JP5874681B2 - Valve drive device - Google Patents

Description

  The present invention relates to a valve drive device, and more particularly to a valve drive device that drives a valve of a supercharger.

  Conventionally, a valve driving device that drives two valves of a supercharger is known. For example, in the valve driving device described in Patent Document 1, two valves of a two-stage supercharger are driven by one actuator. This valve drive device includes a link mechanism between the actuator and the valve. The driving force of the actuator is transmitted to the valve via the link mechanism.

JP 2010-281271 A

  In the valve drive device of Patent Document 1, the second valve is in a closed state by being biased toward the closing side by a spring until the first valve is opened by a predetermined opening or more. When the first valve opens more than a predetermined opening, the second valve opens in conjunction with the first valve by the link mechanism. When the second valve opens in conjunction with the first valve, a biasing force from a spring acts on the first valve and the second valve. In the valve drive device of Patent Document 1, the link mechanism is composed of many members and is complicated. Therefore, there is a possibility that member cost and manufacturing cost may increase.

  When the second valve is open, the biasing force of the spring always acts on the output shaft of the actuator via the link mechanism. For this reason, when the second valve is mainly opened as the operation of the internal combustion engine, the load on the actuator increases, which may increase the stress on the actuator. Further, when the actuator is electric, power consumption may increase.

  Further, the range from when the first valve starts to open until the second valve starts to open, that is, the range in which the first valve can be opened without receiving the biasing force of the spring, It is determined by the gap between the first member and the second member constituting the link mechanism. Therefore, the size of the gap between the first member and the second member depends on the variation of the constituent members, and it may be difficult to set the above range accurately.

  The present invention has been made in view of the above-described problems, and an object of the present invention is to provide a valve driving device having a simple configuration and a long service life of members.

  The invention according to claim 1 is attached to a supercharger including a first valve rotatable about an axis of a first valve shaft and a second valve rotatable about an axis of a second valve shaft, A valve driving device for driving one valve and a second valve, comprising an actuator, a shaft, a first member, a second member, a first valve lever, a second valve lever, a first rod, a second rod, and an urging means It has. The present invention is applied to, for example, a variable displacement supercharger or a two-stage supercharger including a waste gate valve, and controls a first valve (switching valve or variable nozzle) for controlling the amount of exhaust gas supplied to the turbine, and A second valve (waste gate valve) that controls the amount of exhaust gas that bypasses the turbine is driven.

  The actuator has an output shaft movable in the axial direction. The shaft is coaxial and integral with the output shaft, or is provided separately from the output shaft. The first member is provided on an axis of the shaft and has a first contact portion and a first engagement portion.

  The second member is provided on the shaft axis, and has a second contact portion that can contact the first contact portion, and a second engagement portion. The first valve lever is provided so as to be rotatable integrally with the first valve shaft, and is provided so that the shaft is parallel to the first valve shaft at a first predetermined distance from the first valve shaft. Having a first valve lever shaft. The second valve lever is provided so as to be rotatable integrally with the second valve shaft, and is provided so that the shaft is parallel to the second valve shaft at a second predetermined distance from the second valve shaft. A second valve lever shaft.

  One end of the first rod is connected to be rotatable relative to the first valve lever shaft, and the other end is connected to the shaft or the first member. One end of the second rod is connected to be rotatable relative to the second valve lever shaft, and the other end is connected to the second member. The biasing means is provided between the first engagement portion and the second engagement portion, and biases the first member and the second member in a direction in which the first contact portion and the second contact portion approach each other. .

  In the present invention, for example, if the first valve is set so that a predetermined gap is formed between the first contact portion and the second contact portion when the first valve is fully closed, the first valve has a predetermined opening degree. Until the opening is completed, the second valve can be urged to the closed side by the urging means so that the valve is closed. Therefore, the first valve can be driven within a predetermined range by the actuator while the second valve is kept in the fully closed state by the urging force of the urging means. On the other hand, when the first valve opens more than a predetermined opening, for example, the first contact portion and the second contact portion come into contact with each other, and the second valve includes the second valve lever, the second rod, the second member, It opens in conjunction with the first valve via one member, the shaft, the first rod, and the first valve lever.

  Thus, according to the present invention, the link mechanism can be configured with relatively few components, and two valves (first valve and second valve) can be driven by one actuator. In particular, when the shaft is provided coaxially and integrally with the output shaft, the number of components can be reduced. Therefore, member cost and manufacturing cost can be reduced.

  In the present invention, when the first valve is driven with the second valve closed, the urging force of the urging means acts on the output shaft of the actuator via the first member and the shaft. At this time, the load on the actuator increases. On the other hand, when the second valve is opened, that is, when the second valve is driven together with the first valve, the biasing force of the biasing means is, for example, that the first contact portion and the second contact portion are Since it cancels between the 1st member and the 2nd member by contact | abutting, it does not act on the output shaft of an actuator. Therefore, when the second valve is mainly opened as the operation of the internal combustion engine, the load on the actuator is reduced and the stress on the actuator can be reduced. Therefore, the life of the actuator and peripheral members can be increased. Further, when the actuator is an electric type, power consumption can be reduced.

  According to the second aspect of the present invention, the compressor is provided in the intake passage that guides intake air to the internal combustion engine, and is provided in the exhaust passage through which the exhaust from the internal combustion engine circulates so that the compressor can be driven to rotate by being supplied with the exhaust and rotating. A first valve that is provided in an exhaust passage that guides exhaust from the internal combustion engine to the turbine, and that can open and close the exhaust passage by rotating around the axis of the first valve shaft; and an exhaust passage that bypasses the turbine A turbocharger provided with a second valve that is provided in a bypass flow path that connects an internal combustion engine side of a turbine and an opposite side of the internal combustion engine and that can open and close the bypass flow path by rotating around an axis of a second valve shaft. It is a valve drive device that is attached and drives the first valve and the second valve to open and close. The present invention is applied to, for example, a variable displacement turbocharger including a waste gate valve, and controls a first valve (a switching valve or a variable nozzle) that controls the amount of exhaust gas supplied to the turbine, and an exhaust amount that bypasses the turbine. The second valve (waste gate valve) for controlling the motor is driven.

  According to a third aspect of the present invention, the first compressor and the second compressor provided in the intake passage for guiding the intake air to the internal combustion engine, the exhaust passage through which the exhaust from the internal combustion engine circulates are supplied and rotated. The first turbine capable of rotationally driving the first compressor, the second turbine provided in the exhaust passage and supplied with exhaust gas to be rotated to rotate the second compressor, and the first turbine for guiding exhaust gas from the internal combustion engine to the first turbine A first exhaust passage or a second exhaust passage that can be opened and closed by rotating around the axis of the first valve shaft is provided in an exhaust passage or a second exhaust passage that guides exhaust from the internal combustion engine to the second turbine. 1 valve and the internal combustion engine side of the first turbine and the second turbine in the exhaust passage so as to bypass the first turbine and the second turbine, and the side opposite to the internal combustion engine The first valve and the second valve are driven to open and close by being attached to a supercharger provided with a second valve that is provided in the bypass flow path connecting the valve and can be opened and closed by rotating around the axis of the second valve shaft. This is a valve drive device. The present invention is applied to, for example, a two-stage turbocharger including a waste gate valve, and controls a first valve (switching valve) that controls the amount of exhaust gas supplied to two turbines, and an amount of exhaust gas that bypasses the turbine. The second valve (waste gate valve) to be controlled is driven.

