JPH0588373B2 - - Google Patents

Description

Detailed Description of the Invention (Industrial Application Field) The present invention provides a method for forming a plurality of exhaust gas inlets in a turbine casing of an exhaust turbo supercharger, and connecting the plurality of exhaust gas inlets to an appropriate valve device. Therefore, the present invention relates to an exhaust turbo supercharging device that can vary the passage area of the exhaust gas passage in the turbine casing by controlling opening and closing according to the operating state of the engine.

(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 exhaust passage area is fixedly set, and the exhaust passage area is set fixedly. The A/R value determines the turbine efficiency from the viewpoint of obtaining the highest level of turbine efficiency (A: passage area of the exhaust gas passage of the turbine casing, R: curvature of the scroll portion of the turbine casing). It was customary to set the radius) according to the amount of exhaust gas when the engine was operated at medium speed.

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 performance throughout the entire operating range of the engine. Attempts have been made to develop (for example, see Japanese Unexamined Patent Publication No. 18522/1983).

As shown in FIG. 10, this known exhaust turbo supercharging device uses a scroll-shaped exhaust gas passage formed in a turbine casing 101 with a partition wall 107 extending in the direction of the scroll to keep the engine running during all engine operations. The high-speed exhaust gas passage 10 is divided into two exhaust gas passages: a low-speed exhaust gas passage 102 that is opened through the area, and a high-speed exhaust gas passage 103 that is opened only when the engine is operating at high speed.
3 and the low-speed exhaust gas passage 102 are made to communicate with each other via a communication port 105 formed at an upstream position of the exhaust gas, and the communication port 105 is provided at a position near the communication port 105. device 106
It can be opened and closed by

However, in this known example, the valve device 1
06 supported by the operating center shaft 108
09 and a connecting pin 11 at the tip of the valve support 109.
1, the relative positional relationship between the valve body 110 and the valve seat surface 112 on the turbine casing 101 side is set fixedly. It is difficult to manage the adhesion between the valve body 110 and the valve seat surface 112, and even if the adhesion between the valve body 110 and the valve seat surface 112 is set to an optimal state at the time of factory manufacturing, for example, it is difficult to manage the adhesion after long-term use. Gradually the valve body 110 or valve seat surface 1
If the valve body 12 is worn out, the sealing performance of the valve body 110 will be impaired, resulting in a problem that the effect of varying the passage area of the exhaust gas passage by the valve device 106 will not be sufficiently achieved.

Also, the valve support 10 is
The communication port 105 is opened and closed by a valve body 110 attached through a valve 9. Since the communication port 105 is a circular hole, the valve body 110 that opens and closes it also has a disk shape. It is said that Therefore, when the opening area of the communication port 105 is the same, the communication port 105 and the operation The distance from the central axis 108 becomes longer, and as a result, a larger force for opening the valve is required due to the increase in the moment arm, and there is also the problem that the valve device 106 itself becomes larger.

(Object of the Invention) In view of the above problems, the present invention improves the sealing performance of the valve device so that the supercharging performance can be maintained at a high level over a long period of time, and also makes the valve device more compact and easier to operate. This has been accomplished by providing an exhaust turbo supercharging device that can improve the performance of the engine.

(Means for Achieving the Object) In the present invention, as a specific means for achieving the above-mentioned object, a turbine casing in which a plurality of exhaust gas inlets are arranged adjacently in parallel on the end face thereof, and a turbine casing as described above are provided. a common exhaust pipe connected to the turbine casing so as to guide exhaust gas to the plurality of exhaust gas inlets; and a common exhaust pipe connected to the turbine casing to guide exhaust gas to the plurality of exhaust gas inlets; a valve device that opens and closes at least one exhaust gas inlet located outermost in the exhaust gas inlet arrangement direction among the exhaust gas inlets, and the valve device is connected to one of the plurality of exhaust gas inlets. The valve device is arranged outward in the exhaust gas inlet arrangement direction from the exhaust gas inlet opened and closed by the valve device, facing in a direction parallel to the valve seat surface and orthogonal to the exhaust gas inlet arrangement direction, and in an appropriate direction. A central actuation shaft rotated by a valve actuation device, a valve support attached to the central actuation shaft, and a valve support disposed at an appropriate distance in the axial direction of the central actuation shaft. The present invention is characterized by comprising a valve body that is seated on or separated from the valve seat surface in accordance with the rotational displacement of the operating center shaft, which is supported in a floating manner by two connecting pins.

