JPH0223693B2 - - Google Patents

Description

Detailed Description of the Invention (Industrial Application Field) The present invention provides two exhaust gas inlet ports each formed in a turbine casing of an exhaust turbo supercharger,
An exhaust turbo filter is provided in which the passage area of the exhaust gas passage in the turbine casing is made variable by opening and closing one side of the two exhaust gas inlets using a suitable valve device depending on the operating state of the engine. This relates to a feeding device.

(Prior Art) In a conventional exhaust turbo supercharger, a single exhaust passage is formed inside the turbine casing, and the passage area of the exhaust passage is fixedly set, and the area of the exhaust passage is fixedly set. The A/R value determines the turbine efficiency from the viewpoint of obtaining the highest possible level of turbine efficiency (A: passage area of the exhaust gas passage of the turbine casing, R: the passage area of the scroll portion of the turbine casing). It was customary to set the radius of curvature) according to the amount of exhaust gas during medium-speed operation of the engine.

However, if the A/R value is set in accordance with the medium-speed operation of the engine, the amount of exhaust gas will be higher than the standard exhaust gas amount in the high-speed operation region of the engine. This increases the flow resistance of the exhaust gas, making it impossible to fully utilize the exhaust energy of the exhaust gas.Furthermore, on the engine side, the exhaust pressure increases, causing problems such as deterioration of combustibility and the inability to obtain sufficient engine output. On the other hand, in the low-speed operating range of the engine, the flow rate of exhaust gas decreases as the amount of exhaust gas becomes less than the above-mentioned standard exhaust gas amount, and the turbine wheel cannot rotate sufficiently, resulting in lower turbine efficiency. This will cause the problem of a decline.

In order to improve the disadvantages peculiar to an exhaust turbo supercharger equipped with a turbine casing having a single exhaust gas passage, the exhaust gas passage in the turbine casing is divided into multiple sections, and the exhaust gas passage divided into multiple sections is A technology that allows the passage area of the exhaust gas passage to be varied according to the operating condition of the engine by controlling the opening and closing of the gas passage using a valve device, thereby ensuring a high level of supercharging efficiency throughout the entire operating range of the engine. Attempts have been made to develop (for example, see Japanese Unexamined Patent Publication No. 18522/1983).

By the way, this known example exhaust turbo supercharging device has a turbine casing 10 as shown in FIG.
A scroll-shaped exhaust gas passage formed in the turbine casing 1 is divided into two exhaust gas passages arranged in the turbine axial direction by a partition wall 104 extending in the scroll direction, and one of the exhaust gas passages is divided into two exhaust gas passages formed in the turbine casing 1.
A low-speed exhaust gas passage 102 is formed from the exhaust inlet end 101a of 01 to the entire circumference of the scroll portion and is open throughout the entire operating range of the engine, and the other is the low-speed exhaust gas passage 102.
A high-speed exhaust gas passage 103 is formed along the low-speed exhaust gas passage 102 from the middle of the passage, and is opened only when the engine is operating at high speed. Furthermore, this high-speed exhaust gas passage 103
and a low-speed exhaust gas passage 102 are provided in a side wall portion of the low-speed exhaust gas passage 102.
A valve device 106 that is operated and controlled by a valve operating device 107 installed on a component other than the turbine casing 101 is attached to the communication port 105 portion, and the communication port 105 is opened and closed by the valve device 106.

However, in this known example of the exhaust turbo supercharging device, the valve device 106 is used in two cases: when the exhaust gas flows only through the low-speed exhaust gas passage 102, and when the exhaust gas flows only through the low-speed exhaust gas passage 102 and the high-speed exhaust gas passage 103.
In addition, the valve operating device 104 connected to the valve device 6 is placed on the side of the turbine casing 101, which has different heat load characteristics and tends to cause irregular thermal deformation. Since it is attached to the component side, the valve device 106 and the valve actuating device 104 are affected by thermal deformation of the turbine casing 101.
There has been a problem in that the relative position of the valve device 106 changes greatly, and the control accuracy of the valve device 106 (and by extension, the control accuracy of the engine) tends to deteriorate.

Furthermore, as described above, since the valve device 106 and the valve actuating device 104 are arranged as separate members, it is difficult to manage the assembly accuracy between the valve device 106 and the valve actuating device 104, and moreover, when disassembling and reassembling the device, However, the valve device 106 and the valve actuating device 104 had to be connected or disconnected each time, and there was also a problem that the ease of assembly was poor.

