WO2012100387A1

WO2012100387A1 - Multi-nozzle type variable-flow boosting apparatus

Info

Publication number: WO2012100387A1
Application number: PCT/CN2011/000598
Authority: WO
Inventors: 王航; 刘莹; 王聪聪; 李永泰; 宋丽华
Original assignee: Wang Hang; Liu Ying; Wang Congcong; Li Yongtai; Song Lihua
Priority date: 2011-01-27
Filing date: 2011-04-06
Publication date: 2012-08-02
Also published as: CN102094704A

Abstract

A multi-nozzle type variable-flow boosting apparatus comprises a volute (2). An air inlet and a scroll air intake passage (10-14) communicated with the air inlet are disposed in the volute (2), and at least one separation plate (8, 81) is disposed in the scroll air intake passage (10-14). The apparatus can meet boosting requirements in the range of the whole operation conditions of an engine.

Description

Multi-nozzle variable flow booster

Technical field:

The invention relates to a variable section supercharger, in particular to a multi-nozzle type variable flow supercharging device which meets the requirements of high and low speed conditions of an engine through joint work between different cross-section flow paths, belonging to The field of internal combustion engines.

Background technique:

At present, superchargers are widely used in modern engines. In order to meet the performance and emission requirements of various operating conditions of the engine, the supercharger must have an adjustable function of supercharging pressure and exhaust pressure, thereby making the variable section supercharger Become the focus of research and development at home and abroad. The rotary vane variable-section turbocharger (VNT) and the tongue-shaped baffle variable-section turbocharger are simple in structure and can effectively widen the matching range between the turbocharger and the engine to achieve boost pressure and Widely used for the adjustment of exhaust pressure.

The schematic diagram of the rotary vane variable-section turbocharger is shown in Fig. 1. The turbine portion of the rotary vane turbocharger includes a volute, a volute nozzle 3, and a turbine impeller. The nozzle vane 6 is mounted on the nozzle ring support disk 5, and the transmission mechanism 4 changes the flow area of the volute nozzle 3 and the outlet exhaust gas angle by controlling the rotation angle of the nozzle vane 6, so that the exhaust gas is blown toward the periphery of the turbine impeller 7 at a designed angle. The turbine impeller 7 is driven to rotate at a high speed to complete the work process of the turbine impeller 7, and then the compressor 1 is driven to compress the air entering the compressor 1 in the axial direction, thereby increasing the intake density of the air entering the cylinder and achieving the purpose of supercharging. .

The rotary vane variable-section turbocharger changes the intake flow area of the turbine by controlling the rotation angle of the nozzle vane 6, and the control is convenient, but there are some defects in the actual application process:

Under the high flow condition of the engine, the opening degree of the nozzle vane 6 is increased, and is closer to the leading edge of the turbine blade, and the exhaust gas particles cause relatively large wear on the nozzle vane 6. When the engine is under low flow conditions, the opening degree of the nozzle vane 6 is small, and the circumferential speed of the nozzle outlet airflow is high, and the turbine becomes an impulsive turbine. The aerodynamic losses of the external gas flow are also severe, which reduces the efficiency of the supercharger.

The discharge temperature of the exhaust gas of the engine is as high as 650~850 °C. The working environment of the turbocharger is harsh and the strong vibration puts high requirements on the reliability of the transmission mechanism 3. However, the reliability of the transmission mechanism 3 has been solved so far. Has not been effectively resolved.

The tongue-shaped baffle variable-section turbocharger has also been widely used due to its simple structure and easy control. In the invention patent of CN 101418708A, known as exhaust gas turbocharger, the tongue-shaped baffle is described in detail. The working principle of the variable section supercharger is to adjust the opening of the tongue-shaped baffle by the adjusting device to change the inlet area of the annular inlet, and when the tongue-shaped baffle rotates away from the turbine, the annular flow path The inlet area is reduced, the airflow velocity entering the turbine is increased, and the kinetic energy is increased. On the contrary, the speed is reduced, the kinetic energy is reduced, and the tongue-shaped baffle is adjusted as needed to achieve the required kinetic energy to meet the performance requirements of various operating conditions of the engine. . However, the tongue-shaped baffle variable-section supercharger also has some disadvantages: The adjustment device is complicated in processing and installation, and the most important tongue-shaped baffle changes the flow path of the fluid when changing the cross-section of the intake runner. Large changes increase flow losses and create strong eddy currents at the back of the tongue-shaped baffle, making the booster less efficient.