(Function) In the present invention, the following effects can be obtained by such means.

That is, since the valve support body and the valve body attached to the tip of the valve support body are connected to each other via a connecting pin in a freely floating manner, the valve body or the valve seat surface may become damaged due to long-term use, for example. Even if the relative relationship between the valve body and the valve seat surface changes from the initial setting due to wear, the valve body can freely follow the changing state of the relative relationship between the valve body and the valve seat surface. , and is securely brought into close contact with the valve seat surface.

Furthermore, since the valve body and the valve support body are connected via two connecting pins arranged at a predetermined interval in the axial direction of the central axis of operation, the plane direction of the valve body and the valve support body is The relative positioning of the exhaust gas inlet and the valve body is easy, and the once set relative position does not shift during use. It is now possible to form an elliptical shape, and when the passage area of the exhaust gas inlet is the same, the distance between the valve body and the operating center axis (i.e., moment arm) can be made shorter.

(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 center casing that 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 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 connected to 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.
That is, a first exhaust gas passage 27 with an oval cross section located on one side of the partition wall 26 and a cross section with a smaller passage area than the first exhaust gas passage 27 located on the other side of the partition wall 26. The circular 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 these 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 is introduced into the scroll portion 21b side of the turbine casing 21 through the first exhaust gas passage 27. During high-speed operation of the engine, both the first exhaust gas inlet 29 and the second exhaust gas inlet 30 are open, and the exhaust gas flows through both the first exhaust gas passage 27 and the second exhaust gas passage 28. From the scroll part 21 of the turbine casing 21
It will be introduced on the b side.

Further, in this case, in this embodiment, the present invention is applied to the end face 21a of the turbine casing 21.
Of these, a substantially elongated annular portion located at the mouth edge of the second exhaust gas inlet 30, including the end surface 26a of the partition wall 26, serves as a valve seat surface 33 for a valve device 6, which will be described later.

In this way, the end face 21 of the turbine casing 21
If part a is 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, the exhaust gas The flow direction of the second exhaust gas inlet 30 intersects the axial direction of the second exhaust gas inlet 30.
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, this is compared to the case where the planar direction of the valve seat surface 33 and the exhaust gas flow direction are substantially parallel. Therefore, the sealing performance on the valve seat surface 33 is good (that is, the valve device 6 described later
When the valve body 61 is seated on the valve seat surface 33, the extending direction of the sealing surface between them is perpendicular to the flow direction of the exhaust gas, and the flow resistance of the exhaust gas leaking along the sealing surface increases accordingly. Therefore, the exhaust gas flow control will be performed more reliably.

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 to occur than in the case of a turbine casing having a structure that does not have the partition wall 26. However, in this embodiment, the present invention is applied as described later, and the valve device 6 is not placed on the turbine casing 21 side. Since it is provided on the exhaust pipe 4 side where thermal deformation is less likely to occur, the complexity of the structure of the turbine casing 21 is minimized even though it is a turbine casing of an exhaust turbocharger equipped with a valve device 6. In addition, the size of the shape 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, etc. connected in a substantially horizontal direction to
and the branch pipe portion 4 while converging the branch pipes 41A, 41B, etc. at the downstream end of the exhaust gas.
1 and a collecting pipe part 41 extending in a direction perpendicular to the branch pipe part 41, and the end surface 4a of the branch pipe type is connected to the engine main body 1.
It is fastened and fixed to the side part of the engine main body 1 in a state where the sides abut, and on the end surface 4b on the collecting pipe part 42 side (i.e., the upper end surface 42a of the collecting pipe part 42),
As shown in FIGS. 3 and 4, the turbine casing 21 of the exhaust turbo supercharger 2 is abutted and fixed via a gasket 3. As shown in FIGS.

