JP6832075B2 - Turbine equipment and supercharging system - Google Patents

Description

The present disclosure relates to a turbine device of an exhaust turbine supercharger attached to an internal combustion engine, and a supercharging system including the turbine device.

In an internal combustion engine with a supercharger, a catalyst device is installed downstream of the turbine device of the supercharger, and the exhaust gas discharged from the internal combustion engine to the exhaust passage is purified by the catalyst device after rotating the turbine wheel of the turbine. After that, it is released to the outside. In order to perform early activation of the catalyst (exhaust gas purification catalyst) in such an internal combustion engine with a supercharger, the waste gate valve of the turbine device is opened when the internal combustion engine is started, and the high temperature bypasses the turbine wheel. A technique for supplying the exhaust gas of the above to a catalyst device is known (for example, Patent Document 1). The temperature of the exhaust gas before the turbine wheel is rotationally driven is higher than the temperature of the exhaust gas after the turbine wheel is rotationally driven. Therefore, according to the above technique, it is possible to avoid a temperature drop of the exhaust gas due to passing through the turbine wheel and supply the high temperature exhaust gas to the catalyst.

Then, in Patent Document 1, in order to correct the temperature cloth generated in the exhaust passage by the exhaust gas before reaching the catalyst, a supercharging system capable of inflowing the exhaust gas having a uniform temperature in various places into the catalyst is provided. It is disclosed. More specifically, by rotating the low-temperature exhaust gas that has been rotationally driven by the turbine wheel and the high-temperature exhaust gas that has passed through the bypass passage in opposite directions, a collision occurs when the exhaust gas that has passed through each of the two passages merges. It is configured to increase the turbulence caused by the noise and to mix quickly until it reaches the catalyst. Specifically, the wastegate valve is configured to open and close the bypass passage by rotating a valve body capable of covering the outlet (wastegate port) of the bypass passage with an arm. By moving the covering valve body away from the outlet, the exhaust gas flows out from the gap between the outlet and the valve body, and the exhaust gas is swirled by forming the end of the outlet of the bypass passage so as to be tilted.

In addition, Patent Document 2 is a document showing the arrangement relationship between the bypass passage of the turbocharger and the wastegate valve. In the turbine device of Patent Document 2, as a wastegate valve, a slide type sleeve valve that opens and closes the bypass passage by sliding a valve body that can cover the outlet (wastegate port) of the bypass passage is used. .. Then, in the valve open state, the exhaust gas flows out from the wastegate duct (bypass passage), collides with the housing wall for sliding the valve body, changes its direction, and flows downstream of the exhaust passage.

JP-A-2010-190113 US2014 / 0193240

In all of Patent Documents 1 and 2 described above, the flow direction of the exhaust gas flowing along the bypass passage is changed by the collision with the wastegate valve, so that the exhaust gas flow when colliding with the valve body in the fully closed state. The direction is different from the flow direction of the exhaust gas when it flows out from the outlet of the bypass passage and flows to the downstream side in the fully open state. Therefore, the exhaust gas flowing out from the outlet of the bypass passage may flow unevenly inside the exhaust passage (discharge side passage), so that a temperature distribution may occur inside the discharge side passage. In this regard, in the above-mentioned Patent Document 1, since the turbulence caused by the collision of the exhaust gas passing through each of the above two flow paths is generated at the interface between the two exhaust gases, there is a possibility that the mixture of the two is not sufficiently mixed. is there.

In view of the above circumstances, at least one embodiment of the present invention aims to provide a turbine device capable of supplying exhaust gas evenly to a catalyst on the downstream side of an exhaust passage.

(1) The turbine device according to at least one embodiment of the present invention is
Turbine wheels driven by exhaust gas from internal combustion engines
A turbine housing that houses the turbine wheel.
An exhaust gas introduction passage into which the exhaust gas discharged from the internal combustion engine is introduced,
A scroll passage, which is connected to the downstream side of the exhaust gas introduction passage and for supplying the exhaust gas flowing through the exhaust gas introduction passage to the turbine wheel.
A turbine housing having a discharge side passage for discharging the exhaust gas that drives the turbine wheel to the outside, and a bypass passage that bypasses the turbine wheel and connects the exhaust gas introduction passage and the discharge side passage. ,
A wastegate valve having a valve body capable of opening and closing the bypass passage is provided.
The valve body is configured so as to be located between the bypass inlet and the bypass outlet of the bypass passage in the fully closed state and not to be present in the bypass passage in the fully open state.

