WO2020166426A1

WO2020166426A1 - Supercharger casing and supercharger provided with same

Info

Publication number: WO2020166426A1
Application number: PCT/JP2020/004046
Authority: WO
Inventors: 嘉久小野
Original assignee: 三菱重工マリンマシナリ株式会社
Priority date: 2019-02-13
Filing date: 2020-02-04
Publication date: 2020-08-20
Also published as: JP2020133422A; CN113412364A; JP7143234B2; KR20210104151A; KR102632033B1; CN113412364B

Abstract

The purpose of the present invention is to provide a supercharger casing that can be applied to a small supercharger of which the layout is restricted and that is provided with a bypass pipe having a simple structure, and a supercharger provided with said casing. A casing (10) of a supercharger (1) has formed therein an exhaust gas flow path (12) through which exhaust gas discharged from an internal combustion engine flows, and accommodates therein a turbine (30) driven by the exhaust gas flowing through the exhaust gas flow path (12). The casing (10) is provided with a bypass pipe (50) that allows communication between the exhaust gas flow path (12) on the side of an exhaust gas inlet (12A) and the exhaust gas flow path (12) on the side of an exhaust gas outlet (12B), the communication not being by way of the turbine (30). The bypass pipe (50) is configured from a straight pipe (52) that is connected to the exhaust gas inlet (12A) side and that has a straight linear flow path, and an elbow pipe (54) that is connected to the straight pipe (52) and the exhaust gas outlet (12B) side and that has a bent flow path.

Description

Supercharger casing and supercharger including the same

The present disclosure relates to a casing of a supercharger and a supercharger including the casing.

◇For internal combustion engines for ships, internal combustion engines for power generation, etc. (for example, diesel engines), it is required to improve the performance when operating at low load. In order to improve the performance when operating at low load, it is desirable to set the supercharging pressure of the supercharger installed in the internal combustion engine to a high value, but when the internal combustion engine operates at high load The supply pressure becomes too high. Therefore, when the internal combustion engine operates at a high load and the amount of exhaust gas is large, a so-called exhaust gas bypass system that suppresses an excessive rise in boost pressure by allowing the exhaust gas to bypass the turbine of the supercharger is provided. It has been put to practical use.

As a supercharger adopting the exhaust gas bypass system, there is a supercharger disclosed in Patent Document 1, for example. According to this supercharger, the exhaust gas bypasses the turbine by a U-shaped bypass pipe provided with an opening/closing valve.

Further, as another example of the supercharger in which the exhaust gas bypass system is adopted, there is a supercharger disclosed in Patent Document 2, for example. According to this supercharger, exhaust gas bypasses the turbine by a pipe (so-called shrimp pipe) having an arc shape as a whole by connecting pipes cut at an angle.

Japanese Patent No. 6165564 JP, 2013-124626, A

However, in the U-shaped bypass pipe of the supercharger disclosed in Patent Document 1, it is necessary to secure a predetermined space in order to form the two bent portions, and thus the layout is small and compact. Difficult to apply to the turbocharger. Further, even if it is applied to a small supercharger, it may be difficult to secure the flow passage area of the connecting portion between the outlet end of the bypass pipe and the casing due to the shape of the casing and the relationship with other parts. ..

In addition, the bypass pipe of the supercharger disclosed in Patent Document 2 may increase the time and cost required for manufacturing due to its structure.

The present disclosure has been made in view of such circumstances, and can be applied to a small supercharger having a restricted layout, and includes a casing of a supercharger including a pyvas pipe having a simple structure and a casing thereof. The purpose is to provide a supercharger.

In order to solve the above problems, the casing of the supercharger of the present disclosure and the supercharger including the casing adopt the following means.
That is, the casing of the supercharger according to an aspect of the present disclosure forms an exhaust gas passage through which exhaust gas discharged from an internal combustion engine flows, and a turbine driven by the exhaust gas flowing through the exhaust gas passage. Is a casing of a supercharger containing therein a bypass pipe for communicating the exhaust gas flow path on the exhaust gas inlet side and the exhaust gas flow path on the exhaust gas outlet side without going through the turbine, and the bypass pipe. Is composed of a straight pipe connected to the exhaust gas inlet side and having a straight flow passage, and an elbow pipe connected to the straight pipe and the exhaust gas outlet side and having a bent flow passage.

