JPH0718345B2 - Internal combustion engine - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to an internal combustion engine, and more particularly to an internal combustion engine improved to be suitable for a vehicle.

BACKGROUND ART In this main internal combustion engine, the intake port is a direct port, a vortex port, a helical port,
It is formed in a port with a shroud valve, a masked port, etc. to give a swirl to the cylinder chamber, promote mixture generation and combustion, improve combustion, and change its directional port and helical port. In addition to arranging the diaphragm and giving swirl to the cylinder chamber,
Combustion has been improved by changing the amount of intake air according to the engine load.

However, in those intake ports, the swirl ratio cannot be changed according to the engine speed and the load, and the current situation is that combustion is not improved so much.

Objects and problems of the present invention are to expand the variable range of the swirl ratio and flow coefficient of the port, and optimize the swirl ratio and flow coefficient of the port according to the engine speed, load, intake air temperature, etc. Control to improve combustion, realize highly efficient combustion, improve heat load, fuel consumption rate, and startability including cold start, improve exhaust gas characteristics, and improve engine output characteristics. There is an improvement in internal combustion engines.

Outline of Structural Invention Concerning Object / Problem: Contents of Claimed Invention In relation to the above-mentioned object / problem, an internal combustion engine of the present invention is
A low swirl type intake port formed in the cylinder head, which has a port opening for opening a valve seat in the cylinder chamber, and an opening on the inner wall surface of the intake port facing the port opening.・ Valve formed on the head ・ Valve arranged on the guide bore ・
A guide, a valve stem fitted to the valve guide, and an intake valve that is guided by the valve guide to open and close the port opening, and rotatable between the valve guide and the valve stem Supported on the valve guide at one end and the valve guide at the other end.
The sleeve shaft located at the upper end of the guide and the root of the sleeve in the intake port
The vane body is fixed to one end of the shaft, and the tip extends toward the port opening side, the port throttle surface formed on the front side of the vane body, and the port throttle on the side protruding to the inner wall surface of the intake port. A low swirl area that is connected to the surface and is formed by a side flow guide surface formed on the front side of the vane body and a wraparound main flow guide surface formed on the back side of the vane body, and that follows the inner wall surface of the intake port. , With respect to the flow of inflow air, upstream of the low swirl region, the high swirl region protruding to the inner wall surface of the intake port, and with respect to the flow of inflow air, the intake air at the downstream side of the low swirl region. Through the swirl control vane and its sleeve shaft that are rotated in the extremely low swirl area located on the inner wall surface side of the port. Actuator that rotates the swirl control vane to its low swirl range, high swirl range, and extremely low swirl range, and that actuator is driven according to signals from the rotation speed sensor, load sensor, intake air temperature sensor, etc. It is equipped with a controller that changes the swirl ratio and flow rate coefficient of the port according to the engine speed, load, intake air temperature, etc., and optimally controls it. Gives an optimum swirl ratio to the air-fuel mixture flowing into the pipe, and at the same time gives a high flow coefficient to that port,
In addition, in a compression ignition type engine, an optimum swirl ratio is given to the intake air flowing into the cylinder chamber, and at the same time, a high flow coefficient is given to the port to obtain the optimum inflow amount of the air-fuel mixture and intake air, and It makes efficient combustion.

Description of Specific Examples Preferred specific examples of the internal combustion engine according to the present invention will be described below with reference to the drawings.

1 to 12 partially show an embodiment 10 of an internal combustion engine of the invention adapted to be mounted on a truck.

This internal combustion engine 10 is embodied in a diesel engine with a low swirl type intake port 12, and its intake port 15 is seated in a valve seat 22 fixedly arranged in a port opening 21. It is arranged in 12 and is manufactured into a structure that is opened and closed by a valve mechanism (not shown).

In the diesel engine 10, an optimum swirl ratio is given to the intake air flowing into the cylinder chamber 31 in accordance with the engine speed, the load, and the intake air temperature, and at the same time, the intake port 12 has a high flow coefficient (Cms). ) Is given, the means for accurately and surely obtaining the optimum inflow amount of intake air is provided.