According to the configuration of (1) above, the wastegate valve of the turbine device is installed between the bypass inlet and the bypass outlet in the bypass passage, and is configured so that the valve body does not exist in the bypass passage in the fully opened state. (For example, a slide type sleeve valve, a rotary type sleeve valve, etc., which will be described later). That is, when the wastegate valve is in the fully open state, the wastegate valve does not disturb the flow of exhaust gas not only inside the bypass passage but also outside the bypass passage (particularly, the discharge side passage). Therefore, it is possible to form a state in which the exhaust gas that flows along the bypass passage and flows out from the bypass outlet flows downstream without being biased inside the discharge side passage, and flows toward the downstream through the discharge side passage. It is possible to prevent the exhaust gas from causing a temperature distribution inside the discharge side passage. On the other hand, when the valve body or the housing is located in the discharge side passage, the exhaust gas flowing out from the bypass outlet may collide with the valve body or the housing, and the flow of the exhaust gas in the discharge side passage may be disturbed.
As a result, when the wastegate valve is fully opened to promote warm-up of the catalyst device installed downstream of the turbine device when the internal combustion engine is started, the exhaust gas in a state without temperature distribution is the catalyst device. By reaching the catalyst of, the entire catalyst can be heated uniformly, and the catalyst can be activated at an early stage.

(2) In some embodiments, in the configuration of (1) above,
When the plane in which the cross-sectional center of the bypass outlet and the rotation axis of the turbine wheel are present is visually recognized in the vertical direction in the discharge side passage, the cross-sectional center of the bypass outlet is seen from the bypass outlet of the bypass passage. A structure that obstructs the flow of the exhaust gas flowing out from the bypass outlet between the vertical line perpendicular to the cross section of the flow path of the bypass outlet and the intersection of the rotating axis of the turbine wheel. not exist.
According to the configuration of (2) above, structures (objects) that flow along the bypass passage and disturb the flow of exhaust gas flowing out from the bypass outlet, including the wastegate valve installed in the bypass passage, are discharged. Not present in the side passage. Therefore, it is possible to form a state in which the exhaust gas flowing along the bypass passage and flowing out from the bypass outlet flows toward the downstream without causing a temperature distribution inside the discharge side passage.

(3) In some embodiments, in the above configurations (1) and (2),
The wastegate valve is a slide-type sleeve valve capable of opening and closing the bypass passage by moving the valve body forward and backward in the direction of intersection of the bypass passage.
According to the configuration of (3) above, by applying the slide type sleeve valve as the wastegate valve, it is possible to configure the valve body so that the valve body does not exist in the bypass passage in the fully opened state. Further, by having the valve body having a sufficient thickness along the flow direction of the bypass passage, for example, a columnar valve body, sufficient strength against high-pressure exhaust gas is secured, and from between the valve body and the valve seat. It is possible to surely prevent the situation where high-pressure exhaust gas leaks.

(4) In some embodiments, in the configuration of (3) above,
The valve body of the wastegate valve has a plate-like shape.
According to the configuration of (4) above, the wastegate valve can be made compact by making the valve body smaller. Further, since the heat capacity of the wastegate valve can be reduced, the heat transferred from the exhaust gas passing through the bypass passage to the wastegate valve can be reduced, and the decrease in the temperature of the exhaust gas can be further reduced.

(5) In some embodiments, in the configurations (1) and (2) above,
The wastegate valve is a rotary sleeve valve capable of opening and closing the bypass passage by rotating around the intersection direction of the bypass passage as a rotation axis.
According to the configuration (5) above, by applying the rotary type sleeve valve as the wastegate valve, it is possible to configure the valve body so that the valve body does not exist in the bypass passage in the fully opened state. Further, since the bypass passage can be opened and closed by rotating the valve body, the wastegate valve can be made more compact than the slide type sleeve valve.

(6) In some embodiments, in the configurations (1) to (5) above,
The bypass passage is provided with a swirler having a plurality of vanes for swirling the exhaust gas flowing through the bypass passage.
According to the configuration of (6) above, by swirling the exhaust gas flowing out from the bypass outlet, it is possible to further prevent the exhaust gas flowing downstream from the discharge side passage from having a temperature distribution.