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 indicated by a projection line ₁ in FIG. 4 and an imaginary line ₂ in FIG. 5, respectively. As shown, in the state in which the turbine casing 21 is fastened to the end surface 4b of the exhaust pipe 4, in the vertical direction (i.e.
(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 4 in the collecting pipe section 42
3, and a turbine casing 21 consisting of the first exhaust gas passage 27 and the second exhaust gas passage 28.
The side exhaust gas passage is approximately coaxially continuous, and the exhaust gas G flowing in the exhaust pipe 4 from the branch pipe section 41 side to the collecting pipe section 42 side is guided by the continuous section 46. The exhaust gas flows linearly within the collecting pipe section 42 along its axial direction, with almost no flow resistance occurring on the first exhaust gas inlet 29 and second exhaust gas inlet 30 sides of the turbine casing 21. This will allow for smooth implementation.

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 is located inside thereof in a continuous manner with the exhaust gas collecting passage 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 attached to the expanded portion 44 of the exhaust pipe 4 as shown in FIGS. 4 to 7, and is connected to the second exhaust gas inlet 30 of the turbine casing 21.
Particularly in this embodiment, the present invention is applied to make the valve device 6 a swing type valve device as described later.

That is, as shown in FIG. 5, the valve device 6 is connected to one of the pair of side walls of the expanded portion 44 of the exhaust pipe 4 and to the second exhaust gas inlet 30 of the turbine casing 21, which are opposed in the longitudinal direction. The operation of the bearing tube 66, which is provided by penetrating the side wall 47 located on the side opposite to the engine main body 1 in the inner and outer directions (in other words, in the direction parallel to the long axis direction of the second exhaust gas inlet 30) A pair of connecting pins 67 and 68 are connected to a valve support 62 rotatably supporting a central shaft 65 and a valve holding plate 63 formed at a swinging end 62a of the valve support 62 by applying the present invention. The valve body 61 is supported in a freely floating manner through the valve body 61.

The valve body 61 is connected to the valve seat surface 33 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.
The plate is an elliptical plate having a size that can at least close the second exhaust gas inlet 30 and cover the end surface 26a of the partition wall 26 of the turbine casing 21 when the plate is brought into contact with the turbine casing 21. Moreover, a vent hole 71 of an appropriate diameter is formed in the central portion in the longitudinal direction of the valve body 61 and passes through the valve body 61 in its thickness direction.

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 oxidation or cracking of the partition wall 26 may occur as described later. The thermal deterioration phenomenon is suppressed as much as possible, and the flow resistance of exhaust gas is also reduced.

That is, if 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, the frequency at which the end face 26a portion is directly exposed to high-temperature exhaust gas will be reduced. This is significantly reduced compared to a configuration configured to be directly exposed to exhaust gas throughout the entire operating range (note that the rate at which the valve device 6 is closed throughout the entire operating range of the engine is usually approximately 70 to 70%). 80%), 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.
This results in improved durability.

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
This is advantageous in terms of improving supercharging performance, as the weight and size of the pump is promoted, and the flow resistance of exhaust gas when the valve device 6 is in the open state is reduced by the thinner partition wall 26. It is.

