole 24 and the intake valve hole 32.
For this reason, the position of the nozzle mounting hole 24 can be moved closer to the intake side than to the exhaust side of the internal combustion engine 1. As a result, the fuel injection nozzle 16 can be disposed on the intake side having a lower temperature than the exhaust side.
As a result, the deposit (carbon deposit) generated in the fuel injection nozzle 16 can be reduced.

(4) The distance SP-EXTr between the plug attachment hole 26 and the exhaust valve hole 42 is set to be longer than the distance SP-INTr between the plug attachment hole 26 and the intake valve hole 32.
As a result, the position of the plug mounting hole 26 can be set close to the intake side between the exhaust side and the intake side of the internal combustion engine 1. That is, the degree of freedom in designing the position where the spark plug 18 is disposed is improved.
(5) The plug mounting hole 26 is arranged at the center of the combustion chamber 22.
For this reason, the spark generated by the spark plug 18 can be generated at the center of the combustion chamber 22. Thereby, the combustion performance of the air-fuel mixture in the combustion chamber 22 can be improved.
As a result, the torque and output generated by the internal combustion engine 1 can be improved.

(6) The total opening area of the plurality of exhaust valve holes 42 opened in one combustion chamber 22 is made larger than the total opening area of the plurality of intake valve holes 32 opened in one combustion chamber 22.
For this reason, even when the intake air amount is increased by the supercharger CH, the decrease in the ratio of the exhaust amount to the intake air amount is suppressed, and the increase in the intake air amount by the supercharger CH is absorbed. Is possible.
As a result, it is possible to suppress a decrease in combustion efficiency by suppressing a decrease in exhaust efficiency with respect to the internal combustion engine 1. For this reason, it is possible to improve the torque and output generated by the internal combustion engine 1.

(7) A plurality of cylinders 12 in which the stroke directions of the pistons 14 are arranged in parallel are formed in the cylinder block portion 10. Also, the cylinder head portion 20 and the cylinder block portion 10 that are integrally cast together form a plurality of combustion chambers 22 that are arranged with the stroke direction of the pistons 14 parallel.
Further, the upper surface 20a of the cylinder head portion 20 is formed along the direction in which the plurality of cylinders 12 are arranged, and the first region E1 that overlaps the combustion chamber 22 when viewed from the axial direction of the cylinder 12 and two adjacent first regions E1. To the second region E2. In addition, the intake side cam journal portion 56 is disposed in the second region E2 of the upper surface 20a of the cylinder head portion 20.

For this reason, without increasing the distance between the intake-side cam frame portions 52, the position of the intake-side cam journal portion 56 is viewed from the axial direction of the cylinder 12. It becomes possible to displace from between the intake valve holes 32.
As a result, it is possible to improve the design freedom of the cylinder head portion 20 such as the layout of the nozzle mounting hole 24 and the plug mounting hole 26 and the shape and dimensions of the exhaust valve hole 42 and the intake valve hole 32.
Further, the position where the intake side cam journal portion 56 is arranged is not affected by the position where the cylinder head bolt is attached in the internal combustion engine having a separate head block structure.
Thereby, since it becomes possible to improve the design freedom of the cylinder head part 20 and the cylinder block part 10, the design freedom of the internal combustion engine 1 can be improved.

(8) The intake-side cam journal portion 56 is disposed in the second region E2 in the upper surface 20a of the cylinder head portion 20.
For this reason, without increasing the distance between the intake-side cam frame portions 52, the position of the intake-side cam journal portion 56 is viewed from the axial direction of the cylinder 12. It becomes possible to displace from between the intake valve holes 32.
As a result, the internal combustion engine 1 is increased in size and weight compared to the internal combustion engine 1 having a configuration in which the position of the intake side cam journal portion 56 is displaced by increasing the distance between the intake side cam frame portions 52. Can be suppressed.

(9) The intake-side cam journal portion 56 is disposed in the second region E2 in the upper surface 20a of the cylinder head portion 20.
For this reason, compared with the case where the intake side cam journal part 56 is disposed between two intake valve holes 32 provided for one combustion chamber 22, the intake side cam frame part 52 and the plug attachment hole 26. The distance between can be increased.
As a result, the intake-side cam journal portion 56 is inhaled by the influence of heat generated by the spark plug 18 as compared with the case where the intake-side cam journal portion 56 is disposed between the two intake valve holes 32 provided for one combustion chamber 22. The deformation of the side cam journal portion 56 can be suppressed.