In the casing of the supercharger according to this aspect, the bypass pipe is provided with only one bent portion (only the bent portion of the elbow pipe), and therefore the bent portion can be made smaller than in the conventional structure. It can be applied to small turbochargers with limited layout.
In addition, since the bypass pipe has a simple structure composed of two members (straight pipe and elbow pipe), the time and cost required for manufacturing can be suppressed.

Further, in the casing of the supercharger according to an aspect of the present disclosure, the elbow pipe has a substantially circular cross-section along the axis, and a connection that connects the connecting portion with the elbow pipe and the exhaust gas flow passage. The shape of the flow passage is changed from the above-mentioned substantially circular shape to a flat shape while keeping the flow passage area substantially constant.

With the casing of the supercharger according to this aspect, the connection flow passage has its flow passage shape changed from a substantially circular shape conforming to the elbow pipe to a flat shape while keeping the flow passage area substantially constant. As a result, even if there is a restriction in the dimension in the predetermined direction due to the shape of the casing on the exhaust gas outlet side or other parts, the flow passage area is secured by making the flat shape thin in the predetermined direction. be able to.

Further, in the casing of the supercharger according to an aspect of the present disclosure, the connection flow passage is formed by casting.

According to the casing of the supercharger according to this aspect, it is possible to easily form the connection flow path having a complicated shape.

Further, in the casing of the supercharger according to the aspect of the present disclosure, the bypass pipe includes an opening/closing valve whose opening/closing is controlled by a signal from the outside.

According to the supercharger casing of this aspect, the open/close state of the on-off valve provided in the bypass pipe is controlled by, for example, a signal transmitted from the control unit of the internal combustion engine in which the supercharger is mounted. As a result, the flow rate of the exhaust gas flowing through the bypass pipe can be controlled in accordance with the specifications and state of the internal combustion engine.

Further, in the casing of the supercharger according to the aspect of the present disclosure, the straight pipe is arranged such that an axial direction thereof and an inflow direction of the exhaust gas flowing from the exhaust gas inlet are substantially coincident with each other.

According to the casing of the supercharger according to this aspect, the exhaust gas flowing in from the exhaust gas inlet is guided to the bypass pipe without being diverted. Therefore, the pressure loss of the exhaust gas guided to the bypass pipe can be suppressed.

Further, in the casing of the supercharger according to an aspect of the present disclosure, the straight pipe includes an expansion/contraction part that expands/contracts in the axial direction.

With the casing of the supercharger according to this aspect, since the straight pipe can be expanded and contracted in the axial direction, it is possible to absorb thermal expansion and thermal contraction that occur in the bypass pipe due to the flow of exhaust gas.
When the bypass pipe is provided with an on-off valve, it is preferable that the expansion/contraction section is installed downstream of the on-off valve in the exhaust gas flow direction.

Further, the casing of the supercharger according to an aspect of the present disclosure forms an exhaust gas passage through which the exhaust gas discharged from the internal combustion engine flows, and is driven by the exhaust gas flowing through the exhaust gas passage. A casing of a supercharger in which a turbine is housed, comprising a bypass pipe for communicating the exhaust gas passage on the exhaust gas inlet side and the exhaust gas passage on the exhaust gas outlet side without going through the turbine, and the bypass. The pipe has a substantially circular cross-sectional area along the axis, and the connection flow passage that connects the connection portion with the bypass pipe and the exhaust gas flow passage has a flow passage shape that is substantially circular from the substantially circular shape. It keeps constant and changes to a flat shape.

According to the casing of the supercharger according to the present aspect, the connection flow passage that connects the connection portion with the bypass pipe and the exhaust gas flow passage through which the exhaust gas flows, the flow passage while maintaining the flow passage area substantially constant. The shape has changed from a substantially circular shape that matches the bypass pipe to a flat shape. As a result, even if there is a restriction in the dimension in the predetermined direction due to the shape of the casing on the exhaust gas outlet side or other parts, the flow passage area is secured by making the flat shape thin in the predetermined direction. be able to.

A supercharger according to one aspect of the present disclosure includes the casing of the above-described supercharger and the turbine driven by exhaust gas discharged from an internal combustion engine.

According to the present disclosure, it is possible to provide a casing of a supercharger including a pyvas pipe having a simple structure, which can be applied to a small supercharger having a layout restriction, and a supercharger including the casing.