(Object of the Invention) In view of the above problems, the present invention has been proposed to open and close one side of two exhaust gas inlet ports provided in the turbine casing of an exhaust turbo supercharger using a valve device. In an exhaust turbo supercharging device in which the passage area of the exhaust gas passage in the exhaust gas passage is variable, the control accuracy of the valve device is maintained at a high level, and the assembly between the valve device and the valve operating device that operates the same is provided. This was done with the aim of improving performance and assembly accuracy.

(Means for achieving the object) As a means for achieving the above object, the present invention provides a turbine casing in which a first exhaust gas inlet and a second exhaust gas inlet are respectively formed.
An exhaust pipe that guides exhaust gas from the engine is connected to each of the above exhaust gas inlets so as to be able to introduce the exhaust gas into the turbine side through each of the exhaust gas inlets. A second exhaust gas inlet among the exhaust gas inlets can be opened and closed by a valve device that is provided on the exhaust pipe side and operates using an end surface of the turbine casing on the second exhaust gas inlet side as a valve seat surface. At the same time, a valve operating device for operating the valve device via the operating force transmission means is located in the exhaust pipe and closer to the first exhaust gas inlet than the second exhaust gas inlet of the turbine casing. It is characterized by being fixed to the body part.

(Function) With this configuration of the present invention, (1) The mounting position of the valve actuating device with respect to the exhaust pipe can be adjusted to match when the exhaust gas is flowing because the exhaust gas selectively flows. Because the position is set closer to the first exhaust gas inlet, where exhaust gas constantly flows and where the temperature changes less, the exhaust pipe heat is Relative displacement between the valve actuating device and the valve device due to deformation is prevented as much as possible. (2) Since both the valve device and the valve actuating device are attached to the exhaust pipe, Effects such as being able to be attached to and detached from the engine or exhaust turbocharger integrally with the exhaust pipe while remaining attached to the exhaust pipe are obtained.

(Effects of the Invention) Therefore, according to the exhaust turbocharging device of the present invention, (1) Since the valve operating device is installed in the position of the exhaust pipe where the temperature changes the least, the valve operating device and this The relative positional change due to the temperature change between the connected valve device and the valve device is minimized as much as possible, and the control accuracy of the valve device is improved accordingly. (2) The valve device and the valve actuating device are both attached to the exhaust pipe side, so they can be attached and removed from the turbine casing side together with the exhaust pipe when disassembling and reassembling the device. Compared to those that require connection and disconnection, the ease of assembly and accuracy of assembly can be improved.

(Embodiments) Hereinafter, preferred embodiments of the present invention will be described with reference to FIGS. 1 to 9.

(Structure) FIGS. 1 to 3 show an exhaust turbo supercharging device according to an embodiment of the present invention, and the reference numeral 1 in the figures
is an engine body, 2 is an exhaust turbo supercharger (described in detail later), and the exhaust turbo supercharger 2 is fixed to an exhaust pipe 4 (described in detail later) via a gasket 3 (see Fig. 3). has been done.

As shown in FIG. 1, the exhaust turbo supercharger 2 includes a turbine casing 21 (described in detail later) containing a turbine wheel (not shown) and a compressor casing 22 containing a compressor wheel (not shown). They are connected via a center casing 23.

The turbine casing 21 is shown in FIGS.
As shown in the figures, a scroll-shaped exhaust gas passage formed inside the turbine casing 21 is separated into two exhaust gas passages arranged in the axial direction of the turbine casing 21 by a partition wall 26 extending in the direction of the scroll. , a first exhaust gas passage 27 having an oval cross section located on one side of the partition wall 26, and an oval cross section located on the other side of the partition wall 26 and having a smaller passage area than the first exhaust gas passage 27. The second exhaust gas passage 28 is divided into two left and right exhaust gas passages.
These two exhaust gas passages 27 and 28 have exhaust gas inlet ports 29 and 30 formed at the open ends on the exhaust gas upstream side of the turbine casing 21 which act as abutting surfaces toward the exhaust pipe 4 side. It is opened on the end face 21a on the gas upstream side.

Of the two exhaust gas inlet ports 29 and 30, the first exhaust gas inlet port 29 is always open throughout the entire operating range of the engine, but the second exhaust gas inlet port 30 is connected to a valve described later. The device 6 is closed when the engine is running at low speeds with a small flow rate of exhaust gas, and is opened when the engine is running at high speeds with a high flow rate of exhaust gases.

