JPH05231165A - Waste gate valve controlling actuator - Google Patents

Abstract

PURPOSE:To always generate a necessary quantity of supercharge pressure by arbitrarily setting the opening degree of a waste gate valve by installing an iron core on a member interlocked with a waste gate rod, and controlling the operation of the waste gate rod and the opening/closing of the waste gate valve, by attracting the iron core by an electromagnetic coil. CONSTITUTION:A control actuator 29 controls a waste gate valve 18 installed in the bypass pipe 20 of an exhaust turbine supercharger 19. In this case, inside the upper and lower cups 3 and 6 forming a pressure introducing port 1 which communicates to an intake pipe, a pressure chamber 2 and a spring chamber 12 are formed through a diaphragm 7. Further, a waste gate rod 14 which is interlocked with the valve 18 is inserted into the spring chamber 12 and is interlocked with the diaphragm 7. Further, in the spring chamber 12, a spring member 8 for urging the diaphragm 7 to the pressure chamber 2 side and an electromagnetic coil 11 for controlling the operation of the rod 14 at the position opposed to an iron core 10 fixed on the rod 14 are arranged. The electromagnetic coil 11 is controlled by a booster controller 22 connected with the electromagnetic coil 11.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a supercharger attached to an internal combustion engine for compressing intake air and sending the intake air to the internal combustion engine. The present invention relates to a wastegate valve control actuator that controls a wastegate valve attached to a wastegate of a bypass pipe of an exhaust turbine supercharger that compresses intake air by using dynamic energy and thermal energy of exhaust gas of an internal combustion engine. is there.

[0002]

2. Description of the Related Art Generally, in an internal combustion engine mounted on an automobile, a ship, etc., a supercharger for compressing intake air to increase intake density is attached in order to increase output. Then, as one of the superchargers, there is an exhaust turbine supercharger in which the compressor is driven by utilizing the dynamic energy and heat energy of the exhaust gas of the internal combustion engine, and the intake air is compressed by the compressor. As a conventional example of an internal combustion engine equipped with this exhaust turbine supercharger, a structure shown in FIG. 7 is known.

The internal combustion engine shown in FIG. 7 includes an internal combustion engine body (engine) 42 having a plurality of (four in the illustrated example) cylinders (44a to 44d), and an intake pipe connected to the internal combustion engine body 42. 48 (48a, 48b) and the exhaust pipe 46, the throttle 40 provided in the intake pipe 48, and the exhaust turbine supercharger 19 provided between the upstream side of the intake pipe 48 and the downstream side of the exhaust pipe 46. It is roughly composed. The exhaust turbine supercharger 19 is also provided with a bypass pipe 20 that bypasses the exhaust gas sent from the exhaust pipe 46 to a turbine housing that houses the turbine 30. Furthermore, the bypass pipe 20
A waste gate valve 18 that opens and closes a waste gate that is an inlet of the bypass pipe 20 is provided in the. Also, the waste gate valve 18 is installed in the intake pipe 48b.
A waste gate valve control actuator 28 for controlling the opening and closing of the is attached. A solenoid valve 36 controlled by an electronic controller 38 is provided between the waste gate valve control actuator 28 and the intake pipe 48b. The wastegate valve control actuator 28 and the wastegate valve 18 are connected by a link mechanism 21.

In this internal combustion engine, when the throttle 40 is opened and the intake air is sent to the internal combustion engine body 42, the engine speed increases according to the amount of the intake air, and the exhaust gas in the exhaust pipe 46 has a certain flow rate. With the above, the turbine 30 arranged in the exhaust turbine supercharger 19 is rotationally driven by the dynamic energy and thermal energy of the exhaust flow, and
A compressor 32 which is integrated with the turbine 30 by a shaft 31 and is arranged in the exhaust turbine supercharger 19.
Is rotated, the intake air in the intake pipe 48 is compressed, and high-density intake air is supplied to each cylinder 44 of the internal combustion engine body 42. (This effect is called supercharging, and the compressor 3
The compression force of the intake air due to 2 is called supercharging pressure. ) With the above operation, the charging efficiency of intake air in the internal combustion engine is enhanced and the output is increased.

On the other hand, when the throttle 40 is wide open and the engine speed increases, the exhaust gas flow rate also increases, and accordingly, the rotation speeds of the turbine 30 and the compressor 32 in the exhaust turbine supercharger 19 also increase and the engine speed increases. Supply pressure is increased. Excessive supercharging pressure causes knocking, impairs smooth operation, and eventually results in a reduction in output, and may even cause a failure or damage to the internal combustion engine.