(A) is sectional drawing which shows the valve drive device and supercharger by 1st Embodiment of this invention, (B) is the BB sectional drawing of (A). The schematic diagram which shows the supercharger with which the valve drive device by 1st Embodiment of this invention is attached. The schematic diagram which shows the valve drive device by 1st Embodiment of this invention. It is a figure which shows the valve drive device and supercharger by 1st Embodiment of this invention, Comprising: (A) is a figure of the valve drive device when the 1st valve and the 2nd valve are closing, (B) FIG. 3 is a diagram showing a state of a supercharger corresponding to (A). It is a figure which shows the valve drive device and supercharger by 1st Embodiment of this invention, Comprising: (A) is a figure of a valve drive device when an actuator drives predetermined amount from FIG. 4 (A), (B) is. The figure which shows the state of the supercharger corresponding to (A). It is a figure which shows the valve drive device and supercharger by 1st Embodiment of this invention, Comprising: (A) is a figure of a valve drive device when an actuator drives predetermined amount from FIG. 5 (A), (B) is. The figure which shows the state of the supercharger corresponding to (A). (A) is a figure which shows the relationship between the drive amount of the actuator of the valve drive device by 1st Embodiment of this invention, and the opening degree of a 1st valve, and a 2nd valve, (B) is a drive amount of an actuator, and drive of an actuator. The figure which shows the relationship with force. The figure which shows the relationship between the rotation speed of the internal combustion engine to which the valve drive device by 1st Embodiment of this invention is applied, and BMEP or torque. The schematic diagram which shows the valve drive device by 2nd Embodiment of this invention. The schematic diagram which shows the valve drive device by 3rd Embodiment of this invention. The schematic diagram which shows the valve drive device by 4th Embodiment of this invention. The schematic diagram which shows the valve drive device by 5th Embodiment of this invention. (A) is a schematic diagram showing a supercharger to which a valve drive device according to a sixth embodiment of the present invention is attached, and (B) is a schematic diagram showing a supercharger to which a valve drive device according to a seventh embodiment of the present invention is attached. Figure. The schematic diagram which shows the valve drive device and supercharger by 8th Embodiment of this invention.

Hereinafter, valve drive devices according to a plurality of embodiments of the present invention will be described with reference to the drawings. Note that, in a plurality of embodiments, substantially the same components are denoted by the same reference numerals, and description thereof is omitted.
(First embodiment)
A valve driving device according to a first embodiment of the present invention is shown in FIGS.

  As shown in FIG. 1A, the valve drive device 1 is attached to a supercharger 3 that supercharges intake air into an internal combustion engine (hereinafter referred to as “engine”) 2 of a vehicle, for example. The supercharger 3 can increase the output of the engine 2, increase the torque in the practical rotation range, improve the fuel consumption, and the like by supercharging intake air to the engine 2.

  An intake pipe 4 is connected to the engine 2. An intake pipe 5 is provided on the opposite side of the intake pipe 4 from the engine 2. An intake port (not shown) is formed at the end of the intake pipe 5 opposite to the intake pipe 4 and is open to the atmosphere. An intake passage 6 is formed inside the intake pipe 4 and the intake pipe 5. The intake passage 6 guides air (hereinafter referred to as “intake”) from the intake port to the engine 2.

An exhaust pipe 7 is connected to the engine 2. The exhaust pipe 8 has an exhaust port formed through an exhaust purification device 9 and is open to the atmosphere. The exhaust purification device 9 has a catalyst (not shown). An exhaust passage 10 is formed inside the exhaust pipe 7 and the exhaust pipe 8. Exhaust gas including combustion gas generated during operation of the engine 2 flows through the exhaust passage 10. The exhaust gas is purified by passing through the exhaust gas purification device 9 and then discharged from the exhaust port to the atmosphere.
The supercharger 3 includes a compressor 11, a compressor housing 12, a turbine 13, a turbine housing 14, a bearing portion 15, a shaft 16, a first valve 17, a second valve 18, and the like.

  The compressor 11 is formed of a metal such as aluminum, and is provided between the intake pipe 4 and the intake pipe 5 of the intake passage 6. The compressor 11 has a cylindrical portion 111 and a wing portion 112. The cylindrical portion 111 is formed in a cylindrical shape whose outer diameter increases from one end to the other end. The wing part 112 is formed in a curved plate shape so as to extend from one end side to the other end side of the cylinder part 111 on the outer wall of the cylinder part 111. A plurality of wing parts 112 are formed at substantially equal intervals in the circumferential direction of the cylinder part 111. The compressor 11 is provided so as to be accommodated in the compressor housing 12.

  The compressor housing 12 is provided between the intake pipe 4 and the intake pipe 5. The compressor housing 12 is made of, for example, metal. The compressor housing 12 has a scroll 121 and the like. The scroll 121 is formed in an annular shape around the wing 112 of the compressor 11. Thereby, the intake air in the intake pipe 5 is guided to the intake pipe 4 via the compressor 11 and the scroll 121 inside the compressor housing 12.

  The turbine 13 is made of, for example, a metal such as nickel-based high heat-resistant steel, and is provided between the exhaust pipe 7 and the exhaust pipe 8 in the exhaust passage 10. The turbine 13 has a cylindrical portion 131 and a blade portion 132. The cylindrical portion 131 is formed in a cylindrical shape whose outer diameter increases from one end to the other end. The wing part 132 is formed in a curved plate shape so as to extend from one end side to the other end side of the cylinder part 131 on the outer wall of the cylinder part 131. A plurality of wing parts 132 are formed at substantially equal intervals in the circumferential direction of the cylindrical part 131. The turbine 13 is provided so as to be accommodated in the turbine housing 14.

  The turbine housing 14 is provided between the exhaust pipe 7 and the exhaust pipe 8. The turbine housing 14 is formed of a metal such as iron containing nickel, for example. The turbine housing 14 includes a first scroll 141, a second scroll 142, and the like. The first scroll 141 and the second scroll 142 are annularly formed around the wing part 132. Here, the second scroll 142 is formed on one end side in the axial direction of the cylindrical portion 131 with respect to the first scroll 141.

  As shown in FIG. 1B, the turbine housing 14 is formed with a first flow path 143, a second flow path 144, and a third flow path 145. The first flow path 143 is formed so as to connect the inside of the exhaust pipe 7 and the first scroll 141. The second flow path 144 is formed along the first flow path 143 and has one end connected to the second scroll 142. An opening 146 is formed in the partition wall that separates the first flow path 143 and the second flow path 144. Accordingly, the other end of the second flow path 144 is connected to the inside of the exhaust pipe 7 via the opening 146 and the first flow path 143.

  The third flow path 145 is formed so as to connect the first scroll 141 and the second scroll 142 and the inside of the exhaust pipe 8 and along the second flow path 144. Here, the turbine 13 is provided in the vicinity of the first scroll 141 and the second scroll 142 in the third flow path 145. An opening 147 is formed in the partition wall that separates the second flow path 144 and the third flow path 145. Thus, the second flow path 144 is connected to the third flow path 145 via the opening 147 so as to bypass the turbine 13.