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. in the longitudinal direction of the body 61 (i.e.
The fitting shaft portions 67a and 68a are fixed to the valve support 65 at appropriate intervals (in the axial direction of the operation center shaft 65) and protrude toward the upper surface 61a.
The pin receiving hole 72 formed in the valve holding plate 63,
72 so as to be freely movable. Moreover, the above-mentioned fitting shaft portions 67a of the pair of connecting pins 67, 68,
The length of the valve body 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 opening the valve device 6 from its closed state (the state shown in FIG. 6), there is a gap between the valve body 61 and the valve holding plate 63 as shown in FIG. 7 at the beginning of the valve opening operation. A parallel gap 74 communicating with the vent hole 71 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 connected to the vent hole 71.
and are communicated with each other via a 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 supported in a floating manner on the support body 62 and has a vent hole 71 formed in the valve body 61, the valve body 61 and the valve retaining plate are connected at the initial stage of opening of the valve device 6, as shown in FIG. 63 are separated from each other, and the high pressure exhaust gas collection passage 43 and the low pressure second exhaust gas passage 28 are communicated with each other.

Therefore, part of the exhaust gas flows into the second exhaust gas passage 28 side through the vent hole 71, and the pressure difference between the two is reduced as much as possible (in other words, the valve body 61 is opened). direction regulating force is reduced), and it becomes possible to open the valve device 6 smoothly and quickly with a smaller operating force (i.e.,
This facilitates downsizing of the valve operating device 7, which will be described later, and improves the wear resistance of the operating center shaft 65 or bearing shaft 66).

Further, in this case, each pin 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. . For this reason, each pin receiving hole 72, 72 plays an important role in valve function.
This prevents the inner circumferential surface of the valve 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 62, which impairs the function of the valve device 6. be done.

Further, since the valve body 61 and the valve retaining plate 63 are connected to each other in a freely floating manner by applying the present invention, for example, the gasket 3 interposed between the exhaust pipe 4 and the turbine casing 21 may be damaged due to aging. Even if the valve body 61 or the valve seat surface 33 is worn out due to long-term use, the valve body 61 will float and displace to follow the changing state of the relative relationship between them. The adhesion between the valve seat surface 33 and the valve seat surface 33, that is, the sealing performance, is maintained satisfactorily over a long period of time.

Further, in this valve device 6, the present invention is applied to the valve body 61 and the valve retaining plate 63 (i.e.,
Since the valve support body 62) is connected by a pair of connecting pins 67 and 68, relative positioning of the valve body 61 and the valve holding plate 63 in the plane direction is easy, and once the relative positions are set, There is no possibility that it will shift during use (the positioning function for the valve body 61 is ensured). Therefore, it is possible to make the valve body 61 oval instead of circular,
Compared to the case where the valve body 61 is circular, the valve body 61 is
The distance from the center to the operating center axis 65 can be shortened, and as a result, the shape of the valve device 6 as a whole can be made more compact.

Further, the advantage that the positioning of the valve body 61 is easy and the positional deviation does not occur can be obtained by forming the opening shape of the second exhaust gas inlet 30 not in a circle but in an oval shape as described above. , while keeping the relative distance between the second exhaust gas inlet 30 and the operating center width 65 of the valve device 6 as small as possible, and also reducing the opening area of the second exhaust gas inlet 30 as much as possible. As a result, compared to a case where the valve body 61 or the second exhaust gas inlet 30 is circular, the distance between the second exhaust gas inlet 30 and the central axis of operation can be increased. 65, that is, the arm length of the valve support 62, can be made as short as possible to reduce the valve-opening force of the valve device 6 (that is, the valve device 6 can be opened easily and smoothly). operation is realized).

That is, in this embodiment, the valve opening operation of the valve device 6 is improved due to the synergistic effect of shortening the arm length of the valve support 62 and forming the vent hole 71 in the valve body 61 as described above. The power consumption is further reduced.

In this embodiment, as shown in FIGS. 6 and 7, a vent hole 71 formed in the valve body 61 is opened and closed by utilizing the floating function of the valve body 61, and thereby the valve device 6 is opened and closed. 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 connecting pins are used, for example, as shown in FIGS. 8 and 9. 67 and 68 are composed of pins of different lengths, and when the valve device 6 is in the closed state (see FIG. 8), the valve seat surface 3 of the valve body 61
3, and at the beginning of the opening operation (see Fig. 9), the difference in length between the pair of connecting pins 67 and 68 is used to ensure close contact with the valve body 61.
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.