Therefore, when the engine is operating at low speed, only the first exhaust gas inlet 29 is opened, and the exhaust gas passes through the first exhaust gas passage 27 to the turbine casing 2.
On the other hand, when the engine is operating at high speed, both the first exhaust gas inlet 29 and the second exhaust gas inlet 30 are open, and the exhaust gas is introduced into the first scroll portion 21b. Exhaust gas passage 27
and the second exhaust gas passage 28 into the scroll portion 21b side of the turbine casing 21.

In this case, in this embodiment, the partition wall 2 of the end surface 21a of the turbine casing 21
A substantially elongated annular portion located at the mouth edge of the second exhaust gas inlet 30 including the end surface 26a of the exhaust gas inlet 6 serves as a valve seat surface 33 for the valve device 6, which will be described later.

In this way, the end face 2 of the turbine casing 21
If part of 1a is used as the valve seat surface 33 of the valve device 6, the second exhaust gas inlet 30 will open facing the exhaust gas flow direction. Therefore, when the valve device 6 is in the open state, the exhaust gas flows smoothly into the turbine casing 21 in an almost straight line with low flow resistance without detouring, compared to when the exhaust gas flow is a detour flow. As a result, turbine efficiency is improved by the reduction in flow resistance.

In addition, in this case, the entire area of the opening of the second exhaust gas inlet 30 can effectively function as a flow path for exhaust gas, and therefore, for example, when the flow rate of exhaust gas is constant, Compared to a structure in which the flow direction and the axial direction of the second exhaust gas inlet 30 intersect, the second exhaust gas inlet 3
This is advantageous in terms of making the device more compact, as the diameter of the valve 0 can be made smaller and the valve device 6 can also be made smaller accordingly.

Furthermore, since the planar direction of the valve seat surface 33 is substantially perpendicular to the exhaust gas flow direction, when the planar direction of the valve seat surface 33 and the exhaust gas flow direction are substantially parallel, In comparison, the sealing performance at the valve seat surface 33 is good, and the flow control of exhaust gas is performed more reliably, resulting in a higher level of turbine efficiency.

Further, since the partition wall 26 is formed in the turbine casing 21, the structure is more complicated and irregular thermal deformation is more likely than in the case of a turbine casing having a structure without the partition wall 26. In this embodiment, as will be described later, the valve device 6 is not placed on the turbine casing 21 side, but on the exhaust pipe 4 side, which has a relatively simple structure compared to the turbine casing 21 and is less prone to irregular thermal deformation. Since the turbine casing 21 is provided in the exhaust turbocharger equipped with the valve device 6, it is possible to minimize the complexity of the structure of the turbine casing 21. As a result, the increase in size can be suppressed as much as possible.

In FIG. 1, reference numeral 31 is a waste gate valve having a known structure provided on the side of the turbine casing 21, and the waste gate valve 31 is operated in response to intake pressure (supercharging pressure) of the engine. The opening/closing is controlled by the first actuator 8.

The exhaust pipe 4 is connected to an exhaust port of each cylinder of the engine body 1 (not shown) as shown in FIGS. 1 to 3.
A branch pipe section 41 consisting of four branch pipes 41A, 41B... connected in a substantially horizontal direction to the
While the branch pipes 41A, 41B... are collected at the downstream end of the exhaust gas, a collecting pipe part 42 extending from the branch pipe part 41 in a direction orthogonal to the branch pipe part 41 is integrally formed. It is configured,
It is fastened and fixed to the side of the engine main body 1 with the end surface 4a on the side of the branch pipe abutting against the side of the engine main body 1, and the end surface 4b on the side of the collecting pipe section 42
As shown in FIGS. 3 and 4, the turbine casing 21 of the exhaust turbocharger 2 is abutted and fixed to the upper end surface 42a of the collecting pipe portion 42 via the gasket 3.

A continuous portion 46 located at the exhaust gas upstream end of the collecting pipe portion 42 of the exhaust pipe 4 and continuing to the branch pipe portion 41 is defined by a projected line l ₁ in FIG. 4 and an imaginary line l ₂ in FIG. As shown in FIG.
(in the exhaust gas flow direction) facing the first exhaust gas inlet 29 and the second exhaust gas inlet 30 of the turbine casing 21 simultaneously and in a direction along the opening direction of each of the exhaust gas inlets 29 and 30; The opening has a substantially square cross section and has an opening area and an opening direction that can be obtained. Therefore, the exhaust gas collecting passage 43 in the collecting pipe section 42 and the first
The exhaust gas passage 27 and the exhaust gas passage on the turbine casing 21 side formed by the second exhaust gas passage 28 are continuous in a substantially coaxial manner,
Exhaust gas G flowing inside from the branch pipe section 41 side to the collecting pipe section 42 side is guided by the continuous section 46 and flows inside the collecting pipe section 42 along its axial direction, and then flows through the turbine casing. The exhaust gas can be smoothly introduced into the first exhaust gas inlet 29 and the second exhaust gas inlet 30 of the exhaust gas 21 as a substantially straight flow with almost no flow resistance.