With the above configuration, the exhaust discharged from the engine 2 can flow to the exhaust pipe 8 via the inside of the exhaust pipe 7, the first flow path 143, the first scroll 141, the turbine 13, and the third flow path 145. . The exhaust discharged from the engine 2 passes through the inside of the exhaust pipe 7, the first flow path 143, the opening 146, the second flow path 144, the second scroll 142, the turbine 13, and the third flow path 145. The exhaust pipe 8 can be circulated. Here, the first flow path 143, the opening 146, the second flow path 144, and the second scroll 142 correspond to an “exhaust flow path” in the claims. Exhaust gas discharged from the engine 2 passes through the inside of the exhaust pipe 7, the first flow path 143, the opening 146, the second flow path 144, the opening 147, and the third flow path 145 to the exhaust pipe 8. Distribution is possible. Here, the second flow path 144, the opening 147, and the third flow path 145 correspond to the “bypass flow path” in the claims.
FIG. 2 schematically shows the configuration of the supercharger 3.

  The bearing portion 15 is formed of metal, for example, and is provided between the compressor housing 12 and the turbine housing 14. The shaft 16 is formed in a rod shape, for example, from metal, and is provided so as to connect the cylinder part 111 and the cylinder part 131 coaxially. The shaft 16 is supported by the bearing portion 15. Thereby, the compressor 11 and the turbine 13 can rotate together with the shaft 16.

  When the exhaust of the first scroll 141 and the second scroll 142 collides with the blade portion 132 of the turbine 13, the turbine 13 rotates. As a result, the compressor 11 rotates and the intake air in the intake pipe 5 is compressed and guided to the engine 2. In the present embodiment, an intercooler 19 is provided between the compressor housing 12 in the intake passage 6 and the engine 2. The intercooler 19 cools the intake air that has been compressed by the compressor 11 and has risen in temperature. As a result, the air density of the intake air increases, and a larger amount of intake air can be supplied to the engine 2.

  In the present embodiment, a throttle valve 20 is provided between the intercooler 19 in the intake passage 6 and the engine 2. The throttle valve 20 is provided so that the intake passage 6 can be opened and closed. An electronic control unit (hereinafter referred to as “ECU”) 21 is connected to the throttle valve 20. The ECU 21 is a small computer that includes a calculation unit, a storage unit, an input / output unit, and the like. The ECU 21 performs control according to a program stored in the storage unit based on signals from sensors provided in each part of the vehicle, and controls the vehicle in an integrated manner by controlling the operation of devices and devices in each part of the vehicle. To do. The ECU 21 can adjust the amount of intake air supplied to the engine 2 by controlling the operation (opening degree) of the throttle valve 20.

  The first valve 17 is made of, for example, metal, and is provided in the vicinity of the opening 146 of the second flow path 144. The first valve 17 includes an arm 171, a valve portion 172, a first valve shaft 173, and the like. The arm 171 is formed in a rod shape. The valve portion 172 is provided at one end of the arm 171. The first valve shaft 173 is formed in a substantially cylindrical shape, and is provided integrally with the arm 171 so that one end is connected to the other end of the arm 171. The first valve shaft 173 is provided in the turbine housing 14 so that the other end is exposed to the outside of the turbine housing 14 and is rotatable around the shaft. As a result, when the first valve shaft 173 rotates around the shaft, the valve portion 172 approaches or separates from the opening 146. When the valve portion 172 contacts the edge of the opening portion 146 and closes the opening portion 146, the “exhaust flow path” is in a closed state (fully closed, valve-closed state). On the other hand, when the valve portion 172 is separated from the edge portion of the opening 146, the “exhaust flow path” is in an open state (valve open state).

  When the first valve 17 is in the closed state, the exhaust is guided to the turbine 13 via the first flow path 143 and the first scroll 141 to rotate the turbine 13. On the other hand, when the first valve 17 is open, the exhaust is guided to the turbine 13 via the first flow path 143, the opening 146, the second flow path 144, the first scroll 141, and the second scroll 142. Then, the turbine 13 is rotated. As described above, the first valve 17 functions as a switching valve and can control the amount of exhaust gas supplied to the turbine 13. That is, in the present embodiment, the supercharger 3 is a variable capacity supercharger.

The second valve 18 is made of, for example, metal, and is provided in the vicinity of the opening 147 of the third flow path 145. The second valve 18 includes an arm 181, a valve portion 182 and a second valve shaft 183. The arm 181 is formed in a rod shape. The valve part 182 is provided at one end of the arm 181. The second valve shaft 183 is formed in a substantially cylindrical shape, and is provided integrally with the arm 181 so that one end is connected to the other end of the arm 181. The second valve shaft 183 is provided in the turbine housing 14 so that the other end is exposed to the outside of the turbine housing 14 and is rotatable around the shaft. Accordingly, when the second valve shaft 183 rotates around the axis, the valve portion 182 approaches or separates from the opening 147. When the valve part 182 contacts the edge of the opening part 147 and closes the opening part 147, the “bypass flow path” is in a closed state (fully closed, closed state). On the other hand, when the valve part 182 is separated from the edge part of the opening part 147, the “bypass flow path” is in an open state (valve open state).
Hereinafter, the direction in which the first valve 17 and the second valve 18 open is referred to as “the valve opening direction” as appropriate. Further, the direction in which the first valve 17 and the second valve 18 are closed is appropriately referred to as a “valve closing direction”.

  When the first valve 17 is open and the second valve 18 is closed, the exhaust passes through the first flow path 143, the opening 146, the second flow path 144, the first scroll 141, and the second scroll 142. Then, it is guided to the turbine 13 to rotate the turbine 13. On the other hand, when the first valve 17 and the second valve 18 are in the open state, part of the exhaust gas in the second flow path 144 flows to the third flow path 145 via the opening 147. Therefore, the rotation of the turbine 13 is slowed and the supercharging pressure is reduced. Thereby, the excessive raise of a supercharging pressure can be suppressed. As described above, the second valve 18 functions as a waste gate valve and can control the amount of exhaust gas that bypasses the turbine 13.

  As shown in FIG. 3, the valve drive device 1 includes an actuator 30, a shaft 35, a first member 40, a second member 50, a first valve lever 61, a second valve lever 62, a first rod 71, and a second rod 72. And a spring 81 as an urging means and an elastic member, a gap forming portion 90, and the like.

The actuator 30 has a housing 31, an output shaft 32, and the like. The output shaft 32 is formed in a rod shape and is accommodated in the housing 31 so as to be capable of reciprocating in the axial direction. In the present embodiment, the actuator 30 can drive the output shaft 32 in the axial direction by being supplied with electric power. The actuator 30 is attached to the supercharger 3 so that the housing 31 is fixed to the compressor housing 12.
The ECU 21 controls the movement of the output shaft 32 in the axial direction by adjusting the power supplied to the actuator 30.

  The shaft 35 is formed in a rod shape, and is provided coaxially and integrally with the output shaft 32 of the actuator 30. Thereby, the shaft 35 can reciprocate in the axial direction integrally with the output shaft 32. The shaft 35 has a shaft portion 351 extending in a substantially cylindrical shape in a direction orthogonal to the axis.

  The first member 40 has a main body 41. The main body 41 is formed in a substantially disc shape, and is provided so that the center of one surface is connected to the end of the shaft 35 on the side opposite to the actuator 30. That is, the main body 41 is provided on the shaft 35. Thereby, the main body 41 can reciprocate in the axial direction together with the output shaft 32 and the shaft 35. A first contact portion 411 is formed on the other surface of the main body 41. A first engagement portion 412 is formed on one surface of the main body 41.

