JP5966848B2 - Exhaust valve device and turbocharged engine - Google Patents

Description

  The present invention relates to an exhaust valve device for changing the flow area of exhaust gas in an exhaust passage, and an engine with a turbocharger including the exhaust valve device.

  As such an engine, for example, an engine described in Patent Document 1 is known. The engine described in Patent Document 1 includes an engine main body, an exhaust manifold communicating with an exhaust port of each cylinder of the engine main body, a turbocharger connected to the downstream side, the turbocharger, An exhaust variable valve is provided between the exhaust manifold and the exhaust manifold for changing the flow area of the exhaust gas in the exhaust passage. This engine controls the flow rate of the exhaust gas introduced into the turbocharger by changing the flow area of the exhaust gas in accordance with the running state of the vehicle, thereby increasing the supercharging capability of the turbocharger. It has a configuration.

JP 2009-114991 A

  In the conventional engine disclosed in the patent document, a so-called exhaust valve device is provided on the downstream side of the exhaust manifold. Recently, in order to reduce the size and weight of the engine, the exhaust manifold is provided. It is considered to reduce the size and weight of the entire engine by incorporating an exhaust valve device. Specifically, a valve body is arranged in each exhaust passage of the exhaust manifold, and the operation shaft is rotationally driven after the valve body is connected to an operation shaft provided so as to penetrate each exhaust passage. As a result, the distribution area of the exhaust gas in each exhaust passage is changed.

  However, in this configuration, since the operation shaft is provided so as to penetrate each exhaust passage as described above, the exhaust gas in the exhaust passage leaks to the adjacent exhaust passage through the hole portion into which the operation shaft is inserted, and flows backward. It is possible to induce exhaust interference. Therefore, it is required to improve this point.

  The present invention has been made in view of the above circumstances, and provides an exhaust valve device or the like that can reduce the size and weight of an engine while suppressing exhaust gas from leaking into an adjacent exhaust passage. The purpose is to provide.

In order to solve the above-described problems, an exhaust valve device according to the present invention includes a device main body including a plurality of exhaust passages arranged in parallel with each other in a specific direction, and valve members respectively disposed in the exhaust passages. said device is rotatably supported by the main body and includes an operating shaft for connecting the respective valve member, and an exhaust variable valve to change the flow area of the exhaust gas in said respective exhaust passages and said respective exhaust In the middle of the passage, the passage branches into a low-speed exhaust passage and a high-speed exhaust passage in which the variable exhaust valve is arranged. In a high-speed operation region, the passage passes through both the high-speed passage and the low-speed passage. The exhaust variable valve is opened so that the exhaust gas flows down, while the exhaust variable valve is configured so that the exhaust gas does not pass through the low speed passage and flows only through the high speed passage in the low speed operation region. It is open, the operating shaft, before By being inserted into a hole portion formed in the side wall of the exhaust passage, said supported on the apparatus body each fast passage in a state of penetrating in the specific direction, wherein each valve member is in the low speed operation range in a state where the exhaust variable valve is opened, as well as positioned on the upstream side of the exhaust passage than said operating shaft, both ends in the said specific direction, Ri Sorikae toward the upstream side and the hole It has the shape located in the radial direction outer side .

  According to this exhaust valve device, a plurality of exhaust passages and exhaust variable valves (valve members and operation shafts) that open and close these exhaust passages are integrated into a single device body, thereby reducing the size and weight of the engine. It is possible to contribute. Moreover, since both end portions (both end portions in the specific direction) of each valve member are warped toward the upstream side, the exhaust gas in the exhaust passage is suppressed from flowing toward the side wall, that is, toward the hole. The Therefore, the exhaust gas in each exhaust passage is effectively suppressed from leaking to the adjacent exhaust passage through the hole.

In particular , the valve member is formed such that both ends in the specific direction are positioned on the radially outer side of the hole.

