JP2733025B2 - Engine cylinder head - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a cylinder head mounted on a cylinder block head of a vehicle engine.

[0002]

2. Description of the Related Art A cylinder block constituting an engine has a cylinder head mounted on the head thereof. It is known that the cylinder head is important as it affects the performance of the engine.

[0003] Many of these cylinder heads open and close the intake / exhaust port using a poppet valve. However, the poppet valve is so large that friction and internal consumption are so large that fuel consumption cannot be ignored. For this reason, in some cylinder heads, a rotor valve as shown in FIG. 31 was employed in place of the poppet valve.

That is, the cylinder head shown in FIG. 1 includes a rotor 51 rotatably built in a cylinder head body 50, and an intake valve passage 52 and an exhaust valve passage (shown in FIG. The rotor 51 is provided with a rotor shaft 53 and a bearing portion 54 for supporting the rotor shaft 53, as shown in FIG.

As shown in FIGS. 32 and 34, when the rotation of the rotor 51 causes the intake port 55 to communicate with the combustion chamber 56 via the intake valve passage 52, the intake port 55 is set to an open state. By intake port 5
5, the mixed gas is sucked into the combustion chamber 56 via the intake valve passage 52, and the mixed gas sucked into the combustion chamber 56 becomes an exhaust gas after being compressed and exploded and becomes an exhaust gas through the exhaust valve passage of the rotor 51 to the exhaust port side. Exhausted.

In order to prevent the heat generation of the rotor 51 and to secure the outer peripheral adhesion (sealability), there are two types of cylinder heads: a dry type (see FIG. 35) and a wet type (see FIG. 36).

[0007] In consideration of the difficulty of lubricating the rotor 51, the dry cylinder head is made of a ceramic oil-containing product or the like, and the lubrication of the rotor 51 is eliminated. The cylinder head is configured to directly supply oil to the outer peripheral surface of the rotor 51, thereby forming an oil film 57 on the outer peripheral surface of the rotor 51.

[0008]

However, the above-described conventional cylinder head has the following problems.

1. As shown in FIG.
2 has a structure that functions as a valve at both ends, so that three stages of pressure in the intake process, that is, the intake port 55
The pressure P ₂ of the inner, intake air pressure P ₁ of the valve passage 52, since the results pressure P ₀ in the combustion chamber 56, a large pressure difference is not obtained between the combustion chamber 56 and the intake valve passage 52, combustion The mixed gas cannot be sufficiently sucked into the chamber 56.

[0010] 2. As shown in FIG. 34, since the mixed gas in the intake port 55 flows straight into the combustion chamber 56 as it is via the intake valve passage 52, the mixing of gasoline and air becomes incomplete, and the mixed gas is ignited. Poor performance leads to a decrease in engine startability.

3. As shown in FIG. 33, the structure is such that the compression / explosion force of the mixed gas in the combustion chamber 56 is applied to the outer peripheral surface of the rotor 51.
A thick and rigid rotor shaft 53 that cannot withstand the explosive force and a large-diameter bearing portion 54 for supporting the rotor shaft 53 are required. Therefore, the cylinder head itself is heavy and large.

4. Since the exhaust gas passes through the exhaust valve passage of the rotor 51, the exhaust gas
1 is heated, and there is a problem such as an adverse effect due to the heat, such as an increase in the sliding resistance of the rotor 51.

In the conventional dry-type cylinder head, no matter what kind of surface treatment is applied to the outer peripheral surface of the rotor 51, minute irregularities remain on the outer peripheral surface of the rotor 51 as shown in FIG. Is inevitable, so the rotor 51
However, there are problems such as poor outer peripheral adhesion (sealability) and a large amount of heat generated by the rotor 51.

Further, according to the conventional wet cylinder head, since lubricating oil is directly supplied to the outer peripheral surface of the rotor 51, unnecessary lubricating oil is mixed into the combustion chamber and burned depending on the amount of lubricating oil supplied. This causes problems such as generation of smoke.

The present invention has been made in view of the above circumstances, and aims to improve the efficiency of inhaling mixed gas and ignitability, reduce the size, and prevent heat damage due to exhaust gas. Another object of the present invention is to provide a rotary valve type engine cylinder head.

[0016]

In order to achieve the above object, the invention according to claim 1 is provided so as to intersect with an intake port communicating with a combustion chamber, and connects the intake port side to the combustion chamber. And an exhaust valve passage provided to intersect the exhaust port communicating with the combustion chamber and connecting the combustion chamber to the exhaust port. An engine cylinder head having an exhaust rotor section, wherein the inlet rotor section or the exhaust rotor section is provided.
Pressure applied to the rotor is balanced at each rotor
And balance adjusting means causes, and pressure means to equalize the pressure in the pressure between the intake valve in the passage in the intake port comprises
The constant pressure means is formed at a downstream edge of the intake port.
Large diameter chamber with a larger inside diameter than the intake port
It is characterized by consisting of .