  The 2nd member 50 has the main body 51, the cylinder part 52, the extending | stretching part 53 grade | etc.,. The main body 51 is formed in a substantially disc shape. A second contact portion 511 is formed on one surface of the main body 51. The main body 51 is formed with a shaft portion 512 extending in a substantially cylindrical shape in the surface direction (radial direction) of the main body 51.

  The cylinder part 52 is formed so as to extend in a cylindrical shape from the outer edge part of one surface of the main body 51 in the plate thickness direction. The extending portion 53 is formed so as to extend in an annular shape radially inward from the end portion of the cylindrical portion 52 opposite to the main body 51. A second engaging portion 531 is formed on the surface of the extending portion 53 on the main body 51 side.

  The second member 50 is configured such that the first member 40 is positioned between the second contact portion 511 and the second engagement portion 531, and the first contact portion 411 of the first member 40 is the second contact. It is provided on the shaft 35 so as to face the portion 511. Therefore, when the second member 50 and the first member 40 are relatively moved in the axial direction, the second contact portion 511 and the first contact portion 411 can contact each other.

  The first valve lever 61 includes a main body 611, a first valve lever shaft 612, and the like. The main body 611 is formed in a rod shape, and is provided so that one end is fixed to the first valve shaft 173. Thus, the main body 611 (first valve lever 61) can rotate integrally with the first valve shaft 173. Therefore, when the main body 611 rotates with the first valve shaft 173, the first valve 17 opens or closes.

  The first valve lever shaft 612 is formed in a substantially cylindrical shape and is provided at the other end of the main body 611. The first valve lever shaft 612 is provided so that the shaft is parallel to the axis of the first valve shaft 173 at a position separated from the axis of the first valve shaft 173 by a first predetermined distance D1.

  The second valve lever 62 includes a main body 621, a second valve lever shaft 622, and the like. The main body 621 is formed in a rod shape, and is provided so that one end is fixed to the second valve shaft 183. Thereby, the main body 621 (second valve lever 62) can rotate integrally with the second valve shaft 183. Therefore, when the main body 621 rotates with the second valve shaft 183, the second valve 18 opens or closes.

The second valve lever shaft 622 is formed in a substantially cylindrical shape and is provided at the other end of the main body 621. The second valve lever shaft 622 is provided so that the shaft is parallel to the axis of the second valve shaft 183 at a position away from the axis of the second valve shaft 183 by a second predetermined distance D2.
The first rod 71 is formed in a rod shape, and one end is connected to the first valve lever shaft 612 so as to be relatively rotatable, and the other end is connected to the shaft portion 351 of the shaft 35 so as to be relatively rotatable.
The second rod 72 is formed in a rod shape, and has one end connected to the second valve lever shaft 622 so as to be relatively rotatable and the other end connected to the shaft portion 512 of the second member 50 so as to be relatively rotatable.

  The spring 81 is formed in a coil shape by an elastic member such as metal. That is, the spring 81 is a so-called coil spring, and is provided outside the shaft 35 and between the first member 40 and the extending portion 53 of the second member 50. One end of the spring 81 is engaged with the first engagement portion 412 of the first member 40, and the other end is engaged with the second engagement portion 531 of the second member 50. In the present embodiment, the spring 81 is set to a predetermined elastic modulus and has a force extending in the axial direction. That is, the spring 81 urges the first member 40 and the second member 50 in a direction in which the first contact portion 411 and the second contact portion 511 approach each other.

  The gap forming portion 90 is provided in the second member 50 in the present embodiment. The gap forming portion 90 includes a screw portion 91, a nut portion 92, and the like. The screw portion 91 is formed in a substantially cylindrical shape, and a screw thread is formed on the outer wall. The screw portion 91 is screwed into a screw hole formed in the main body 51 (second contact portion 511) of the second member 50 and having a screw groove on the inner wall. The screw portion 91 is provided in a state of protruding a predetermined amount from the second contact portion 511 to the first contact portion 411 side by being screwed into the screw hole of the main body 51. The screw part 91 can change the protrusion amount from the second contact part 511 to the first contact part 411 side by adjusting the screwing amount into the screw hole.

  The nut portion 92 is formed in an annular shape and has a thread groove corresponding to the thread of the thread portion 91 on the inner wall. The nut portion 92 is provided so as to be screwed into the screw portion 91 from the end of the screw portion 91 opposite to the first contact portion 411 and to come into contact with the main body 51. As a result, the screw portion 91 cannot move relative to the main body 51.

As shown in FIGS. 3 and 4A, when both the first valve 17 and the second valve 18 are closed (fully closed), the screw portion 91 and the first contact portion 411 are separated from each other. Yes. On the other hand, as shown in FIG. 5A, when the second valve 18 is closed (fully closed) and the first valve 17 is opened by a predetermined amount, the screw portion 91 and the first contact portion 411 are Abut. At this time, a predetermined gap is formed between the first contact portion 411 and the second contact portion 511.
In the present embodiment, as shown in FIG. 3, the first valve lever 61 and the second valve lever 62 are formed such that the first predetermined distance D1 and the second predetermined distance D2 are substantially the same.

  Thus, in the present embodiment, the shaft 35, the first rod 71, the first valve lever 61, the second rod 72, and the second valve lever 62 constitute a “link mechanism”. When the output shaft 32 and the shaft 35 move in the axial direction by driving the actuator 30, the moving operation is transmitted to the first valve 17 and the second valve 18 via the “link mechanism”, and the first valve 17 and the second valve 18 are moved. 2 Valve 18 opens and closes.

Next, the operation of the valve drive device 1 according to the present embodiment will be described with reference to FIGS.
As shown in FIG. 4A, when both the first valve 17 and the second valve 18 are closed (fully closed), the first contact portion 411 and the screw portion 91 are separated from each other. The amount of movement of the output shaft 32 in the axial direction at this time, that is, the driving amount of the actuator 30 is defined as a first driving amount K1. At this time, the biasing force from the spring 81 acts on the second valve 18 via the second member 50, the second rod 72, and the second valve lever 62, and biases the second valve 18 in the valve closing direction. ing. Thereby, the fully closed state of the second valve 18 is maintained. At this time, the urging force from the spring 81 acts on the first member 40 (the shaft 35 and the output shaft 32). At this time, as shown in FIG. 4B, exhaust is supplied to the turbine 13 via the first scroll 141.

Further, the first member 40 (the shaft 35 and the output shaft 32) is in contact with the first contact from the position where the first valve 17 is closed (see FIG. 4A) with the second valve 18 closed. In the range up to the position where the portion 411 and the screw portion 91 abut (see FIG. 5A), it can move in the axial direction while receiving the urging force of the spring 81.
In the state of FIG. 4A, when the ECU 21 drives and controls the actuator 30, the first member 40 (the shaft 35 and the output shaft 32) moves in a direction in which the first member 40 moves away from the actuator 30. Transmission to the first valve 17 through the first rod 71 and the first valve lever 61 causes the first valve 17 to open. At this time, the first contact portion 411 moves in a direction approaching the second contact portion 511 (gap forming portion 90).

  Further, when the ECU 21 moves the first member 40 (the shaft 35 and the output shaft 32), the first contact portion 411 contacts the screw portion 91 of the gap forming portion 90 (see FIG. 5A). The driving amount of the actuator 30 at this time is defined as a second driving amount K2. At this time, the first valve 17 is opened by a predetermined amount, and the second valve 18 is closed (fully closed). At this time, as shown in FIG. 5B, the exhaust gas is supplied to the turbine 13 via the first scroll 141 and the second scroll 142.