(7) The supercharging system according to at least one embodiment of the present invention is
With an internal combustion engine
The turbine device according to any one of (1) to (6) above, which is installed in the exhaust passage of the internal combustion engine.
A catalyst device installed on the downstream side of the turbine device in the exhaust passage is provided.
According to the configuration (7) above, when the wastegate valve is fully opened to promote warming up of the catalyst device such as when starting the internal combustion engine, the exhaust gas flows evenly through the discharge side passage and the catalyst. Therefore, the entire catalyst can be heated uniformly, and the catalyst can be activated at an early stage.

According to at least one embodiment of the present invention, there is provided a turbine device capable of supplying exhaust gas evenly to a catalyst on the downstream side of an exhaust passage.

It is a schematic diagram of the supercharging system of the internal combustion engine including the supercharger which concerns on one Embodiment of this invention. It is an enlarged view of the turbine device of the supercharger of FIG. It is a figure which shows the case where the wastegate valve (sliding type sleeve valve) installed in the bypass passage of the turbine apparatus of FIG. 2 is in a fully closed state. It is a figure which shows the case where the wastegate valve (slide type sleeve valve) installed in the bypass passage of the turbine apparatus of FIG. 2 is in a fully open state. It is a figure which shows the case where the wastegate valve (plate-shaped slide type sleeve valve) installed in the bypass passage of the turbine apparatus which concerns on one Embodiment of this invention is in a fully closed state. It is a figure which shows the case where the wastegate valve (plate-shaped slide type sleeve valve) installed in the bypass passage of the turbine apparatus which concerns on one Embodiment of this invention is in a fully open state. It is a figure which shows the case where the wastegate valve (rotary type sleeve valve) installed in the bypass passage of the turbine apparatus which concerns on one Embodiment of this invention is in a fully closed state. It is a figure which shows the case where the wastegate valve (rotary type sleeve valve) installed in the bypass passage of the turbine apparatus which concerns on one Embodiment of this invention is in a fully open state. It is a schematic diagram of the swirler provided with the inner cylinder and the outer cylinder which concerns on one Embodiment of this invention. It is a schematic diagram of a swirler provided with an outer cylinder in one embodiment of the present invention.

Hereinafter, some embodiments of the present invention will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of the components described as embodiments or shown in the drawings are not intended to limit the scope of the present invention to this, but are merely explanatory examples. Absent.
For example, expressions that represent relative or absolute arrangements such as "in a certain direction", "along a certain direction", "parallel", "orthogonal", "center", "concentric" or "coaxial" are exact. Not only does it represent such an arrangement, but it also represents a state of relative displacement with tolerances or angles and distances to the extent that the same function can be obtained.
For example, expressions such as "same", "equal", and "homogeneous" that indicate that things are in the same state not only represent exactly the same state, but also have tolerances or differences to the extent that the same function can be obtained. It shall also represent the state of existence.
For example, the expression representing a shape such as a quadrangular shape or a cylindrical shape not only represents a shape such as a quadrangular shape or a cylindrical shape in a geometrically strict sense, but also an uneven portion or chamfering within a range where the same effect can be obtained. The shape including the part and the like shall also be represented.
On the other hand, the expressions "equipped", "equipped", "equipped", "included", or "have" one component are not exclusive expressions that exclude the existence of other components.

FIG. 1 is a schematic view of a supercharging system of an internal combustion engine including a supercharger 1 according to an embodiment of the present invention. FIG. 2 is an enlarged view of the turbine device 2 of the turbocharger 1 of FIG. FIG. 3A is a diagram showing a case where the wastegate valve 5 (sliding type sleeve valve) installed in the bypass passage 26 of the turbine device 2 of FIG. 2 is in a fully closed state. FIG. 3B is a diagram showing a case where the wastegate valve 5 (sliding type sleeve valve) installed in the bypass passage 26 of the turbine device 2 of FIG. 2 is in a fully open state. In addition, FIGS. 4A to 5B are views showing a wastegate valve 5 installed in the bypass passage 26 according to another embodiment of the present invention.