[0017]

[0018]

[0019]

[0020]

[0021]

[0022]

[0023]

[0024]

[0025]

[0026]

[0027]

[0028]

[0029]

[0030]

According to the present invention, since the pressure in the intake valve passage and the pressure in the combustion chamber are set equal by the constant pressure means, the pressure in the intake port is maintained just before the combustion chamber, and the pressure immediately before the combustion chamber and the pressure in the combustion chamber are maintained. A large pressure difference is created between

Further, according to the present invention, the balance adjusting means is provided with an inlet rotor section or an exhaust rotor section.
Pressure applied to the rotor is balanced at each rotor.
With this configuration, unnecessary load (compressive explosive force of the mixed gas) applied to the inlet rotor is reduced as much as possible.

[0032]

[0033]

[0034]

[0035]

[0036]

[0037]

[0038]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of an engine cylinder head according to the present invention will be described below in detail with reference to FIGS.

As shown in FIG. 1, the cylinder head has a combustion chamber 2 in a cylinder head main body 1 and an intake port 3 communicating therewith, and an inlet rotor section 4 is provided between the intake port 3 and the combustion chamber 2. The inlet rotor section 4 is installed so as to intersect with the intake port 3.

An intake valve passage 5 for connecting the combustion chamber 2 to the intake port 3 is formed in the body abdomen of the inlet rotor portion 4, and the intake valve passage 5 is provided at a crossing point with the intake port 3. And inlet rotor section 4
Is formed so as to penetrate the central axis of. Therefore, the mixed gas of gasoline and air in the intake port 3 can flow into the combustion chamber 2 from the downstream end 3 a of the intake port 3 via the intake valve passage 5.

At the boundary between the inlet rotor section 4 and the intake port 3, that is, at the downstream end 3a of the intake port 3, an enlarged diameter chamber 600 is provided at the edge as a constant pressure means 6.
No. 00 is formed with the outer peripheral surface of the inlet rotor section 4 as a part of the inner wall.

The diameter expansion chamber 600 is provided with a sufficiently larger inner diameter than the intake port 3 in order to equalize both pressures in the intake port 3 and the intake valve passage 5.

At the combustion chamber inlet 2a for introducing the mixed gas from the intake valve passage 5 into the combustion chamber 2, a flow plate 7 is provided as shown in FIG. 2, and the flow plate 7 is indicated by an arrow in the figure. Thus, the swirl is formed in the flow of the mixed gas.

As shown in FIG. 3, the inlet rotor section 4 is provided with balance adjusting means 8, and the balance adjusting means 8 comprises a balance adjusting chamber 800 and a pressure transmission path 801.

The balance adjustment chamber 800 is located on the side facing the combustion chamber 2 via the inlet rotor section 4 and is formed with the outer peripheral surface of the inlet rotor section 4 as a part of the inner wall. Is open to the balance control chamber 800, and the other end of the pressure transmission path 801 is connected to the combustion chamber 2
It is open to.

A sealing means 9 as shown in FIG. 4 is provided at the boundary between the inlet rotor section 4 and the combustion chamber 2, and the sealing means 9 is provided with a sealing chamber 900 cut out on the inner wall of the combustion chamber inlet 2a. A pair of inner and outer seal portions 901 and 902 housed in the seal chamber 900, a compression spring 903, and a ring seal portion 904. The sealing means 9 is also provided at the boundary between the inlet rotor 4 and the downstream end 3a of the suction port 3 (see FIG. 1).

The inner seal 901 is fixed to the front side of the seal chamber 900 and forms a wall between the seal chamber 900 and the combustion chamber 2, while the outer seal 902 is formed in the seal chamber 9.
00 and is provided to be vertically movable with respect to the inlet rotor unit 4.

Both of the seal portions 901 and 902 have contact portions 901a and 902a at their distal ends.
1a, 902a so as to be in contact with the outer peripheral surface of the inlet rotor portion 4, and the contact portions 901a, 9
In reference numeral 02a, the contact surface side with the inlet rotor section 4 is curved to match the outer peripheral shape of the inlet rotor section 4.

The compression spring 903 is inserted between the seal chamber 900 and the outer seal portion 902, and the outer seal portion 90
2 is constantly urged toward the inlet rotor portion 4, the ring seal portion 904 is interposed between the pair of inner and outer seal portions 901 and 902, and the mounting groove 901 b of the inner seal portion 901 is provided.
It is attached to.

As shown in FIG. 5, the cylinder head body 1
Has an exhaust port 10 communicating with the combustion chamber 2, and an exhaust rotor section 11 between the exhaust port 10 and the combustion chamber 2.
The exhaust rotor section 11 is configured to intersect with the exhaust port 10.

An exhaust valve passage 12 for connecting the combustion chamber 2 and the exhaust port 10 is formed in the abdomen of the body of the exhaust rotor portion 11, and the exhaust valve passage 12 is provided at the intersection with the exhaust port 10. And an oblique hole passing through the central axis of the exhaust rotor section 11.

The exhaust rotor section 11 is provided with a cooling passage 130 as a heat damage preventing means 13. The cooling passage 130 is formed independently of the exhaust valve passage 12, and is provided at the center axis of the exhaust rotor section 11. Along the vicinity of the exhaust valve passage 12.