Summary of the invention:

The problem to be solved by the present invention is to provide a simple structure for the problem of reliability and efficiency of the rotary vane variable turbocharger and the problem that the tongue-shaped baffle variable section supercharger is too low in efficiency. A multi-nozzle variable flow booster with low cost, high reliability, and high efficiency at low flow rates while taking into account the efficiency and flow capacity of high flow.

In order to solve the above problems, the present invention adopts the following technical solutions:

A multi-nozzle type variable flow supercharging device comprises a volute, an ventilator having an air inlet and a scroll inlet passage communicating with the air inlet, and at least one intermediate portion in the scroll inlet passage Partition.

The following is a further improvement of the above solution by the present invention: The intermediate partition is disposed along the circumference of the volute.

Further improvement:

The number of the intermediate partitions is one piece, and the intermediate partition partitions the spiral inlet flow passage into the inner flow passage of the nozzle and the outer flow passage of the nozzle, and the outer flow passage of the nozzle is provided with an intake valve at a position close to the intake port. The gas regulating mechanism can adjust the opening degree of the intake valve according to the actual working condition of the engine, realize the selection of the nozzle flow path and the control of the exhaust gas flow.

Further improvement:

An angle of an intake region of the inner flow passage of the nozzle and the outer flow passage of the nozzle is formed between the end of the intermediate partition away from the intake port and the volute.

Further improvement:

The angle of the intake area of the flow passage in the nozzle is any angle between 0 and 360 degrees, and the angle of the intake area of the outer flow passage of the nozzle is any angle between 360 and 0 degrees, and the flow passage and the outflow of the nozzle inside the nozzle The sum of the angles of the intake regions of the track is 360 degrees.

The invention adopts the above scheme, the engine is in the closed state under the low speed condition, and all the working gas only works on the turbine through the inner flow passage of the nozzle, and the intake air sectional area becomes smaller, and the intake of the turbine can be effectively improved. The pressure increases the available energy in the exhaust gas, and the outlet area of the nozzle becomes smaller. The intake angle of the turbine can be controlled in a relatively high efficiency region. The energy available for the exhaust gas and the low turbine efficiency can effectively increase the engine low speed. The turbine output work under working conditions meets the low-speed performance of the engine and achieves the goal of reducing emissions.

In the high-speed working condition of the engine, the intake valve is in the open state, and the opening degree of the intake valve is adjusted by the intake valve control mechanism according to the actual working condition of the engine, through the selection of different nozzle flow passages and different exhaust gas flow distribution. Control to meet the high speed performance requirements of the engine.

Another improvement: The intermediate partition is two pieces, and the two intermediate partitions divide the entire spiral inlet flow passage in the volute into three flow passages: a nozzle inner flow passage, a nozzle outer flow passage and a nozzle intermediate flow passage.

Further improvement: the nozzle intermediate flow passage and the outer flow passage of the nozzle are respectively provided with intake valves near the intake port.

Further improvement: the angle of the inlet area of the flow passage in the nozzle is any angle between 0 and 360 degrees, and the angle of the inlet area of the outer flow passage of the nozzle is at any angle between 360 and 0 degrees, and the intermediate passage of the nozzle The angle of the intake region is any angle between 0 and 360 degrees, and the sum of the angles between the inner flow passage of the nozzle and the outer flow passage of the nozzle and the intermediate passage of the nozzle is 360 degrees.

The invention adopts the above scheme. When the engine is under low speed condition, each inlet valve is in a closed state, and all the working gas passes through the inner flow passage of the nozzle to work on the turbine, and the intake cross-sectional area becomes smaller, which can effectively improve the turbine advancement. The gas pressure increases the available energy in the exhaust gas, and the outlet area of the nozzle becomes smaller. The intake angle of the turbine can be controlled in a relatively high efficiency region, and the engine can be effectively increased by the energy available for the exhaust gas and the efficiency of the low-speed turbine. Turbine output at low speeds meets the low speed performance of the engine and reduces emissions.

In the medium speed condition, only the intake valve installed in the middle flow passage of the nozzle is opened, and the intake valve in the outer flow passage of the nozzle is closed.

When the engine is running at high speed, the intake valve installed in the intermediate passage of the nozzle and the intake valve in the outer flow passage of the nozzle are opened.

The valve control mechanism realizes the selection of the nozzle flow passage and the control of different flow distribution by controlling the combined operation of the two intake valves to meet the performance requirements of the engine under medium and high speed conditions.

