JPS63306233A - Turbocharger - Google Patents

Abstract

PURPOSE:To make a flow running out of a high speed nozzle part at an engine high speed driving area to be hard to collide with that running out of a low speed nozzle part and thereby reduce a collision loss by making the nozzle part of a high speed scroll chamber so as to rise in the radial direction. CONSTITUTION:At a high engine speed area, exhaust gas out of an engine flows into a turbine wheel 4 by two low-high speed scroll chambers 2a and 2b partitioned off by a partition wall 1 and their nozzle parts 3a and 3b. A flow out of the low speed nozzle part 3a installed in opposition to a turbine wheel inlet part 4a smoothly flows into the turbine wheel 4. In a flow out of the high speed nozzle part 3b as well, since a nozzle part casing wall surface 6 is made to rise in the radial direction of the turbine wheel 4, making a nozzle part central axis come nearer to the radial direction, such a possibility that the flow out of the nozzle part 3a might collide with that out of the nozzle part 3b is prevented from occurring.

Description

[Detailed Description of the Invention] [Field of Industrial Application] The present invention relates to a turbocharger in which a turbine and a compressor are arranged on the same axis, and is a two-channel type (channel switching type) particularly suitable for passenger car engines. The present invention relates to a turbocharger equipped with a turbine.

[Conventional technology]

The conventional two-channel variable displacement turbo supercharger is disclosed in U.S. Patent No. 3.
, 557,549, two scroll chambers divided into two by a partition are both provided above the inlet of the impeller of the turbine, and the tip 1' of the partition is located above the impeller of the turbine. It was located almost in the center of the entrance area.

Furthermore, in the device disclosed in Japanese Patent Application Laid-open No. 61-46420, of the two scroll chambers partitioned by a partition wall, the nozzle portion of one of the low-speed scroll chambers is provided opposite to the inlet portion of the impeller of the turbine, and The nozzle portion of the high-speed scroll chamber was provided at a position in the outer diameter direction on the outlet side of the impeller of the turbine, and was provided on the side surface of the inlet portion of the impeller of the turbine. Means is provided for controlling the flow rate of the high speed scroll chamber in accordance with the operating conditions of the engine.

Furthermore, in the device described in Japanese Utility Model Application Publication No. 61-33922, in order to reduce the thermal stress applied to the turbine casing under high temperatures, the tip of the partition wall 1 is made of a material that has better heat resistance than the material of the turbine casing 5. A member having a low coefficient of thermal expansion is provided close to the inlet of the impeller of the turbine.

[Problem that the invention seeks to solve]

In U.S. Pat. No. 3,557,549, the nozzle portions of the two scroll chambers separated by the partition wall 1 are provided above the impeller inlet portion of the turbine.
The ratio of the flow rate between when exhaust gas from the engine flows into the turbine from one scroll chamber (engine low-speed operating range) and when it flows into the turbine from both scroll chambers (engine high-speed operating range) (variable capacity range) is at most twice as large, and the variable displacement range is small.Furthermore, since the partition wall is located almost at the center of the turbine impeller inlet, exhaust gas in the low-speed engine operating range is diverted from the low-speed scroll chamber to the turbine. When the exhaust gas flows into the impeller inlet, the width of the impeller inlet of the turbine through which the exhaust gas can effectively flow is only half, resulting in a biased inflow state, which poses a problem of significantly reducing the efficiency of the turbine.

Furthermore, in JP-A No. 61-46420, in order to improve turbine efficiency in the low-speed engine operating range, the nozzle part of the low-speed scroll chamber used in the low-speed engine operating range is opposed to the inlet part of the impeller of the turbine. The nozzle width of the nozzle portion of the scroll chamber is increased. On the other hand, the other high-speed scroll chamber used in the high-speed engine operating range and its nozzle part are provided almost on the side of the turbine impeller inlet, and the structure allows for a large area of the high-speed scroll chamber used in the high-speed engine operating range. The aim is to expand the variable capacity range.

However, when this high-speed scroll chamber and its nozzle section are provided almost on the side of the impeller inlet of the turbine, in the engine high-speed operating range, the low-speed scroll chamber used in the engine low-speed operating range is There has been a problem in that the flow flowing out from the nozzle section of the high-speed scroll chamber collides with the flow flowing into the impeller of the turbine from the nozzle section of the scroll chamber, and the turbine efficiency is significantly reduced due to the collision loss.