One end of the cooling passage 130 communicates with a cool air feed passage 131 provided on the outer peripheral surface side of the exhaust rotor section 11, and the other end of the cooling passage 130 is provided on the end surface side of the exhaust rotor section 11. Cold air return passage 13
2.

The cooling passage 130 has a plurality of blades 22
Are provided at the boundary between the cooling passage 130 and the cool air return passage 132, and are mounted and fixed to the inner wall of the cooling passage 130. Therefore, when the exhaust rotor section 11 rotates, the blades 22,
22 rotate integrally with the exhaust rotor section 11, whereby the cool air return passage 132 is moved from the cool air feed passage 131 side.
Forced cold air is fed toward the side.

A rotor shaft 14 is integrally formed on the end surfaces of the inlet rotor portion 4 and the exhaust rotor portion 11, and the rotor shaft 14 is supported by a bearing portion 15 such as a ball bearing, and is not shown. It is connected to the crankshaft side via power transmission means such as gears and belts.

Next, the operation of the cylinder head configured as described above will be described with reference to FIGS.

According to this cylinder head, when the crankshaft of the engine rotates, its rotational force is transmitted to the rotor shaft 14 via power transmission means (not shown) such as gears and belts, and thereby the inlet rotor 4
And the exhaust rotor part 11 rotates integrally.

The intake valve passage 5 is connected to the intake port 3
, The intake port 3 is set to the open state, and the mixed gas is supplied from the intake port 3 to the combustion chamber 2 via the intake valve passage 5.

At this time, a large-diameter chamber 600 having a larger diameter than the intake port 3 is provided at the downstream end of the intake port 3. mixed gas flows, in the intake valve passage 5 the intake port 3 becomes equal pressure P _2.

That is, the intake port 3 until just before the combustion chamber 2
Maintained the pressure P ₂ of the inner is thereby since the large pressure difference between the pressure P ₀ in the combustion chamber 2 and the combustion chamber 2 just before the pressure P ₂ is obtained, a large amount of mixed gas within the combustion chamber 2 Inhaled.

When the mixed gas is sucked into the combustion chamber 2 as described above, the mixed gas passes through the flow plate 7 and a swirl is formed in the flow. For this reason, the mixing of gasoline and air is further promoted, and the mixing is completed.

The mixed gas in the combustion chamber 2 explodes after being compressed. In this compression explosion, a part of the compression explosion pressure is transmitted through the pressure transmission path 801 to the balance control chamber 80.
0, thereby canceling out the excessive compression explosion pressure acting on the inlet rotor section 4 from the combustion chamber 2 side, and the pressure balance of the inlet rotor section 4 is maintained.

When a gap is formed between the inlet rotor section 4 and the combustion chamber 2 due to the above-mentioned compression explosion pressure, the gap is closed by the sealing means 9.

That is, when the inlet rotor section 4 moves even slightly to the intake port 3 side, the outer seal section 902 moves in the same direction, and the contact section 902a of the outer seal section 902 and the inlet rotor section 4 move. The sliding gap is kept constant. For this reason, the mixed gas leaking from the outer peripheral surface side of the inlet rotor section 4 is reduced as much as possible.

When the intake valve passage 5 is independent of the intake port 3 without communicating with the intake port 3, the intake port 3 is set to a closed state.

On the other hand, the exhaust valve passage 12 is connected to the exhaust port 1
0, the exhaust port 10 is opened, exhaust gas is discharged from the combustion chamber 2 through the exhaust valve passage 12 to the exhaust port 10, and the exhaust port 10 is connected to the exhaust valve passage 1.
The exhaust port 10 is set to a closed state when the exhaust port 10 is independent without communicating with the exhaust port 2.

Therefore, the following effects can be obtained with the cylinder head of this embodiment.

1. Intake port 3 at the downstream end of intake port 3
Since the large-diameter chamber 600 is provided, a large amount of mixed gas flows into the intake valve passage 5 through the large-diameter chamber 600, and the pressure P in the intake port 3 is equal to that in the intake valve passage 5. ₂ , that is, it is possible to maintain the pressure P ₂ in the intake port 3 until immediately before the combustion chamber 2, whereby the pressure P ₂ immediately before the combustion chamber 2 and the pressure P ₀ in the combustion chamber 2 can be maintained.
Since a large pressure difference is obtained between the first and second combustion chambers, a large amount of the mixed gas is sucked into the combustion chamber 2 and the suction efficiency can be improved.

2. A flow plate 7 is installed at the combustion chamber inlet 2a,
Since the swirling plate 7 is configured to form a swirl in the flow of the mixed gas, the swirl further promotes the mixing of gasoline and air, and completes the mixing, thereby igniting the mixed gas. The performance can be improved.

3. A part of the compression explosion pressure acts on the balance control chamber 800 through the pressure transmission path 801, thereby canceling out the excessive compression explosion pressure acting on the inlet rotor unit 4 from the combustion chamber 2 side. For this reason, unnecessary load acting on the inlet rotor section 4 is reduced as much as possible, so that the rotor shaft 14 of the inlet rotor section 4 and the bearing section 15 supporting the same can be made small in diameter and small. Thus, the size and weight of the entire cylinder head can be reduced.