More specifically, the diesel engine 10
Is a low swirl type intake port 12 formed in the cylinder head 11 and a port opening 21 having a valve seat 22 attached to the cylinder chamber 31.
Is projected to the inner wall surface 20 of the intake port 12,
Valve mounting boss formed on the cylinder head 11
13 and a valve guide bore 23 formed in the cylinder head 11 by being opened at the lower end surface of the valve mounting boss 13 corresponding to the inner wall surface 20 of the intake port 12 and facing the port opening 21. Valve guide 14 located at
An intake valve 15 that fits a valve stem 16 to the valve guide 14 and that opens and closes the port opening 21 guided by the valve guide 14, the valve guide 14 and the valve stem 16 A sleeve shaft 17 which is rotatably supported between the one end and the other end of the guide 14 and the other end of the valve guide 14, respectively. Fixed at one end of 17 and its intake port
Within 12, the swirl control vane 18 rotated through the low swirl region 24, the high swirl region 25, and the extremely low swirl region 26 and the swirl control vane 18 through the sleeve shaft 17 thereof. Its low swirl range 24, high swirl range 25, and extremely low swirl range
An actuator (not shown) that rotates the actuator 26, a worm gear mechanism 27 that transmits the torque of the actuator to the sleeve shaft 17, a rotation speed sensor (not shown), a load sensor (not shown), and An intake air temperature sensor (not shown) is electrically connected, and a controller (not shown) for driving the actuator according to signals from the sensors is provided.

The shape of the intake port 12 is designed with the swirl control vane 18 in a low swirl region 24 along the inner wall surface of the intake port 12, but in that case, Even in various intake ports, the port shape is designed to have a high flow coefficient (Cms) at a low swirl ratio over the entire engine speed range.

For example, when the intake port 12 is manufactured as a helical port, the port shape of the intake port 12 is such that the normal helical port is brought close to the directional port.

The low swirl type intake port 12 is manufactured in a port shape assuming a helical port as understood from FIGS. 6, 8 and 10.

The sleeve shaft 17 is fitted between the valve stem 16 of the intake valve 15 and the valve guide 14, and is rotatably supported around the valve stem 16 and has one end thereof. The swirl control vane 18 and the worm wheel 35 of the worm gear mechanism 27 of the swirl control vane 18 can be attached to the lower end of the guide 14 and the other end of the guide 14 to the upper end of the valve guide 14.

The swirl control vane 18 is, as can be seen from FIGS. 1 to 6, one end of its sleeve shaft 17 projecting below the lower end of its valve guide 14, below its valve mounting boss 13, namely, Fixed to the lower end of the sleeve shaft 17
As the shaft 17 is rotated around its valve stem 16, its low swirl range 24, high swirl range 25,
And it is rotated to the extremely low swirl area 26. Of course, the low swirl area 24 is a location along the inner wall surface 20 of the intake port 12, as shown in FIGS. 8 and 9.
As shown in FIGS. 6 and 7, the high swirl region 25 has an inner wall surface 20 of the intake port 12 on the upstream side of the low swirl region 24 with respect to the flow of inflow air, that is, intake air. Further, the extremely low swirl region 26 is, as shown in FIGS. 10 and 11, the downstream side of the low swirl region 24 with respect to the flow of the intake air that is the inflowing air. It is a portion located on the inner wall surface 20 side of the intake port 12.

More specifically, as shown in FIGS. 6, 8 and 10, the flow direction of the intake air is at the axis (x) and the swirl control vane 18 has a low swirl range.
If the centers of 24 are respectively indicated by the axis (y), the low swirl area 24 is about 30 degrees clockwise and about 30 degrees counterclockwise and clockwise about the axis (y). The range of 120 degrees to about 150 degrees, the high swirl area 25 is a range of about 30 to about 120 degrees in the clockwise direction with respect to the axis (y), and the extremely low swirl area 26. Is about 30 to 210 degrees in the counterclockwise direction with respect to its axis (y).

The swirl control vane 18 is structurally fixed to the sleeve shaft 17 by fixing the root to one end of the sleeve shaft 17 as understood from FIGS. 2, 3 and 4. A vane body 28 supported and having a tip extending toward the port opening 21 side, and
A port throttle surface 31 is formed on the front side 29 of the vane body 18, and a sidestream guide surface 32 is connected to the port throttle surface 31 on the side protruding toward the inner wall surface 20 of the intake port 12. Formed on the front side 29 of the vane body 28, and further, the wraparound mainstream guide surface 33 is provided on the back side 30 of the vane body 28.
Is formed into a structure.

In particular, in the swirl control vane 18, the port throttle surface 31 and the wrap-around mainstream flow guide surface 33 are partially cylindrical curved surfaces, and the sidestream flow guide surface 32 is a flat surface.