Another improvement:

The intermediate partition is arranged along the radial direction of the volute, and the spiral inlet flow passage is divided into a parallel nozzle left flow passage and a nozzle right flow passage. After adopting the arrangement, each nozzle flow passage can realize non- Intake all week, at the same time It can also achieve full-cycle intake.

Further improvement: An intermediate partition is arranged in the axial direction of the volute in the right flow passage of the nozzle, and the right flow passage of the nozzle is divided into two inner and outer flow passages.

The arrangement of the nozzles is arranged in parallel and on the upper and lower sides. The left flow passage of the nozzle can realize partial circumferential intake and full-cycle intake, and the right flow passage of the nozzle can realize partial circumferential intake.

Another improvement:

The intermediate partitions are two pieces which are vertically arranged to intersect each other, and the spiral inlet flow passages are partitioned into four nozzle flow paths.

With this arrangement, the structure is made more flexible, and the nozzles are arranged in parallel and up and down, and partial circumferential air intake of each nozzle can be achieved. Of course, we can still set other nozzle flow channels according to actual needs to meet the requirements of different engine performance design.

The invention solves the existence of reliability and efficiency of the current rotary vane variable turbocharger by adopting the multi-nozzle variable intercept flow turbine intake structure by designing and developing the volute nozzle flow passage. The problem and the problem that the tongue-shaped baffle variable section supercharger is too inefficient.

After adopting the multi-nozzle variable flow turbine, the intake valve is closed in the small flow condition, only the inner flow passage of the nozzle participates in operation, and the intake air cross-sectional area becomes smaller, which can effectively increase the turbine intake pressure. , the available energy in the exhaust gas is increased, the function of the turbine is enhanced, and the nozzle outlet area at the low speed of the engine after the partial partial intake is smaller than that of the full-cycle intake, and the intake angle of the turbine is controlled to be relatively high. Efficiency area. Through the increase of the available energy of the exhaust gas and the improvement of the low-speed turbine efficiency, the turbine output work under the small flow condition of the engine can be effectively increased, the supercharging pressure is increased, the low-speed supercharging pressure of the engine is met, and the low-speed performance of the engine is improved. Achieve the goal of reducing engine emissions.

In the engine at high speed, the intake valve is in the open state, the inner flow passage of the nozzle works together with the outer flow passage of the nozzle, and the intake valve control mechanism realizes the flow passage of the nozzle by controlling the opening angle of the intake valve. Selection and control of exhaust flow distribution to meet engine performance requirements at medium to high speeds.

The structure of the turbine volute of the invention is basically the same as that of the conventional supercharger volute, the structure is simple, the bearing is good, the cost is low, and the engineering is easy to be quickly realized. The air intake adjustment control mechanism in the present invention is simple, the control method is easy to implement, and the reliability is high.

In summary, the multi-nozzle variable flow supercharging system can effectively meet the supercharging requirements of the full operating range of the engine. The overall structure of the supercharger does not undergo large changes, and the cost is low and easy to implement. It has a wide market value and can achieve good application results.

The present invention will be further described below in conjunction with the accompanying drawings and embodiments -

Figure 1 is a schematic structural view of a rotary vane variable-section turbocharger in the background art of the present invention;

Figure 2 is a schematic structural view of a multi-nozzle variable flow turbine in Embodiment 1 of the present invention; Figure 3 is a view showing a change in an intake region angle ? of the multi-nozzle variable flow turbine in Embodiment 2 of the present invention; Rear structural diagram;

Figure 4 is a schematic view showing the structure of a multi-nozzle variable flow turbine in Embodiment 2 of the present invention at a high speed condition in an engine;

Figure 5 is a schematic view showing the cross-sectional structure of the multi-nozzle variable flow turbine inlet in the first and second embodiments of the present invention;

6 is a schematic structural view of a multi-nozzle variable flow turbine in Embodiment 3 of the present invention; and FIG. 7 is a schematic structural view of a cross-sectional surface of a multi-nozzle variable flow turbine inlet according to Embodiments 3 and 4 of the present invention;

Figure 8 is a schematic structural view showing a change in the angle α of the intake region of the multi-nozzle variable flow turbine in Embodiment 4 of the present invention; Figure 9 is a schematic structural view of a multi-nozzle variable flow turbine in Embodiment 4 of the present invention under an engine medium speed condition;

Figure 10 is a schematic view showing the structure of a multi-nozzle variable flow turbine in Embodiment 4 of the present invention under high-speed engine conditions;

Figure 11 is a schematic view showing the cross-sectional structure of a multi-nozzle variable flow turbine inlet in the embodiment 5 of the present invention;

Figure 12 is a schematic view showing the cross-sectional structure of the inlet of the multi-nozzle variable flow turbine in the embodiment 6 of the present invention;

Figure 13 is a schematic view showing the cross-sectional structure of the multi-nozzle variable flow turbine inlet in the seventh embodiment of the present invention.