As shown in FIG. 1, the supercharger 1 includes a turbine device 2 installed in an exhaust passage 8 of an internal combustion engine and a compressor device 3 installed in an intake passage 9 of an internal combustion engine. A turbine wheel 21 is housed inside the turbine device 2, a compressor wheel (not shown) is housed inside the compressor device 3, and the turbine wheel 21 and the compressor wheel (not shown) are coaxial with each other by a shaft 12. Combined with. Then, when the exhaust gas discharged from the combustion chamber (not shown) of the internal combustion engine flows outward through the exhaust passage 8, the turbine wheel 21 of the turbine device 2 is rotationally driven to drive the turbine wheel 21 (not shown). Is driven to rotate. As a result, the intake air flowing through the intake passage 9 is compressed by the compressor wheel (not shown), and the compressed intake air is supplied to the internal combustion engine. The supercharging system includes such a turbine device 2 of the supercharger 1, a catalyst device 6 (described later), and an internal combustion engine (not shown).

Then, as shown in FIGS. 1 and 2, the turbine device 2 of the supercharger 1 includes the above-mentioned turbine wheel 21 driven by the exhaust gas from the internal combustion engine, the turbine housing 22 accommodating the turbine wheel 21, and the waste. It includes a gate valve 5. Hereinafter, the turbine housing 22 and the wastegate valve 5 will be described.

The turbine housing 22 has an exhaust gas introduction passage 23, a scroll passage 24, an exhaust side passage 25, and a bypass passage 26, which are passages forming a part of the exhaust passage 8 of the internal combustion engine, and the exhaust gas can pass through. Two channels are formed inside it. The first flow path (turbine passage flow path) is a flow path formed by the exhaust gas introduction passage 23, the scroll passage 24, and the discharge side passage 25. The exhaust gas introduction passage 23 is a passage into which the exhaust gas discharged from the internal combustion engine is introduced, and the exhaust gas flowing from the upstream side through the exhaust gas passage 8 is introduced into the turbine housing 22 from the exhaust gas introduction passage 23. The scroll passage 24 has a spiral shape, and is connected to the downstream side of the exhaust gas introduction passage 23 to supply the exhaust gas flowing through the exhaust gas introduction passage 23 to the turbine wheel 21. In this way, the turbine wheel 21 is rotationally driven by supplying the exhaust gas through the exhaust gas introduction passage 23 and the scroll passage 24 in order. Further, the discharge side passage 25 is a passage for discharging the exhaust gas that drives the turbine wheel 21 to the outside, and the exhaust gas is discharged to the outside of the turbine housing 22 via the discharge side passage 25.

On the other hand, the second flow path (turbine bypass flow path) formed in the turbine housing 22 is a flow path formed by the exhaust gas introduction passage 23, the bypass passage 26, and the discharge side passage 25. .. The bypass passage 26 bypasses the turbine wheel 21 and connects the exhaust gas introduction passage 23 and the exhaust side passage 25. Specifically, in the bypass passage 26, the bypass inlet 26i on one end side thereof is connected to the exhaust gas introduction passage 23, and the bypass outlet 26e on the other end side is connected to the discharge side passage 25. In other words, the bypass passage 26 is a passage branched from the exhaust gas introduction passage 23, and by passing through the bypass passage 26, the exhaust gas can bypass the turbine and flow to the discharge side passage 25.

The exhaust gas that has flowed to the discharge side passage 25 through the turbine passage passage or the turbine bypass flow passage described above forms a part of the exhaust passage 8 that connects the discharge side passage 25 and the catalyst device 6. It is purified by flowing the 82 toward the downstream and passing through the catalyst held inside the catalyst device 6 installed in the exhaust passage 8.

In the embodiment shown in FIGS. 1 to 3B, as shown in FIGS. 1 and 2, the bypass passage 26 has a linear shape (straight pipe shape) from the bypass inlet 26i to the bypass outlet 26e. .. Then, as shown in FIGS. 3A to 3B, the flow direction of the exhaust gas in the vicinity of the valve body 51 (valve body) of the wastegate valve 5 and the exhaust gas when flowing out from the bypass outlet 26e to the discharge side passage 25. Is configured to have the same outflow direction. More specifically, in FIG. 3A, the flow direction when colliding with the valve body 51 and in FIG. 3B, the flow direction when passing beside the valve body 51 are the same as the above-mentioned outflow direction. In some other embodiments, the bypass passage 26 may have a shape other than the linear shape. For example, the bypass passage 26 is a portion curved between the bypass inlet 26i and the bypass outlet 26e. May have.