Therefore, in an internal combustion engine equipped with an exhaust turbine supercharger, when the supercharging pressure exceeds a set value, the wastegate valve control actuator 28 communicating with the intake pipe 48 via a solenoid valve causes a wastegate valve control. 18 is opened. When the waste gate valve 18 is opened, the exhaust turbine 46 is exhausted from the exhaust pipe 46.
The exhaust flow sent to the turbine 30 flows into a turbine housing that houses the turbine 30, pushes turbine blades to give a rotational force to the turbine 30, and then goes to an outlet behind the turbine 30, and the waste gate valve 18 Is opened to pass through the waste gate, and is separated into an exhaust flow that flows toward the outlet downstream of the exhaust pipe through the bypass pipe 20 without flowing into the turbine housing that houses the turbine 30. Therefore, the exhaust gas in the exhaust pipe 46 can be sent to the downstream side of the turbine 30 by bypassing the turbine 30, so that the rotation of the turbine 30 and the compressor 32 is suppressed, and unnecessary increase of the boost pressure is suppressed. ..

The wastegate valve control actuator 28 will be further described with reference to FIG. In the wastegate valve control actuator 28, the pressure chamber 2 and the spring chamber 12 are surrounded by the upper cup 3 in which the pressure inlet 1 is formed, the upper cup 3 and the pair of lower cups 6, and the diaphragm 7 is interposed therebetween. Is formed. Spring members 8, 8 for urging the diaphragm 7 toward the pressure chamber 2 are arranged in the spring chamber 12. Further, a rubber 4 is interposed between a stopper 5 surrounding the pressure chamber 2 and the diaphragm 7. The peripheral end of the rubber 4 is fixed to the upper cup 3. Further, a wastegate rod 14 that interlocks with a wastegate valve 18 via a link mechanism 21 is loosely inserted into the spring chamber 12, and the tip thereof is located inside the pressure chamber 2. The waste gate rod 14 is fixed to the diaphragm 7 and the stopper 5, and works together. Therefore, the spring member 8
Thus, not only the diaphragm 7 but also the waste gate rod 14 and the stopper 5 are urged toward the pressure chamber 2 side (right side in FIG. 8).

Reference numeral 9 is a bearing that pivotally supports the wastegate rod 14, and reference numeral 13 is a support that supports the wastegate valve control actuator 28 as a whole. Further, the link mechanism 21 transmits the operation of the waste gate rod 14 to the waste gate valve 18 provided at the waste gate of the bypass pipe of the exhaust turbine supercharger 19 to open and close the waste gate valve 18, and the waste gate link 18 The valve arm 17 is connected to the shaft 15 with a support shaft 16.

In the wastegate valve control actuator 28 of this example, the throttle valve 40 is opened,
When the intake air flows through the intake pipe 48b, a part of the intake air from the intake pipe 48b is introduced into the pressure introduction port 1 and a pressure corresponding to the pressure of the intake air is generated in the pressure chamber 2. When the pressure in the pressure chamber 2 increases and exceeds the urging force of the spring members 8, 8, the waste gate rod 14, the stopper 5, and the diaphragm 7
Moves to the spring chamber side (left side in FIG. 8) according to the magnitude of the generated pressure. At this time, the rubber 4 is stretched toward the spring chamber 12 centering on the central portion where the waste gate rod 14 is located. When the waste gate rod 14 operates,
The link mechanism 21 also interlocks so as to respond to the operation of the waste gate rod 14, so that the waste gate valve 1
8 opens.

Then, when the pressure in the pressure chamber 2 decreases and the biasing force of the spring members 8, 8 overcomes, the waste gate rod 14
The stopper 5 and the diaphragm 7 are located on the pressure chamber 2 side (see FIG. 8).
At the right) again. When the wastegate rod 14 operates so as to move to the pressure chamber 2 side, the link mechanism 21 also interlocks with this, so that the wastegate valve 18 is closed. Therefore, the waste gate rod 14 operates according to the pressure generated in the pressure chamber 2, and the link mechanism 21 interlocks with the operation, so that the waste gate valve 1
8 opens and closes. That is, when the supercharging pressure of the intake air in the intake pipe 48b is low, the pressure generated in the pressure chamber 2 is also small and the wastegate rod 14 does not operate. Therefore, although the wastegate valve 18 of the bypass pipe is closed, When the supply pressure increases, the pressure generated in the pressure chamber 2 increases, the waste gate rod 14 operates, the waste gate valve 18 opens, and the exhaust gas passes through the bypass pipe 20 according to the opening degree of the waste gate valve 18 and the turbine. Bypassing 30, the supercharging pressure is suppressed.

[0011]

The supercharging pressure characteristic generally required for the internal combustion engine is as shown by the line a in FIG. That is, when the engine speed increases, the supercharging pressure also increases with the engine speed, and when the engine speed reaches an arbitrary engine speed, the supercharging pressure also produces a certain constant supercharging pressure. ..