Furthermore, in U.S. Pat. No. 61-33922, as in the previous U.S. Pat. No. 3,557,549, the nozzle portions of the two scroll chambers partitioned by a partition are provided above the inlet portion of the impeller of the turbine. The variable capacity range cannot be wide, and the low coefficient of thermal expansion member provided at the tip of the partition wall can be installed close to the turbine impeller inlet to reduce the internal pressure of the two scroll chambers in the engine's low-speed operating range. , a part of the exhaust gas flowing out from the nozzle part of one scroll chamber is prevented from leaking into the other scroll chamber through the gap between the member with a low coefficient of thermal expansion and the impeller inlet part of the turbine. There is. However, no particular consideration was given to the shape of the nozzle, which has a large effect on turbine efficiency.

The purpose of the present invention is to avoid increasing the outer diameter in particular.
To obtain a turbo supercharger that can obtain high turbine efficiency from a low speed rotation range to a high speed rotation range of an engine.

[Means for solving problems]

In order to achieve the above object, the first invention of the present application mounts a turbine and a compressor on the same rotating shaft, and partitions the inside of the scroll for guiding exhaust gas from the engine to the impeller of the turbine into a low-speed scroll chamber. In a turbocharger divided into a high-speed scroll chamber, the low-speed scroll chamber is used from a low-speed rotation range to a high-speed rotation range of the engine, and is located at a position substantially opposite to the inlet of the turbine impeller. The high-speed scroll chamber is used in a high-speed rotation range of the engine, and is provided so as to extend from the outlet of the turbine impeller to a position in the outer radial direction in the exit direction, and is located further in the meridian direction than the low-speed scroll chamber. The nozzle portions of the low-speed scroll chamber are arranged across half or more of the width of the inlet portion of the turbine impeller, and the nozzle portions of the low-speed scroll chamber have a large cross-sectional area with respect to the rotation axis direction of the casing side wall surface of the nozzle portion of the high-speed scroll chamber. The nozzle part is formed by rising in the radial direction so that the rising angle is in the range of 30' to 70°, and the peripheral part of the high-speed scroll chamber connected to the nozzle part of the high-speed scroll chamber is formed in the axial direction of the rotation axis of the impeller. The turbocharger is formed parallel to the

Further, a second invention of the present application is such that a turbine and a compressor are mounted on the same rotating shaft, and the inside of the scroll for guiding exhaust gas from the engine to the impeller of the turbine is divided into a low-speed scroll chamber and a high-speed scroll chamber by a partition wall. In the turbo supercharger, the low-speed scroll chamber is used from a low-speed rotation range to a high-speed rotation range of the engine, and is disposed at a position substantially facing the inlet of the turbine impeller, and the low-speed scroll chamber The chamber is used in a high-speed rotation range of the engine, is provided to extend from the outlet of the turbine impeller to an outer radial position in the exit direction, and has a larger meridional cross-sectional area than the low-speed scroll chamber. The nozzle portion of the low-speed scroll chamber is disposed over half or more of the width of the inlet portion of the turbine impeller, and the rising angle of the casing side wall surface of the nozzle portion of the high-speed scroll chamber with respect to the rotational axis direction is 30°.
The nozzle section is formed by standing up in the radial direction so that the nozzle section is in the range of 70 degrees, and the radial height of the high speed scroll chamber periphery connected to the nozzle section of the high speed scroll chamber is The turbo supercharger is formed to have a section that increases until the end of the turbocharger.

Furthermore, the third invention of the present application is characterized in that a turbine and a compressor are mounted on the same rotating shaft, and the inside of the scroll for guiding exhaust gas from the engine to the impeller of the turbine is divided into a low-speed scroll chamber and a high-speed scroll chamber by a partition wall. In the turbocharger made by
The low-speed scroll chamber is used from a low-speed rotation range to a high-speed rotation range of the engine, and is disposed at a position substantially facing the inlet of the turbine impeller, and the high-speed scroll chamber is used in a high-speed rotation range of the engine. A nozzle of the low-speed scroll chamber is used, and is provided extending to an outer radial position in the exit direction from the outlet of the turbine impeller and has a larger meridional cross-sectional area than the low-speed scroll chamber, and the nozzle of the low-speed scroll chamber The part is disposed over half or more of the width of the inlet part of the turbine impeller, and the tip part of the partition that divides the inside of the scroll into a low-speed scroll chamber and a high-speed scroll chamber is located close to and faces the inlet part of the turbine impeller. , the side surface of the high-speed scroll chamber nozzle part near the tip of the partition is formed into an inclined surface facing near the center of the high-speed scroll chamber, and the width of the surface facing the turbine impeller at the tip of the partition is the same as that of the turbine. 10 to 20 of the impeller inlet width
% range.