(10) The mass of the exhaust valve head 44b is made larger than the mass of the intake valve head 34b. Further, the intake side cam frame portion 52 and the exhaust side cam frame portion 54 are formed in the same shape. In addition, the exhaust side camshaft 48 is rotatably supported by more exhaust side cam journals 58 than the intake side cam journals 56.
For this reason, the exhaust side camshaft 48 that displaces the exhaust valve 44 having a mass larger than that of the intake valve 34 according to the rotation is replaced with the exhaust side cam journal portion 58 that is larger than the intake side cam journal portion 56, and the exhaust side camshaft 58. 48 can be rotatably supported.
As a result, the exhaust side camshaft 48, which is required to be stronger than the intake side camshaft 38, is supported by more exhaust side cam journals 58 than the intake side cam journals 56. It is possible to distribute the applied load. Thereby, the durability of the exhaust side cam frame portion 54 can be increased. Further, it is possible to improve the stability of supporting the exhaust side camshaft 48.

(Modification)
(1) In the first embodiment, the intake side cam journal portion 56 is disposed in the second region E2 in the upper surface 20a of the cylinder head portion 20, but this is not a limitation.
That is, as shown in FIG. 7, the exhaust-side cam journal portion 58 may be disposed in the second region E <b> 2 in the upper surface 20 a of the cylinder head portion 20.
In this case, without increasing the distance between the exhaust side cam frame portion 54, the position of the exhaust side cam journal portion 58 is viewed from the axial direction of the cylinder 12, and two positions provided for one combustion chamber 22 are provided. It is possible to displace from between the exhaust valve holes 42.

Thereby, for example, it is possible to improve the design freedom of the cylinder head portion 20 such as the layout of the nozzle mounting holes 24 and the plug mounting holes 26 and the shapes and dimensions of the exhaust valve holes 42 and the intake valve holes 32.
Therefore, in the present invention, the position where the exhaust-side cam journal portion 58 is arranged is not affected by the position where the cylinder head bolt is attached in the internal combustion engine having a separate head block structure.
Thereby, since it becomes possible to improve the design freedom of the cylinder head part 20 and the cylinder block part 10, the design freedom of the internal combustion engine 1 can be improved.

(2) In the first embodiment, the intake side cam journal portion 56 is disposed in the second region E2 in the upper surface 20a of the cylinder head portion 20, but this is not a limitation.
That is, as shown in FIG. 8, the intake-side cam journal portion 56 and the exhaust-side cam journal portion 58 may be disposed in the second region E <b> 2 of the upper surface 20 a of the cylinder head portion 20.
In this case, without increasing the distance between the intake side cam frame portions 52, the position of the intake side cam journal portion 56 is viewed from the axial direction of the cylinder 12. It becomes possible to displace from between the intake valve holes 32. In addition to this, the position of the exhaust side cam journal portion 58 is not limited to the distance between the exhaust side cam frame portions 54, and the position of the exhaust side cam journal portion 58 is provided for one combustion chamber 22 when viewed from the axial direction of the cylinder 12. It is possible to displace from between the two exhaust valve holes 42.

Thereby, for example, it is possible to improve the design freedom of the cylinder head portion 20 such as the layout of the nozzle mounting holes 24 and the plug mounting holes 26 and the shapes and dimensions of the exhaust valve holes 42 and the intake valve holes 32.
Therefore, in the present invention, the positions at which the intake side cam journal part 56 and the exhaust side cam journal part 58 are arranged are not affected by the position at which the cylinder head bolt is attached in the internal combustion engine having a separate head block structure.
Thereby, since it becomes possible to improve the design freedom of the cylinder head part 20 and the cylinder block part 10, the design freedom of the internal combustion engine 1 can be improved.

(3) In the first embodiment, the internal combustion engine 1 is configured to ignite the air-fuel mixture in the combustion chamber 22 with the spark generated by the spark plug 18 (gasoline engine), but is not limited thereto. .
That is, the internal combustion engine 1 may be configured to ignite the air-fuel mixture in the combustion chamber 22 without using the spark plug 18 (diesel engine). In this case, for example, as shown in FIG. 9, the cylinder head portion 20 is configured not to have a plug mounting hole.
(4) In the first embodiment, the configuration of the internal combustion engine 1 is an in-line three-cylinder internal combustion engine (in-line three-cylinder engine), but is not limited thereto.
That is, the internal combustion engine 1 may be a V-type internal combustion engine (V-type engine) or a horizontally opposed internal combustion engine (horizontal opposed engine).