4. An outer seal portion 902 is provided that can follow the small radial movement of the inlet rotor portion 4, and the contact portion 902 a of the outer seal portion 902 is configured to contact the outer peripheral surface of the inlet rotor portion 4.
For this reason, if the inlet rotor part 4 moves even slightly to the intake port 3 side, the outer seal part 902 will move in the same direction.
Follows, and the sliding gap between the contact portion 902a of the outer seal portion 902 and the inlet rotor portion 4 is kept constant, so that the mixed gas leaking from the outer peripheral surface side of the inlet rotor portion 4 is as small as possible. It is possible to improve the sealing performance.

5. A cooling passage 130 is provided in the exhaust rotor section 11, and the exhaust rotor section 11 is cooled by cold air passing through the cooling passage 130. For this reason, the heating of the exhaust rotor section 11 by the exhaust gas is reduced as much as possible, and a bad effect due to the heat, for example, an increase in sliding resistance due to thermal expansion of the exhaust rotor section 11 can be prevented. The above embodiment
In the state, the balance adjusting means 8 of the inlet rotor 4 is
As described above, such a balance adjusting means 8 is
It can also be provided on the exhaust rotor section 11 side. You
That is, the balance adjusting means 8 of the inlet rotor section 4
Is connected to the combustion chamber via the inlet rotor 4 as described above.
2 and the inlet rotor 4
A balance adjustment chamber 800 having an outer peripheral surface as a part of the inner wall;
One end is opened to the balance control chamber 800, and the other end is set to the combustion chamber 2
And a pressure transmission path 801 opened to the outside.
Balance adjusting means of the exhaust rotor unit 11 (not shown,
3 (refer to reference numeral 8 in FIG. 3) via the exhaust rotor section 11.
And is located on the side facing the combustion chamber 2 and the exhaust
Balance adjustment with the outer peripheral surface of the rotor section 11 as a part of the inner wall
Chamber (not shown, see reference numeral 800 in FIG. 3) and its balun
Pressure opening at one end to the combustion chamber 2 and opening at the other end to the combustion chamber 2
Consists of a force transmission path (not shown, see 801 in FIG. 3)
Is done. And, the balance adjustment of the inlet rotor section 4
In the means 8, as described above, the
Adjustments are made to balance the pressure
The balance adjusting means of the rotor 11 has an inlet
Pressure applied to the exhaust rotor section 11 instead of the rotor section 4
Adjustments are made to balance the forces. Each rose in this way
The means for adjusting the inlet is the inlet rotor section 4 or exhaust.
The pressure applied to the rotor section 11 is applied to each rotor section.
And it is configured to balance.

FIG. 6 shows another embodiment of the cylinder head according to the present invention. The difference between the cylinder head shown in FIG.
01 and an intake communication channel 602.

In the cylinder head shown in the figure, the downstream end side of the intake port 3 is formed in a tapered shape having the same sectional area.
This is used as the port widening section 601 as the inlet rotor section 4.
Is formed to extend to the end face side.

That is, the port widening portion 601 has a flared shape as shown in FIGS. 8 to 13, but is formed to have the same sectional area regardless of where it is cut.

On the other hand, an intake communication path 602 is formed in the inlet rotor section 4, and the intake communication path 602 is formed from the end face side of the inlet rotor section 4 toward the back, and the port widening is performed. It is provided so as to communicate with the portion 601 and the intake valve passage 5.

The inlet rotor portion 4 of this embodiment is formed such that the port widening portion 601 side is formed in a thin cylindrical body, and the inside of the cylindrical body is used as an intake communication passage 602. Such an intake valve of the inlet rotor portion 4 The passage 5 is configured to penetrate the thin abdomen of the cylindrical body and communicate with the intake communication passage 602.

In particular, the intake communication path 602 is provided with a sufficiently larger inner diameter than the intake port 3 in order to equalize both pressures in the intake port 3 and the intake valve passage 5.

As shown in FIG. 7, four blades 22, 22,... Are provided in the intake communication path 602 in a cross shape, and these blades 22, 22,.
Further, it is mounted and fixed to the inner wall of the intake communication path 602.

When the inlet rotor portion 4 rotates, the blades 22, 22... Rotate integrally with the inlet rotor portion 4, thereby causing the intake port 3 and the port widening portion 60 to rotate.
1 and the mixed gas is forcibly fed to the intake valve passage 5 via the intake communication passage 602.

Note that one end of the rotor shaft 14 of the inlet rotor section 4 penetrates the port widening section 601 and is supported by a bearing section (not shown) such as a ball bearing. ,
And the end face of the inlet rotor section 4 and the port widening section 60
Seals 16 and 16 are provided between them.

According to the cylinder head having such a configuration, the mixed gas in the intake port 3 flows into the intake valve passage 5 through the port widening portion 601 and the intake communication passage 602.