1 is a vertical cross-sectional view of a casing of a supercharger and a supercharger including the casing according to an embodiment of the present disclosure. It is a partial enlarged view of the A section shown in FIG. 1, and is a perspective view showing the shape of the outlet side connection flow path.

Hereinafter, a casing of a supercharger according to an embodiment of the present disclosure and a supercharger including the casing will be described with reference to FIGS. 1 and 2.

First, the configuration of the casing 10 and the supercharger 1 including the casing 10 will be described.
As shown in FIG. 1, the supercharger 1 forcibly compresses combustion air supplied to an internal combustion engine mounted on a ship or the like to force high density air into the combustion chamber of the internal combustion engine. It is configured to be sent. The casing 10 according to the present embodiment is particularly suitable for being used in a small supercharger.

The supercharger 1 includes a turbine 30 driven by exhaust gas discharged from an internal combustion engine (not shown), a rotor shaft 33 rotatably driven by the turbine 30 around an axis X, and an exhaust gas. And a casing 10 that forms a flow path (exhaust gas flow path 12).

The turbine 30 is an axial turbine including a turbine disk 31 to which a moving blade 32 is attached and a nozzle ring 34 to which a guide vane 34a is attached.

The rotor blade 32 is arranged in the exhaust gas flow path 12 so as to be close to a downstream end of a guide vane 34 a (described later) along the axis X direction, and is provided at one end of the rotor shaft 33 of the disk-shaped turbine disk 31. A plurality of sheets are attached to the peripheral portion.
The exhaust gas passage 12 upstream of the moving blade 32 in the flow direction of the exhaust gas is indicated by reference numeral 12a, and the exhaust gas passage 12 downstream of the moving blade 32 is indicated by reference numeral 12b.

The nozzle ring 34 includes a cylindrical outer peripheral side ring 34c extending in the direction of the axis X, an inner peripheral side ring 34b having a smaller diameter than the outer peripheral side ring 34c, and an outer peripheral side ring 34c and an inner peripheral side ring 34b. And the attached guide vanes 34a.

The nozzle ring 34 is attached to the casing 10 such that the outer peripheral ring 34c and the inner peripheral ring 34b are part of the wall portion that forms the exhaust gas passage 12a along the axis X direction. At this time, the casing 10 is divided before and after the nozzle ring 34 along the direction of the axis X.

A plurality of guide vanes 34a are attached in the circumferential direction of the axis X between the inner peripheral wall of the outer peripheral ring 34c and the outer peripheral wall of the inner peripheral ring 34b.
The guide vanes 34a are blade-shaped members for appropriately guiding the exhaust gas toward the moving blade 32 by adjusting the flow velocity and the direction of the exhaust gas flowing toward the moving blade 32 side in the exhaust gas passage 12a. It

In the turbine 30, the high temperature exhaust gas passing through the guide vanes 34a passes through the moving blades 32 and expands, so that the turbine disk 31 and the rotor shaft 33 rotate. An impeller (not shown) of a compressor (not shown) is provided at the other end of the rotor shaft 33. When the rotor shaft 33 is rotationally driven, the impeller is rotationally driven to generate air. Compressed.

The casing 10 has a gas inlet (exhaust gas inlet) 12A formed in the lower part and opened downward, and a gas outlet (exhaust gas outlet) 12B formed in the upper part and opened upward, An exhaust gas passage 12 (12a, 12b, 12c) that connects the gas inlet 12A and the gas outlet 12B through 30 is formed, and the casing 10 surrounds a part of the turbine 30 and the rotor shaft 33. Housed in.

Furthermore, the casing 10 forms a bypass pipe 50 that forms a flow path (bypass flow path 51) that connects the exhaust gas flow path 12a on the gas inlet 12A side and the exhaust gas flow path 12c on the gas outlet 12B side without the turbine 30. Equipped with.

The bypass pipe 50 is a straight pipe having an L-shaped flow path (straight flow path 53) with an axial line that is straight when viewed from the side as shown in FIG. 1 and extending from the gas inlet 12A side toward the gas outlet 12B side. 52 and one elbow pipe 54 having a flow path (bending flow path 55) whose axis is bent substantially at a right angle. Accordingly, since the bent portion provided in the bypass pipe 50 can be provided at one place, it can be applied to the small-sized supercharger 1 having a layout restriction. Further, the bypass pipe 50 may have a simple structure composed of two members (straight pipe 52 and elbow pipe 54).
The straight tube 52 and the elbow tube 54 preferably have a substantially circular flow path shape along the axis.