[Effect]

According to the first and second inventions of the present application, the nozzle portion of the high-speed scroll chamber is raised in the radial direction,
Therefore, the direction of the flow that has flowed out of the nozzle portion approaches the radial direction of the turbine impeller, making it easier to flow into the turbine impeller. As a result, in a high-speed engine operating range, the flow flowing out from the high-speed nozzle portion is less likely to collide with the flow flowing out from the nozzle portion of the low-speed scroll chamber, and collision loss can also be reduced. Moreover, according to the present invention, although the nozzle portion of the high-speed scroll chamber is raised to approach the radial direction of the turbine impeller, the peripheral portion of the high-speed scroll chamber is made parallel to the axial direction of the rotating shaft. By making the shape concave toward the rotating shaft, the meridional cross-sectional area of the high-speed scroll chamber can be increased without increasing the outer diameter of the turbocharger, and the nozzle of the low-speed scroll chamber can be connected to the turbine impeller. By arranging it over half or more of the width of the inlet portion of the engine, high turbine efficiency can be obtained from the low speed rotation range to the high speed rotation range of the engine.

Further, in the third invention of the present application, the side surface of the high speed scroll chamber nozzle near the tip of the partition wall dividing the inside of the scroll is formed into an inclined surface facing toward the center of the high speed scroll chamber. The high-speed scroll chamber nozzle part is raised in the radial direction of the impeller, and
The width of the surface facing the turbine impeller at the tip of the partition wall is set in a range of 5 to 25% of the width of the impeller to prevent the flows flowing out from the high-speed scroll chamber nozzle section and the low-speed scroll chamber nozzle section from colliding. , above No. 1. The same effect as the second invention, that is, the flow can be made easier to flow into the impeller of the turbine, and the collision loss of the flow from both scroll chambers can be significantly reduced, and the flow is high from the low speed rotation range to the high speed operation range of the engine. Turbine efficiency can be obtained.

〔Example〕

Hereinafter, specific embodiments of the present invention will be described based on the drawings.

FIG. 26 shows the overall structure of a turbocharger according to the present invention. As shown in FIG. A compressor impeller 14 that sucks in, compresses, and sends it to the engine is attached to the same rotating shaft 22. Between the turbine impeller 4 and the compressor impeller 14, bearings 20a and 20b for supporting the rotating shaft 22 are provided in the center member 16. The center member 16 has an oil inlet hole 17 that guides lubricating oil to the bearing parts 20a and '20b.
An oil outlet hole 18 is provided for discharging the lubricating oil that has lubricated the bearing parts 20a and 20b.

The turbine casing 5 has a fastening member 19 and a connecting member 19'.
is fixed to the center member 16 by.

As is clear from the figure, of the two scroll chambers 2a and 2b formed by the partition wall 1, the low-speed scroll 2a, which is used in the low-speed rotation range of the engine, is extended toward the compressor impeller 14 side to increase its meridional cross-sectional area. I can't. That is, since the center member 16 is provided with an oil inlet hole 17 and an oil outlet hole 18, and the casing 5 is provided with a fastening member 19, the turbine casing 5 cannot be extended toward the compressor.

In a low-speed engine operating range, exhaust gas A from the engine flows into the turbine impeller 4 through a low-speed scroll chamber inlet 2a' that communicates with the low-speed scroll chamber 2a, which is always open. Further, when the flow rate of exhaust gas from the engine is large in the engine high speed operating range, the flow rate control valve 21 is opened, and the exhaust gas A from the engine is passed through the high speed scroll which communicates with the low speed scroll chamber 2a and the high speed scroll chamber inlet 2b'. room 2b
It is designed to flow into the turbine impeller 4 from there.

The structure of the turbine section, which is a characteristic part of the present invention, will be explained below for each embodiment.

Parts given the same reference numerals in each episode indicate the same or corresponding parts.

A first embodiment of the present invention will be described with reference to FIG.

The turbine and the compressor are fixedly arranged on the same rotating shaft, and the inside of the scroll of the turbine is divided by a partition wall 1 into two scroll chambers 2'a and 2b. One scroll chamber 2a divided by the partition wall 1 is always open, and this low-speed scroll chamber 2a is connected to the turbine impeller 4.
The nozzle portion 3a is provided to face the impeller inlet portion 4a. The high-speed scroll chamber 2b is disposed at a position in the outer radial direction on the outlet side of the turbine impeller 4, and the low-speed scroll chamber 2b
It has a larger calf cross-sectional area than a, and is used in the high-speed operating range of the engine.