In the figure: 1-compressor; 2-volute; 3-volute nozzle; 4-transmission mechanism; 5-nozzle ring support plate; 6-nozzle blade; 7-turbine wheel; 8, 81-intermediate partition; - intake air door; 10-spoke inner flow passage; 11-nozzle outer flow passage; 12-nozzle intermediate flow passage; 13-nozzle left flow passage; 14-nozzle right flow passage; α-intake area angle .

detailed description:

Embodiment 1, as shown in FIG. 2 and FIG. 5, a multi-nozzle type variable flow supercharging device includes a volute 2, and an air inlet and a scroll connected to the air inlet are provided in the volute 2. In the air flow passage, a curved intermediate partition 8 is arranged in the spiral intake air passage along the circumferential direction of the volute, and the intermediate partition 8 divides the spiral intake passage into the nozzle inner flow passage 10 and the nozzle outer flow passage 11, Both the inner nozzle 10 and the outer nozzle 11 of the nozzle achieve partial circumferential intake.

An intake valve 9 is provided at a position of the nozzle outer flow passage 11 near the intake port.

The intermediate partition 8 is integrally formed with the volute 2, and an angle α between the end of the intermediate partition 8 away from the intake port and the volute 2 is formed to form an intake region 10 of the nozzle inner passage 10 and the outer nozzle 11 of the nozzle, Inside the nozzle The intake region angle α of the flow path 10 is 30 degrees, and the corresponding intake region angle α of the nozzle outer flow passage 11 is 330 degrees.

Embodiment 2, as shown in FIG. 3, FIG. 4, FIG. 5, in Embodiment 1, after the intermediate partition 8 is further extended in the circumferential direction, the intake region angle α of the flow passage 10 in the nozzle At 340 degrees, the angle α of the intake region of the corresponding nozzle outer flow passage 11 is 20 degrees.

As shown in Fig. 3, the engine is in the closed state under low speed conditions, and all the working gas passes through the nozzle inner flow passage 10 to work on the turbine. Since the intake cross-sectional area becomes smaller, the turbine can be effectively lifted. The intake pressure increases the available energy in the exhaust gas, and the outlet area of the nozzle becomes smaller. The intake angle of the turbine can be controlled in a relatively high efficiency region, and the available energy of the exhaust gas and the efficiency of the low-speed turbine can be effectively improved. Increase the turbine output power under low engine speed conditions to meet the low speed performance of the engine and achieve the goal of reducing emissions.

As shown in FIG. 4, in the high-speed working condition of the engine, the intake valve 9 is in an open state, and the opening degree of the intake valve 9 is adjusted by the intake valve control mechanism according to the actual working condition of the engine, and the different nozzles are passed. The choice of flow path and control of different exhaust gas flow distribution to meet the high speed performance requirements of the engine.

The invention aims at the requirement of the variable-section turbocharger for the engine, completes the development of the turbine portion of the multi-nozzle variable-flow supercharging system, and effectively utilizes the exhaust gas energy, taking into account the low-speed and medium-high speed conditions of the engine. Turbo demand. This type of multi-nozzle variable flow intake turbine can be completed using the casting and machining techniques of existing conventional superchargers.

In the above Embodiment 1 and Embodiment 2, the angle of the intake region of the inner flow passage 10 of the nozzle and the outer flow passage 11 of the nozzle can be changed by the reasonable separation of the intermediate partition 8, and the angle of the intake region of the flow passage 10 in the nozzle can be realized. α is an arbitrary angle between 0 and 360 degrees, the angle a of the intake region of the nozzle outer flow passage 11 is an arbitrary angle between 360 and 0 degrees, and the angle of the intake region of the flow passage 10 in the nozzle and the outflow of the nozzle Road 11 The sum of the angles of the intake regions is 360 degrees.