Therefore, since the hole is covered from the upstream side by the both ends of the valve member, the exhaust gas is more reliably suppressed from flowing into the hole.

  The above-described configuration is particularly useful in a configuration in which the operation shaft has a half-moon shaped cross section and the valve member is mounted along a plane portion of the outer peripheral surface thereof.

  That is, in this configuration, a relatively large semicircular gap is formed between the inner peripheral surface of the hole and the operation shaft, so that exhaust gas leaks between adjacent exhaust passages. However, according to the configuration of the exhaust valve device as described above, it is possible to effectively suppress such leakage of the exhaust gas.

  On the other hand, an engine with a turbocharger according to the present invention includes an engine body, a turbocharger driven by the energy of exhaust gas discharged from the engine body, and the engine body and the turbocharger. An exhaust valve device interposed between the engine body and variably setting a flow rate of exhaust gas sent from the engine body to the turbocharger through the exhaust passage by changing a flow area of the exhaust gas in the exhaust passage; The exhaust valve device is any one of the exhaust valve devices described above.

  According to the turbocharged engine, a plurality of exhaust passages and an exhaust variable valve that changes the flow area of the exhaust gas in the exhaust passages are integrated into one (exhaust valve device). It becomes possible to reduce the size and weight.

  As described above, according to the exhaust valve device of the present invention, the plurality of exhaust passages and the exhaust variable valves that change the flow area of the exhaust gas in the exhaust passages are integrated into one (exhaust valve device). Therefore, it can contribute to the reduction in size and weight of the engine. In addition, since both end portions of each valve member constituting the exhaust variable valve are warped toward the upstream side, the exhaust gas in the exhaust passage is adjacent to the exhaust gas through the hole portion into which the operation shaft is inserted. Leakage into the passage is also effectively suppressed.

1 is a schematic plan view of a partial cross section showing a turbocharged engine to which the present invention is applied. It is a cross-sectional schematic diagram of an engine showing the relationship between an exhaust passage and an EGR passage. It is the side view which looked at the exhaust valve device from the turbocharger side (III-III line sectional view of Drawing 1). It is sectional drawing (IV-IV sectional view taken on the line of FIG. 3) which shows an exhaust valve apparatus. It is sectional drawing (VV sectional view taken on the line of FIG. 3) which shows an exhaust valve apparatus. It is a perspective view which shows a valve body and an operating shaft.

  Hereinafter, a preferred embodiment of the present invention will be described in detail with reference to the accompanying drawings.

  1 and 2 show an engine according to an embodiment of the present invention. The engine shown in the figure is an in-line four-cylinder four-cycle engine equipped with a turbocharger 50. This engine includes an in-line four-cylinder engine main body 1 having four cylinders 2A to 2D (first cylinder 2A, second cylinder 2B, third cylinder 2C, fourth cylinder 2D) arranged in a row, An unillustrated intake manifold for introducing air, an after-mentioned exhaust manifold for discharging exhaust gas generated by the engine body 1, an exhaust valve device 20 according to the present invention, and the turbocharger 50 are provided. The turbocharger 50 is operated by the exhaust gas discharged through the exhaust manifold, and the intake air pumped to each of the cylinders 2A to 2D is compressed to increase the intake pressure. . And according to the driving | running state of a vehicle, the flow rate of the exhaust gas introduce | transduced into the turbocharger 50 is controlled by the said exhaust valve apparatus 20 interposed between the engine main body 1 and the turbocharger 50. FIG. Thus, the intake pressure characteristic by the turbocharger 50 is changed.

  In the following description, in order to clarify the directional relationship, the arrangement direction of the cylinders 2A to 2D in the engine body 1 is referred to as “left-right direction” with reference to FIG. ) Is the “front-rear direction”, and the turbocharger 50 side is the “front side” of the engine.