The nozzle part 3b of this high-speed scroll chamber 2b is arranged almost on the side of the impeller inlet part 4a of the turbine.
In the shape b, the casing wall surface 6 facing the partition wall 1 is raised so as to approach the turbine impeller 4 in the radial direction, and the casing wall surface of the inner circumferential portion 7 of the high-speed scroll chamber 2b connected to the nozzle portion 3b is aligned with the rotating shaft 22. The radial height of the high-speed scroll chamber casing wall surface up to the inlet of the nozzle portion 3b is configured to be parallel to the axial direction of the high-speed scroll chamber (see FIG. 1). By configuring the high-speed scroll chamber 2b in this way, the calf cross-sectional area of the high-speed scroll chamber 2b can be made large, even though the nozzle portion 3b is configured to rise in the radial direction. The effect is obtained that the height of the casing 5 in the radial direction does not become large.

Next, the operation will be explained with reference to FIG. In the high-speed rotation range of the engine, exhaust gas A from the engine is divided into two scroll chambers 2a and 2b separated by a partition wall 1, and
Those nozzle parts 3a.

3b and flows into the impeller 4 of the turbine. At this time,
A flow 3a' from a nozzle portion 3a provided opposite to the turbine impeller inlet portion 4a smoothly flows into the impeller 4 of the turbine. In addition, the flow 3b' from the nozzle part 3b also raises the nozzle part casing wall surface 6 in the radial direction of the turbine impeller 4 and approaches the nozzle part center axis in the radial direction. 3b flow 3
b' flows into the turbine impeller 4 from the radial direction, preventing it from colliding with the flow 3a' flowing out from the nozzle part 3a, and preventing a drop in efficiency due to collision loss, resulting in a significant improvement in turbine efficiency. It can be achieved. The effect of the present invention is shown in FIG. 25, which shows the turbine efficiency of a turbocharger compared with that of a conventional (invention disclosed in Japanese Patent Application Laid-Open No. 61-46420) (dotted line 31).

The efficiency of the embodiment shown in FIG. 1 is greatly improved as shown by the solid line 32.

In FIG. 1, θ is the rising angle of the nozzle part casing side wall surface 6 with respect to the rotational axis direction, and in this embodiment, this angle θ is set to 45°, but it may vary from 30° to 70°.
It can be arbitrarily selected within a range of about 100°. This is because if the angle θ is increased, the flow into the impeller becomes smoother, but the width of the nozzle portion cannot be increased.

Further, in the figure, 6' is the partition side wall surface of the nozzle part 36, and 7 is the partition wall surface of the nozzle part 36.
' is the outer periphery of the high-speed scroll chamber 2b.

FIG. 3 shows a second embodiment of the present invention. In this embodiment, the tip of the partition wall 1 that divides the inside of the scroll into a low-speed scroll chamber 2a and a high-speed scroll chamber 2b has a structure as shown in the figure. An inclined surface 8 is formed. That is, the tip of the partition wall 1 is brought close to the inlet section 4a of the turbine impeller 4, and the tip of the tip on the high speed scroll chamber nozzle section is made to be approximately parallel or close to parallel to the casing side wall surface 6 of the nozzle section. An inclined surface 8 is formed on the surface.

The other configurations are the same as the embodiment shown in FIG. 1 above.

According to this embodiment, the nozzle outlet width of the high-speed scroll chamber nozzle portion 3b can be increased, and the overall efficiency is improved. Further, according to this embodiment, by providing the inclined surface 8, the center axis of the nozzle portion 3b can be raised more in the radial direction of the impeller. As a result, as shown in FIG. 4, the flow 3b' of the exhaust gas flowing into the turbine impeller 4 from the high-speed scroll chamber 2b becomes more radial, and the flow into the turbine impeller 4 becomes smoother. The turbine efficiency according to the example is further improved over that of FIG. 1, as shown by thick solid line 33 in FIG.

FIG. 5 shows a third embodiment of the present invention, in which the partition wall 1 that divides the inside of the scroll into a low-speed scroll chamber 2a and a high-speed scroll chamber 2b is constructed from a separate member from the turbine casing 5. This is different from the second embodiment, and the other configurations are the same as the second embodiment. According to this embodiment, since the partition wall 1 can be constructed from a separate member such as a steel plate, it is not only possible to make the partition wall 1 thinner than when it is integrally formed by casting or the like, but also to facilitate high-precision machining. The gap between the tip portion and the turbine impeller inlet portion 4a can be made smaller, and the efficiency is improved to the extent that fluid leakage from this gap can be reduced.

FIG. 6 shows a fourth embodiment of the present invention. In this embodiment, a side plate 9 is attached to the tip 1' of the partition wall 1, and one end surface of this side plate 9 is connected to the inlet 4a of the turbine impeller 4. In addition to closely facing each other, an inclined surface 8 is formed so that the side of the high-speed scroll chamber nozzle section 3b near the tip of the side plate 9 is approximately parallel or nearly parallel to the casing side wall surface 6 of the nozzle section 3b. be.