Embodiment 3, this embodiment differs from Embodiment 1 in that two curved intermediate partitions 8 are disposed in the volute 2, as shown in FIG. 6 and FIG. 7, two intermediate partitions 8 and a volute 2 is integrally formed, and the two intermediate partitions divide the entire spiral inlet flow passage in the volute 2 into three flow passages: a nozzle inner flow passage 10, a nozzle outer flow passage 11, and a nozzle intermediate flow passage 12.

The angle α of the intake region of the flow passage 10 in the nozzle is 35 degrees, the angle α of the intake region of the nozzle intermediate passage 12 is 35 degrees, and the angle α of the intake region of the corresponding nozzle outer passage 11 is 290 degrees. .

The nozzle intermediate flow passage 12 and the nozzle outer flow passage 11 are respectively provided with an intake valve 9 near the intake port, and the valve control mechanism adjusts the opening degree of each intake valve by the performance requirements of different working conditions of the engine, thereby realizing The control of the nozzle flow path and the exhaust gas flow distribution meets the performance requirements of the engine operating conditions.

Embodiment 4, this embodiment is different from Embodiment 2 in that two curved intermediate partitions 8 are disposed in the volute 2, as shown in FIG. 7 and FIG. 8, two intermediate partitions 8 and a volute 2 is integrally formed, and the two intermediate partitions divide the entire spiral inlet flow passage in the volute 2 into three flow passages: a nozzle inner flow passage 10, a nozzle outer flow passage 11, and a nozzle intermediate flow passage 12.

The angle a of the intake region of the flow passage 10 in the nozzle is 225 degrees, the angle α of the intake region of the nozzle intermediate passage 12 is 90 degrees, and the angle α of the intake region of the corresponding nozzle outer passage 11 is 45 degrees. .

As shown in Fig. 8, when the engine is in the low speed condition, the inlet valves 9 are in the closed state, and all the working gas passes through the nozzle inner flow passage 10 to work on the turbine. Since the intake cross-sectional area becomes smaller, the turbine can be effectively lifted. The intake pressure increases the available energy in the exhaust gas, and the outlet area of the nozzle becomes smaller. The intake angle of the turbine can be controlled in a relatively high efficiency region, and the available energy of the exhaust gas and the efficiency of the low-speed turbine can be effectively improved. Increase the turbine output power under low engine speed conditions to meet the low speed performance of the engine and achieve the goal of reducing emissions.

As shown in Figure 9, the engine is only installed in the intermediate flow passage 12 of the nozzle under medium speed conditions. The intake valve 9 is opened, and the intake valve 9 in the nozzle outer flow passage 11 is in a closed state. As shown in Fig. 10, the engine is opened at a high speed condition, and the intake valve 9 installed in the nozzle intermediate flow passage 12 and the intake valve 9 in the nozzle outer flow passage 11 are opened.

In the above-mentioned Embodiment 3 and Embodiment 4, the change of the angle α of the intake region of the nozzle inner flow passage 10 and the nozzle outer flow passage 11 and the nozzle intermediate flow passage 12 can be realized by reasonable separation of the two intermediate partition plates 8. The angle α of the intake region of the flow passage 10 in the nozzle is an arbitrary angle between 0 and 360 degrees, and the angle α of the intake region of the outer flow passage 11 of the nozzle is at an arbitrary angle between 360 and 0 degrees, in the middle of the nozzle The angle α of the intake region of the flow passage 12 is any angle between 0 and 360 degrees, the angle of the intake region of the flow passage 10 in the nozzle and the angle of the intake region of the outer nozzle 11 of the nozzle and the intermediate passage of the nozzle The sum of the angles of the intake regions of 12 is 360 degrees.

Embodiment 5 In Embodiment 1 and Embodiment 2, as shown in FIG. 11, an intermediate partition 8 may be disposed in the spiral intake air passage in the radial direction of the volute, and the intermediate partition 8 spaces the spiral intake passage In parallel with the nozzle left flow channel 13 and the nozzle right flow channel 14, after this arrangement, each nozzle flow channel can realize non-full-cycle intake, and can also achieve full-cycle intake.

Embodiment 6, on the basis of Embodiment 5, as shown in FIG. 12, an intermediate partition 81 may be disposed in the axial direction of the volute in the right flow passage 14 of the nozzle, and the right flow passage 14 of the nozzle may be partitioned into the inside and outside. Two flow passages, such a nozzle arrangement is arranged in parallel and up and down, and the left flow passage 13 of the nozzle can realize partial circumference To the intake air, full-cycle intake can also be achieved, and the nozzle right flow passage 14 can achieve partial circumferential intake.