  In the cylinder head 10 of the engine body 1, three independent exhaust passages are formed for the four cylinders 2A to 2D. Specifically, a first upstream exhaust passage 14 used for exhausting the first cylinder 2A, and a second upstream exhaust passage 15 commonly used for exhausting the second cylinder 2B and the third cylinder 2C, A third upstream exhaust passage 16 used for exhausting the fourth cylinder 2D is formed. The second upstream exhaust passage 15 has a shape in which the upstream side branches in a Y shape so that it can be used in common for the second cylinder 2B and the third cylinder 2C.

  These upstream exhaust passages 14, 15, 16 are formed such that their downstream end portions are concentrated at the substantially center in the left-right direction of the cylinder head 10, and are arranged in a row in the left-right direction close to each other. 10 is open to the front.

  Further, an EGR downstream passage 18 is formed in the cylinder head 10. As shown in FIG. 1, the EGR downstream passage 18 is formed so as to cross the left side of the first cylinder 2 </ b> A in the cylinder head 10 in the front-rear direction. The upstream end of the EGR downstream passage 18 is open to the front surface of the cylinder head 10 and on the left side of the upstream exhaust passage 14. On the other hand, the downstream end of the EGR downstream passage 18 is open to the rear surface of the cylinder head 10. Reference numeral 12 in FIG. 1 denotes an intake port of each of the cylinders 2A to 2D formed in the cylinder head 10. Among these intake ports 12, the above-described position is located on the left side of the intake port 12 of the first cylinder 2A. The downstream end of the EGR downstream passage 18 is open.

  The exhaust valve device 20 changes the flow area of the exhaust gas discharged from the engine body 1 to change the flow rate of the exhaust gas introduced into the turbocharger 50. It is fixed with bolts.

  The exhaust valve device 20 includes three independent downstream exhaust passages 24, 25, and 26 (first downstream exhaust passage 24, second passage) that communicate with the upstream exhaust passages 14, 15, 16 on the cylinder head 10 side. An apparatus main body 21 formed with a downstream exhaust passage 25, a third downstream exhaust passage 26), and an EGR intermediate passage 28 communicating with the EGR downstream passage 18 on the cylinder head 10 side; a downstream exhaust passage 24; And an exhaust variable valve for changing the flow area of the exhaust gas in the interiors of 25 and 26. In addition, the apparatus main body 21 is comprised with the metal casting.

  Each of the downstream exhaust passages 24, 25, and 26 has a downstream side branched in a Y shape. That is, as shown in FIGS. 2 and 3, the first downstream exhaust passage 24 has a common passage 24a communicating with the first upstream exhaust passage 14 on the cylinder head 10 side, and a bifurcated shape from the common passage 24a. A high-speed passage 24b and a low-speed passage 24c branch off. Similarly, the second downstream exhaust passage 25 and the third downstream exhaust passage 26 have common passages 25a and 26a (not shown) respectively communicating with the upstream exhaust passages 15 and 16 on the cylinder head 10 side, and the common passage 25a. , 26a, and high-speed passages 25b, 26b and low-speed passages 25c, 26c that bifurcate up and down. In the present embodiment, the high speed passages 24b, 25b, and 26b correspond to a plurality of exhaust passages of the present invention.

  Each of the high-speed passages 24b, 25b, and 26b has a substantially rectangular cross-sectional shape and is formed so as to be aligned in a line in the left-right direction. Similarly, each of the low speed passages 24c, 25c, and 26c has a substantially rectangular cross-sectional shape, and is formed so as to be aligned in one example in the left-right direction at a position above each of the high speed passages 24b, 25b, and 26b. Although not shown in detail, the low-speed passages 24c, 25c, and 26c are formed so that the cross-sectional area of the passage gradually decreases from the upstream side to the downstream side, and the low-speed passages 24c and 26c on both sides are formed. It is formed so as to approach the central low-speed passage 25c. As a result, as shown in FIG. 3, the high-speed passages 24b, 25b, 26b are arranged in a line in the left-right direction close to each other on the front end surface of the apparatus main body 21, that is, the mounting surface 21a of the turbocharger 50. Of the high-speed passages 24b, 25b, and 26b, the low-speed passage 24c is arranged in a line in the left-right direction close to each other at a position above the central high-speed passage 25b. 25c, 26c are open at the downstream end.