At this time, since the inside diameter of the intake communication path 602 is provided sufficiently larger than that of the intake port 3, as shown by the arrow in FIG.
A large amount of the mixed gas flows into the intake valve passage 5 through the intake port 3, and the pressure P ₂ in the intake valve passage 5 becomes the pressure P in the intake port 3.
Equals ₂ .

That is, even with this cylinder head,
As described above, the pressure P ₂ in the intake port 3 is maintained until immediately before the combustion chamber 2, so that a large pressure difference is obtained between the pressure P ₂ immediately before the combustion chamber 2 and the pressure P ₀ in the combustion chamber 2. As a result, a large amount of the mixed gas is sucked into the combustion chamber 2, and the suction efficiency can be improved.

The blades 22, 22,...
15 and may be omitted as shown in FIG.

FIG. 16 shows another embodiment of the cylinder head according to the present invention. The difference between the cylinder head shown in FIG. 16 and the above-mentioned embodiment is that the constant pressure means 6 includes an intake pipe widening section 603, a vertical hole section 604, The point is that it is constituted by an intake pipe extension 605.

In the cylinder head shown in the figure, the intake port 3 (see FIG. 1) comprises an intake pipe 300, and the downstream end of the intake pipe 300 is arranged on the end face side of the inlet rotor section 4.

The downstream end side of the intake pipe 300 is the intake pipe widening section 6.
03, and the intake pipe widening portion 603 is formed in a tapered shape having the same sectional area. That is, the intake pipe widening portion 603 has a flared shape similarly to the port widening portion 601 shown in FIG. 8, but is formed so that the cross-sectional area is the same regardless of where it is cut.

On the other hand, a vertical hole 604 is provided in the inlet rotor section 4, and the vertical hole 604 is formed from the end face of the inlet rotor section 4 toward the back and communicates with the intake valve passage 5. Further, an intake pipe extension 605 is inserted into the vertical hole 604.

The intake pipe extension section 605 is provided with an intake pipe widening section 603.
In other words, the intake pipe extension 605 is formed from the intake pipe widening portion 603 to the inside of the vertical hole 604 as described above, and the upstream end 605a of the intake pipe extension 605 is an intake pipe widening. The downstream end 605 b of the intake pipe extension 605 is provided so as to face one end of the intake valve passage 5.

In short, the inlet rotor section 4 of the present embodiment is formed by forming the intake pipe widening section 603 side into a thin cylindrical body and inserting the intake pipe extension section 605 inside the cylindrical body. The intake valve passage 5 of the inlet rotor portion 4 penetrates the thin abdomen of the cylindrical body and extends the intake pipe extension portion 605.
Is configured so as to face the downstream end 605b.

In particular, the intake pipe extension 605 is connected to the intake port 3
In order to equalize both pressures in the inside and the intake valve passage 5, the inside diameter is provided sufficiently larger than the intake port 3.

At the downstream end 605b of the intake pipe extension 605, a seal 16 is provided between the intake pipe extension 605 and the vertical hole 604 as shown in FIG.
Is given.

According to the cylinder head having the above-described structure, the mixed gas in the intake pipe 300 is supplied to the intake pipe widening portion 603,
The air flows into the intake valve passage 5 through the intake pipe extension 605.

At this time, since the inside diameter of the intake pipe extension 605 is sufficiently larger than that of the intake port 3, a large amount of mixed gas flows into the intake valve passage 5 from the intake pipe widening section 603 via the intake pipe extension 605. Then, the pressure P ₂ is equalized in the intake port 3 and the intake valve passage 5.

That is, even with this cylinder head,
As described above, the pressure P ₂ in the intake port 3 is maintained until immediately before the combustion chamber 2, so that a large pressure difference is obtained between the pressure P ₂ immediately before the combustion chamber 2 and the pressure P ₀ in the combustion chamber 2. As a result, a large amount of the mixed gas is sucked into the combustion chamber 2, and the suction efficiency can be improved.

FIG. 18 shows another embodiment of the cylinder head according to the present invention. The cylinder head shown in FIG. Instead of providing the exhaust valve passage 12 as a cool air passage, the present invention is not limited thereto.

The heat damage preventing means 13 of the cylinder head shown in FIG. 9 includes a concave passage 133, a cool air feed passage 131, an outer peripheral passage 134, and a cool air return passage 132.

The concave passage 133 is provided in the exhaust rotor 1
1 is provided from the end face toward the back thereof, and the tip is formed to extend to a position near the exhaust valve passage 12.

The cool air feed passage 131 communicates with the concave passage 133 from the end face side of the exhaust rotor section 11 and supplies cool air to the concave passage 133.

The outer peripheral passage 134 is connected to the exhaust rotor 1
1, the exhaust rotor portion 11
Is formed as a part of the inner wall, and one end 134a of the outer peripheral passage 134 communicates with the concave passage 133, while the other end of the outer peripheral passage 134 uses the exhaust valve passage 12 as a cooling passage except during exhaust. As a cooling medium supply port 134b.

That is, the cooling medium supply port 134b of the outer peripheral passage 134 is located on the side facing one end of the exhaust valve passage 12,
In addition, one end of the exhaust valve passage 12 is provided at a position where the exhaust valve passage 12 passes except during exhaust.