In the exhaust turbine supercharger using the conventional wastegate valve control actuator, the wastegate valve is closed when the boost pressure is low (that is, when the engine speed is low). The supercharging pressure also rises as the rotation speed increases. Then, when the supercharging pressure reaches an arbitrary supercharging pressure, the pressure in the pressure chamber 2 of the wastegate valve control actuator overcomes the biasing force of the spring members 8, 8 as described above, and the wastegate rod 14
Is activated, the waste gate valve 18 provided at the waste gate of the bypass pipe 20 is opened, and an increase in the amount of exhaust gas flowing into the turbine housing is suppressed. Therefore, the rotational driving force of the turbine 30 does not increase, and therefore the compressor is not increased. Three
Since the number of rotations of 2 is also suppressed, the boost pressure will not increase. Therefore, the boost pressure characteristic as shown by the line a in FIG. 6 can be produced.

However, when the internal combustion engine is mounted on an automobile or the like for use, a supercharging pressure characteristic shown by lines b and c in FIG. 6 is required in addition to the line a. There are cases where At the time of acceleration, acceleration performance is improved by obtaining a supercharging pressure larger than usual such as the line b.
Further, especially in a diesel engine, a large amount of black smoke is generated at the time of acceleration, and at this time, it is possible to suppress the generation of black smoke by increasing the supercharging pressure.

Further, when high torque or high output is not required, it is possible to improve fuel efficiency by suppressing the supercharging pressure as shown by the line c in FIG.

Further, at the time of cold start (starting in a cooling state of the internal combustion engine), the three-way catalyst provided in the exhaust pipe downstream of the exhaust turbine supercharger is activated by being warmed by the high temperature exhaust gas to improve the performance. However, since the bypass pipe is closed when idling, the exhaust flow reaches the three-way catalyst after passing through the exhaust turbine supercharger, so it is necessary to sufficiently warm the three-way catalyst with exhaust gas. It takes a long time. Therefore, the three-way catalyst does not operate sufficiently and pollutants are released into the atmosphere.

Further, since the opening of the waste gate valve is determined by the balance between the pressure generated in the pressure chamber and the urging force of the spring member, it is highly accurate and often required for setting conditions and designing the material and wire diameter of the spring member. The requirement of (3) is required, which causes not only an increase in cost but also the occurrence of defects.

Therefore, in order to solve the above problem, the waste gate valve control actuator 28 and the intake pipe 48 are arranged.
A (duty) solenoid valve 36 is provided between b,
The solenoid valve 36 is replaced by an electronic controller 38
In some cases, a means for adjusting the amount of intake air entering the pressure chamber 2 of the wastegate valve control actuator 28 by controlling with the above, and thereby controlling the supercharging pressure is adopted. However, in the method of using the solenoid valve 36, it is necessary to provide a new circuit or piping for that purpose, and the handling is complicated, the size of the internal combustion engine is increased, and the weight is increased. .. Further, it is difficult to finely adjust the supercharging pressure, and exhaust energy is wasted, resulting in deterioration of fuel consumption.

The present invention has been made in order to solve the above-mentioned problems, and makes it possible to arbitrarily set the opening degree of a waste gate valve provided in a bypass pipe of an exhaust turbine supercharger, which is always required. A wastegate valve control actuator for producing a quantity of boost pressure in an exhaust turbine supercharger.

[0019]

A wastegate valve control actuator according to claim 1, wherein the wastegate valve control actuator controls a wastegate valve provided in a bypass pipe of an exhaust turbine supercharger, the wastegate valve control actuator communicating with an intake pipe. A pressure chamber and a spring chamber are formed between them through a diaphragm in a cup having a pressure introducing port. A waste gate rod that interlocks with the waste gate valve is loosely inserted into the spring chamber and interlocks with the diaphragm. In the spring chamber, a spring member for urging the diaphragm toward the pressure chamber and an electromagnetic coil for controlling the operation of the wastegate rod are arranged at a position facing the iron core fixed to the wastegate rod. ing. The electromagnetic coil is controlled by a boost controller connected to the electromagnetic coil.

A waste gate valve control actuator according to a second aspect of the present invention is a waste gate valve control actuator for controlling a waste gate valve provided in a bypass pipe of an exhaust turbine supercharger, wherein a pressure introduction port communicating with an intake pipe is formed. A pressure chamber and a spring chamber are formed in the cup with a diaphragm interposed therebetween. A waste gate rod that interlocks with the waste gate valve is loosely inserted into the spring chamber and interlocks with the diaphragm. In the spring chamber, a spring member for urging the diaphragm toward the pressure chamber, and an electromagnetic coil for controlling the operation of the waste gate rod at a position facing an iron core fixed to a member interlocking with the waste gate rod. Are arranged. The electromagnetic coil is controlled by a boost controller connected to the electromagnetic coil.

A wastegate valve control actuator according to a third aspect of the present invention is the wastegate valve control actuator according to the second aspect, wherein an iron core is fixed to a diaphragm.