Further, when the ECU 21 moves the first member 40 (the shaft 35 and the output shaft 32), the second member 50 rotates together with the first member 40 in a state where the first contact portion 411 and the screw portion 91 are in contact. Move in the direction. As a result, when the second member 50 moves in a direction in which the second member 50 moves away from the actuator 30, the movement is transmitted to the second valve 18 via the second rod 72 and the second valve lever 62, and the second valve 18 opens. At this time, the biasing force of the spring 81 is canceled between the first member 40 and the second member 50 when the first contact portion 411 and the screw portion 91 are in contact with each other. Does not work.
Further, when the ECU 21 moves the first member 40 (the shaft 35 and the output shaft 32), the second valve 18 is opened together with the first valve 17 (the opening degree is increased), which is shown in FIG. It becomes a state.

  The actuator 30 can drive the first member 40 (the shaft 35 and the output shaft 32) until the first member 40 (the shaft 35 and the output shaft 32) reaches the position shown in FIG. The driving amount of the actuator 30 in the state shown in FIG. 6A is a third driving amount K3. At this time, the opening degree of the first valve 17 and the second valve 18 becomes the maximum opening degree. At this time, as shown in FIG. 6B, exhaust is supplied to the turbine 13 via the first scroll 141 and the second scroll 142, and the exhaust is purified by bypassing the turbine 13. It flows to the device 9 side.

As shown in FIG. 7A, in the present embodiment, when the drive amount of the actuator 30 is the second drive amount K2, the opening degree of the first valve 17 is set to “necessary opening degree”. Here, the required opening means the minimum opening of the valve opening that does not change the flow rate of the fluid passing through the valve.
Further, when the drive amount of the actuator 30 is the third drive amount K3, the opening degree of the second valve 18 is set to be “necessary opening degree”.

In other words, in the present embodiment, the first drive amount K1 to the second drive amount K2 are set as the substantial control range of the first valve 17, and the second drive amount K2 to the third drive amount K3 are the second valve. It is set as 18 substantial control ranges.
Further, as shown in FIG. 7B, the load acting on the actuator 30 in the range where the drive amount of the actuator 30 is from the first drive amount K1 to the second drive amount K2 (the control range of the first valve 17) is “ The torque generated by the spring 81 (valve closing direction) ”−“ the valve acting force of exhaust pulsation (valve opening direction) ”. The load acting on the actuator 30 in the range where the driving amount of the actuator 30 is from the second driving amount K2 to the third driving amount K3 is only “valve acting force of exhaust pulsation (valve opening direction)”.

As described above, in the present embodiment, when the first valve 17 is in the fully closed state, a predetermined gap is set between the first member 40 and the second member 50 (gap forming portion 90). ing. Thereby, until the 1st valve 17 opens more than predetermined opening degree, the 2nd valve 18 can be urged | biased to the close side with the spring 81, and it can be in the valve-closed state. Therefore, the first valve 17 (switching valve) can be driven within a predetermined range by the actuator 30 while the second valve 18 (waste gate valve) is kept fully closed by the biasing force of the spring 81. On the other hand, when the first valve 17 opens more than a predetermined opening, the first member 40 and the gap forming portion 90 (screw portion 91) come into contact with each other, and the second valve 18 includes the second valve lever 62 and the second rod 72. The second member 50, the first member 40, the shaft 35, the first rod 71, and the first valve lever 61 are opened in conjunction with the first valve 17.
Thus, in this embodiment, a link mechanism can be comprised with comparatively few structural members, and two valves (the 1st valve 17 and the 2nd valve 18) can be driven by one actuator 30. Therefore, member cost and manufacturing cost can be reduced.

  In this embodiment, when the first valve 17 is driven with the second valve 18 closed, the biasing force of the spring 81 acts on the output shaft 32 of the actuator 30 via the first member 40. At this time, the load on the actuator 30 increases. On the other hand, when the second valve 18 is opened, that is, when the second valve 18 is driven together with the first valve 17, the urging force of the spring 81 is applied to the first member 40 and the gap forming portion 90 (screw portion). 91) is canceled out between the first member 40 and the second member 50, and does not act on the output shaft 32 of the actuator 30. Therefore, when the second valve 18 is mainly opened as the operation of the engine 2, the load on the actuator 30 is reduced and the stress on the actuator 30 can be reduced.

  FIG. 8 is a diagram showing the relationship between “the rotational speed of the engine 2” and “BMEP (net average effective pressure) or torque”. As shown in FIG. 8, most of the use range of the engine 2 is included in the open control range of the second valve 18. Therefore, in this embodiment, the stress on the actuator 30 can be reduced in most of the usage range of the engine 2. Therefore, the life of the actuator 30 and the peripheral members can be extended. Moreover, in this embodiment, since the actuator 30 is electric, power consumption can be reduced.

  Further, in the present embodiment, the spring 81 is formed by an elastic member having a predetermined elastic modulus, one end engages with the first engaging portion 412 of the first member 40, and the other end is the second of the second member 50. It is provided to engage with the engaging portion 531. Thus, the first valve 17 can be driven within a predetermined range by the actuator 30 while the second valve 18 is kept in the fully closed state by the biasing force of the spring 81. The actuator 30 is attached to the compressor housing 12. Therefore, it can suppress that the spring 81 becomes high temperature by the heat | fever of exhaust_gas | exhaustion. Therefore, the spring 81 can be formed of an inexpensive member having low heat resistance.

  In this embodiment, the second contact portion 511 is provided on the second contact portion 511 so as to protrude from the second contact portion 511 to the first contact portion 411 side. A gap forming part 90 is further provided for forming a predetermined gap between the contact part 411 and the second contact part 511. The gap forming portion 90 (screw portion 91) is provided so that the amount of protrusion from the second contact portion 511 can be changed. By the way, in the present embodiment, the range from when the first valve 17 starts to open until the second valve 18 starts to open is the gap between the first contact portion 411 and the second contact portion 511. Determined. In the present embodiment, the gap between the first contact part 411 and the second contact part 511 can be adjusted by the gap forming part 90. Therefore, the control range (operation range) of the first valve 17 can be accurately determined by adjusting the variation in the positional relationship between the first member 40 and the second member 50 and the variation in the biasing force of the spring 81. Therefore, the component tolerance can be increased and the manufacturing cost can be reduced.

(Second Embodiment)
A valve driving apparatus according to a second embodiment of the present invention is shown in FIG. In the second embodiment, the configurations of the first member, the second member, and the biasing means are different from those of the first embodiment.
In the second embodiment, an annular first contact portion 411 is formed on the outer edge portion of the other surface of the main body 41 of the first member 40. A first engagement portion 412 is formed at the center of the other surface of the main body 41.

  The second member 50 does not have the extending portion 53 shown in the first embodiment. A second contact portion 521 is formed at the end of the cylindrical portion 52 of the second member 50 opposite to the main body 51. The second contact portion 521 can contact the first contact portion 411. A second engagement portion 513 is formed at the center of one surface of the main body 51 of the second member 50.

  In the present embodiment, the spring 81 is provided between the main body 51 and the first member 40 so as to be accommodated inside the cylindrical portion 52 of the second member 50. One end of the spring 81 is engaged with the first engagement portion 412 of the first member 40, and the other end is engaged with the second engagement portion 513 of the second member 50. In the present embodiment, the spring 81 is set to a predetermined elastic modulus and has a force to contract in the axial direction. That is, the spring 81 urges the first member 40 and the second member 50 in a direction in which the first contact portion 411 and the second contact portion 521 approach each other.