Each member in FIGS. 8 and 9 has the same configuration as each member in FIGS. 6 and 7, and the reference numerals assigned to each member in FIGS. 6 and 7 are the same. Detailed explanation thereof will be omitted by assigning the same reference numerals.

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 is rotated in the B direction, and the valve is in the closed position shown by the solid line in FIG.
In this case, in the open position of the valve device 6, the valve device 6 is housed in the expansion space 45 of the exhaust pipe 4. (In other words, it is located closer to the expanded portion 44 than the projection line 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 so, when the valve device 6 is in the open state, the passage area of the exhaust gas collecting passage 43 of the exhaust pipe 4 is substantially reduced by the valve device 6 positioned at the valve open position. Therefore, the flow resistance of the exhaust gas is reduced as much as possible, and when the valve device 6 is in the closed state, the valve support 62 and the operating center shaft 65 of the valve device 6 are
(Substantially the bearing sleeve 66) prevents the exhaust gas from directly hitting the exposed portion facing the expansion space 45 of the end surface 21a of the turbine casing 21 as much as possible, and the end surface 21a Heat deterioration is suppressed. From this, the durability of the turbine casing 21 is improved.

Further, since the valve device 6 is provided on the exhaust pipe 4 side, where the partition wall 26 is not formed and the structure is relatively simple, and therefore there is less irregular thermal deformation, the structure is relatively complex and the structure is relatively simple, and therefore the valve device 6 has a relatively simple structure and is therefore less prone to irregular thermal deformation. 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 effect of thermal deformation on the operating characteristics of the valve device 6 is smaller, and the operating accuracy of the valve device 6 is maintained at a higher level. It becomes possible to do so.

The valve actuating device 7 opens and closes the valve device 6 according to the operating state of the engine, and moves its actuator 10 forward and backward in response to air pressure that is appropriately controlled to be supplied depending on the operating state of the engine. It is composed of a second actuator 9 having a diaphragm-type pressure responsive mechanism configured to cause displacement, and as shown in FIGS. Installed in a thermally insulated manner. That is, the collecting pipe portion 42 of the exhaust pipe 4
, an exhaust pipe insulator 12 made of a plate bent into a substantially U-shape is attached to the collecting pipe section 42.
The collecting pipe portion 4 is arranged so as to surround the outside of the other three side surfaces excluding the side surface facing the engine main body 1 side.
an insulator mounting part 42b that is fitted from the outside of 2 and formed in a bulge on one side of the collecting pipe part 42; and one side 12a of the actuator insulator 11 that faces the insulator mounting part 42b.
It is fixed by fastening them with a pair of mounting bolts 15, 15.

Furthermore, when installing the exhaust pipe insulator 12, the flat bracket 13 is attached to the tip end 13a of the exhaust pipe insulator 12.
are secured together by the mounting bolts 15, 15 in a state in which they protrude outward from the outer end of the exhaust pipe insulator 12 on the side opposite to the engine main body 1.