The actuator consists of a stepper motor, which is placed on the cylinder head 11, and the motor
A shaft (not shown) is connected to the shaft (not shown) of the worm 34 of the worm gear mechanism 27. Of course, since the worm 34 is meshed with the worm wheel 35, the actuator, i.e., stepper motor, is driven through the worm gear mechanism 27 and the sleeve shaft 17 into the swirl control vane. Rotate 18 into its low swirl area 24, high swirl area 25, and extremely low swirl area 26.

As shown in FIGS. 1 and 5, the worm gear mechanism 27 includes a worm wheel 35 fixed to the other end of the sleeve shaft 17 and a worm 34 meshed with the worm wheel 35. Become that warm
The shaft of 34 is connected to the motor shaft of the step motor so that the rotational force of the step motor can be transmitted to the sleeve shaft 17.

The controller includes a rotation speed sensor (not shown), a load sensor (not shown), and an intake air temperature sensor (not shown).
Are electrically connected and the pulse current (electrical pulse) flowing through the step motor is controlled according to the signals from the sensors to drive the step motor.

The controller is of course composed of an input and output circuit, an arithmetic circuit, a memory circuit, a control circuit, a power supply circuit, and the like.

In that way, in the low swirl type intake port 12 in which the swirl control vane 18 operated by the actuator is arranged, if the relation of the flow coefficient (Cms) to the swirl ratio is compared with the conventional intake port, The flow coefficient (Cms) of the low swirl type intake port 12 is shown by a characteristic line (f) in which a loop is drawn from the solid line portion and the dotted line portion in FIG. 12, and that of the conventional intake port is the same. , Shown by the characteristic line (g) in FIG.
As can be seen from FIG. 12, the flow coefficient (Cms) of the low swirl type intake port 12 is higher than that of the conventional intake port, and the swirl ratio and the variable range of the flow coefficient are increased. Can be spread.

Then that diesel engine so configured
The intake control when the 10 is operated will be described. Now, when the diesel engine 10 is operated at low speed and high load, the controller calculates according to the signals from the rotation speed sensor, load sensor, and intake air temperature sensor, and the pulse current to flow to the step motor. Determine (electrical pulse).

As such, when the stepper motor is rotated by a pulsed current (electrical pulse) controlled by the controller, the worm coupled to the motor shaft
34 is rotated, and its worm wheel 35 meshed with the worm 34 is rotated.

Along with the rotation of the worm wheel 35, the sleeve shaft 17 rotates the worm wheel 17 around the valve stem 16 of the intake valve 15 in the clockwise direction.
The swirl control vane 18, which is rotated integrally with the wheel 35, is also shown in FIG.
With its sleeve shaft 17, it is rotated clockwise and its low swirl range with respect to its intake flow.
On the upstream side of 24, the inner wall surface of the intake port 12
Moved to high swirl area 25 where it is projected to 20.

As such, when the swirl control vane 18 is moved to the high swirl zone 25, its intake port 12
Port swottling surface of the swirl control vane 18
It is throttled at 31, and at this time, the main stream 36 flows along the swirl chamber 19 and the final stream 36 is blocked because the generation of the side stream is blocked by the swirling main flow guide surface 33 of the swirl control vane 18. The intake air flowing into the cylinder chamber 39 through the port opening 21 along the mainstream flow guide surface 33 of the swirl control vane 18 of the mainstream 37 is also in a high swirl state.

Therefore, the swirl ratio and the flow coefficient (Cms) of the low swirl type intake port 12 become the values shown by the point A on the characteristic curve (f) in FIG.

In this way, this low swirl type intake port 12
In high-load operation, the throttle amount of the swirl control vane 18 increases, the flow coefficient (Cms) decreases, and the intake air with a high swirl ratio is transferred to the cylinder chamber.
The so-called high-swirl intake air is introduced into the cylinder chamber 39 to improve combustion.

Also, when the diesel engine 10 is operated at medium speed and high load, the controller is
It calculates according to the signals from the load sensor and the intake air temperature sensor, and determines the pulse current (electrical pulse) to flow to the step motor.

The stepper motor is rotated in the opposite direction to the low speed / high load operation described above by a pulse current (electric pulse) controlled by the controller, and accordingly, the worm 34 and the worm 34 connected to the motor shaft are rotated. That warm
Its worm wheel 35 meshed with 34 is rotated in the opposite direction.

The sleeve shaft 17 is rotated integrally with the worm wheel 35 in a counterclockwise direction around the valve stem 16 of the intake valve 15 with the reverse rotation of the worm wheel 35. , Its swirl control vane 18 is also rotated counterclockwise, with its sleeve shaft 17,
In the direction shown in the figure, the so-called high swirl area 25 is moved to the low swirl area 24 side.