[0022]

In the wastegate valve control actuator of the present invention, the iron core is provided on the wastegate rod that works with the wastegate valve or a member that works with the wastegate rod, such as a diaphragm, and the iron core is attracted by the magnetic force of the electromagnetic coil. It controls the operation of the wastegate rod and the opening and closing of the wastegate valve. Therefore, the opening and closing of the wastegate valve can be controlled by controlling the timing, time and magnitude of the magnetic force generated in the electromagnetic coil by the boost controller. Therefore, since the exhaust gas flow rate to the bypass pipe can be controlled, the supercharging pressure generated in the exhaust turbine supercharger can be freely adjusted.

[0023]

【Example】

[Embodiment 1] An embodiment of the waste gate valve control actuator of the present invention will be described with reference to FIG. The wastegate valve control actuator 29 has a pressure chamber 2 and a spring chamber 12 formed in a space covered by a pair of upper cup 3 and lower cup 6. A diaphragm 7, a rubber 4 and a stopper 5 are interposed between the pressure chamber 2 and the spring chamber 12 in this order from the spring chamber 12 side. Rubber 4
A plate-shaped heat-resistant rubber can be applied to, and its peripheral end is fixed to the upper cup 3. Further, a waste gate rod 14 is loosely inserted in the spring chamber 12, and one end of the waste gate rod 14 penetrates through a hole formed in each central portion of the diaphragm 7, the rubber 4, and the stopper 5, and the stopper 5 in the pressure chamber 2 is inserted. Located at the bottom of the. The waste gate rod 14, the diaphragm 7, the rubber 4, and the stopper 5 are fixed to each other and interlock with each other. The pressure chamber 2 is sealed except that the upper cup 3 is formed with a pressure inlet 1 communicating with the intake pipe.

The other end of the wastegate rod 14 is connected to a link mechanism 21, and is linked with the wastegate valve 18 via the link mechanism 21.
Further, spring members 8 are arranged in the spring chamber 12,
The diaphragm 7 and the waste gate rod 14 interlocking with the diaphragm 7 and the stopper 5 are urged toward the pressure chamber 2. The wastegate rod 14 is rotatably supported by the bearing 9, and the wastegate valve control actuator 29 is supported and fixed to the engine mounted by the support 13.

Furthermore, in the wastegate valve control actuator 29 of the first embodiment, the iron core 10 is fixed to the wastegate rod 14. The iron core 10 has a shape in which a hole is formed in the center of a disk-shaped iron plate. The waist gate rod 14 penetrates the hole formed in the center, and the iron core 10 is fixed to the waste gate rod 14. There is. Also, the iron core 10 and the waste gate rod 1
In order to increase the fixing force of the core 4, a flange 10a is formed on the periphery of the hole formed in the center of the core 10, and thus the core 10
It is preferable to increase the contact area between the wastegate rod 14 and the wastegate rod 14 to increase the fixing force between the iron core 10 and the wastegate rod 14.

Further, an electromagnetic coil 11 is arranged near the iron core 10 at a position opposite to the pressure chamber 2. The electromagnetic coil 11 is connected to the boost controller 22 by a controller wiring 24, and the magnetization of the electromagnetic coil 11 is controlled by a control signal 25 from the boost controller 22. Various information 23, for example, boost pressure, engine speed, throttle opening, running state, etc. are input to the boost controller 22. Boost controller 2
2 controls the electromagnetic coil 11 by obtaining a necessary supercharging pressure based on the obtained information and transmitting control information to the electromagnetic coil 11, that is, energizing it so that the obtained optimum supercharging pressure is generated. Of course, the boost controller 22 can be arbitrarily operated at any time to freely control the electromagnetic coil 11.

In the wastegate valve control actuator 29 of this construction, when the supercharged intake air from the intake pipe through the pressure introduction port 1 into the pressure chamber 2 is not delivered, the wastegate rod 14 and the diaphragm 1 are disposed.
4 and stopper 5 are urged by the spring member 8 toward the pressure chamber 2 side (right side in FIG. 1). When the engine speed increases, the amount of exhaust increases, and the exhaust turbine supercharger begins to operate sufficiently, the compressor in the exhaust turbine supercharger rotates at high speed and the intake air is supercharged. When the supercharged intake air is fed from the intake pipe into the pressure chamber 2 through the pressure introduction port 1 of the waste gate valve control actuator 29, the pressure in the pressure chamber 2 gradually increases according to the supercharging pressure. When the pressure in the pressure chamber 2 increases and overcomes the biasing force of the spring member 8, the pressure generated in the pressure chamber 2 increases to the biasing force of the spring member 8 and the waste gate rod 14 and the diaphragm 7 or the stopper 5 is increased. Moves to the spring chamber 12 side (left side in FIG. 1). At this time, the center of the rubber 4 is also in the spring chamber 12
It is stretched to the side.