Further, in this embodiment, the nozzle portion casing side wall surface 6 is not flat but slightly rounded. In this case, the angle θ is defined as the average angle of the wall surface 6 from the center to the tip of the nozzle portion.

The other configurations are the same as those of the embodiment shown in FIGS. 1 to 5, and according to this embodiment, the same effects as in the embodiment shown in FIG. 5 can be obtained.

FIG. 7 shows a fifth embodiment of the present invention.

In this embodiment, the nozzle portion 3b of the high-speed scroll chamber 2b
The high-speed scroll chamber peripheral portion 7 connected to the nozzle portion 3b is formed so as to have a section in which the height in the radial direction increases until reaching the wall surface 6 of the nozzle portion 3b. The other configurations are the same as the embodiment shown in FIG. 1. According to this embodiment, the same effects as the embodiment shown in FIG. Since the meridional cross-sectional area of the chamber 2b can be made larger, the effect that the variable capacity range of the turbocharger can be made larger can be obtained.

FIG. 8 shows a sixth embodiment of the present invention. In this embodiment, a tip 1' of a partition wall 1 that divides the inside of the scroll into a low-speed scroll chamber 2a and a high-speed scroll chamber 2b is shown.
In this case, an inclined surface 8 as shown in the figure is formed. That is, the tip of the partition wall 1 is connected to the inlet portion 4a of the turbine impeller 4.
An inclined surface 8 is formed so that the tip end thereof on the high speed scroll chamber nozzle section side is substantially parallel or nearly parallel to the casing side wall surface 6 of the nozzle section. The other configurations are the same as the embodiment shown in FIG. 7 above. According to this embodiment, the high speed scroll chamber nozzle section 3
The width of the nozzle exit b can be increased, and the separation ratio thereof is improved. Further, according to this embodiment, by providing the inclined surface 8, the nozzle portion 3b can be raised more in the radial direction of the impeller. As a result, the flow of exhaust gas flowing into the turbine impeller 4 from the high-speed scroll chamber 2b becomes more radial, and the flow into the turbine impeller 4 becomes smoother.The turbine efficiency according to this embodiment is as shown in FIG. This can be further improved.

FIG. 9 shows a seventh embodiment of the present invention, in which the inside of the scroll is divided into a low-speed scroll chamber 2b, a high-speed scroll chamber 2b, and a roll chamber 2b.
This embodiment differs from the sixth embodiment in that the partition wall 1 that is divided into two parts is made of a separate member from the turbine casing 5, and the other configurations are the same as the sixth embodiment. According to the above, since the partition wall 1 can be constructed from a separate member such as a steel plate, the partition wall 1 can not only be made thinner than when it is integrally formed by casting etc., but also can be easily processed with high precision. The gap between ' and the turbine impeller inlet portion 4a can be made smaller, and the efficiency is improved by reducing the leakage flow of fluid from this gap.

FIG. 10 shows an eighth embodiment of the present invention. In this embodiment, a side plate 9 is attached to the tip 1' of the partition wall 1, and one end surface of this side plate 9 is connected to the inlet 4a of the turbine impeller 4. In addition to closely facing each other, an inclined surface 8 is formed so that the side of the high-speed scroll chamber nozzle section 3b near the tip of the side plate 9 is approximately parallel or nearly parallel to the casing side wall surface 6 of the nozzle section 3b. be.

The other configurations are the same as those of the embodiment shown in FIGS. 7 to 9, and according to this embodiment, the same effects as the embodiment shown in FIG. 9 can be obtained.

FIG. 11 shows a ninth embodiment of the present invention. In this embodiment, a distal end 1' of a partition wall 1 that divides the inside of the scroll into a low-speed scroll chamber 2a and a high-speed scroll chamber 2b is located close to and opposed to an inlet section 4a of a turbine impeller 4. Further, the side surface of the nozzle portion 3b of the high-speed scroll chamber 2b near the tip 1' of the partition wall 1 is formed into an inclined surface 8 facing toward the center C of the high-speed scroll chamber 2b. Further, the width Wl of the surface facing the turbine impeller 4 at the tip end 1' of the partition wall 1 is set in a range of 5 to 25% of the width W2 of the inlet portion of the turbine impeller 4. In addition,
In this embodiment, the inner peripheral portion 7 of the high-speed scroll chamber 2b is configured such that its radial height decreases as it approaches the nozzle portion 3b.