  On the other hand, the EGR intermediate passage 28 is formed at the left end of the apparatus main body 21 as shown in FIGS. The EGR intermediate passage 28 has a substantially rectangular cross-sectional shape, and is located on the left side of the high speed passage 24b in the first downstream exhaust passage 24, along with the high speed passages 24b, 25b, and 26b in the left-right direction (of the present invention). (Corresponding to a specific direction). Note that the EGR intermediate passage 28 and the high-speed passages 24b, 25b, and 26b are on the same axis (the reference numeral in FIG. 3) where the cross-sectional centers (vertical center) of these passages 24b, 25b, 26b, and 28 extend in the left-right direction. The device main body 21 is formed so as to be located on the axis indicated by O.

  The exhaust variable valve changes the flow area of the exhaust gas in the high-speed passages 24b, 25b, 26b among the downstream exhaust passages 24, 25, 26. The exhaust variable valve includes a total of three valve bodies 30 disposed in the high-speed passages 24b, 25b, and 26b, and an operation shaft 36 (corresponding to an operation shaft of the present invention) that connects the valve bodies 30. And a drive source (motor 42 in FIG. 1) for rotationally driving the operation shaft 36. That is, the exhaust variable valve opens and closes the high-speed passages 24b, 25b, and 26b simultaneously by rotationally driving the valve bodies 30 through the operation shaft 36 by the motor 42.

  Here, the configuration of the exhaust variable valve will be specifically described. As shown in FIGS. 1 to 4, the apparatus main body 21 penetrates the EGR intermediate passage 28 and the high-speed passages 24b, 25b, and 26b in the left-right direction. Thus, the operation shaft 36 is provided. Specifically, the apparatus main body 21 is formed with a through hole 22 (corresponding to a hole of the present invention) having a circular cross section that penetrates the apparatus main body 21 in the left-right direction, and the operation shaft 36 is inserted into the through hole 22. At the same time, the apparatus main body 21 is rotatably supported by bearings 38 at both ends. The operation shaft 36 is supported by the apparatus main body 21 so as to pass through the cross-sectional centers (vertical center; see FIG. 3) of the EGR intermediate passage 28 and the high-speed passages 24b, 25b, and 26b.

  As shown in FIG. 6, the operating shaft 36 has a circular cross section (referred to as a circular portion 36a) in a certain region from one end side (the left end in the figure), and a semicircular cross section (semicircular) in the region on the other end side. As shown in FIG. 5, in the state supported by the apparatus main body 21, the region on the left side of this partition is defined by the partition between the EGR intermediate passage 28 and the high-speed passage 24b. The circular portion 36a is located on the right side, that is, the semicircular portion 36b is located on the right side, that is, the region corresponding to the high-speed passages 24b, 25b, and 26b.

  As shown in FIGS. 4 to 6, the valve body 30 includes a plate-shaped valve main body 32 (corresponding to the valve member of the present invention) and a pair of semicircular arc-shaped bridge portions 34 a, and the back side of the valve main body 32. And a semi-circular portion 36b of the operation shaft 36 is inserted inside the bridge portion 34a so that the flat surface 37 of the operation shaft 36 (corresponding to the plane portion of the present invention). To be installed). That is, the operation shaft 36 (semi-circular portion 36b) and each valve body 30 are not fixed with bolts or the like, and the back surface of the valve body 32 and the flat surface 37 of the semi-circular portion 36b are in contact with each other. Thus, by inserting the operation shaft 36 inside the bridge portion 34a, the relative rotation of the valve body 32 with respect to the operation shaft 36 is prevented, so that each valve body 30 and the operation shaft 36 rotate integrally. It has become. Therefore, each valve body 30 is attached to the operation shaft 36 in a state where relative displacement in the axial direction is allowed with respect to the operation shaft 36. According to such a configuration, even when the operation shaft 36 thermally expands and contracts (thermally deforms) in the axial direction, the valve element 30 moves in the axial direction relative to the operation shaft 36, so that the high-speed passage It is possible to avoid the inconvenience that the valve body 30 is pressed against the side walls of 24b, 25b, and 26b and the operation thereof is hindered.