The wastegate valve 5 has a valve body 51 capable of opening and closing the bypass passage 26. The wastegate valve 5 opens when the boost pressure exceeds a predetermined value in order to maintain a state in which the boost pressure to the internal combustion engine does not exceed a certain value, and when the boost pressure is smaller than this predetermined value, the wastegate valve 5 is opened. It is configured to be fully closed. Further, the wastegate valve 5 is opened at the time of starting the internal combustion engine (at the time of cold start) to supply high-temperature exhaust gas that has passed through the turbine bypass flow path that bypasses the turbine wheel 21 to the catalyst device 6 to provide a catalyst. It is configured to promote early activation of. In the embodiment shown in FIGS. 1 to 3B, the wastegate valve 5 is configured to be in a fully open state when the internal combustion engine is started, and is configured to allow the maximum amount of exhaust gas to flow through the turbine bypass flow path. ing. However, the present invention is not limited to this embodiment, and in some other embodiments, the wastegate valve 5 is opened at an intermediate opening degree between the fully open state and the fully closed state when the internal combustion engine is started. Is also good.

More specifically, as shown in FIG. 3A, the wastegate valve 5 is configured such that the valve body 51 is located between the bypass inlet 26i and the bypass outlet 26e of the bypass passage 26 in the fully closed state (described later). The same applies to FIGS. 4A and 5A. That is, when the wastegate valve 5 is in the fully closed state, the exhaust gas is blocked by the valve body 51 so that the bypass passage 26 cannot pass from the bypass inlet 26i to the bypass outlet 26e. .. Therefore, the exhaust gas can flow only in the flow path via the turbine inside the turbine housing 22. On the contrary, as shown in FIG. 3B, the wastegate valve 5 is configured so that the valve body 51 does not exist in the bypass passage 26 in the fully opened state (the same applies to FIGS. 4B and 5B described later). That is, when the wastegate valve 5 is in the fully open state, the exhaust gas is configured to be able to pass through the bypass passage 26 from the bypass inlet 26i toward the bypass outlet 26e. Therefore, the exhaust gas can flow through the turbine bypass passage in addition to the turbine passage passage inside the turbine housing 22.

Further, as shown in FIGS. 3B, 4B, and 5B, when the wastegate valve 5 is fully opened, there is no object that obstructs the flow of exhaust gas in the bypass passage 26 including the valve body 51. That is, the flow of the exhaust gas is not disturbed when flowing through the bypass passage 26, and the rectified exhaust gas can be discharged from the bypass outlet 26e by flowing the exhaust gas along the bypass passage 26. Therefore, it is possible to form a state in which the exhaust gas that flows along the bypass passage 26 and flows out from the bypass outlet 26e flows downstream without being biased inside the discharge side passage 25.

According to the above configuration, the wastegate valve 5 of the turbine device 2 is installed between the bypass inlet 26i and the bypass outlet 26e in the bypass passage 26, and the valve body 51 does not exist in the bypass passage 26 in the fully open state. It is a valve (for example, a slide type sleeve valve of FIGS. 3A to 4B, a rotary type sleeve valve of FIGS. 5A to 5B, etc.) that can be configured as such. That is, when the wastegate valve 5 is in the fully open state, the wastegate valve 5 disturbs the flow of exhaust gas not only inside the bypass passage 26 but also outside the bypass passage 26 (particularly, the discharge side passage 25). There is no. Therefore, it is possible to form a state in which the exhaust gas flowing along the bypass passage 26 and flowing out from the bypass outlet 26e flows downstream without being biased inside the discharge side passage 25, and the discharge side passage 25 is downstream. It is possible to prevent the temperature distribution from being generated inside the discharge side passage 25 due to the exhaust gas flowing toward. As a result, when the wastegate valve 5 is fully opened to promote warm-up of the catalyst device 6 installed downstream of the turbine device 2 when the internal combustion engine is started, the exhaust gas in a state without temperature distribution. When the catalyst reaches the catalyst of the catalyst device 6, the entire catalyst can be uniformly heated, and the catalyst can be activated at an early stage.