  In the present embodiment, the gap forming portion 90 is provided in the first contact portion 411 of the main body 41. The threaded portion 91 can change the amount of protrusion from the first contact portion 411 to the second contact portion 521 side. Thereby, the clearance gap between the 1st contact part 411 of the 1st member 40 and the 2nd contact part 521 of the 2nd member 50 can be adjusted.

  Also in the second embodiment, the first valve 17 (switching valve) is driven within a predetermined range by the actuator 30 while the second valve 18 (waste gate valve) is kept in the fully closed state by the urging force of the spring 81. And the same effects as those of the first embodiment can be obtained.

(Third embodiment)
A valve drive device according to a third embodiment of the present invention is shown in FIG. In 3rd Embodiment, the structure of a 1st member, a 2nd member, and an urging | biasing means differs from 1st Embodiment.

  In the third embodiment, the first member 40 further includes a main body 42. The main body 42 is formed so as to protrude radially outward from the middle of the shaft 35 in the axial direction. A first contact portion 421 is formed on the main body 41 side of the main body 42. Here, the main body 41 corresponds to the “upper member” in the claims, and the main body 42 corresponds to the “lower member”.

  The second member 50 has a main body 54. The main body 54 is formed in a substantially cylindrical shape, and is provided between the main body 41 and the main body 42 so as to be reciprocally movable in the axial direction with the shaft 35 inserted therethrough. A second contact portion 541 is formed on the main body 42 side of the main body 54. A second engaging portion 542 is formed on the main body 41 side of the main body 54. The main body 54 is formed with a shaft portion 543 extending in a substantially cylindrical shape in the radial direction of the main body 54. The other end of the second rod 72 is connected to the shaft portion 543 so as to be relatively rotatable.

  In the present embodiment, the spring 81 is provided outside the shaft 35 and between the main body 41 and the main body 42 of the first member 40. One end of the spring 81 is engaged with the first engaging portion 412 of the first member 40, and the other end is engaged with the second engaging portion 542 of the second member 50. In the present embodiment, the spring 81 is set to a predetermined elastic modulus and has a force extending in the axial direction. That is, the spring 81 urges the first member 40 and the second member 50 in a direction in which the first contact portion 421 and the second contact portion 541 approach each other.

  In the present embodiment, the gap forming portion 90 is provided in the first contact portion 421 of the main body 42. The threaded portion 91 can change the protruding amount from the first contact portion 421 to the second contact portion 541 side. Thereby, the clearance gap between the 1st contact part 421 of the 1st member 40 and the 2nd contact part 541 of the 2nd member 50 can be adjusted.

  Also in the third embodiment, the first valve 17 (switching valve) is driven within a predetermined range by the actuator 30 while the second valve 18 (waste gate valve) is kept in the fully closed state by the urging force of the spring 81. And the same effects as those of the first embodiment can be obtained.

(Fourth embodiment)
FIG. 11 shows a valve driving device according to a fourth embodiment of the present invention. In the fourth embodiment, the configurations of the actuator, the shaft, the first member, and the second member are different from those in the first embodiment.
In the fourth embodiment, the shaft 35 is provided separately from the output shaft 32 of the actuator 30. The shaft 35 is provided so that one end is fixed to the compressor housing 12.

In the actuator 30, the housing 31 is fixed to the compressor housing 12 so that the output shaft 32 is substantially orthogonal to the axis of the shaft 35. In addition, a shaft portion 321 that extends in a substantially cylindrical shape in the radial direction is formed at the distal end portion of the output shaft 32.
The first member 40 includes a main body 43, a cylindrical portion 44, an extending portion 45, and the like.

The main body 43 is formed in a substantially annular shape, and is provided so as to be capable of reciprocating in the axial direction with the shaft 35 inserted therein. A first engagement portion 431 is formed on one surface of the main body 43. The cylinder portion 44 is formed so as to extend in a cylindrical shape from the outer edge portion of the main body 43. The extending portion 45 is formed so as to extend in an annular shape radially inward from an end portion of the cylindrical portion 44 on the side opposite to the main body 43. A first contact portion 451 is formed on the surface of the extending portion 45 on the main body 43 side. The main body 43 is formed with a shaft portion 432 extending in a substantially cylindrical shape in the surface direction (radial direction) of the main body 43. The other end of the first rod 71 is connected to the shaft portion 432 so as to be relatively rotatable.
The second member 50 has a main body 54. Since the second member 50 of the present embodiment has the same configuration as the second member 50 of the third embodiment, the description thereof is omitted.

  In the present embodiment, the spring 81 is provided outside the shaft 35, inside the cylinder portion 44, and between the main body 43 and the main body 54. One end of the spring 81 is engaged with the first engagement portion 431 of the first member 40, and the other end is engaged with the second engagement portion 542 of the second member 50. In the present embodiment, the spring 81 is set to a predetermined elastic modulus and has a force extending in the axial direction. That is, the spring 81 urges the first member 40 and the second member 50 in a direction in which the first contact portion 451 and the second contact portion 541 approach each other.

  In the present embodiment, the gap forming portion 90 is provided in the first contact portion 451 of the extending portion 45 of the first member 40. The threaded portion 91 can change the amount of protrusion from the first contact portion 451 to the second contact portion 541 side. Thereby, the clearance gap between the 1st contact part 451 of the 1st member 40 and the 2nd contact part 541 of the 2nd member 50 can be adjusted.

  In the present embodiment, a third rod 73 is further provided. The third rod 73 is formed in a rod shape, and one end is connected to the shaft portion 321 of the output shaft 32 so as to be relatively rotatable, and the other end is connected to be able to rotate relative to the shaft portion 432 of the first member 40. . Thus, when the output shaft 32 moves in the axial direction, the movement is transmitted to the first valve 17 via the third rod 73, the first rod 71 and the first valve lever 61, and the first valve 17 is opened and closed. To do.

  Thus, in this embodiment, the shaft 35 is provided separately from the output shaft 32. The first member 40 and the second member 50 are provided to be movable relative to the shaft 35. The other end of the first rod 71 is connected to the first member 40. A third rod 73 that connects the output shaft 32 and the first member 40 is further provided. Thereby, the moving direction of the shaft 35 and the moving direction of the output shaft 32 can be made different, and the freedom degree of arrangement | positioning of the actuator 30 and a link mechanism can be raised.

  Also in the fourth embodiment, the first valve 17 (switching valve) is driven within a predetermined range by the actuator 30 while the second valve 18 (waste gate valve) is kept fully closed by the biasing force of the spring 81. And the same effects as those of the first embodiment can be obtained.

(Fifth embodiment)
A valve driving apparatus according to a fifth embodiment of the present invention is shown in FIG. In the fifth embodiment, the configuration of the first member is different from that of the first embodiment.

  In the fifth embodiment, the first member 40 further includes a cylindrical portion 46. The cylindrical portion 46 is formed so as to extend from the outer edge portion of the main body 41 toward the extending portion 53 side of the second member 50 in a substantially cylindrical shape. That is, the cylindrical portion 46 is formed coaxially with the shaft 35. Here, the cylindrical portion 46 is formed so as to be positioned inside the cylindrical portion 52 of the second member 50 and outside the spring 81.