Further, the tip portion 13a of the bracket 13 is provided with the second insulator whose outer periphery is covered by the actuator insulator 11 having a substantially airtight container shape.
The actuator 9 is attached to one side surface 11 of the actuator insulator 11 on the actuator 10 side.
a is sandwiched between the tip 13a of the bracket 13 and the front end 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 connected to the actuator insulator 11 and the exhaust pipe insulator 1 with respect to the collecting pipe portion 42 of the exhaust pipe 4.
It will be fixed in a substantially adiabatic manner via the two members No. 2. The operating center shaft 65 of the valve device 6 is connected to the operating element 10 of the second actuator 9 mounted on the exhaust pipe 4 side through link levers 69 and 70. protrudes in the direction of arrow a (see Fig. 1), the valve device 6 rotates in the direction of arrow A (see Fig. 4), and the second exhaust gas inlet 30 is opened. When the actuator 10 moves backward 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 the actuator insulator 11 is attached to the tip 13a of the bracket 13, which is attached together with the exhaust pipe insulator 12 to the exhaust pipe 4 side. The encapsulated second actuator 9 is attached to its end surface 9a.
When the actuator insulator 11 is interposed between the bracket tip 13a and the insulators 11 and 12 are tightened together, the insulators 11, 12
This action prevents radiant heat from being transferred from the exhaust pipe 4 side to the second actuator 9 side as much as possible, and also prevents conductive heat transfer from the exhaust pipe 4 side via the bracket 13 to the actuator insulator 11. The amount of heat transferred to the second actuator 9 side is reduced as much as possible. Furthermore, when the entire circumference of the second actuator 9 is covered with the actuator insulator 11 as described above, the second actuator 9 is protected from collisions with flying stones, adhesion of sludge or rainwater, etc.
Actuator 9 can be protected. For these reasons, the durability of the second actuator 9 is improved.

Furthermore, since the temperature rise of the second actuator 9 is suppressed as much as possible as described above, the material of the diaphragm (not shown) of the second actuator 9 can be made of a low-grade material with relatively poor heat resistance. Therefore, the cost of the second actuator 9 can be reduced accordingly.

Further, the valve device 6 and a second valve device that operates the valve device 6 are provided.
Since both the actuator 9 and the actuator 9 are attached to the exhaust pipe 4 side, even if the exhaust pipe 4 is thermally deformed due to the influence of heat from exhaust gas, the second actuator 9 attached to the exhaust pipe 4 The relative relationship between the actuator 9 and the valve device 6 can be kept substantially constant, and the control accuracy of the valve device 6 can be maintained at a high level at all times. Furthermore, since both the valve device 6 and the second actuator 9 are attached to the exhaust pipe 4, the valve device 6 and the second actuator 9 are
This can be done while the actuator 9 is interlocked with each other, and its operation can be inspected with high precision in either the disassembled or assembled state of the device.
The assembly accuracy and ease of assembly between the second actuator 9 and the second actuator 9 are made good.

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 engine main body 1 side is sent to the collecting pipe section 42 through each branch pipe 41A, 41B, etc. of the exhaust pipe 4.
After that, the exhaust gas passages in the turbine casing 21 of the exhaust turbo supercharger 2, that is, the first exhaust gas passage 27 and the second exhaust gas passage 28, are The exhaust energy is used to drive the turbine wheel, and the compressor wheel prepresses the intake air (intake supercharging).

At this time, the valve device 6
opens and closes to select the exhaust gas introduction form. That is, when the operating state of the engine is in a constant speed operating region where the flow rate of exhaust gas is low, the second actuator 9 moves the valve device 6 to the open position (fourth position).
On the other hand, when the engine operating state is in a high-speed operation region where the flow rate of exhaust gas is high, the second actuator 9 moves the valve device 6 to the open position (FIG. 4, the position shown by the chain line). (position shown).

Therefore, in the low-speed operating range of the engine where the amount of exhaust gas discharged is small, the first exhaust gas passage 2
Since the exhaust gas is introduced into the turbine casing 21 only from 7, the gas flow velocity of the exhaust gas in the turbine casing 21 is sufficiently ensured even though the amount of exhaust gas is small, and the rotation of the turbine wheel is on the high rotation side. This makes it possible to obtain the supercharging effect of the exhaust turbo supercharger 2 from a more constant speed range. Furthermore, in this case, the passage area of the exhaust gas passage is narrower than when 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 operation range of the engine where the amount of exhaust gas discharged is large, both the first exhaust gas passage 27 and the second exhaust gas passage 28 are opened, so a large amount of exhaust gas is transmitted from both to the turbine 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 the exhaust pressure on the engine side is reduced, resulting in good combustion performance. As a result, higher output of the engine will be realized.