One end of the straight pipe 52 is connected to the casing 10 forming the exhaust gas passage 12a on the gas inlet 12A side.
An inlet-side connection flow channel 16 that connects the exhaust gas flow channel 12a and the outside of the casing 10 is formed in the portion of the casing 10 to which the straight pipe 52 is connected. The inlet-side connection flow path 16 has an axis in the inflow direction of the exhaust gas (arrow Gi in the figure) flowing in from the gas inlet 12A.
The straight pipe 52 is arranged with respect to the casing 10 such that the axis of the linear flow passage 53 is located on an extension of the axis of the inlet side connection flow passage 16. That is, the axial direction of the straight flow path 53 coincides with the inflow direction of the exhaust gas flowing in from the gas inlet 12A. As a result, the exhaust gas flowing in from the gas inlet 12A is guided to the bypass passage 51 without being diverted.

One end of the elbow pipe 54 is connected to the other end of the straight pipe 52 (an end portion different from the end portion connected to the casing 10 ). The other end of the elbow pipe 54 is connected to the casing 10 forming the exhaust gas passage 12c on the gas outlet 12B side.
An outlet-side connection flow channel (connection flow channel) 18 that connects the outside of the casing 10 and the exhaust gas flow channel 12c is formed in the portion of the casing 10 to which the elbow pipe 54 is connected.
As described above, since the axis of the elbow pipe 54 is smoothly bent at a substantially right angle, the axial direction of the outlet-side connection flow path 18 and the axial direction of the straight flow path 53 are substantially orthogonal to each other.

As shown in FIGS. 1 and 2, the shape of the outlet-side connection flow path 18 is a substantially circular shape that matches the flow path shape of the elbow pipe 54 at the connection portion 14 with the elbow pipe 54. Further, the shape of the outlet-side connection flow channel 18 is changed to a flat shape in which the width direction is enlarged and the height direction is reduced as it goes from the connection portion 14 side to the exhaust gas flow channel 12c side.
At this time, the shape is changed from the side of the connecting portion 14 toward the side of the exhaust gas channel 12c so that the channel area of the outlet side connecting channel 18 is maintained substantially constant. Accordingly, even if the dimension in the height direction is restricted due to the shape of the casing 10 on the gas outlet 12B side or the relationship with other components, the flow path can be reduced to a flat shape that becomes thinner in the height direction. The area can be secured.
The casing 10 of the portion forming the outlet-side connection flow path 18 may be manufactured by casting. This makes it possible to easily form the outlet-side connection flow path 18 having a complicated shape.

As shown in FIG. 1, an opening/closing valve 60 capable of controlling the opening is attached to the straight pipe 52 described above.
The opening/closing valve 60 has its opening controlled by a signal from a control unit (not shown) that controls the internal combustion engine in which the supercharger 1 is mounted, for example. Thereby, the flow rate of the exhaust gas flowing through the bypass passage 51 can be adjusted.
The mounting position of the on-off valve 60 can be changed as appropriate, and may be mounted on the elbow pipe 54, for example.

Further, the straight tube 52 described above may be provided with an expansion (expansion/contraction portion) 62 that expands and contracts in the axial direction. The expansion 62 can absorb the expansion and contraction of the straight tube 52 in the axial direction. This makes it possible to absorb thermal expansion and thermal contraction that occur in the bypass pipe 50.
When the opening/closing valve 60 is attached to the straight pipe 52, the expansion 62 is preferably attached to the straight pipe 52 on the downstream side of the opening/closing valve 60 (outlet side connection flow path 18 side). Thereby, the opening/closing valve 60 can be easily attached to the casing 10. The mounting position of the expansion 62 can be changed as appropriate, and the expansion 62 may be mounted on the straight pipe 52 on the upstream side of the on-off valve 60.