Embodiment 7, on the basis of Embodiment 1 and Embodiment 2, as shown in FIG. 13, the intermediate partitions 8 are two pieces, which are vertically arranged to intersect each other, and the spiral intake air flow passages are divided into four nozzle flows. After adopting this arrangement, the structure becomes more flexible, and the nozzles are arranged in parallel and up and down, and partial circumferential air intake of each nozzle can be realized. Of course, we can still set other nozzle flow channels according to actual needs to meet the requirements of different engine performance design.

The invention aims at the requirement of the variable-section turbocharger for the engine, completes the development of the turbine portion of the multi-nozzle variable-flow supercharging system, and effectively utilizes the exhaust gas energy, taking into account the low-speed and medium-high speed conditions of the engine. Turbocharging requirements, this type of multi-nozzle variable flow intake turbine can be completed using the casting and machining techniques of existing conventional superchargers.

Claims

Rights request

A multi-nozzle variable flow supercharging device comprising a volute (2), an volute (2) having an air inlet and a scroll inlet passage communicating with the air inlet, wherein: At least one intermediate partition (8) is provided in the scroll inlet passage.

A multi-nozzle type variable flow supercharging apparatus according to claim 1, wherein: said intermediate partition (8) is disposed along a circumferential direction of the volute.

The multi-nozzle type variable flow supercharging apparatus according to claim 2, wherein: the number of the intermediate partitions (8) is one piece, and the intermediate partition (8) spaces the spiral intake passages The nozzle inner flow passage (10) and the nozzle outer flow passage (11) are provided, and the nozzle outer flow passage (11) is provided with an intake valve (9) near the intake port.

The multi-nozzle type variable flow supercharging device according to claim 2 or 3, characterized in that: the intermediate partition (8) is separated from the end of the air inlet and the volute (2) respectively The angle (α) of the intake region forming the inner flow passage (10) of the nozzle and the outer flow passage (11) of the nozzle.

The multi-nozzle type variable flow supercharging device according to claim 4, characterized in that: the angle (ft) of the intake region of the inner flow passage (10) of the nozzle is an arbitrary angle between 0 and 360 degrees. , the angle of the intake region of the outer flow passage (11) of the nozzle (o is an arbitrary angle between 360 and 0 degrees, the angle of the intake region of the flow passage (10) in the nozzle and the intake of the outer flow passage (11) of the nozzle The sum of the area angles is 360 degrees.

The multi-nozzle type variable flow supercharging device according to claim 2, wherein: the intermediate partition (8) is two pieces, and the two intermediate partitions cover the entire volute (2) The spiral inlet passages are divided into three flow passages: a nozzle inner flow passage (10), a nozzle outer flow passage (11), and a nozzle intermediate flow passage (12).

The multi-nozzle type variable flow supercharging device according to claim 6, wherein: the nozzle intermediate flow passage (12) and the nozzle outer flow passage (11) are respectively disposed adjacent to the intake port. Intake valve (9).

8. The multi-nozzle variable flow boosting device according to claim 6 or 7, wherein: The angle (α) of the intake region of the inner flow passage (10) in the nozzle is an arbitrary angle between 0 and 360 degrees, and the angle (α) of the intake region of the outer flow passage (11) of the nozzle is between 0 and 360 degrees. At any angle, the angle (α) of the intake region of the nozzle intermediate flow passage (12) is at any angle between 0 and 360 degrees, and the angle of the intake region of the inner flow passage (10) of the nozzle and the outflow of the nozzle The sum of the angle of the intake region of the passage (11) and the angle of the intake region of the intermediate passage (12) of the nozzle is 360 degrees.

9. The multi-nozzle variable flow supercharging device according to claim 1, wherein: the intermediate partition (8) is disposed radially along the volute, and the spiral intake passage is spaced into parallel sprays. Tube left flow channel (13) and nozzle right channel (14).

10. The multi-nozzle type variable flow supercharging device according to claim 9, wherein: an intermediate partition (81) is disposed in the axial direction of the volute in the right flow passage (14) of the nozzle, and the spray is sprayed. The right flow channel (14) is divided into two inner and outer flow channels.

11. The multi-nozzle type variable flow supercharging device according to claim 1, wherein: the intermediate partition plate (8) is two pieces which are vertically arranged to intersect each other, and the spiral intake air flow path is divided into four. A nozzle flow path.