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 air intake into the engine, etc., or may be controlled according to the engine speed in an operating region where the engine load is relatively high. However, the control signal and control area are not limited.

(Effects of the Invention) The exhaust turbo supercharging device of the present invention includes a turbine casing in which a plurality of exhaust gas inlets are arranged adjacently in parallel on the end face thereof, and a turbine casing in which exhaust gas is guided to the plurality of exhaust gas inlets. a common exhaust pipe connected to the turbine casing; and an exhaust gas inlet arrangement among the plurality of exhaust gas inlets provided in the exhaust pipe with the exhaust gas inlet side end face of the turbine casing as a valve seat surface. a valve device that opens and closes at least one exhaust gas inlet located at the outermost side in the direction, and the valve device is an exhaust gas inlet that is opened and closed by the valve device among the plurality of exhaust gas inlets. an operating center that is located outside of the exhaust gas inlet arrangement direction in a direction that is parallel to the valve seat surface and orthogonal to the exhaust gas inlet arrangement direction, and is rotated by an appropriate valve operating device; The above valve is supported in a floating manner by a shaft, a valve support attached to the central operating shaft, and two connecting pins that are appropriately spaced from each other in the axial direction of the central operating shaft with respect to the valve support. It is characterized by comprising a valve body that is seated on or separated from the valve seat surface as the central axis of operation is rotated.

Therefore, according to the exhaust turbocharging device of the present invention, the valve support of the valve device and the valve body attached to the tip of the valve device support are connected to each other in a freely floating manner, so that, for example, Even if the valve body or valve seat surface is worn out due to long-term use and the relative relationship between the valve body and the valve seat surface has changed from the initial setting, the distance between the valve body and the valve seat surface may change. It can be freely displaced to follow changes in the relative relationship of That's what you get.

Further, the valve support body and the valve body are connected in a floating manner via two connecting pins arranged at appropriate intervals in the axial direction of the central axis of operation, thereby connecting the valve body and the exhaust inlet. The exhaust gas inlet port and the valve body can be formed into an elliptical shape having a long axis in the axial direction of the operating central axis. Therefore, compared to the case where the valve body is formed into a disk shape, for example, the distance between the valve body and the central axis of operation (i.e.,
By shortening the moment arm), the valve can be opened easily with less operating force, improving operability, and the valve device can be made more compact due to the shorter distance between the valve body and the central axis of operation. This effect can also be obtained.

[Brief explanation of the drawing]

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 axis, 71 ...
...vents.

Claims (1)

[Scope of Claims] 1. A turbine casing having a plurality of exhaust gas inlets arranged adjacent to each other on its end face, and a common turbine casing connected to the turbine casing so as to guide exhaust gas to the plurality of exhaust gas inlets. an exhaust pipe, and at least one of the plurality of exhaust gas inlets provided in the exhaust pipe and located at the outermost side in the exhaust gas inlet arrangement direction of the plurality of exhaust gas inlets with the end surface on the exhaust gas inlet side of the turbine casing as a valve seat surface. a valve device that opens and closes one exhaust gas inlet, and the valve device is arranged in an exhaust gas inlet arrangement direction that is closer to the exhaust gas inlet opened and closed by the valve device among the plurality of exhaust gas inlets. an operating center axis that is arranged on the outside of the valve seat in a direction parallel to the valve seat surface and perpendicular to the exhaust gas inlet arrangement direction, and is rotated by an appropriate valve operating device; The valve support is floatingly supported by an attached valve support and two connecting pins arranged at an appropriate distance from each other in the axial direction of the operation center shaft with respect to the valve support, and rotates with the rotational displacement of the operation center shaft. An exhaust turbo supercharging device comprising: a valve body that is seated on or separated from the valve seat surface;