A link mechanism 21 is interlocked with the operation of the waste gate rod 14. That is, the wastegate link 15 rotates about the support shaft 16, and thus the valve arm 17
Rotates, and the waste gate valve 18 provided at the waste gate of the bypass pipe 20 of the exhaust turbine supercharger 19 opens. By opening the waste gate valve 18,
A part of the exhaust gas sent from the main body of the internal combustion engine to the exhaust turbine supercharger passes through the bypass pipe 20 according to its opening degree, the rotation of the turbine is suppressed, and the supercharging pressure is controlled.

When the supercharging pressure decreases, the pressure in the pressure chamber 2 decreases, and the pressure becomes smaller than the urging force of the spring member 8, the waste gate rod 1 is restarted by the reduced pressure.
4 is pulled back to the pressure chamber 2 side. When the wastegate rod 14 is pulled back, the wastegate valve 18 is closed by that amount via the link mechanism 21.

Further, in the wastegate valve control actuator 29 of this embodiment, the boost controller 2 is used.
When the electromagnetic coil 11 is energized according to the control signal from 2, the magnetic force is generated in the electromagnetic coil 11 and the generated attractive force attracts the iron core 10 to the electromagnetic coil 11. Iron core 1
When 0 is attracted to the electromagnetic coil 11 arranged at a position farther from the pressure chamber 2 than the iron core 10, the waste gate rod 14 fixedly integrated with the iron core 10
Moves to the left in FIG. 1, and the waste gate valve 18 opens. Then, the power supply to the electromagnetic coil 11 is stopped and the iron core 1
When 0 is no longer attracted to the electromagnetic coil 11, the waste gate rod 14 is pulled back to the pressure chamber 2 side by the biasing force of the spring member 8. Since the attractive force due to the magnetic force generated in the electromagnetic coil 11 depends on the amount of electricity from the boost controller 22, the boost controller 22 also controls the degree to which the waste gate rod 14 is attracted to the electromagnetic coil 11.

That is, the operation of the waste gate rod 14 is determined by the magnitude of the pressure generated in the pressure chamber 2 with respect to the biasing force of the spring member 8 and the magnitude of the attractive force generated in the electromagnetic coil 11. The pressure generated in the pressure chamber 2 is determined by the supercharging pressure of the intake air in the intake pipe, and the attractive force generated in the electromagnetic coil 11 can always be arbitrarily set by the boost controller 22. Therefore, the boost controller 22
Is operated, the opening degree of the waste gate valve 18 can be freely manipulated, and the exhaust gas amount bypassing the bypass pipe can be controlled, so that an arbitrary boost pressure can be generated.

By using the wastegate valve control actuator of this embodiment, it becomes possible to arbitrarily change the supercharging pressure characteristic of the exhaust turbine supercharger. It is possible to create pressure supply characteristics. That is, when the conventional wastegate valve control actuator is used, the boost pressure characteristic as shown by the line a in FIG. 4 can be obtained, but when the wastegate valve control actuator of the present embodiment is used, The spring coefficient of the spring member is adjusted, the opening timing of the waste gate valve 18 is delayed, the supercharging pressure is normally set to a high value, and the supercharging pressure is increased to a high value during acceleration.
A control signal is sent from the boost controller 22 to the electromagnetic coil 11 to generate a magnetic force in the electromagnetic coil 11 to operate the wastegate rod 14 to operate the wastegate valve 1.
By opening 8 to suppress the supercharging pressure and generate a normal constant supercharging pressure, the supercharging pressure characteristic shown by the line d can be obtained.

Therefore, with the exhaust turbine supercharger using the wastegate valve control actuator 29 of this embodiment, the supercharging pressures in the regions I and II shown in FIG. 5 can be obtained. In FIG. 5, the line a shows the normal supercharging pressure characteristic when the supercharging pressure control by the electromagnetic coil 11 is not performed. The electromagnetic coil 11 operates the wastegate rod 14 to open the wastegate valve 18. As a result, any supercharging pressure in the region I can be generated.

Further, in FIG. 5, a line e shows the supercharging pressure characteristic when the spring coefficient of the spring member 8 is set to a large value and the supercharging pressure is set to a high value, and the supercharging pressure control by the electromagnetic coil 11 is performed. It is the case when not performing. If the supercharging pressure is set high in this way and the wastegate rod 14 is operated by the electromagnetic coil 11 to open the wastegate valve 18, the supercharging pressure can be reduced. The supercharging pressure in the region II, which is larger than the supercharging pressure shown by, can be generated and used as needed at any time. Therefore, the acceleration performance can be improved, and the generation of black smoke during acceleration can be reduced. Also, when high torque and high output are not required, boost pressure can be suppressed and fuel consumption can be improved. That is, since the supercharging pressure characteristic can be freely adjusted, not only the supercharging pressure characteristic of the line a shown in FIG. 6 but also the supercharging pressure characteristic shown by the lines b and c can be created. Also,
Since the supercharging pressure can be set arbitrarily, it is possible to obtain the same constant supercharging pressure as in flatland even in a highland where the atmospheric pressure is low.