As such, when the swirl control vane 18 is moved from its high swirl region 25 to its low swirl region 24 side, its intake port 12 is reduced at the port throttling surface 31 of its swirl control vane 18. The main stream 36 flows along the swirl chamber 19 and the final stream 36 is squeezed and again, since the generation of the side stream 38 is blocked by the swirling main flow guide surface 33 of the swirl control vane 18. The intake air that flows into the cylinder chamber 39 through the port opening 21 along the mainstream flow guide surface 33 of the swirl control vane 18 of the mainstream 37 is also in a high swirl state lower than the above case.

Therefore, the swirl ratio and the flow coefficient (Cms) of the low swirl type intake port 12 become the values shown by the point B on the characteristic curve (f) in FIG.

As such, this low swirl type intake port 12
In high-load operation, the throttle amount of the swirl control vane 18 is reduced, the flow coefficient (Cms) is increased accordingly, and the intake air with a reduced swirl ratio is introduced into the cylinder chamber 39, The so-called low-swirl intake air is guided to the cylinder chamber 39 to optimize combustion. In other words, in this medium speed / high load operation, the intake port 12 is given optimum values of the flow coefficient (Cms) and the swirl ratio, and the intake port 12 is optimally burned to the diesel engine 10. give.

Further, when the diesel engine 10 is operated at high speed and high load, the controller operates according to the signals from the rotation speed sensor, the load sensor, and the intake air temperature sensor, and the step motor Determine the pulse current (electrical pulse) to flow through.

The step motor is rotated in the reverse direction from the case of the medium speed / high load operation by the pulse current (electric pulse) controlled by the controller, and accordingly, the step motor connected to the motor shaft is rotated. The worm 34 and its worm wheel 35 meshed with the worm 34 are further rotated in the opposite direction.

With such counter rotation of the worm wheel 35, its sleeve shaft 17 is rotated around the valve stem 16 of its intake valve 15 in a counterclockwise direction.
Rotated integrally with its worm wheel 35, its swirl control vane 18, also with its sleeve shaft 17, is further rotated counterclockwise, as shown in FIGS. 8 and 9. Moved to low swirl area 24.

As such, when the swirl control vane 18 is moved to the low swirl area 24, its intake port 12
Port swottling surface of the swirl control vane 18
31 is not throttled, and at this time, the generation of the sidestream 38 is blocked by the wraparound mainstream guide surface 33 of the swirl control vane 18, so that the mainstream 36 flows along the swirl chamber 19. , The final mainstream 37 is also its swirl control
The intake air that flows into the cylinder chamber 39 through the port opening 21 along the wraparound mainstream guide surface 33 of the vane 18 is in a low swirl state.

Therefore, the swirl ratio and the flow coefficient (Cms) of the low swirl type intake port 12 become the values shown by the point C on the characteristic curve (f) in FIG.

In this high speed, high load operation, the swirl control vane 18 is retracted into the low swirl area 24, so the intake port 12 becomes the state of the port itself,
With a low swirl ratio, a high flow coefficient (Cms) improves the combustion of the diesel engine 10.

Still further, when the diesel engine 10 is run idle, its controller operates in response to signals from its speed sensor, load sensor, and intake air temperature sensor, and then sends a pulse to its stepper motor. Determine the current (electrical pulse).

The step motor is rotated in the opposite direction by a larger rotation angle than in the case of the high speed / high load operation described above by the pulse current (electric pulse) controlled by the controller,
Along with that, the worm 34 connected to the motor shaft and the worm wheel 35 meshed with the worm 34 are further rotated in the opposite directions to the extent corresponding to the large rotation angle.

With such a large counter-rotating angle of rotation of the worm wheel 35, its sleeve shaft 17 and its worm wheel 35 in a counterclockwise direction around the valve stem 16 of its intake valve 15. The swirl control vanes 18 are rotated together, and the sleeve shaft 17 is also rotated in a clockwise direction at a large angle to rotate the swirl control vanes 18 from the low swirl regions 24 to 10 in FIG. 8 and FIG. And moved to the extremely low swirl area 26 in FIG.

As such, when the swirl control vane 18 is moved to its extremely low swirl area 26, its intake port
In FIG. 12, the sidestream 38 is generated from the mainstream 36, and the mainstream 37 that is circulated in the swirl chamber 19 of the intake port 12 is the slewing control vane 18 that is the mainstream flow guide surface of the swirl control vane 18.
As it flows along 33, its intake port 12 port opening
The intake air that has flowed into the cylinder chamber 39 through 21 is brought into an extremely low swirl state by the circulating main flow 37 and the auxiliary flow 38.