Further, this exhaust pipe 4 has a side wall 4 of the side wall of the collecting pipe portion 42 on the side facing the second exhaust gas inlet 30 of the turbine casing 21.
8 is bulged outward by an appropriate amount from the continuous portion 46 at a position closer to the end surface 4b, and inside thereof is located continuously to the exhaust gas collecting pipe portion 43 and on the side thereof, and has one end thereof. The expansion portion 44 has an expansion space 45 of an appropriate size that opens on the end surface 4b. This expanded portion 44 functions as an attachment and storage space for a valve device 6, which will be described later.

The valve device 6 is a swing type valve device that controls opening and closing of the second exhaust gas inlet 30 of the turbine casing 21, as shown in FIGS. 4 to 7.
In this embodiment, this is attached to the expanded portion 44 of the exhaust pipe 4. That is, this valve device 6 is
As shown in FIG. 5, the side wall of the expanded portion 44 of the exhaust pipe 4 and the side wall of the second exhaust gas inlet 30 of the turbine casing 21 located on the side opposite to the engine main body 1 among the pair of side walls facing each other in the longitudinal direction 4
The operating center shaft 65 is rotatably supported by a bearing tube 66 which is provided through the exhaust gas inlet 7 in the inner and outer directions (in other words, in the direction parallel to the longitudinal axis of the second exhaust gas inlet 30). The valve body 61 has a valve support body 62 and a valve body 61 supported in a freely floating manner via a pair of connecting pins 67 and 68 with respect to a valve holding plate 63 formed at a swing end 62a of the valve support body 62. ing. The valve body 61 is formed on the valve seat surface 3 formed at the mouth edge of the second exhaust gas inlet 30 on the end surface 21a of the turbine casing 21, as shown in FIG.
3, at least the second exhaust gas inlet 30 is closed and the end surface 26a of the partition wall 26 of the turbine casing 21 is closed.
It is an oblong plate having a size that can cover the valve body 61, and a vent hole 71 of an appropriate diameter is formed in the central part in the longitudinal direction to pass through the valve body 61 in the thickness direction. There is.

In this way, when the end face 26a of the partition wall 26 is covered by the valve body 61 when the valve device 6 is in the closed state, thermal deterioration of the partition wall 26 is prevented as much as possible, as will be described later. This will also reduce the flow resistance of the exhaust gas. That is, when the valve device 6 is in the closed state, the valve body 61 closes the partition wall 2.
When the end face 26a of 6 is covered, the end face 2
The frequency with which the end face 26a is directly exposed to high-temperature exhaust gas is significantly reduced compared to a structure in which the end face 26a is directly exposed to exhaust gas throughout the entire operating range of the engine. The rate at which the valve device 6 is closed throughout the entire operating range is usually as high as about 70 to 80%), so that thermal oxidation in the vicinity of the end face of the partition wall 26 is prevented as much as possible. Furthermore, since the temperature rise of the partition wall 26 is suppressed, the occurrence of cracks due to thermal stress in the vicinity of the end face of the partition wall 26 is prevented, and the durability of the turbine casing 21 is thereby improved. It will be improved. Furthermore, since thermal oxidation and crack generation near the end faces of the partition walls 26 are prevented as described above, it is possible to reduce the thickness of the partition walls 26. Therefore, the turbine casing 21 is made lighter and more compact, and
The thinner partition wall 26 reduces the flow resistance of exhaust gas when the valve device 6 is open, which is advantageous in improving supercharging efficiency. In this embodiment, the thickness of the partition wall 26 is approximately 6 mm.