According to this embodiment, by forming the inclined surface 8, the width of the high-speed scroll chamber nozzle portion 3b can be increased, and the casing side wall surface 6 of the nozzle portion 3b is aligned in the radial direction of the turbine impeller 4. Since the exhaust gas can be raised closer to each other, the flow of exhaust gas from the nozzle part 3b to the impeller 4 is smooth, and since it flows in from the radial direction, it does not collide with the flow flowing out from the nozzle part 3a, reducing collision loss. Therefore, turbine efficiency can be improved. Furthermore, in this embodiment, since the width Wl of the partition wall tip is in the range of 5 to 25% of the inlet width W2 of the turbine impeller, the flow from the high-speed scroll chamber 2a is between the partition wall tip and the impeller. The amount of exhaust gas leaking from the gap can be significantly reduced, and a sufficient width for the exhaust gas to flow into the impeller 4 from the high-speed scroll chamber nozzle portion 3a can be secured, so that the turbine efficiency can be further improved.

12 and 13 are diagrams showing the relationship between the width of the partition wall tip face and the turbine efficiency in the embodiment shown in FIG. Figure 13 shows the turbine efficiency in the high speed engine rotation range (when both low speed and high speed scroll chambers are used). Further, in both figures, the horizontal axis represents the width W1 of the partition wall tip surface relative to the inlet portion MW2 of the turbine impeller in %. From these figures, by setting the tip face width in the range of 5 to 25%, high turbine efficiency can be obtained at both low speed and high speed, preferably in the range of 6 to 20%, especially around 7 to 8%. The highest efficiency was obtained.

FIG. 14 shows a tenth embodiment of the present invention, in which the partition u, 1 is started separately from the turbine casing 5, and the tip part 1 of the partition wall 1 is separated from the turbine casing 5.
', the inclined surface 8 is formed so that the nozzle width of the nozzle part 3b becomes wider.
Furthermore, the width Wz of the front end face of the partition wall 1 is set to be in the range of 5% to 25% of the width W1 of the turbine impeller inlet part. The rest of the structure is the same as the embodiment shown in FIG. 11 above.

FIG. 15 shows an eleventh embodiment of the present invention. In this embodiment, a side plate 9 is attached to the tip 1' of the partition wall 1, and the tip of the side plate 9 has an inclined surface so that the nozzle width of the nozzle part 3b becomes wider. 8, and the width W2 of the front end face of the partition wall is set in a range of 5 to 25% of the width Wl of the turbine impeller inlet part. The rest of the structure is the same as the embodiment shown in FIG. 11 or FIG. 14 above.

According to the embodiments shown in FIGS. 14 and 15 above, the 11th
The same effects as the embodiment shown in the figure can be obtained.

In particular, according to the embodiments shown in FIGS. 14 and 15, the partition wall 1 is constructed as a separate member or the side plate 9 is provided at the tip of the partition, so the tip of the partition can be machined with high precision. Since the gap between the partition wall tip and the impeller can be made smaller, leakage flow from this gap can be further reduced.

FIG. 16 shows a twelfth embodiment of the present invention, and this embodiment is similar to the embodiment shown in FIG.
The height in the radial direction of the inner circumferential portion 7 of the high-speed scroll chamber decreases as it approaches the nozzle portion 3b, but the difference from the embodiment shown in FIG. This is a big change.

17 and 18 are the 13th and 14th sections of the present invention, respectively.
This embodiment differs from the embodiment shown in Fig. 16 in that the partition wall 1 is made into a separate member (Fig. 17), or the side plate 9 is provided at the tip 1' of the partition wall 1 (Fig. 18). This is the point.

FIG. 19 shows a fifteenth embodiment of the present invention, in which the shape of the high-speed scroll chamber periphery 7 is the same as that of the embodiment shown in FIG. 1, and the shape of the tip 1' of the partition wall 1 is According to this embodiment, which is the same as the embodiment shown in FIG. 11, the effects of the embodiment shown in FIG. 1 and the embodiment shown in FIG. 11 can be obtained.

Figures 20 and 21 are the 16th and 17th figures of the present invention, respectively.
This embodiment differs from the embodiment shown in FIG. 19 in that the partition wall 1 is made into a separate member (FIG. 20), or the partition wall tip 1'
The point is that a side plate 9 is provided at the top (Fig. 21).

FIG. 22 shows an 18th embodiment of the present invention, in which the shape of the high-speed scroll chamber periphery 7 is the same as that of the embodiment shown in FIG. This is the same as the embodiment shown in FIG. According to this embodiment, the effects of both the embodiments shown in FIG. 7 and FIG. 11 can be obtained.

23 and 24 are the 19th and 2nd cases of this example, respectively.
0 embodiment, the difference from the embodiment shown in FIG. 22 is that the partition wall 1
is a separate member (Fig. 23), or the partition wall tip 1
' (Fig. 24).