The plurality of blades 22, 22 are provided in the concave passage 133.
Are provided, and these blades 22, 22 are provided with a concave passage 133, a cool air feed passage 131, and an outer peripheral passage 134.
And is attached to the inner wall of the concave passage 133.

When the exhaust rotor 11 rotates, the blades 22, 22,...
1 and thereby, the forced air supply of the cool air is performed from the cool air feed passage 131 side to the outer circumferential passage 134 side via the concave passage 133.

According to the cylinder head having such a structure, the exhaust valve passage 12 not only communicates with the exhaust port 10 when the exhaust rotor section 11 rotates, but also the cooling medium in the outer peripheral passage 134 except when exhaust gas is exhausted. Supply port 1
34b.

As described above, when the exhaust valve passage 12 communicates with the cooling medium supply port 134b of the outer peripheral passage 134, the cool air feed passage 131, the concave passage 133, the outer peripheral passage 134, the exhaust valve passage 12, and the cool air return passage 132 are provided. Cool air passes through the exhaust rotor unit 1
1 is cooled from both inside and outside.

FIG. 19 shows another embodiment of the cylinder head according to the present invention. The cylinder head shown in FIG. 19 has a point that the exhaust port 10 (see FIG. The exhaust valve passage 12 and its peripheral structure are different from those of the above embodiment.

That is, the exhaust valve passage 12 of this cylinder head is provided at the boundary 11a between the end face of the exhaust rotor section 11 and its outer peripheral face, and one end of the exhaust valve path 12 is provided on the outer peripheral face side of the exhaust rotor section 11. The exhaust valve passage 12 is configured to communicate with the exhaust pipe 100 from the end face side of the exhaust rotor section 11.

The exhaust pipe 100 is provided independently of the cylinder head body 1, and is configured to send exhaust gas from the exhaust valve passage 12 to an exhaust manifold (not shown).

According to the cylinder head having the above structure, the exhaust valve passage 12 is provided at the boundary 11a between the end face of the exhaust rotor section 11 and the outer peripheral surface thereof. Passage 12
Is sent to an exhaust pipe 100 independent of the cylinder head body 1. For this reason, since the contact area between the exhaust rotor section 11 and the exhaust gas is reduced, the heating of the exhaust rotor section 11 by the exhaust gas is reduced as much as possible, and adverse effects due to the heat, for example, thermal expansion of the exhaust rotor section 11 are caused. An increase in sliding resistance and the like can be prevented.

FIG. 20 shows another embodiment of the cylinder head according to the present invention. The cylinder head shown in FIG. 20 also has a point that the exhaust port 10 (see FIG. The exhaust valve passage 12 and its peripheral structure are different from those of the above embodiment.

That is, in this cylinder head, the end face side of the exhaust rotor section 11 has a thin cylindrical body 110.
The exhaust valve passage 12 is formed in the abdomen of the cylindrical body 110.
Is provided so as to penetrate therethrough, and an exhaust pipe 100 having an L-shaped tip which is communicated with the exhaust valve passage 12 is inserted into the cylindrical body 110. It is to be noted that the exhaust pipe 100 is provided independently of the cylinder head main body 1 as in the above embodiment.

Even in the cylinder head having such a configuration, since the exhaust valve passage 12 having a short length enough to penetrate the thin portion of the cylinder 110 is provided, the contact area between the exhaust rotor portion 11 and the exhaust gas is reduced. Heating of the exhaust rotor section 11 by the exhaust gas is small as much as possible, so that adverse effects due to the heat can be prevented.

FIG. 21 shows another embodiment of the cylinder head according to the present invention. When the cylinder head shown in FIG. 21 is different from the above-described embodiment, the exhaust rotor section 11 is positively moved through a cooling passage or the like. Instead of cooling down
The point is that the heat of the exhaust gas transmitted to the exhaust rotor section 11 is blocked by the heat insulator 18.

That is, in this cylinder head, a cylindrical heat insulator 18 made of ceramic or the like is mounted on the inner wall of the exhaust valve passage 12.
2 is formed so as to cover the entire inner wall.

As in the above-described embodiment, even when the heat is blocked by the heat insulator 18, the heating of the exhaust rotor portion 11 by the exhaust gas is reduced as much as possible, and the adverse effect due to the heat can be prevented. is there.

FIG. 22 shows another embodiment of the cylinder head according to the present invention. In the cylinder head shown in FIG. 22, the first and second inlet rotor sections 4, 4 and the exhaust rotor sections 11, 11 are integrated. The first and second exhaust rotor portions 11 and 11 are provided with a first and second exhaust rotor portions 11 and 11, respectively.
Are provided between the inlet rotor portions 4 and 4.

Since the basic structures of the inlet rotor sections 4, 4 and the exhaust rotor sections 11, 11 are the same as those of the above embodiment, detailed description thereof will be omitted, and here, means for preventing heat damage of the exhaust rotor sections 11, 11 will be described. 13 will be described.