Therefore, the swirl ratio and the flow coefficient (Cms) of the low swirl type intake port 12 become the values shown by the point D on the characteristic curve (f) in FIG.

As such, in idling, the low swirl type intake port 12 has a high flow coefficient (Cms), and causes the intake air having a low swirl ratio to flow into the cylinder chamber 39,
The so-called extremely low swirl intake air is introduced into the cylinder chamber 39 to improve combustion.

Figures 13 and 14 partially show another embodiment 40 of an internal combustion engine of the present invention adapted to be mounted on a truck.

This internal combustion engine 40 is embodied as a diesel engine, which is a modification of the swirl control vane 18 of the internal combustion engine 10 described above, and the components corresponding to those of the internal combustion engine 10 are designated by the same reference numerals. , Omit their explanation.

Swirl control vane 41 of its internal combustion engine 40
Consists of double fins 42 and 43, and expands the swirl variable range compared to the case with the swirl control vane 18. And with this double fin type swirl control vane 41, the high swirl range has been greatly improved.

In the diesel engine 10 described above, the worm gear mechanism 27 is used as a means for transmitting the rotational force of the actuator to the sleeve shaft 17, but the worm gear mechanism 27 is attached to the sleeve shaft 17. An operating arm to be fixed, an operating rod having a ball head fitted to the yoke of the operating arm, and a gear fixed to the motor shaft of the step motor and fitted to the rack portion of the operating rod. It could be replaced by a rack gear mechanism, and moreover, the actuator could
If it is composed of a large number of permanent magnets fixed to the outer circumference of the shaft 17 at a predetermined interval and an electric induction coil arranged on the cylinder head facing them,
The worm gear mechanism 27 is omitted.

Further, the worm wheel 35 in the worm gear mechanism 27 is keyed to the sleeve shaft 17, but may be prevented from rotating around the sleeve shaft 17 by a sled joint, in which case ,
If the worm wheel 35 is slit so that it can be screwed on, the worm wheel 35 is securely detented by the sleeve shaft 17.

Convenience and Benefits of the Invention As described above, the internal combustion engine of the present invention has a low swirl type intake port, as compared with the internal combustion engine that has been proposed and has been used. Is formed in the cylinder head with a port opening for mounting the valve seat, and a sleeve shaft is rotatably supported between the valve guide and the valve stem of the intake valve. ,
Position one end on the lower end of the valve guide and the other end on the upper end of the valve guide, and a swirl control vane secures the root to one end of the sleeve shaft in its intake port. , And a vane body whose tip extends toward the port opening side,
A port throttling surface formed on the front side of the vane body, a side flow guide surface formed on the front side of the vane body connected to the port throttling surface on the side protruding toward the inner wall surface of the intake port, and It consists of a wraparound mainstream guide surface formed on the back side of the vane body, and is controlled by an actuator controlled by a controller in response to signals from the rotation speed sensor, load sensor, intake air temperature sensor, etc. along the inner wall surface of the intake port. The low swirl region that is allowed to flow, the high swirl region that protrudes to the inner wall surface of the intake port on the upstream side of the low swirl region, and the flow of the inflow air that is lower than the low swirl region. On the downstream side, since the structure is rotated to the extremely low swirl region located on the inner wall surface side of the intake port, the invention is In a fuel engine, the variable range of the port swirl ratio and flow coefficient (Cms) is expanded, and the port swirl ratio and flow coefficient (Cms) are optimally controlled according to the engine speed, load, and intake air temperature. Is
In particular, even when the intake port is a low swirl type in which a main flow is accompanied by a side flow, the engine speed, load,
In addition to the main flow, the sub-flow and the wrap-around main flow are controlled according to the intake air temperature, etc., and the turbulence generated around the swirl control valve is effectively reduced, and the influence of the turbulence is mitigated. Therefore, the swirl ratio and the flow coefficient (Cms) of the port are optimally controlled, and accordingly, in the spark ignition engine, the optimum swirl ratio is given to the mixture flowing into the cylinder chamber, and at the same time, the high flow coefficient ( Cms) is given, and in the compression ignition type engine, the optimum swirl ratio is given to the intake air that flows into the cylinder chamber, and at the same time, a high flow coefficient (Cms) is given to the port, The optimum inflow is obtained accurately and surely, combustion is improved, high efficiency combustion can be realized, and heat load, fuel consumption rate, and start including cold start Etc. is improved, the improved exhaust gas characteristics are improved output characteristics of the engine, to be practical institutional.