On the other hand, the pair of connecting pins 67 and 68 connecting the valve body 61 and the valve holding plate 63 of the valve support body 62 are connected to the valve body 61 as shown in FIGS.
1, the fitting shaft portions 67a and 68a protruding toward the upper surface 61a of the valve body 61 are fixed to the valve body 61 at an appropriate distance from each other in the longitudinal direction.
The pin receiving hole 7 formed in the valve holding plate 63 of No. 2
2, 72 so as to be freely movable. Moreover, the above-mentioned fitting shaft portion 67 of this pair of connecting pins 67, 68
The length of a, 68a is set to be longer than the thickness of the valve retainer plate 63 by an appropriate length so that the valve body 61 and the valve retainer plate 63 can be supported so as to be able to float relative to each other. Therefore, when the valve device 6 is opened from its closed state (the state shown in FIG. 6), the valve body 61 and the valve retaining plate 63 are connected to each other as shown in FIG. 7 at the beginning of the valve opening operation.
In between, there is a parallel gap 7 communicating with the ventilation hole 71.
4 is formed, and the second exhaust gas passage 28 of the turbine casing 21 and the exhaust gas collecting passage 43 of the exhaust pipe 4 are made to communicate with each other via the ventilation hole 71 and the gap 74.

Therefore, when the valve device 6 is rotated from its closed state in the direction of arrow A (see FIG. 4) to open the valve as shown in FIG. 6, the static pressure of the exhaust gas is and dynamic pressure is applied to the upper surface 61a of the valve body 61.
Since the load is applied to the valve side, a large actuation force is required to open the valve body 61 against the pressure of the exhaust gas, but in this embodiment, the valve body 61 is Since the valve body 61 is freely supported on the support body 62 and has a vent hole 71 formed therein, the valve body 61 and the valve retaining plate are connected to each other in the initial stage of opening of the valve device 6, as shown in FIG. 63 are separated from each other, so that the high-pressure exhaust gas collection passage 43 and the low-pressure second exhaust gas passage 28 communicate with each other, and a portion of the exhaust gas passes through the vent hole 71 to the second exhaust gas passage 28 side. The pressure difference between the two is reduced as much as possible (in other words, the force for regulating the valve opening direction on the valve body 61 is reduced), and the valve device 6 can be operated smoothly and quickly with a smaller operating force. It becomes possible to open the valve (that is, the miniaturization of the valve actuating device 7, which will be described later), is facilitated, and the central axis of operation 6 is
5 and the wear resistance of the bearing sleeve 66 is improved).

Further, in this case, each pen receiving hole 72, 72 of the valve holding plate 63 is connected to the connecting pin 67, 68, respectively.
Since the heads 67b and 68b of the exhaust gas collecting passage 43 are substantially closed, the second
Exhaust gas flowing out to the exhaust gas passage 28 side flows into the vent hole 71 side from the gap 74 between the valve body 61 and the valve holding plate 63 without passing through the pin receiving holes 72, 72. Become. For this reason, each pin receiving hole 72, 7 plays an important role in valve function.
This prevents the inner circumferential surface of the valve device 6 from being exposed to high temperature exhaust gas and thermally deteriorating, resulting in an excessive amount of free movement between the valve body 61 and the valve support body 62, which impairs the function of the valve device 6. Prevented.

In addition, since the valve body 61 and the valve holding plate 63 are connected to each other so as to be freely movable, for example, if the gasket 3 interposed between the exhaust pipe 4 and the turbine casing 21 breaks down due to aging, Even if an assembly error occurs between the valve device 6 and the valve actuating device 7, which will be described later, the close contact between the valve body 61 and the valve seat surface 33 is maintained at a high level, and the valve seat surface The sealing performance at 33 will be maintained well over a long period of time.

Furthermore, in this valve device 6, the valve body 61 and the valve holding plate 63 are connected to a pair of connecting pins 67, 6.
8, the relative positioning of the valve body 61 and the valve holding plate 63 in the plane direction is easy, and the once set relative position does not shift during use (the valve body 61 Securing positioning function). Therefore, it is possible to make the valve body 61 oval rather than circular, and it is possible to make the valve body 61 more compact than when the valve body 61 is circular.
Further, the advantage that positioning of the valve body 61 is easy and that positional deviation does not occur is achieved by forming the opening shape of the second exhaust gas inlet 30 not in a circle but in an oval shape as described above. The relative distance between the second exhaust gas inlet 30 and the operating center axis 65 of the valve device 6 is kept as small as possible, and the opening area of the second exhaust gas inlet 30 is made as large as possible. As a result, the valve body 61 or the second exhaust gas inlet 3
0 is circular, the relative distance between the second exhaust gas inlet 30 and the operating center axis 65, that is, the arm length of the valve support body 62, is made as short as possible. It is possible to reduce the valve-opening force of the valve device 6 (that is, light and smooth operation of the valve device 6 is realized). That is, in this embodiment, the arm length of the valve support body 62 can be shortened in this way, and the vent hole 71 is provided in the valve body 61 as described above.
Due to the synergistic effect with the formation of , the valve-opening force of the valve device 6 is further reduced.