Next, the flow of exhaust gas will be described.
[When the on-off valve is closed]
In order to improve the performance of the supercharger even when the internal combustion engine in which the supercharger 1 is mounted operates at a low load, for example, a nozzle (a nozzle that can obtain a high supercharging pressure even at a low load) ( A nozzle smaller than the usual design may be selected. If a part of the exhaust gas is bypassed by the bypass pipe 50 at such a low load, the output of the turbine 30 is reduced by the amount of the bypassed exhaust gas, and the desired boost pressure cannot be obtained. Therefore, when the load is low, the on-off valve 60 is closed so that the exhaust gas does not flow through the bypass passage 51.

When the on-off valve 60 is in the closed state, all the exhaust gas flowing from the gas inlet 12A drives the turbine 30 while flowing through the exhaust gas passage 12a and the exhaust gas passage 12b, and flows through the exhaust gas passage 12c. It flows out from the outlet 12B (arrow Go in the figure).

[When the on-off valve is open]
In order to improve the performance of the supercharger even when the internal combustion engine in which the supercharger 1 is mounted operates at a low load, for example, a nozzle (a nozzle that can obtain a high supercharging pressure even at a low load) ( A nozzle smaller than the usual design may be selected. However, when such an internal combustion engine operates at a high load, the supercharging pressure of the supercharger 1 becomes too high. Therefore, at the time of high load, the opening/closing valve 60 is opened so that the exhaust gas flows through the bypass passage 51 in order to intentionally reduce the output of the turbine 30. The “open state” mentioned here includes not only a state where the opening degree is 100% (fully opened state) but also a state where the opening degree is larger than 0% and smaller than 100.

When the on-off valve 60 is in the open state, a part of the exhaust gas flowing from the gas inlet 12A drives the turbine 30 while flowing through the exhaust gas passage 12a and the exhaust gas passage 12b, and flows through the exhaust gas passage 12c. It flows out from the gas outlet 12B.

On the other hand, the other exhaust gas is guided from the exhaust gas flow path 12a to the straight flow path 53 (bypass flow path 51) via the inlet side connection flow path 16 (arrow Bi in the figure).

The exhaust gas guided to the straight flow path 53 reaches the bent flow path 55, is deflected, and then is guided to the outlet side connection flow path 18.

The exhaust gas guided to the outlet side connection flow path 18 passes through the space S1 formed by the outer peripheral wall of the outer peripheral side ring 34c and the casing 10 and is guided to the exhaust gas flow path 12c on the gas outlet 12B side ( Arrow Bo in the figure).

After that, it merges with the exhaust gas that has driven the turbine 30 and flows out from the gas outlet 12B (arrow Go in the figure).

When the on-off valve 60 is operated from the open state to the closed state, if the on-off valve 60 is suddenly operated, the flow rate of the exhaust gas flowing into the turbine 30 is rapidly increased, and accordingly, the output of the turbine 30 is increased. Will increase rapidly. At the same time, the rotation speed of the impeller (not shown) of the compressor rapidly increases. Then, surging may occur in the compressor.
For this reason, it is preferable to gradually close the on-off valve 60 in order to avoid surging in the compressor. For example, when operating the open/close valve 60 from the fully open state to the fully closed state, it is preferable to operate it for 5 seconds or more.
Needless to say, the operating time of the on-off valve 60 can be changed as appropriate according to the specifications of each device. However, the time for operating the on-off valve 60 from the open state to the closed state is preferably longer than the time for operating the on-off valve 60 from the closed state to the open state.

Further, even if the moving parts (the turbine 30, the rotor shaft 33, the compressor (not shown), etc.) of the supercharger 1 fail, the internal combustion engine needs to be operated, so the exhaust gas passage The exhaust gas supplied to 12 cannot be interrupted. Therefore, a mechanism for locking the movable part may be provided in order to avoid further damage to the movable part. In the case of this embodiment, since the bypass pipe 50 is installed on the turbine 30 side, it is preferable to provide a lock mechanism on the compressor side in consideration of the ease of access by an operator.

This embodiment has the following effects.
Since the bypass pipe 50 provided in the casing 10 has only one bent portion in the elbow pipe 54, it can be applied to the small-sized supercharger 1 having a layout restriction. Further, for example, compared with the case where there are two bent portions, the pressure loss caused by the bent portions can be suppressed. Furthermore, since the bypass pipe 50 has a simple structure composed of two members (straight pipe 52 and elbow pipe 54), the time and cost required for manufacturing can be suppressed.