As shown in FIG. 22, an exhaust valve passage 12 is provided in the first and second exhaust rotor portions 11, 11.
The cooling passage 130 is provided separately and independently from the exhaust rotor unit 1.
Exhaust valve passages 12, 12 along the central axis of
Of the cooling passage 130
Are provided with openings 130a, 130a for introducing and discharging cooling water from between the two exhaust rotor sections 11, 11.

Openings 130a, 130 of cooling passage 130
A plurality of blades 22 are attached to a.
When the rotor 19 rotates, the blades 22, 22,... Also rotate integrally with the rotor 19, thereby forcibly sending cold water to the cooling passage 130 from between the two exhaust rotor portions 11, 11 through the opening 130a.

The inlet rotor section 4 and the exhaust rotor section 11 can be provided separately from each other instead of being integrated. In this case, as shown in FIG. 23, the cooling passage 130 extends from one end to the other end of the exhaust rotor section 11. The cooling water may be supplied to the cooling passage 130, and a plurality of blades 22, 22... Similar to those in the above embodiment are attached to both ends of the cooling passage 130. , 22... Is preferably performed.

FIG. 24 shows another embodiment of the cylinder head according to the present invention. The cylinder head shown in FIG. 24 is provided with oil supply means 21 for supplying oil to the inlet rotor section 4, and The supply means 21 includes an oil supply passage 210 provided in the cylinder head main body 1, an oil recovery chamber 211, and an oil cut plate 212.

One end of the oil supply passage 210 is opened at a position facing the outer peripheral surface of the inlet rotor section 4.
Oil is fed into the oil supply passage 210 from the other end.

[0124] The oil recovery chamber 211 is
The oil recovery chamber 211 is provided halfway from one end of the oil recovery passage 2 to the combustion chamber 2, and the outer peripheral surface of the inlet rotor portion 4 is formed as a part of the inner wall. Have been.

[0125] The oil cut plate 212 is
1 is arranged on the inlet rotor section 4 side, and one side edge thereof is configured to contact the outer peripheral surface of the inlet rotor section 4.

The oil cut plate 212 is constantly urged toward the inlet rotor section 4 by compression springs 214 and 214 as shown in FIG.
14 is the inner wall of the oil recovery chamber 211 and the oil cut plate 21
2 are interposed.

According to the cylinder head having such a configuration, when the inlet rotor section 4 rotates, the oil supply passage 2
Oil is supplied from 10 to the outer peripheral surface of the inlet rotor section 4, and the supplied oil is removed by an oil cut plate 212 except for a part at a stage preceding the combustion chamber 2.

That is, as shown in FIG. 26, not all of the supplied oil remains on the outer peripheral surface of the inlet rotor portion 4, but the heat generation of the inlet rotor portion 4 is suppressed, and the outer peripheral surface of the inlet rotor portion 4 is closely contacted. Only the amount of oil sufficient to improve the performance remains, and the other excess oil is removed by the oil cut plate 212 before the combustion chamber 2. Then, the removed oil reaches the oil recovery passage 213 through the oil recovery chamber 211.

Therefore, according to the cylinder head as described above, it is possible not only to prevent the heat generation of the inlet rotor section 4 and to improve the close contact of the outer circumference of the inlet rotor section 4 but also to reduce the oil mixed in the combustion chamber 2. Since the amount is reduced as much as possible, it is also possible to prevent the generation of smoke emissions due to the burning of such oils.

The supply of oil to the inlet rotor section 4 is performed as shown in FIG.
An orifice portion 215 is provided at one end of the oil supply passage 10, and oil is supplied from the orifice portion 215 to the outer peripheral surface of the inlet rotor portion 4. Alternatively, as shown in FIG. May be inserted and supplied, and oil may be supplied to the outer peripheral surface of the inlet rotor section 4 via the oil absorber 216.

Further, as described above, the oil supply passage 210
Instead of supplying oil via the engine, oil-containing air in the crank chamber of the engine may be supplied to the outer peripheral surface of the inlet rotor section 4. In this case, as shown in FIG. A passage 217 communicating with the crank chamber (not shown) may be provided, and a part of the outer peripheral surface of the inlet rotor portion 4 may be located in the middle of the passage 217.

As shown in FIG. 30, two oil cut plates 212 may be provided, and the number is not limited.

[0133]

Since the cylinder head according to the present invention is provided with a constant pressure means for equalizing the pressure in the intake port and the pressure in the intake valve passage, the boundary between the intake valve passage and the combustion chamber, that is, combustion, The pressure in the intake port is maintained until just before the chamber, and a large pressure difference is obtained between the pressure immediately before the combustion chamber and the pressure in the combustion chamber. Can be improved.

In addition, the cylinder head reduces the pressure applied to the inlet rotor or the exhaust rotor.
Each of the rotor units is provided with balance adjusting means for balancing. For this reason, unnecessary load acting on the inlet rotor portion and the like is reduced as much as possible, and it is possible to make the rotor shaft of the inlet rotor portion and the like and the bearing portion and the like supporting the rotor shaft small and small. Through this, the size and weight of the entire cylinder head can be reduced.