In this embodiment, as shown in FIGS. 6 and 7, the vent hole 71 formed in the valve body 61 is opened and closed by utilizing the floating function of the valve body 61, thereby opening and closing the vent hole 71 formed in the valve body 61. Although this is intended to reduce the operating force when opening the valve, in other embodiments of the present invention, the vent hole 71 is not formed and a pair of connections are used, for example, as shown in FIGS. 8 and 9. pins 67, 68
are composed of pins of different lengths to ensure the close contact of the valve element 61 to the valve seat surface 33 when the valve device 6 is in the closed state (see FIG. (see FIG. 9), the valve body 61 is
The valve body 61 is opened from one side in its longitudinal direction.
It is also possible to form an inclined gap 75 between the valve seat surface 33 and the valve seat surface 33 so that part of the exhaust gas can escape from the gap 75 to the second exhaust gas passage 28 side. In addition, each member of this FIG. 8 and FIG.
It has the same configuration as each member shown in FIGS. 6 and 7, and detailed explanation thereof will be omitted by giving the same reference numerals as those given to each member in FIGS. 6 and 7.

On the other hand, this valve device 6 has a valve operating device 7 which will be described later.
Accordingly, arrow A is centered on the operation center axis 65.
- The valve opening device is rotated in the B direction and is shown in solid lines in FIG.
In this case, in the valve open position of the valve device 6, the valve device 6 is stored in the expansion space 45 of the exhaust pipe 4. (In other words, it is located closer to the extended portion 44 than the projection line l ₁ of the continuous portion 46)
As such, the arm length of the valve support 62 or the mounting position of the operating center shaft 65 are set appropriately. By doing this, when the valve device 6 is in the open state, the exhaust gas collecting passage 43 of the exhaust pipe 4
A valve device 6 whose passage area is positioned at the valve open position.
The flow resistance of the exhaust gas is reduced as much as possible, and the valve support of the valve device 6 is not substantially reduced when the valve device 6 is in the closed state. body 62 and central axis of operation 65
(Substantially the bearing sleeve 66) prevents the exhaust gas from directly hitting the exposed portion of the end surface 21a of the turbine casing 21 facing the expansion space 45 as much as possible. thermal deterioration is suppressed. As a result, the durability of the turbine casing 21 is improved.

Further, since the valve device 6 is not formed on the partition wall 26 and has a relatively simple structure, and is provided on the exhaust pipe 4 side where irregular thermal deformation is less likely to occur, the structure is relatively complex and therefore irregular thermal deformation is less likely to occur. Compared to the case where the valve device 6 is provided on the turbine casing 21 side where thermal deformation is likely to occur, the influence of thermal deformation on the operating characteristics of the valve device 6 is reduced, and the operating accuracy of the valve device 6 is maintained at a high level accordingly. becomes possible.

The valve operating device 7 opens and closes the valve device 6 according to the operating state of the engine, and as shown in FIGS. 1 to 3, the air supply is controlled as appropriate depending on the operating state of the engine. It is composed of a second actuator 9 having a diaphragm type pressure responsive mechanism that moves its actuator 10 forward and backward in response to pressure, and is located on the side of the collecting pipe section 42 of the exhaust pipe 4 and in addition to the turbine casing. The exhaust gas introduction port 21 is located closer to the first exhaust gas introduction port 29 than the second exhaust gas introduction port 30 of the exhaust gas introduction port 21, and is installed in a substantially adiabatic manner as will be described later.

That is, in the collecting pipe part 42 of the exhaust pipe 4, an exhaust pipe insulator 12 made of a plate bent into a substantially U-shape is provided, excluding the side surface of the collecting pipe part 42 facing the engine main body 1 side. An insulator mounting portion 42b is fitted from the outside of the collecting pipe portion 42 so as to surround the outside of the other three side surfaces, and is bulged on one side of the collecting pipe portion 42, and faces the insulator mounting portion 42b. It is fixed by fastening one side 12a of the actuator insulator 11 with a pair of mounting bolts 15, 15. Further, when installing the exhaust pipe insulator 12, a flat bracket 13 is attached to the exhaust pipe insulator 12 at a position near the first exhaust gas inlet 29, and the tip end 13a of the bracket 13 is attached to the exhaust pipe insulator 12 at a position near the first exhaust gas inlet 29. The pipe insulator 12 is fixed together by the mounting bolts 15, 15 in a state of protruding outward from the outer end of the pipe insulator 12 on the side opposite to the engine main body 1.