(5) In the first embodiment, the internal combustion engine 1 is configured such that a plurality of cylinders 12 are formed in the cylinder block portion 10 and a plurality of combustion chambers 22 are formed by the cylinder head portion 20 and the cylinder block portion 10. However, the present invention is not limited to this.
That is, for example, as shown in FIG. 10, the internal combustion engine 1 is configured such that only one cylinder 12 is formed in the cylinder block portion 10, and only one combustion chamber 22 is formed by the cylinder head portion 20 and the cylinder block portion 10. It is good also as a structure to form (single cylinder engine).
(6) In 1st embodiment, although the structure of the internal combustion engine 1 was set as the head block integrated structure, it is not limited to this.
That is, the configuration of the internal combustion engine 1 may be a head block separate structure.

DESCRIPTION OF SYMBOLS 1 ... Internal combustion engine, 2 ... Intake device, 4 ... Fuel tank, 6 ... Drive device, 8 ... Exhaust device, 10 ... Cylinder block part, 12 ... Cylinder, 14 ... Piston, 16 ... Fuel injection nozzle, 18 ... Spark plug, DESCRIPTION OF SYMBOLS 20 ... Cylinder head part, 20a ... Upper surface of cylinder head part, 22 ... Combustion chamber, 24 ... Nozzle attachment hole, 26 ... Plug attachment hole, 30 ... Intake passage, 32 ... Intake valve hole, 34 ... Intake valve, 34a ... Intake air Valve stem, 34b ... intake valve head, 34c ... intake valve spring, 36 ... intake valve guide hole, 38 ... intake side camshaft, 38a ... intake side shaft portion, 38b ... intake side cam, 40 ... exhaust passage, 42 ... exhaust Valve hole, 44 ... exhaust valve, 44a ... exhaust valve stem, 44b ... exhaust valve head, 44c ... exhaust valve spring, 46 ... Air valve guide hole, 48 ... exhaust side camshaft, 48a ... exhaust side shaft portion, 48b ... exhaust side cam, 50 ... out frame portion, 52 ... intake side cam frame portion, 52a ... intake side frame through hole, 54 ... exhaust Side cam frame, 54a ... Exhaust side frame through hole, 56 ... Intake side cam journal, 58 ... Exhaust side cam journal, CH ... Supercharger, St ... Piston stroke, BID ... Cylinder bore diameter, EXHvdi ... Inner diameter of exhaust valve hole, INTvdi: Inner diameter of intake valve hole, INJ-EXTr: Distance between center of nozzle mounting hole and center of exhaust valve hole, INJ-INTr: Center of nozzle mounting hole and center of intake valve hole , SP-EXTr ... Distance between the center of the plug mounting hole and the center of the exhaust valve hole, SP-INTr ... The distance between the centers of the intake valve holes of grayed mounting hole, E1 ... first region, E2 ... virtual attachment position of the second region, VSP ... cylinder head bolt

Claims

A cylinder block part that forms a cylinder, and a cylinder head part that forms a combustion chamber together with the cylinder block part,
The cylinder head portion has an intake passage for communicating the intake pipe and the combustion chamber, and an exhaust passage for communicating the exhaust pipe and the combustion chamber.
Connect a turbocharger to the intake pipe,
An opening area of an exhaust valve hole that is an opening portion of the exhaust passage that opens to the combustion chamber is made larger than an opening area of an intake valve hole that is an opening portion of the intake passage that opens to the combustion chamber. An internal combustion engine.
2. The internal combustion engine according to claim 1, wherein the stroke of the piston that reciprocates in the cylinder is equal to or larger than the bore diameter of the cylinder.
The cylinder head part further has a nozzle mounting hole for inserting a fuel injection nozzle into the combustion chamber,
The internal combustion engine according to claim 1 or 2, wherein a distance between the nozzle mounting hole and the exhaust valve hole is longer than a distance between the nozzle mounting hole and the intake valve hole. organ.
The cylinder head further has a plug mounting hole for inserting a spark plug into the combustion chamber,
The distance between the plug mounting hole and the exhaust valve hole is longer than the distance between the plug mounting hole and the intake valve hole. An internal combustion engine according to claim 1.
The cylinder head further has a plug mounting hole for inserting a spark plug into the combustion chamber,
The internal combustion engine according to any one of claims 1 to 4, wherein the plug mounting hole is disposed at a center of the combustion chamber.
The cylinder head portion has a plurality of intake passages and a plurality of exhaust passages for one combustion chamber,
The total opening area of the plurality of exhaust valve holes opened in the one combustion chamber is larger than the total opening area of the plurality of intake valve holes opened in the one combustion chamber. An internal combustion engine according to any one of claims 1 to 5.