  The valve body 32 of each valve body 30 is a rectangle corresponding to the cross-sectional shape of each of the high-speed passages 24b, 25b, and 26b. Each valve body 30 is arranged in each high speed passage 24b, 25b, 26b so that the valve main body 32 is directed upstream (engine main body 1 side), and further upstream of the operation shaft 36. The main body 32 is mounted on the operation shaft 36 in a state where the main body 32 is positioned. The valve body 32 of each valve body 30 warps toward the upstream side of the high-speed passages 24b, 25b, and 26b at both ends in the left-right direction (that is, both ends in the direction along the axial direction of the operation shaft 36). A bent portion 32a formed as described above is provided. As shown in FIGS. 4 and 5, each bent portion 32a is positioned so that at least its tip is located radially outside the through hole 22 formed in the partition wall of each high-speed passage 24b, 25b, 26b. Is formed. That is, such bent portions 32 a are formed at both ends of the valve body 32, so that the exhaust gas in each of the high speed passages 24 b, 25 b, 26 b is adjacent to the high speed passages 24 b, 25 b through the through holes 22. , 26b can be prevented from leaking and flowing backward.

  As shown in FIGS. 1 and 2, the turbocharger 50 is fixed to the device body 21 of the exhaust valve device 20 with bolts. The turbocharger 50 is connected to the turbine 56 via a turbine housing 52 fixed to the mounting surface 21a of the apparatus main body 21, a turbine 56 disposed in the turbine housing 52, and a connecting shaft 57, And a compressor disposed in an intake passage (not shown). The turbine housing 52 includes a collecting portion 54 through which the downstream exhaust passages 24, 25, and 26 (the high-speed passages 24b, 25b, and 26b and the low-speed passages 24c, 25c, and 26c) communicate with the exhaust valve device 20. The exhaust gas from the downstream exhaust passages 24, 25, 26 joins at the collecting portion 54 and is sent to the turbine 56. In other words, this engine is not provided with an independent part as the exhaust manifold, but the upstream exhaust passages 14, 15, 16 of the engine body 1 (cylinder head 10) and the downstream exhaust passage 24 of the exhaust valve device 20. , 25 and 26 and the collecting portion 54 of the turbocharger 50 cooperate to constitute the exhaust manifold.

  Further, an EGR upstream side passage 58 that branches from the collecting portion 54 and communicates with the EGR intermediate passage 28 of the exhaust valve device 20 is formed on the left side of the upstream side of the turbine housing 52. A part of the exhaust gas flowing into the exhaust gas is introduced into the intake passage through the EGR upstream passage 58, the EGR intermediate passage 28, and the EGR downstream passage 18 as EGR gas. That is, in this engine, the EGR passage is constituted by the EGR downstream side passage 18, the EGR intermediate passage 28, and the EGR upstream side passage 58.