  In the present embodiment, the outer wall of the cylindrical portion 46 of the first member 40 and the inner wall of the cylindrical portion 52 of the second member 50 are slidable. Therefore, when the second member 50 moves relative to the first member 40, the posture of the second member 50 is stabilized. Thereby, the shaft runout of the second member 50 with respect to the shaft 35 can be suppressed, and the life of the member can be extended. Here, the cylindrical portion 46 corresponds to the “first cylindrical portion” in the claims, and the cylindrical portion 52 corresponds to the “second cylindrical portion”.

(Sixth embodiment)
FIG. 13A shows a valve driving device according to a sixth embodiment of the present invention. In 6th Embodiment, although the structure of the valve drive device 1 is the same as that of 1st Embodiment, the structure of the supercharger to which the valve drive device 1 is attached differs from 1st Embodiment.

  In the sixth embodiment, the supercharger 22 has a first flow path 221, a second flow path 222, and a third flow path 223. The first flow path 221 is formed so as to connect the engine 2 and the first scroll 141. The second flow path 222 is formed to connect the first flow path 221 and the second scroll 142. Here, the first flow path 221 and the second flow path 222 correspond to the “exhaust flow path” in the claims. The third flow path 223 is formed so as to bypass the turbine 13 and connect the first flow path 221 and the exhaust purification device 9. Here, the third flow path 223 corresponds to a “bypass flow path” in the claims.

In the present embodiment, the first valve 17 (switching valve) is provided in the second flow path 222 so that the second flow path 222 can be opened and closed. The second valve 18 (waste gate valve) is provided in the third flow path 223 so that the third flow path 223 can be opened and closed.
In this embodiment, the same effect as that of the first embodiment can be obtained.

(Seventh embodiment)
FIG. 13B shows a valve driving device according to a seventh embodiment of the present invention. In 7th Embodiment, although the structure of the valve drive device 1 is the same as that of 1st Embodiment, the structure of the supercharger to which the valve drive device 1 is attached differs from 1st Embodiment.

  In the seventh embodiment, the supercharger 23 includes a first flow path 231, a second flow path 232, a third flow path 233, and a fourth flow path 234. The first flow path 231 is formed to connect the engine 2 and the first scroll 141. The second flow path 232 is formed to connect the first flow path 231 and the second scroll 142. The third flow path 233 is formed so as to bypass the turbine 13 and connect the second flow path 232 and the exhaust purification device 9. The fourth flow path 234 is formed so as to bypass the turbine 13 and connect the first flow path 231 and the third flow path 233. Here, the first flow path 231 and the second flow path 232 correspond to the “exhaust flow path” in the claims. The third flow path 233 and the fourth flow path 234 correspond to “bypass flow paths” in the claims.

In the present embodiment, the first valve 17 (switching valve) is provided in the second flow path 232 so that the second flow path 232 can be opened and closed. The second valve 18 (waste gate valve) is provided at a connection point between the third flow path 233 and the fourth flow path 234 so that the third flow path 233 and the fourth flow path 234 can be opened and closed.
In this embodiment, the same effect as that of the first embodiment can be obtained.

(Eighth embodiment)
FIG. 14 shows a valve driving device according to an eighth embodiment of the present invention. In the eighth embodiment, the configuration of the valve driving device 1 is the same as that of the first embodiment, but the application target of the valve driving device 1 is different from that of the first embodiment.

In the eighth embodiment, the valve drive device 1 is attached to a supercharger 24 that supercharges intake air to the engine 2. The supercharger 24 includes a first compressor 251, a second compressor 252, a first turbine 261, a second turbine 262, a first shaft 263, a second shaft 264, a first valve 17, a second valve 18, and the like. .
The first compressor 251 and the second compressor 252 are provided in the intake passage 6 that guides intake air to the engine 2.

  The first turbine 261 and the second turbine 262 are provided in the exhaust passage 10 through which the exhaust from the engine 2 flows. The first turbine 261 is connected to the first compressor 251 by the first shaft 263. Thus, the first turbine 261 can rotate the first compressor 251 by being supplied with exhaust gas and rotating. Here, the first turbine 261 is used as a turbine for low speed (for small flow rate), for example.

  The second turbine 262 is connected to the second compressor 252 by the second shaft 264. Thereby, the second turbine 262 can rotate the second compressor 252 by being supplied with exhaust gas and rotating. Here, the second turbine 262 is used as, for example, a turbine for high speed (for large flow rate).

  In the present embodiment, a first exhaust passage 271 that guides exhaust from the engine 2 to the first turbine 261 and a second exhaust passage 272 that guides exhaust from the engine 2 to the second turbine 262 are formed in the exhaust passage 10. ing. Here, the second exhaust passage 272 is formed so that the end opposite to the second turbine 262 is connected to the first exhaust passage 271.

  Further, a bypass flow path 273 is formed to connect the first turbine 261 and the second turbine 262 of the exhaust passage 10 to the opposite side of the engine 2 and the opposite side of the engine 2 so as to bypass the first turbine 261 and the second turbine 262. ing.

  The first valve 17 is provided in the second exhaust passage 272 so that the second exhaust passage 272 can be opened and closed by rotating around the axis of the first valve shaft 173. The second valve 18 is provided in the bypass flow path 273 so that the bypass flow path 273 can be opened and closed by rotating around the axis of the second valve shaft 183.

  When the first valve 17 is in the closed state, the exhaust is guided to the first turbine 261 via the first exhaust flow path 271 to rotate the first turbine 261. On the other hand, when the first valve 17 is open, the exhaust is guided to the first turbine 261 via the first exhaust passage 271 and to the second turbine 262 via the second exhaust passage 272. Guided to rotate the first turbine 261 and the second turbine 262. As described above, the first valve 17 functions as a switching valve and can control the amount of exhaust gas supplied to the two turbines (the first turbine 261 and the second turbine 262). That is, in this embodiment, the supercharger 22 is a two-stage supercharger.

  When the second valve 18 is in the open state, a part of the exhaust in the exhaust passage 10 flows through the bypass passage 273. For this reason, the rotation of the first turbine 261 and the second turbine 262 is delayed, and the supercharging pressure is reduced. Thereby, the excessive raise of a supercharging pressure can be suppressed. Thus, the second valve 18 functions as a waste gate valve and can control the amount of exhaust gas that bypasses the first turbine 261 and the second turbine 262.

  The valve drive device 1 is attached to the supercharger 24 so that the first valve 17 and the second valve 18 can be driven. That is, in the present embodiment, the valve drive device 1 is applied to a two-stage supercharger (supercharger 24) having a wastegate valve, and is supplied to two turbines (first turbine 261 and second turbine 262). The first valve 17 that controls the amount of exhaust to be performed, and the second valve 18 (waste gate valve) that controls the amount of exhaust that bypasses the turbines (the first turbine 261 and the second turbine 262) are driven.

  The actuator 30, the shaft 35, the first member 40, the second member 50, the first valve lever 61, the second valve lever 62, the first rod 71, the second rod 72, and the spring 81 of the present embodiment are the first embodiment. Therefore, the actuator 30 drives the first valve 17 (switching valve) within a predetermined range while keeping the second valve 18 (waste gate valve) in the fully closed state by the urging force of the spring 81. Can do. Therefore, 8th Embodiment can have the same effect as 1st Embodiment.