Further, in some embodiments, as shown in FIG. 2, in the discharge side passage 25, a plane in which the cross-sectional center Cb of the bypass outlet 26e and the rotation axis Lt of the turbine wheel 21 exist is visually recognized in the vertical direction. In the case (that is, FIG. 2), the rotation of the vertical line Lb and the turbine wheel 21 from the bypass outlet 26e of the bypass passage 26, passing through the cross-section center Cb of the bypass outlet 26e and perpendicular to the cross-section of the bypass outlet 26e. There is no structure that obstructs the flow of the exhaust gas flowing out from the bypass outlet 26e up to the intersection C with the axis Lt. In other words, the outflow direction when the exhaust gas flowing along the bypass passage 26 flows out from the bypass outlet 26e (in the case of FIG. 2, the direction along the vertical line Lb) and the rotation axis Lt of the turbine wheel 21. There is no structure that obstructs the flow of the exhaust gas flowing out from the bypass outlet 26e up to the intersection C. Therefore, the exhaust gas flowing out from the bypass outlet 26e flows toward the downstream side (outside) of the discharge side passage 25 where the pressure is relatively low, without changing the flow direction by the structure in the discharge side passage 25. Become.

In the embodiment shown in FIGS. 1 to 3B, as shown in FIG. 2, the bypass passage 26 has a linear shape, and the vertical line Lb (virtual line drawn along the outflow direction) is the bypass passage. The direction is along 26. Further, as described above, there is no structure between the bypass outlet 26e and the intersection C of the vertical line Lb and the rotation axis Lt of the turbine wheel 21. Moreover, in the embodiment shown in FIGS. 1 to 3B, the discharge side passage 25 on the downstream side of the flow path cross section of the discharge side passage 25 including the vertical line Lb is from the bypass outlet 26e of the bypass passage 26. There is no structure that obstructs the flow of the exhaust gas flowing out from the bypass outlet 26e up to the intersection C. That is, in the cross-sectional view of FIG. 2, no structure exists on the downstream side of the vertical line Lb. Further, in the cross-sectional view of FIG. 2, when a line Lw is drawn from the discharge side passage 25 along the passage wall on the upstream side of the bypass passage 26 to the rotation axis Lt of the turbine wheel 21, the line Lw is used. There is no structure on the downstream side.

According to the above configuration, the structure (object) that flows along the bypass passage 26 and disturbs the flow of the exhaust gas flowing out from the bypass outlet 26e includes the wastegate valve 5 installed in the bypass passage 26. It does not exist in the discharge side passage 25. Therefore, it is possible to form a state in which the exhaust gas flowing along the bypass passage 26 and flowing out from the bypass outlet 26e flows downstream without causing a temperature distribution inside the discharge side passage 25.

Hereinafter, embodiments relating to the configuration of the wastegate valve 5 will be described.
In the embodiments shown in FIGS. 3A-5B, as shown in FIGS. 3A-5B, the wastegate valve 5 is a valve housing 52 accommodating the valve body 51 and a part of the valve housing 52. It includes a valve seat 53 on which the valve body 51 is seated, and a drive shaft 54 which is connected to a drive device (not shown) and the valve body 51 and transmits the power of the drive device (not shown) to the valve body 51. Further, an opening 26o is formed in the passage wall of the bypass passage 26. The inside of the valve housing 52 and the bypass passage 26 communicate with each other through the opening 26o, and the valve main body 51 can be installed across the inside of the valve housing 52 and the bypass passage 26. A valve seat 53 is provided on the passage wall of the bypass passage 26 which is opposite to the opening 26o in the crossing direction where the bypass passage 26 intersects the direction in which the exhaust gas flows, and the opening 26o and the valve seat 53 are bypass passages. It is provided so as to face each other with 26 in between. In the embodiment shown in FIGS. 3A to 5B, the valve housing 52 is provided so as to intersect from a direction orthogonal to the direction along the bypass passage 26, but the present invention is not limited to this. In some other embodiments, the valve housing 52 may be provided so as to intersect diagonally with respect to the direction along the bypass passage 26.

Then, in some embodiments, as shown in FIGS. 3A to 4B, the wastegate valve 5 is a slide capable of opening and closing the bypass passage 26 by moving the valve body 51 forward and backward in the intersecting direction of the bypass passage 26. It consists of a mold sleeve valve. More specifically, the valve body 51 is configured to be slidable and movable along the wall of the valve housing 52 by the drive shaft 54. Then, the tip end portion 51t of the valve body 51 is advanced to the valve seat 53 and is seated on the valve seat 53 to be in a fully closed state (see FIGS. 3A and 4A). On the contrary, the valve body 51 is retracted in the direction away from the valve seat 53, and the tip portion 51t of the valve body 51 is retracted beyond the opening 26o of the bypass passage 26, so that the valve body 51 is fully opened (FIGS. 3B and 3B). See 4B). In this way, the valve body 51 is configured not to exist in the bypass passage 26 in the fully open state.