  In the engine configured as described above, the exhaust gas generated in the engine body 1 is turbocharged from the upstream exhaust passages 14, 15, 16 through the downstream exhaust passages 24, 25, 26 of the exhaust valve device 20. Introduced into the feeder 50. At that time, the flow area of the exhaust gas flowing through each of the high speed passages 24b, 25b, 26b of the exhaust valve device 20 is changed in the driving state of the vehicle. Specifically, the exhaust valve device 20 is controlled so as to close the high-speed passages 24b, 25b, and 26b in the low-speed driving region of the vehicle. That is, by concentrating a small amount of exhaust gas in the low-speed passages 24c, 25c, and 26c, the flow rate of the exhaust gas is increased, thereby increasing the driving force of the turbine 56 of the turbocharger 50 and increasing the intake pressure. ing. On the other hand, the exhaust valve device 20 is controlled to open the high-speed passages 24b, 25b, and 26b in the high-speed driving region of the vehicle. That is, by introducing exhaust gas into the turbocharger 50 through both the high-speed passages 24b, 25b, and 26b and the low-speed passages 24c, 25c, and 26c, the exhaust variable valve (the valve body 30 and the operation shaft 36) is exhausted. The turbocharger 50 is driven to increase the intake pressure while preventing resistance.

  According to the engine of this embodiment, the exhaust valve device 20 in which the exhaust variable valve is incorporated is provided in the device main body 21 made of a metal casting in which the downstream exhaust passages 24, 25, and 26 are formed. 20 is interposed between the engine main body 1 and the turbocharger 50, and is formed in the downstream exhaust passages 24, 25, 26 of the exhaust valve device 20 and the engine main body 1 (cylinder head 10). The upstream exhaust passages 14, 15, 16 and the collecting portion 54 formed in the turbocharger 50 (turbine housing 52) cooperate to constitute an exhaust manifold. According to such a configuration, there is no exhaust manifold as an independent part, and downstream exhaust passages 24, 25, and 26 (high-speed passages 24b, 25b, and 26b) for forming the exhaust manifold, and these passages The exhaust variable valve for changing the flow area of the exhaust gas in 24, 25, 26 is integrated into one exhaust valve device 20. Therefore, a conventional engine (conventional engine described in the background art), that is, an exhaust manifold is incorporated in the engine as an independent part, and a dedicated exhaust valve device is further incorporated in the engine separately from the exhaust manifold. Compared with an engine, the engine can be made smaller and lighter.

  In addition, as described above, the variable exhaust valve of the exhaust valve device 20 is provided with bent portions 32a formed so as to bend toward the upstream side at both left and right direction portions of the valve body 32 of each valve body 30. Therefore, the exhaust gas in each high-speed passage 24b, 25b, 26b is prevented from leaking to the adjacent high-speed passages 24b, 25b, 26b through the through hole 22. In particular, in the present embodiment, the bent portion 32a is positioned so that at least the tip of the bent portion 32a is located on the radially outer side of the through hole 22 formed in the partition wall of each high-speed passage 24b, 25b, 26b. Since the through hole 22 is formed, the through hole 22 is covered from the upstream side by both end portions (folded portion 32a) of the valve body 32, so that it is effective that the exhaust gas flows into the through hole 22. To be suppressed. Therefore, according to the exhaust valve device 20, while adopting a configuration in which the downstream exhaust passages 24, 25, and 26 (the high speed passages 24b, 25b, and 26b) and the exhaust variable valve are integrated into one, the adjacent high speed It is possible to effectively prevent the exhaust gas from leaking and flowing backward between the working passages 24b, 25b, and 26b to induce exhaust interference.

  The engine of the above-described embodiment described above is an example of a preferred embodiment of a multi-cylinder engine with a turbocharger according to the present invention, and a specific configuration of the engine and the exhaust valve device 20 incorporated therein. Can be appropriately changed without departing from the scope of the present invention.

  For example, in the above embodiment, the upstream exhaust passages 14, 15, and 16 are gathered in the engine body 1 (cylinder head 10), the downstream exhaust passages 24, 25, and 26 are gathered in the turbocharger 50. By providing each of the portions 54, the upstream exhaust passages 14, 15, 16, the downstream exhaust passages 24, 25, 26 and the collecting portion 54 cooperate to constitute an exhaust manifold. Only the exhaust ports of the respective cylinders 2A to 2D may be formed, and passages corresponding to the upstream exhaust passages 14, 15, 16 may be formed on the exhaust valve device 20 (device main body 21) side. Moreover, it is good also as a structure by which the part corresponded to the gathering part 54 of the turbocharger 50 was formed in the exhaust valve apparatus 20 (apparatus main body 21) side.