Relationship between the Invention and Specific Examples As described above, from the specific examples of the present invention described with reference to the drawings, various design modifications can be made to those having ordinary knowledge in the technical field to which the present invention belongs. And changes are easily made, and moreover, the content of the present invention is essential for the establishment of an invention that accomplishes the subject of the invention, and is derived from the technical essence of the invention, which is the nature of the invention. And then it is easily replaced by an objectively recognized embodiment.

[Brief description of drawings]

FIG. 1 shows an internal combustion engine of the present invention embodied in a diesel engine suitable for being mounted on a truck, in which swirl control vanes are located on the low swirl region side and the high swirl region side. Fig. 2 is a vertical sectional view of the swirl type intake port, Fig. 2 is a front view of the swirl control vane showing the port throttle surface, and Fig. 3 is a side view of the swirl control vane showing the side flow guide surface. , Fig. 4 is a front view of the back side of the swirl control vane showing the circulation main flow guide surface, and Fig. 5 is a low swirl type intake port section in which the swirl control vane is located on the extremely low swirl region side. FIG. 6 is a schematic cross-sectional view of the low swirl type intake port portion where the swirl control vane is in the high swirl region, and FIG. 7 is Fig. 6 is a front view of the low swirl type intake port portion seen from the upstream side, Fig. 8 is a schematic plan view of the low swirl type intake port portion in which the swirl control vane is in the low swirl region, and Fig. 9 is , A front view of the low swirl type intake port portion shown in FIG. 8 as seen from the upstream side,
FIG. 10 is a schematic plan view of the low swirl type intake port part where the swirl control vane is in an extremely low swirl region, and FIG. 11 is a view showing the low swirl type intake port part shown in FIG. 10 from the upstream side. Fig. 12 is a front view, Fig. 12 is a characteristic diagram showing the flow coefficient (Cms) with respect to the swirl ratio of the intake port shown in Fig. 1 and the conventional intake port, and Fig. 13 is another diagram suitable for being mounted on a truck. FIG. 14 is a vertical cross-sectional view of a low swirl type intake port portion of an internal combustion engine of the present invention embodied in a diesel engine of FIG.
FIG. 3 is a perspective view of a double fin swirl control vane used in the diesel engine shown. 12 …… Low swirl type intake port, 13 …… Valve mounting boss, 14 …… Valve guide, 15 …… Intake valve, 16 ……
Valve stem, 17 …… Sleeve shaft, 18,41…
… Swirl control vanes, 24 …… Low swirl range, 25 …… High swirl range, 26 …… Extremely low swirl range, 28…
… Vane body, 31 …… Port throttling surface, 32 …… Side flow guide surface, 33 …… Surrounding main flow guide surface.

Claims (1)

[Claims] 1. A low swirl type intake port formed in a cylinder head and having a port opening for opening a valve seat to be opened in a cylinder chamber, and an opening on an inner wall surface of the intake port facing the port opening. The valve guide located in the valve guide bore formed in the cylinder head and the valve stem fitted to the valve guide, and guided by the valve guide to open the port opening. Is rotatably supported between the intake valve that opens and closes, the valve guide and the valve stem, and one end is at the lower end of the valve guide.
A sleeve shaft having the other end positioned at the upper end of the valve guide, and a vane body having a root fixed to one end of the sleeve shaft in the intake port and a tip extending toward the port opening side, A port throttling surface formed on the front side of the vane body, a side flow guide surface formed on the front side of the vane body connected to the port throttling surface on the side protruding toward the inner wall surface of the intake port, and A low swirl area consisting of a wraparound mainstream guide surface formed on the back side of the vane body, along the inner wall surface of the intake port, and with respect to the flow of inflow air, upstream of the low swirl area, the intake port With respect to the high swirl area protruding to the inner wall surface and the flow of the inflowing air, the suction air flow is more downstream than the low swirl area. The swirl control vane that is rotated in the extremely low swirl region located on the inner wall surface side of the air port, and the swirl control vane through the sleeve shaft is used for the low swirl region, the high swirl region, and the polar region. An internal combustion engine that includes an actuator that rotates in a low swirl range, and a controller that drives the actuator in response to signals from a rotation speed sensor, a load sensor, an intake air temperature sensor, and the like.