Region III in FIG. 5 is the characteristic when the engine is idling. Reducing the supercharging pressure by not operating the exhaust turbine supercharger during idling not only improves fuel efficiency, but is particularly preferable at cold start. At the time of cold start, not only the internal combustion engine itself but also various other mechanisms and devices are often in a ready state. For example, the three-way catalyst installed downstream of the exhaust turbine supercharger in the exhaust pipe is activated. It has not been. The three-way catalyst is generally warmed by hot exhaust gas reaching the three-way catalyst, and is activated and starts operating. If the three-way catalyst does not operate satisfactorily, pollutants in the exhaust gas (for example, HC, C
O, etc.) is released into the atmosphere as it is. In an internal combustion engine that uses a conventional wastegate valve control actuator, the wastegate valve is closed during idling, and exhaust gas passes through the exhaust turbine supercharger,
After reaching the three-way catalyst after the exhaust temperature has dropped somewhat,
It took a long time for the three-way catalyst to warm up and be fully activated. However, in the internal combustion engine using the wastegate valve control actuator 29 of the present embodiment, when idling, an attractive force is generated in the electromagnetic coil 11 to move the wastegate rod 14, and the wastegate valve 18 is opened to discharge a large amount of exhaust gas. The exhaust gas can reach the three-way catalyst at a high temperature by passing through the bypass pipe. Therefore, the three-way catalyst can be warmed and activated in a short time, and the emission of pollutants to the atmosphere can be reduced.

Further, when an abnormal situation occurs due to a failure or the like (for example, when intake air is not introduced into the pressure chamber due to some cause, the waste gate valve 18 is not opened, and excessive supercharging pressure occurs). First, the boost controller 22 can be operated, the wastegate rod 14 can be operated by using the electromagnetic coil 11, and the wastegate valve 18 can be opened to prevent the occurrence of excessive boost pressure. That is, no separate relief valve or other mechanism is required.

Further, since the supercharging pressure can be freely adjusted by using an electromagnetic coil, it is necessary to provide a solenoid valve and a controller for controlling the solenoid valve between the waste gate valve control actuator and the intake pipe. Therefore, the overall size of the internal combustion engine is reduced,
The weight can be reduced.

Furthermore, the movement of the wastegate rod 14 by operating the electromagnetic coil 11 causes the pressure chamber 2 to move.
Fine adjustment can be performed as compared with the case where the waste gate valve 18 is moved by the pressure generated therein, and thus the fine adjustment of the opening degree of the waste gate valve 18 is possible. By finely adjusting the opening degree of the wastegate valve 18, exhaust energy, which was conventionally wasted, can be used with high efficiency without excess or deficiency. Therefore, it is possible to improve fuel efficiency.

Further, since the boost controller 22 can be used for fine adjustment of the boost pressure, the precision required for manufacturing the spring member can be reduced and the defect occurrence rate can be suppressed. Moreover, this wastegate valve control actuator is highly versatile, even when used in various internal combustion engines that require different boost pressure characteristics, without the need to change the design of the material and wire diameter of the spring member. It is a thing. Therefore, a significant cost reduction can be achieved.

The shape of the iron core 10 is not limited as long as it is firmly fixed to the waste gate rod 14 and has a size that can be attracted by the attractive force of the electromagnetic coil 11, for example, a rectangular shape. Alternatively, it may be formed radially around the waste gate rod 14.

[Second Embodiment] A wastegate valve control actuator according to a second embodiment will be described with reference to FIG.
2. FIG. 2 is a sectional view of a main part of the wastegate valve control actuator. In the wastegate valve control actuator of the second embodiment, the iron core 26 is not fixed to the wastegate rod 14 but to the diaphragm 7. The waste iron valve 26 has the same structure as the waste gate valve control actuator of the first embodiment except that the iron core 26 is fixed to the diaphragm 7 and the electromagnetic coil 11 is arranged at a position corresponding to the position of the iron core 26.

Even when the iron core 26 is not fixed to the waste gate rod 14 but fixed to the diaphragm 7 at a position near the periphery of the waste gate rod 14, the diaphragm 7 and the waste gate rod 14 are fixed to each other. Since they are linked, the movement of the wastegate rod 14 can be controlled by operating the electromagnetic coil 11. That is, in order to increase the degree of opening of the wastegate valve, an attractive force is generated by the electromagnetic coil 11, the iron core 26 is attracted to the electromagnetic coil 11 to move the diaphragm 7, and thus the wastegate rod 14 that operates in conjunction with the diaphragm 7 is operated. Therefore, the opening degree of the waste gate valve can be increased.