  In the exhaust variable valve of the above embodiment, the semicircular portion 36b is formed on the operation shaft 36, and the semicircular portion 36b is inserted into the bridge portion 34a of the valve body 30 so that each valve body 30 is operated. For example, a key groove extending in the axial direction is formed on the outer peripheral surface of the operation shaft 36 having a circular cross section, while the valve body 30 is connected to the shaft 36 so as to be relatively displaceable in the axial direction. A configuration may be adopted in which a key is formed on the side and the valve body 30 is externally fitted (key coupled) to the operation shaft 36 so that the valve body 30 can be displaced in the axial direction with respect to the operation shaft 36. According to this configuration, the cross-sectional shape of the operation shaft 36 can be made closer to a circle. Therefore, in combination with the function and effect of the bent portion 32a of the valve body 32, it is possible to more reliably suppress the exhaust gas from leaking between the adjacent high-speed passages 24b, 25b, and 26b. .

  In the above embodiment, the exhaust valve device of the present invention is applied to an in-line four-cylinder four-cycle engine. However, the exhaust valve device of the present invention can of course be applied to engines other than the above embodiment. It is.

DESCRIPTION OF SYMBOLS 1 Engine main body 10 Cylinder head 20 Exhaust-valve apparatus 21 Apparatus main body 22 Through hole 24 1st downstream exhaust passage 24a, 25a, 26a Common passage 24b, 25b, 26b High-speed passage 24c, 25c, 26c Low-speed passage 25 Second downstream Side exhaust passage 26 Third downstream side exhaust passage 30 Valve body 32 Valve body 32a Bending portion 34 Mounting member 34 Bridge portion 36 Operation shaft 36a Circular portion 36b Semicircular portion 37 Flat surface 50 Turbocharger

Claims (3)

An exhaust valve device,
An apparatus body comprising a plurality of exhaust passages arranged in parallel with each other and in a specific direction;
A valve member disposed in each of the exhaust passages, and an operation shaft that is rotatably supported by the apparatus main body and connects the valve members, and changes a flow area of the exhaust gas in the exhaust passages. An exhaust variable valve that
Each of the exhaust passages is branched in the middle thereof into a low speed exhaust passage and a high speed exhaust passage in which the exhaust variable valve is disposed,
In the high speed operation region, the exhaust variable valve is opened so that the exhaust gas flows down through both the high speed passage and the low speed passage. On the other hand, in the low speed operation region, the exhaust gas passes through the low speed passage. The exhaust variable valve is fully closed so that only the high-speed passage flows down without passing through,
The operating shaft, said by being inserted into a hole formed in the side wall of the exhaust passages, it is supporting the respective high-speed passages in said apparatus body in a state of penetrating in the specific direction,
Wherein each valve member is in a state in which the exhaust variable valve is fully closed in the low speed operation range, as well as positioned on the upstream side of the exhaust passage than said operating shaft, both end portions in the said specific direction, the exhaust valve apparatus characterized by having a shape and located radially outwardly of the hole which Ri Sorikae toward the upstream side. The exhaust valve device according to claim 1,
The exhaust valve device according to claim 1, wherein the operating shaft has a half-moon shaped cross section, and the valve member is mounted along a plane portion of the outer peripheral surface thereof. An engine body, a turbocharger driven by the energy of exhaust gas discharged from the engine body, and interposed between the engine body and the turbocharger, and turbocharged from the engine body through an exhaust passage An exhaust valve device that variably sets the flow rate of the exhaust gas sent to the supercharger by changing the flow area of the exhaust gas in the exhaust passage,
The exhaust valve device, the engine turbocharged, characterized in that an exhaust valve apparatus according to claim 1 or 2.

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