[0135]

[0136]

[0137]

[0138]

[0139]

[0140]

[Brief description of the drawings]

FIG. 1 is a sectional view showing one embodiment of the present invention.

FIG. 2 is a sectional view showing one embodiment of the present invention.

FIG. 3 is a sectional view showing one embodiment of the present invention.

FIG. 4 is a sectional view showing one embodiment of the present invention.

FIG. 5 is a sectional view showing one embodiment of the present invention.

FIG. 6 is a sectional view showing another embodiment of the present invention.

FIG. 7 is a sectional view taken along line II of FIG. 6;

FIG. 8 is an explanatory diagram of a port widening portion.

FIG. 9 is a sectional view taken along line II of FIG. 8;

FIG. 10 is a sectional view taken along line II-II of FIG. 8;

FIG. 11 is a sectional view taken along the line III-III of FIG. 8;

FIG. 12 is a sectional view taken along line IV-IV of FIG. 8;

FIG. 13 is a sectional view taken along line VV of FIG. 8;

FIG. 14 is a sectional view showing another embodiment of the present invention.

FIG. 15 is a sectional view taken along line III-III of FIG. 8;

FIG. 16 is a sectional view showing another embodiment of the present invention.

FIG. 17 is a sectional view taken along line II of FIG. 16;

FIG. 18 is a sectional view showing another embodiment of the present invention.

FIG. 19 is a sectional view showing another embodiment of the present invention.

FIG. 20 is a sectional view showing another embodiment of the present invention.

FIG. 21 is a sectional view showing another embodiment of the present invention.

FIG. 22 is a sectional view showing another embodiment of the present invention.

FIG. 23 is a sectional view showing another embodiment of the present invention.

FIG. 24 is a sectional view showing another embodiment of the present invention.

FIG. 25 is an explanatory diagram around the oil cut plate.

FIG. 26 is an explanatory diagram of the operation of the oil cut plate.

FIG. 27 is a sectional view showing another embodiment of the present invention.

FIG. 28 is a sectional view showing another embodiment of the present invention.

FIG. 29 is a sectional view showing another embodiment of the present invention.

FIG. 30 is a sectional view showing another embodiment of the present invention.

FIG. 31 is a sectional view of a conventional cylinder head.

FIG. 32 is a sectional view of a conventional cylinder head.

FIG. 33 is a sectional view of a conventional cylinder head.

FIG. 34 is a sectional view of a conventional cylinder head.

FIG. 35 is a sectional view of a conventional cylinder head.

FIG. 36 is a sectional view of a conventional cylinder head.

[Explanation of symbols]

 Reference Signs List 2 Combustion chamber 3 Intake port 4 Inlet rotor part 5 Intake valve passage 6 Constant pressure means 7 Flowing plate 8 Balance adjusting means 9 Sealing means 10 Exhaust port 11 Exhaust rotor part 12 Exhaust valve passage 18 Heat insulator 21 Oil supply means 100 Exhaust pipe 130 Cooling passage 134b Cooling medium supply port 210 Oil supply passage 211 Oil recovery chamber 212 Oil cut plate 300 Intake pipe 600 Large diameter chamber 601 Port widening section 602 Intake communication path 603 Intake pipe widening section 604 Vertical hole section 605 Intake pipe extension section 800 Balance adjustment Chamber 801 Pressure transmission path 900 Seal chamber 902 Seal part 902a Contact part 903 Compression spring

──────────────────────────────────────────────────の Continued on the front page (51) Int.Cl. ⁶ Identification code Agency reference number FI Technical display location F01P 3/14 F01P 3/14 Z F02F 1/24 F02F 1/24 F 1/42 1/42 E H N (56) References JP-A-63-227915 (JP, A) JP-A-63-55311 (JP, A) JP-A-60-107307 (JP, U) JP-A-57-51111 (JP, U) Japanese Utility Model Application No. Sho 57-49507 (JP, U) Japanese Utility Model Application No. Sho 63-14812 (JP, U) Japanese Utility Model Application No. Sho 61-41809 (JP, U) US Pat. No. 4,546,743 (US, A) Japanese Patent Publication No. Sho 59-26770 (JP) , B2) Jikken Sho 59-10332 (JP, Y2) Jigaku Sho 58-34249 (JP, Y2)

Claims (1)

(57) [Claims] 1. An inlet rotor section provided to intersect an intake port communicating with a combustion chamber, and having an intake valve passage for connecting the intake port side to the combustion chamber, and communicating with the combustion chamber. An exhaust rotor portion provided with an exhaust valve passage for connecting the combustion chamber and the exhaust port side, wherein the exhaust rotor portion is provided so as to intersect with the exhaust port, and the inlet rotor portion or For the exhaust rotor
Balance the applied pressure in each rotor section
That a balance adjustment means, comprising a pressure means for equalizing the pressure in the pressure between the intake valve in the passage in the intake port, together with the pressure means, is formed in the downstream edge of the intake port, the intake port
A cylinder head for an engine comprising an enlarged chamber having an inner diameter larger than that of the cylinder head.