[Third Embodiment] A wastegate valve control actuator according to a third embodiment will be described with reference to FIG. In the waste gate valve control actuator of the third embodiment, the iron core 2 is provided on the outer peripheral portion of the diaphragm 7 outside the spring member 8.
7 is provided. The iron core 27 is fixed to the peripheral portion of the diaphragm 7, and the electromagnetic coil 11 is arranged at a position corresponding to the position of the iron core 27, except that the wastegate valve control actuator of the first embodiment has the same configuration. ing.

Like the wastegate valve control actuator of the third embodiment, even if the iron core 27 is fixed at a position relatively far from the wastegate rod 14, the diaphragm 7 works together with the wastegate rod 14. By pulling the iron core 27 with the electromagnetic coil 11 and moving the diaphragm 7, as a result, the waste gate rod 14 can be operated, and thus the opening of the waste gate valve can be controlled.

Also in the wastegate valve control actuators of the second and third embodiments, the shape of the iron core is not only the donut shape, but also a rectangular shape or the like that is firmly fixed to the diaphragm 7 and is attracted to the electromagnetic coil 11. Should have.

[Embodiment 4] In the wastegate valve control actuators of Embodiments 1 to 3, it is also effective to configure the iron core with a (permanent) magnet instead of iron. The surface of the magnet forming the iron core on the side of the electromagnetic coil 11 is the electromagnetic coil 11.
If the magnetic force generated in the magnetic core 11 has a heteropolar relationship with the iron core side, the attractive force when the magnetic force is generated in the electromagnetic coil 11 is strong.
By applying a small amount of current to the coil, a sufficient attractive force is generated between the electromagnetic coil 11 and the iron core made of a magnet, and the wastegate rod 14 and the wastegate valve can be controlled.

Further, the electromagnetic coil 1 of the magnet which constitutes the iron core
If the surface on the 1st side is in the same polarity as the iron core side of the magnetic force generated in the electromagnetic coil 11, a repulsive force is generated when the electromagnetic coil 11 is magnetized. In the wastegate valve control actuator in which a repulsive force is generated between the electromagnetic coil 11 and the iron core made of a magnet, the electromagnetic coil 11 is not operated when the wastegate valve opening is desired to be increased, but the opening of the wastegate valve is increased. When you want to reduce the size of the electromagnetic coil 11
Is operated to move the iron core away from the electromagnetic coil 11 and move the waste gate rod to the pressure chamber side to control the opening degree of the waste gate valve. In the waste gate valve control actuator in which a repulsive force is generated between the electromagnetic coil 11 and the iron core, the spring coefficient of the spring member is set to a small value, and when the boost pressure larger than usual is required, the repulsive force is applied to the electromagnetic coil 11. It may be caused by delaying the opening time of the waste gate valve. Therefore, the supercharging pressure required at any time can be obtained by reversing the operation timing of the electromagnetic coil 11 from the above-mentioned wastegate valve control actuator having a means for controlling by generating an attractive force between the electromagnetic coil 11 and the iron core. Can occur.

Further, when the iron core is set so that a repulsive force is generated between the iron core and the electromagnetic coil 11, the iron core is fixed to the stopper and the electromagnetic coil 11 is opposed to the iron core on the inner wall of the upper cup. Can be provided in position. In the wastegate valve control actuator having this configuration, when the wastegate valve is desired to be opened, a repulsive force is generated between the electromagnetic coil 11 and the iron core, and the stopper to which the iron core is fixed and the wastegate rod that is interlocked with the stopper are moved. It becomes possible to open the gate valve.

Furthermore, the waste gate valve 18 is linked with the waste gate rod through a link mechanism, but various means such as a gear mechanism such as a pinion rack can be used in addition to the link mechanism.

[0050]

The wastegate valve control actuator according to the present invention is installed not only in the supercharging pressure that actually causes the operation of the wastegate rod interlocking with the wastegate valve but also in the wastegate valve control actuator. The wastegate valve can be opened and closed so as to generate an optimum boost pressure at all times.

Therefore, it is possible to obtain a supercharging pressure higher than usual and to enhance the acceleration performance. Furthermore, it is possible to reduce the generation of black smoke during acceleration. Also, when high torque and high output are not required, boost pressure can be suppressed and fuel consumption can be improved. Further, since the supercharging pressure can be set arbitrarily, it is possible to obtain the same constant supercharging pressure as in flatland even in a highland where the atmospheric pressure is low.

Further, since the waste gate valve can be kept open during idling, the fuel consumption can be improved by suppressing the supercharging pressure without operating the exhaust turbine supercharger during idling. Moreover, since the three-way catalyst can be warmed and activated in a short time, the emission of pollutants to the atmosphere can be reduced.