Furthermore, the tip 13a of the bracket 13 is provided with the second insulator, the outer periphery of which is covered by the actuator insulator 11 having a substantially airtight container shape.
The actuator 9 is connected to one side surface 11a of the actuator insulator 11 on the actuator 10 side.
is sandwiched between the tip 13a of the bracket 13 and the front end surface 9a of the second actuator 9, and is fastened and fixed by a pair of mounting bolts 16, 16. Therefore, the second actuator 9 is fixed to the collecting pipe portion 42 of the exhaust pipe 4 via the two members, the actuator insulator 11 and the exhaust pipe insulator 12, in a substantially adiabatic manner.

In this way, the second
The operating center shaft 65 of the valve device 6 is connected to the actuating element 10 of the actuator 9 via link levers 69 and 70 (corresponding to actuating force transmitting means in the claims). 10 is arrow a
By projecting in the direction (see FIG. 1), the valve device 6 rotates in the direction of arrow A (see FIG. 4), opening the second exhaust gas inlet 30. When the child 10 retreats in the direction of arrow b, the valve device 6 rotates in the direction of arrow B, and the second exhaust gas introduction port 30 is closed.

In this way, the exhaust pipe insulator 12 is attached to the outside of the exhaust pipe 4, and together with the exhaust pipe insulator 12, it is attached to the exhaust pipe 4 side and at a position closer to the first exhaust gas inlet 29 of the turbine casing 21. A second actuator 9 whose periphery is surrounded by an actuator insulator 11 is placed on the tip 13a of the bracket 13, and the actuator insulator 11 is interposed between the end surface 9a of the second actuator 9 and the bracket tip 13a. If they are fastened and fixed together in this state, the action of the insulators 11 and 12 will prevent radiant heat from being transmitted from the exhaust pipe 4 side to the second actuator 9 side as much as possible, and will also prevent the radiant heat from being transmitted from the exhaust pipe 4 side through the bracket 13. The conductive heat transferred is transferred to the actuator insulator 11 side, and the amount of heat transferred to the second actuator 9 side is also reduced as much as possible.

Furthermore, in this case, since the second actuator 9 is disposed on the side of the first exhaust gas inlet 29 where the temperature change is the smallest among the exhaust pipes 4, the second actuator 9
The amount of heat transferred to the actuator 9 side is smaller than, for example, when it is installed near the second exhaust gas inlet 30, and in addition to this, as described above, the amount of heat transferred to the actuator 9 is reduced. Since the second actuator 9 that operates the valve device is both attached to the exhaust pipe 4 side, even if the exhaust pipe 4 is thermally deformed due to the heat of the exhaust gas, the valve device can be attached to the exhaust pipe 4. The relative relationship between the second actuator 9 and the valve device 6 can be maintained substantially constant.

Therefore, for these reasons, changes in the relative positional relationship between the valve device 6 and the valve operating device 7, that is, the second handle actuator 9 due to temperature changes are suppressed as much as possible, and the valve The operating accuracy of the device 6 will be maintained at a high level.

Furthermore, when the entire circumference of the second actuator 9 is covered with the actuator insulator 11 as described above, the second actuator 9 can be protected from collisions with flying stones, adhesion of sludge or rainwater, etc. This results in improved durability of the second actuator 9.

Furthermore, since the temperature rise of the second actuator 9 is suppressed as much as possible as described above, it is preferable to use a material of the diaphragm (not shown) of the second actuator 9 that is relatively low in heat resistance. This is possible, and the cost of the second actuator 9 can be reduced accordingly.

Furthermore, since both the valve device 6 and the second actuator 9 are attached to the exhaust pipe 4, when disassembling and reassembling the device, the valve device 6 and the second actuator 9 must be interlocked and connected to each other. In addition, the operation inspection can be performed with high precision in either the disassembled state or the assembled state of the device, and the assembly accuracy and ease of assembly between the valve device 6 and the second actuator 9 are ensured. .

Next, the operation and effects of this exhaust turbocharging device will be explained.