According to the present embodiment, the shape of the nozzle portion of the high-speed scroll chamber is designed so that the flow flowing out of the nozzle portion of the high-speed scroll chamber used in the high-speed engine rotation range can flow into the impeller inlet of the turbine from the radial direction. As a result, in the high-speed engine operating range, the collision loss caused by the flow flowing out from the nozzle section of the high-speed scroll chamber colliding with the flow flowing out from the nozzle section of the low-speed scroll chamber can be reduced, which has the effect of significantly improving turbine efficiency. There is.

【Effect of the invention〕

According to the present invention, the meridional cross-sectional area of the high-speed scroll chamber can be increased without increasing the outer diameter of the turbocharger, and the flow from the high-speed scroll chamber to the turbine impeller and the flow from the low-speed scroll chamber can be increased. As a result, it is possible to obtain a turbocharger having high turbine efficiency over a wide range from the low speed rotation range to the high speed rotation range of the engine.

[Brief explanation of the drawing]

1 and 2 are longitudinal cross-sectional views of essential parts showing a first embodiment of the present invention, FIGS. 3 and 4 are longitudinal cross-sectional views of essential parts showing a second embodiment of the present invention, and FIG. 11 are longitudinal cross-sectional views of main parts showing third to ninth embodiments of the present invention, and FIGS. 12 and 13 show the width of the partition wall tip surface and the turbine efficiency in the embodiment of FIG. 11, respectively. 14 to 24 are longitudinal cross-sectional views of essential parts showing the tenth to twentieth embodiments of the present invention, respectively, and FIG. 25 is a diagram showing the effects of the present invention in comparison with the prior art. 26 is a diagram showing the relationship between turbine speed ratio and turbine efficiency, and FIG. 26 is a longitudinal sectional view showing the overall configuration of the turbocharger. 1... Partition wall, 2a... Low speed scroll chamber, 2b...
・High-speed scroll chamber, 3a... Nozzle part, 3b...
Nozzle part, 4... Turbine impeller, 4a... Turbine impeller inlet part, 5... Turbine casing, 6...
・Nozzle part casing side wall surface, 7... High-speed scroll chamber periphery, 8... Inclined surface, 9... Side plate, Wl...
Partition wall tip surface width, Wz...Turbine impeller inlet width,
C... Center of high-speed scrolling room. Agent Patent Attorney Katsuma Ogawa -゛2nd Speech 3rd - Fast 4 Speech 6 Prisoner 7th Speech δ Speech 9th Speech! 2 Mouth tip width jet Otsu

Claims (1)