Further, it is possible to prevent the occurrence of excessive boost pressure even when an abnormal situation such as a failure occurs. That is, no separate relief valve or other mechanism is required.

Further, since the supercharging pressure can be freely adjusted by using an electromagnetic coil, it is necessary to provide a solenoid valve and a controller for controlling the solenoid valve between the wastegate valve control actuator and the intake pipe. Therefore, the overall size of the internal combustion engine is reduced,
The weight can be reduced.

Furthermore, the movement of the waste gate rod by operating the electromagnetic coil can be finely adjusted as compared with the case where the waste gate rod is moved by the pressure generated in the pressure chamber. Therefore, the fine adjustment of the opening degree of the waste gate valve is possible. Is possible. By finely adjusting the opening of the waste gate valve, exhaust energy that was conventionally discarded in vain can be used with high efficiency without excess or deficiency. Therefore, it is possible to improve fuel efficiency.

Further, since the boost controller can be finely adjusted by the boost controller, the precision required for manufacturing the spring member can be reduced, and the defect occurrence rate can be suppressed. Moreover, this wastegate valve control actuator is highly versatile, even when used in various internal combustion engines that require different boost pressure characteristics, without the need to change the design of the material and wire diameter of the spring member. It is a thing. Therefore, a significant cost reduction can be achieved.

[Brief description of drawings]

FIG. 1 is a cross-sectional view of a wastegate valve control actuator according to a first embodiment.

FIG. 2 is a cross-sectional view of essential parts of a wastegate valve control actuator according to a second embodiment.

FIG. 3 is a sectional view of essential parts of a waste gate valve control actuator according to a third embodiment.

FIG. 4 is a graph showing a relationship between elapsed time and supercharging pressure by an exhaust turbine supercharger using the wastegate valve control actuator of the present embodiment.

FIG. 5 is a graph showing a relationship between engine speed and supercharging pressure by an exhaust turbine supercharger using the wastegate valve control actuator of this embodiment.

FIG. 6 is a graph showing a relationship between engine speed and supercharging pressure by an exhaust turbine supercharger using a conventional wastegate valve control actuator.

FIG. 7 is a configuration diagram of an internal combustion engine using a conventional wastegate valve control actuator.

FIG. 8 is a cross-sectional view of a conventional wastegate valve control actuator.

[Explanation of symbols]

 1 Pressure Inlet 2 Pressure Chamber 3 Upper Cup 4 Rubber 5 Stopper 6 Lower Cup 7 Diaphragm 8 Spring Member 10 Iron Core 11 Electromagnetic Coil 12 Spring Chamber 14 Wastegate Rod 15 Wastegate Link 18 Wastegate Valve 19 Exhaust Turbine Turbocharger 20 Bypass Pipe 21 Link Mechanism 22 Boost Controller 24 Controller Wiring 26 Iron Core 27 Iron Core 28 Wastegate Valve Control Actuator 29 Wastegate Valve Control Actuator 30 Turbine 32 Compressor 38 Electronic Control Controller 42 Internal Combustion Engine Body 46 Exhaust Pipe 48a Intake Pipe 48b Intake Pipe

Claims (3)

[Claims] 1. A wastegate valve control actuator for controlling a wastegate valve provided in a bypass pipe of an exhaust turbine supercharger, wherein a pressure chamber and a spring chamber are provided in a cup having a pressure introduction port communicating with an intake pipe. A waste gate rod that is formed between them via a diaphragm and works in conjunction with a waste gate valve is loosely inserted in the spring chamber and works in conjunction with the diaphragm, and the spring chamber biases the diaphragm toward the pressure chamber. A spring member and an electromagnetic coil for controlling the operation of the wastegate rod are disposed at positions facing the iron core fixed to the wastegate rod, and the electromagnetic coil is controlled by a boost controller connected to the electromagnetic coil. A wastegate valve control actuator characterized in that: 2. A wastegate valve control actuator for controlling a wastegate valve provided in a bypass pipe of an exhaust turbine supercharger, wherein a pressure chamber and a spring chamber are provided in a cup having a pressure introduction port communicating with the intake pipe. A waste gate rod that is formed between them via a diaphragm and works in conjunction with a waste gate valve is loosely inserted in the spring chamber and works in conjunction with the diaphragm, and the spring chamber biases the diaphragm toward the pressure chamber. An electromagnetic coil for controlling the operation of the waste gate rod is disposed at a position facing the spring member and the iron core fixed to the member interlocking with the waste gate rod, and the electromagnetic coil is connected to the electromagnetic coil. Wastegate valve control actuator characterized by being controlled by a boost controller Over data. 3. The waste gate valve control actuator according to claim 2, wherein an iron core is fixed to a diaphragm.