Further, in the embodiment shown in FIGS. 3A to 3B, as shown in FIGS. 3A to 3B, the valve body 51 has, for example, a columnar shape, and has a sufficient thickness along the flow direction of the bypass passage 26. By having the valve body 51, the strength against the high-pressure exhaust gas is sufficiently secured, and the situation where the high-pressure exhaust gas leaks from between the valve body 51 and the valve seat 53 is prevented. In some other embodiments, the valve body 51 of the wastegate valve 5 has a plate-like shape, as shown in FIGS. 4A-4B. By making the valve body 51 smaller in this way, the wastegate valve 5 can be made compact. Further, since the heat capacity of the wastegate valve 5 can be reduced, the heat transferred from the exhaust gas passing through the bypass passage 26 to the wastegate valve 5 can be reduced, and the decrease in the temperature of the exhaust gas can be further reduced.

In some other embodiments, as shown in FIGS. 5A-5B, the wastegate valve 5 is a rotary type capable of opening and closing the bypass passage 26 by rotating around the intersection direction of the bypass passage 26 as a rotation axis. It consists of a sleeve valve. More specifically, the valve body 51 of the rotary sleeve valve is formed with a through hole 51h penetrating the valve body 51. Further, in both the fully closed state and the fully open state, the valve body 51 is installed with the tip portion 51t seated on the valve seat 53 sandwiching the bypass passage 26. In this state, the valve body 51 is configured to be rotatable with the drive shaft 54 as the axis Lr, and the bypass passage 26 is opened and closed depending on whether or not the through hole 51h and the flow path of the bypass passage 26 overlap. Is to be decided.

Specifically, when the valve body 51 is rotated so that the through hole 51h of the valve body 51 and the flow path of the bypass passage 26 overlap, the exhaust gas flowing from the bypass inlet 26i of the bypass passage 26 Can reach the bypass outlet 26e through the through hole 51h. Further, when the through hole 51h of the valve body 51 and the flow path of the bypass passage 26 completely overlap, the valve body is fully opened. On the contrary, when the valve body 51 is rotated so that the through hole 51h of the valve body 51 and the flow path of the bypass passage 26 do not overlap, the valve body 51 is fully closed. In the embodiment shown in FIGS. 5A to 5B, when the valve body 51 is rotated and the cross-sectional center of the flow path of the bypass passage 26 coincides with the cross-sectional center of the through hole 51h, the valve body 51 is fully opened. When both are orthogonal to each other, it is in a fully closed state. As a result, the valve body 51 can be configured not to exist in the bypass passage 26 in the fully open state. Further, since the bypass passage 26 can be opened and closed by rotating the valve body 51, the wastegate valve 5 can be made more compact than the slide type sleeve valve.

Further, in some embodiments, as shown in FIGS. 1 and 2, the bypass passage 26 has a swirler 7 having a plurality of vanes 71 for swirling the exhaust gas flowing through the bypass passage 26 (FIGS. 6A to 6A). 6B) may be provided. The exhaust gas is swirled by flowing along the vane 71 as it passes through the swirler 7. In the embodiment shown in FIGS. 1 to 3B, the swirler 7 is installed at the bypass outlet 26e of the bypass passage 26. In this case, since the exhaust gas is swirled when it flows out from the bypass outlet 26e, it is possible to make it less susceptible to the influence of the exhaust gas passing through the flow path via the turbine, and to ensure the formation of the swirling flow of the exhaust gas. Can be done. However, the present embodiment is not limited to this, and in some other embodiments, the swirler 7 may be installed at another position of the bypass passage 26, such as installing the swirler 7 at the bypass inlet 26i of the bypass passage 26. good.

More specifically, a swirler 7 as shown in FIGS. 6A-6B may be installed in the bypass passage 26. In the embodiment shown in FIG. 6A, the swirler 7 has an outer cylinder 72 and an inner cylinder 73 located inside the outer cylinder 72, and a plurality of vanes are provided between the outer cylinder 72 and the inner cylinder 73. 71 is installed. By supporting the vane 71 on the outer cylinder 72 and the inner cylinder 73, it is possible to secure the strength against high-pressure exhaust gas. In the embodiment shown in FIG. 6B, the swirler 7 is configured such that a plurality of vanes 71 supported by the outer cylinder 72 support each other at the center position of the outer cylinder 72. In some other embodiments, the vane 71 may be supported by the wall surface of the bypass tube forming the bypass passage 26.