[Claims] 1. A turbine and a compressor are installed on the same rotating shaft,
In a turbo supercharger in which the interior of the scroll for guiding exhaust gas from the engine to the impeller of the turbine is divided by a partition into a low-speed scroll chamber and a high-speed scroll chamber, the low-speed scroll chamber is located in a low-speed rotation range of the engine. The high-speed scroll chamber is used in the high-speed rotation range of the engine and is disposed at a position substantially facing the inlet of the turbine impeller, and the high-speed scroll chamber is used in the high-speed rotation range of the engine and is disposed at a position substantially facing the inlet of the turbine impeller. The nozzle portion of the low speed scroll chamber is provided extending to an outer radial position in the exit direction from the outlet of the wheel, and has a larger meridional cross-sectional area than the low speed scroll chamber, and the nozzle portion of the low speed scroll chamber has a width equal to the width of the inlet portion of the turbine impeller. The nozzle portion of the high-speed scroll chamber is formed by rising in the radial direction so that the rising angle of the casing side wall surface in the nozzle portion of the high-speed scroll chamber with respect to the rotational axis direction is in the range of 30° to 70°. death,
A turbo supercharger in which a peripheral portion of the high-speed scroll chamber connected to the nozzle portion of the high-speed scroll chamber is formed to be parallel to the axial direction of the rotation shaft of the impeller. 2. In claim 1, a side plate is attached near the tip of the partition wall that divides the inside of the scroll into a low-speed scroll chamber and a high-speed scroll chamber, and one end surface of this side plate is placed close to the inlet of the turbine impeller. A turbo supercharger in which an inclined surface is formed so that the high-speed scroll chamber nozzle section side near the tip of the side plate is substantially parallel or nearly parallel to the central axis of the nozzle section. 3. In claim 1, the partition wall that divides the inside of the scroll into a low-speed scroll chamber and a high-speed scroll chamber is constructed from a separate member from the turbine casing, and the tip of the partition wall is located close to the inlet of the turbine impeller. A turbo supercharger in which a high-speed scroll chamber nozzle section side near the tip of the partition wall is formed with an inclined surface so as to be substantially parallel or nearly parallel to the central axis of the nozzle section. 4. In claim 2 or 3, the width of the surface facing the turbine impeller at the tip of the partition wall or the tip of the side plate is 10 to 20% of the inlet width of the turbine blade.
A range of turbochargers. 5. Install the turbine and compressor on the same rotating shaft,
In a turbo supercharger in which the interior of the scroll for guiding exhaust gas from the engine to the impeller of the turbine is divided by a partition into a low-speed scroll chamber and a high-speed scroll chamber, the low-speed scroll chamber is located in a low-speed rotation range of the engine. The high-speed scroll chamber is used in the high-speed rotation range of the engine and is disposed at a position substantially facing the inlet of the turbine impeller, and the high-speed scroll chamber is used in the high-speed rotation range of the engine and is disposed at a position substantially facing the inlet of the turbine impeller. The nozzle portion of the low-speed scroll chamber is provided extending to an outer diameter direction position in the direction of the large mouth than the outlet of the wheel, and has a larger meridional cross-sectional area than the low-speed scroll chamber, and the nozzle portion of the low-speed scroll chamber has a width equal to the width of the inlet portion of the turbine impeller. The nozzle portion of the high-speed scroll chamber is formed by rising in the radial direction so that the rising angle of the casing side wall surface in the nozzle portion of the high-speed scroll chamber with respect to the rotational axis direction is in the range of 30° to 70°. death,
A turbo supercharger in which a peripheral portion of the high-speed scroll chamber connected to a nozzle portion of the high-speed scroll chamber is formed to have a section in which the radial height thereof increases until reaching the nozzle portion. 6. In claim 5, a side plate is attached near the tip of the partition wall that divides the inside of the scroll into a low-speed scroll chamber and a high-speed scroll chamber, and one end surface of this side plate is placed close to the inlet of the turbine impeller. A turbo supercharger in which an inclined surface is formed so that the high-speed scroll chamber nozzle section side near the tip of the side plate is substantially parallel or nearly parallel to the central axis of the nozzle section. 7. In claim 5, the partition wall that divides the inside of the scroll into a low-speed scroll chamber and a high-speed scroll chamber is constructed from a separate member from the turbine casing, and the tip of the partition wall is located close to the inlet of the turbine impeller. A turbo supercharger in which a high-speed scroll chamber nozzle section side near the tip of the partition wall is formed with an inclined surface so as to be substantially parallel or nearly parallel to the central axis of the nozzle section. 8. In claim 6 or 7, the width of the surface facing the turbine impeller at the tip of the partition wall or the tip of the side plate is 10 to 20% of the inlet width of the turbine blade.
A range of turbochargers. 9. Install the turbine and compressor on the same rotating shaft,
In a turbo supercharger in which the interior of the scroll for guiding exhaust gas from the engine to the impeller of the turbine is divided by a partition into a low-speed scroll chamber and a high-speed scroll chamber, the low-speed scroll chamber is located in a low-speed rotation range of the engine. The high-speed scroll chamber is used in the high-speed rotation range of the engine and is disposed at a position substantially facing the inlet of the turbine impeller, and the high-speed scroll chamber is used in the high-speed rotation range of the engine and is disposed at a position substantially facing the inlet of the turbine impeller. The nozzle portion of the low speed scroll chamber is provided extending to an outer radial position in the exit direction from the outlet of the wheel, and has a larger meridional cross-sectional area than the low speed scroll chamber, and the nozzle portion of the low speed scroll chamber has a width equal to the width of the inlet portion of the turbine impeller. The high-speed scroll near the front end of the partition wall is disposed over half or more of the partition wall and divides the inside of the scroll into a low-speed scroll chamber and a high-speed scroll chamber, and the top end of the partition wall is arranged to face the inlet of the turbine impeller in close proximity to the inlet of the turbine impeller. The side surface of the chamber nozzle part is formed into an inclined surface facing near the center of the high-speed scroll chamber, and the width of the surface facing the turbine impeller at the tip of the partition wall is 5 to 2 times the width of the inlet part of the turbine impeller.
A turbo supercharger characterized by a range of 5%. 10. In claim 9, a side plate is attached near the tip of the partition wall that divides the inside of the scroll into a low-speed scroll chamber and a high-speed scroll chamber, and one end surface of this side plate is placed close to the inlet of the turbine impeller. Turbo supercharger facing each other. 11. The turbocharger according to claim 9, wherein the partition wall that divides the inside of the scroll into a low-speed scroll chamber and a high-speed scroll chamber is constructed from a separate member from the turbine casing.