(Other embodiments)
In another embodiment of the present invention, the first valve may be used as a variable nozzle that controls the amount of exhaust gas supplied to the turbine, that is, a “variable nozzle” of a variable displacement supercharger. In this case, the first valve (variable nozzle) can be driven within a predetermined range by the actuator while the second valve (waist gate valve) is kept fully closed by the urging force of the urging means.

In the above-mentioned embodiment, each member (1st member, 2nd member) showed the example which has a cylindrical cylinder part. On the other hand, in another embodiment of the present invention, the cylindrical portion does not need to be continuously formed in the circumferential direction, and may be formed in a shape in which a part of the circumferential direction is missing.
Moreover, in other embodiment of this invention, the urging | biasing means may be formed with the elastic member which consists of not only a metal coil spring but another material and a shape.

  Moreover, in other embodiment of this invention, the clearance gap formation part may be provided in either the 1st contact part or the 2nd contact part. Further, the valve driving device may not include the gap forming portion. In this case, the first abutting portion and the second abutting portion can be brought into contact with each other, and the gap between the first abutting portion and the second abutting portion cannot be adjusted. The first valve can be driven within a predetermined range by the actuator while the second valve is kept in the fully closed state by the force.

In another embodiment of the present invention, the actuator may be driven by other methods such as a pressure method and a hydraulic method as long as the output shaft moves in the axial direction. Good.
Further, the above-described embodiments may be implemented in any combination as long as there are no structural obstruction factors.
Thus, the present invention is not limited to the above-described embodiment, and can be applied to various embodiments without departing from the scope of the invention.

DESCRIPTION OF SYMBOLS 1 ... Valve drive device 17 ... 1st valve 173 ... 1st valve shaft 18 ... 2nd valve 183 ... 2nd valve shaft 30 ... Actuator 32 ... ··· Output shaft 35 ··· Shaft 40 ··· First member 411, 421, 451 ... First contact portion 412, 431 ... First engaging portion 50 ··· Second member 511, 521, 541 ... 2nd contact part 513, 531, 542 ... 2nd engaging part 61 ... 1st valve lever 612 ... 1st valve lever shaft 62 ... ... 1st 2 valve lever 622 ... 2nd valve lever shaft 71 ... 1st rod 72 ... 2nd rod 81 ... ... Spring (biasing means)

Claims (10)

A supercharger (3) comprising a first valve (17) rotatable about an axis of a first valve shaft (173) and a second valve (18) rotatable about an axis of a second valve shaft (183). 22, 23, 24), and a valve driving device (1) for driving the first valve and the second valve,
An actuator (30) having an output shaft (32) movable in the axial direction;
A shaft (35) provided coaxially and integrally with the output shaft, or provided separately from the output shaft;
A first member (40) provided on an axis of the shaft and having a first contact portion (411, 421, 451) and a first engagement portion (412, 431);
A second contact part (511, 521, 541) provided on the shaft of the shaft and capable of contacting the first contact part, and a second engagement part (513, 531, 542). Two members (50);
The first valve shaft is provided so as to be rotatable integrally with the first valve shaft, and the shaft is provided parallel to the first valve shaft at a first predetermined distance (D1) from the first valve shaft. A first valve lever (61) having a first valve lever shaft (612),
Provided so as to be rotatable integrally with the second valve shaft, and provided so that the shaft is parallel to the axis of the second valve shaft at a second predetermined distance (D2) from the shaft of the second valve shaft. A second valve lever (62) having a second valve lever shaft (622),
A first rod (71) having one end connected to the first valve lever shaft so as to be relatively rotatable and the other end connected to the shaft or the first member;
A second rod (72) having one end connected to the second valve lever shaft so as to be relatively rotatable and the other end connected to the second member;
Provided between the first engagement portion and the second engagement portion, and bias the first member and the second member in a direction in which the first contact portion and the second contact portion approach each other. Biasing means (81) for
A valve driving device comprising:   A compressor (11) provided in an intake passage (6) for introducing intake air to the internal combustion engine (2), an exhaust passage (10) provided in an exhaust passage (10) through which the exhaust from the internal combustion engine flows, and the compressor is rotated by being supplied with the exhaust. A turbine (13) that can be driven to rotate, and an exhaust passage (142, 143, 144, 146, 221, 222, 231, 232) that guides exhaust from the internal combustion engine to the turbine, and around the axis of the first valve shaft The first valve capable of opening and closing the exhaust passage by rotating in the direction, and the bypass connecting the internal combustion engine side of the turbine and the opposite side of the internal combustion engine of the exhaust passage so as to bypass the turbine The bypass is provided in the flow path (144, 145, 147, 223, 233, 234) by rotating around the axis of the second valve shaft. 2. The turbocharger (3, 22, 23) provided with the second valve capable of opening and closing a flow path is configured to open and close the first valve and the second valve. Valve drive device.   A first compressor (251) and a second compressor (252) provided in an intake passage (6) for introducing intake air to the internal combustion engine (2), and an exhaust passage (10) through which exhaust from the internal combustion engine circulates. A first turbine (261) capable of rotationally driving the first compressor by being supplied and rotating, and a second turbine (262) capable of rotationally driving the second compressor by being supplied with and rotated by being provided with exhaust gas. ), The first valve provided in the first exhaust passage (271) for guiding the exhaust from the internal combustion engine to the first turbine or the second exhaust passage (272) for guiding the exhaust from the internal combustion engine to the second turbine. The first valve capable of opening and closing the first exhaust passage or the second exhaust passage by rotating around an axis of the shaft, and the first turbine and The second turbine is provided in a bypass passage (273) that connects the internal combustion engine side of the first turbine and the second turbine to the opposite side of the internal combustion engine so as to bypass the second turbine. It is attached to the supercharger (24) including the second valve capable of opening and closing the bypass flow path by rotating around the axis of the valve shaft, and opening and closing the first valve and the second valve. The valve drive apparatus according to claim 1, wherein   The urging means is formed of an elastic member having a predetermined elastic modulus, and is provided so that one end engages with the first engagement portion and the other end engages with the second engagement portion. The valve drive device according to any one of claims 1 to 3, wherein The shaft is provided coaxially and integrally with the output shaft,
The first member is provided integrally with the shaft,
The second member is provided to be movable relative to the shaft,
The valve driving device according to any one of claims 1 to 4, wherein the first rod has the other end connected to the shaft. The first member includes an upper member (41) in which the first engagement portion (412) is formed, and a lower member (42) in which the first contact portion (421) is formed,
The valve driving device according to claim 5, wherein the second member is provided between the upper member and the lower member. The shaft is provided separately from the output shaft,
The first member and the second member are provided to be movable relative to the shaft,
The other end of the first rod is connected to the first member,
The valve driving device according to any one of claims 1 to 4, further comprising a third rod (73) for connecting the output shaft and the first member. The first member has a first tube portion (46) formed coaxially with the shaft,
It said second member, the valve driving apparatus according to any one of claims 1 to 5 7, characterized in that it comprises a second cylindrical portion (52) located outside of said first cylindrical portion. The first contact portion or the second contact portion is provided on one side of the first contact portion or the second contact portion so as to protrude from one side of the first contact portion or the second contact portion to the other side. A gap forming portion (90) that forms a predetermined gap between the first contact portion and the second contact portion when contacting the other of the two contact portions;
The gap forming part is provided so as to be able to change the amount of protrusion from one of the first contact part or the second contact part. Valve drive device.   10. The valve driving device according to claim 1, wherein the actuator drives the output shaft in an axial direction by being supplied with electric power. 11.

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