According to the above configuration, by swirling the exhaust gas flowing out from the bypass outlet 26e, it is possible to further prevent the exhaust gas flowing downstream in the discharge side passage 25 from having a temperature distribution.

The present invention is not limited to the above-described embodiment, and includes a modified form of the above-described embodiment and a combination of these embodiments as appropriate.

1 Supercharger 12 Shaft 2 Turbine device 21 Turbine wheel 22 Turbine housing 23 Exhaust gas introduction passage 24 Scroll passage 25 Discharge side passage 26 Bypass passage 26e Bypass outlet 26i Bypass inlet 26o Opening 3 Compressor device 5 Wastegate valve 51 Valve body 51h Through hole 51t Tip 52 Valve housing 53 Valve seat 54 Drive shaft 6 Catalyst device 7 Swallower 71 Vane 72 Outer cylinder 73 Inner cylinder 8 Exhaust passage 82 Catalyst introduction passage 9 Intake passage C Intersection point Cb Cross section center Lb Vertical line Lt Turbine wheel rotation axis Lr Drive shaft rotation axis Lw Extension of the passage wall of the bypass passage

Claims (7)

Turbine wheels driven by exhaust gas from internal combustion engines
A turbine housing that houses the turbine wheel.
An exhaust gas introduction passage forming portion that forms an exhaust gas introduction passage into which the exhaust gas discharged from the internal combustion engine is introduced.
A scroll passage forming unit , which is connected to the downstream side of the exhaust gas introduction passage and forms a scroll passage for supplying the exhaust gas flowing through the exhaust gas introduction passage to the turbine wheel.
It is a discharge side passage for discharging the exhaust gas that drives the turbine wheel to the outside, and is linear from the inlet to the outlet of the discharge side passage along the extending direction of the rotation axis of the turbine wheel. the discharge-side passage forming portion for forming a discharge side passage extending, and to bypass the turbine wheel, a bypass passage which connects the middle portion of the discharge-side passage and the exhaust gas introduction passage of said bypass passage A bypass passage that is formed linearly from the bypass inlet to the bypass outlet and extends so as to be inclined and intersects the downstream side of the discharge side passage with respect to the extending direction of the rotation axis of the turbine wheel. A turbine housing having a bypass passage forming portion,
A valve body capable of opening and closing the bypass passage and a wastegate valve having a valve housing for accommodating the valve body are provided.
The valve body is configured to be located between the bypass inlet and the bypass outlet of the bypass passage in the fully closed state and not to be present in the bypass passage in the fully open state .
The valve housing is arranged between the exhaust gas introduction passage forming portion and the exhaust side passage forming portion.
The exhaust gas introduction passage forming portion, the scroll passage forming portion, and the discharge side passage forming portion are integrally formed.
When the plane in which the cross-sectional center of the bypass outlet and the rotation axis of the turbine wheel are present is visually recognized in the vertical direction in the discharge side passage, the cross-sectional center of the bypass outlet is seen from the bypass outlet of the bypass passage. A structure that obstructs the flow of the exhaust gas flowing out from the bypass outlet between the vertical line perpendicular to the cross section of the flow path of the bypass outlet and the intersection of the rotating axis of the turbine wheel. A turbine device characterized by non-existence. The turbine device according to claim 1, wherein the wastegate valve is opened when the internal combustion engine is started. The turbine device according to claim 1 or 2 , wherein the wastegate valve is a slide type sleeve valve capable of opening and closing the bypass passage by advancing and retreating the valve body in the direction of intersection of the bypass passage. .. The turbine device according to claim 3 , wherein the valve body of the wastegate valve has a plate-like shape. The turbine device according to claim 1 or 2 , wherein the wastegate valve is a rotary type sleeve valve capable of opening and closing the bypass passage by rotating around the intersection direction of the bypass passage as a rotation axis. The turbine device according to any one of claims 1 to 5 , wherein the bypass passage is provided with a swirler having a plurality of vanes for swirling the exhaust gas flowing through the bypass passage. With an internal combustion engine
The turbine device according to any one of claims 1 to 6 , which is installed in the exhaust passage of the internal combustion engine.
A supercharging system including a catalyst device installed on the downstream side of the turbine device in the exhaust passage.

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