Further, the outlet-side connection flow passage 18 has its flow passage shape changed from a substantially circular shape adapted to the elbow pipe 54 to a flat shape while keeping the flow passage area substantially constant. Thus, for example, even if the shape of the casing 10 on the gas outlet 12B side or the size of the casing 10 in the predetermined direction is restricted due to the relationship with other components, the flattened shape that thins in the predetermined direction reduces the flow passage area. Can be secured.

The open/close state of the open/close valve 60 provided in the bypass pipe 50 is controlled by a signal transmitted from, for example, a control unit of an internal combustion engine in which the supercharger 1 is mounted. This makes it possible to control the flow rate of the exhaust gas flowing through the bypass passage 51 in accordance with the specifications and state of the internal combustion engine.

Moreover, the axial direction of the linear flow path 53 coincides with the inflow direction of the exhaust gas flowing from the gas inlet 12A. As a result, the exhaust gas flowing in from the gas inlet 12A is guided to the bypass passage 51 without being diverted. Therefore, the pressure loss of the exhaust gas guided to the bypass pipe can be suppressed.

Also, the straight pipe 52 is provided with an expansion 62 that expands and contracts in the axial direction. This makes it possible to absorb the thermal expansion and thermal contraction that occur in the bypass pipe 50 due to the flow of the exhaust gas.

The shape of the bypass pipe 50 is not limited to that of the above-described embodiment, and may be arbitrarily changed according to the specifications of the internal combustion engine or the supercharger and the layout of each device (not shown).

Further, although the above embodiment has been described using the axial flow turbine, it can be applied to a rotating machine such as a power turbine.

DESCRIPTION OF SYMBOLS 1 Supercharger 10 Casing 12 (12a, 12b, 12c) Exhaust gas flow path

12A Gas inlet

12B Gas outlet 14 Connection part 16 Entrance side connection flow path 18 Exit side connection flow path 30 Turbine 31 Turbine disk 32 Moving blade 33 Rotor shaft 34 Nozzle ring 34a Guide vane 34b Inner peripheral side ring 34c Outer peripheral side ring 50 Bypass pipe 51 Bypass flow path 52 Straight pipe 53 Straight flow path 54 Elbow pipe 55 Bending flow path 60 Open/close valve 62 Expansion

Claims

A casing of a supercharger that forms an exhaust gas passage through which exhaust gas discharged from an internal combustion engine flows, and that accommodates a turbine driven by the exhaust gas flowing through the exhaust gas passage,
A bypass pipe that connects the exhaust gas passage on the exhaust gas inlet side and the exhaust gas passage on the exhaust gas outlet side without going through the turbine,
The bypass pipe is composed of a straight pipe connected to the exhaust gas inlet side and having a linear flow passage, and an elbow pipe connected to the straight pipe and the exhaust gas outlet side and having a bent flow passage. The casing of the turbocharger.
The elbow tube has a substantially circular cross section along the axis,
The shape of the connection flow path that connects the connection portion with the elbow pipe and the exhaust gas flow path is changed from the substantially circular shape to a flat shape while keeping the flow path area substantially constant. Supercharger casing.
The casing of the supercharger according to claim 2, wherein the connection channel is formed by casting.
The casing of the supercharger according to claim 1, wherein the bypass pipe includes an opening/closing valve whose opening/closing is controlled by a signal from the outside.
The casing of the supercharger according to claim 1, wherein the straight pipe is arranged so that an axial direction thereof and an inflow direction of the exhaust gas flowing from the exhaust gas inlet substantially coincide with each other.
The casing of the turbocharger according to any one of claims 1 to 5, wherein the straight pipe includes an expansion/contraction part that expands/contracts in the axial direction.
A casing of a supercharger that forms an exhaust gas passage through which exhaust gas discharged from an internal combustion engine flows, and that accommodates a turbine driven by the exhaust gas flowing through the exhaust gas passage,
A bypass pipe that connects the exhaust gas passage on the exhaust gas inlet side and the exhaust gas passage on the exhaust gas outlet side without going through the turbine,
The bypass pipe has a substantially circular cross-sectional area along the axis,
The connection flow passage that connects the connection portion with the bypass pipe and the exhaust gas flow passage has a flow passage shape that changes from the substantially circular shape to a flat shape while maintaining a substantially constant cross-sectional area. ..
A casing of the supercharger according to claim 1 or 7,
The turbine driven by the exhaust gas;
Equipped with a supercharger.