When the engine is operated, exhaust gas G discharged from each cylinder on the side of the engine body 1 is collected in the collecting pipe part 42 via each branch pipe 41A, 41B of the exhaust pipe 4, and then collected in the collecting pipe part 42. 42 exhaust gas collecting passage 43 into the exhaust gas passage in the turbine casing 21 of the exhaust turbo supercharger 2, that is, into the first exhaust gas passage 27 and the second exhaust gas passage 28, and the exhaust energy is introduced into the exhaust gas passage 27 and the second exhaust gas passage 28. The turbine wheel is driven, and the compressor wheel prepresses the intake air (intake supercharging). At this time, the valve device 6 is opened and closed depending on the operating state of the engine, and the introduction form of the exhaust gas is selected. That is, when the operating state of the engine is in a low-speed operating region where the flow rate of exhaust gas is low, the second actuator 9 sets the valve device 6 to the valve open position (FIG. 4, the position shown by the solid line), and conversely, the engine When the operating state of the valve device 6 is in a high-speed operating region where the flow rate of exhaust gas is high, the second actuator 9 operates the valve device 6.
is set to the valve open position (FIG. 4, the position shown by the chain line). Therefore, in the low-speed operating range of the engine where the amount of exhaust gas discharged is small, the exhaust gas flows only from the first exhaust gas passage 27 to the turbine casing 21.
Since the exhaust gas is introduced into the turbine casing 21, a sufficient gas flow velocity is ensured even though the amount of exhaust gas is small, and the rotation of the turbine wheel is maintained at a high rotation speed, so that the exhaust gas is discharged from a lower speed range. It becomes possible to obtain the supercharging effect by the turbo supercharger 2. Furthermore, in this case, the passage area of the exhaust gas passage is narrower than in the case where both the first exhaust gas passage 27 and the second exhaust gas passage 28 are effective, so that the exhaust gas passage area on the exhaust inlet side of the turbine casing 21 is The difference between the exhaust gas pressure at the exit of the scroll section and the exhaust gas pressure at the exit of the scroll section can be made larger (that is, the expansion ratio of the exhaust gas is increased), and a higher level of supercharging performance can be obtained.

On the other hand, in the high-speed operating range of the engine where a large amount of exhaust gas is emitted, both the first exhaust gas passage 27 and the second exhaust gas passage 28 are opened, so a large amount of exhaust gas is simultaneously transmitted to the turbine from both of them. It can be smoothly introduced into the casing 21 without causing large flow resistance. Therefore, the exhaust energy of a large amount of exhaust gas is effectively used as driving force for the turbine wheel, improving supercharging performance, and since the exhaust pressure on the engine side is reduced, its combustibility is improved, This will result in higher engine output.

The valve device 6 of the present invention may be controlled by directly detecting, for example, the flow rate of exhaust gas, the amount of intake air into the engine, etc., or may be controlled according to the engine speed in an operating region where the engine load is relatively high. etc., the control signal and control area are not limited.

[Brief explanation of drawings]

FIG. 1 is a front view of an exhaust turbo supercharging device according to an embodiment of the present invention, FIG. 2 is a view in the direction of the - arrow in FIG. 1, FIG. 3 is a view in the direction of the - arrow in FIG. 1, and FIG. 3 is a sectional view of FIG. 3, FIG. 5 is a sectional view of FIG. 4, FIG. 6 is a sectional view of FIG. 8 and 9 are operating state diagrams of a valve device according to another embodiment of the present invention, and FIG. 10 is a structural explanatory diagram of a turbine casing portion of a conventional exhaust turbo supercharging device. 1...Engine body, 2...Turbo supercharger, 4
...Exhaust pipe, 6...Valve device, 7...Valve actuation device,
8, 9... Actuator, 11, 12... Insulator, 21... Turbine casing, 22
... Compressor casing, 23 ... Center casing, 26 ... Partition wall, 27, 28 ... Exhaust gas passage, 29, 30 ... Exhaust gas inlet, 31
...Waste gate valve, 33...Valve seat surface, 4
DESCRIPTION OF SYMBOLS 1... Branch pipe part, 42... Collection pipe part, 44... Expansion part, 61... Valve body, 62... Valve support body, 63...
... Valve holding plate, 65 ... Operation center shaft, 69,
70... Link lever (operating force transmission means), 71
...Vent.

Claims (1)

[Claims] 1. A turbine casing in which a first exhaust gas inlet and a second exhaust gas inlet are respectively formed,
An exhaust pipe that guides exhaust gas from the engine is connected to each of the above exhaust gas inlets so as to be able to introduce the exhaust gas into the turbine side through each of the exhaust gas inlets. A second exhaust gas inlet among the exhaust gas inlets can be opened and closed by a valve device that is provided on the exhaust pipe side and operates using an end surface of the turbine casing on the second exhaust gas inlet side as a valve seat surface. At the same time, a valve operating device for operating the valve device via the operating force transmission means is located in the exhaust pipe and closer to the first exhaust gas inlet than the second exhaust gas inlet of the turbine casing. An exhaust turbo supercharging device characterized by being fixed to a certain part.