WO2012100387A1 - Appareil d'amplification à écoulement variable du type à buses multiples - Google Patents

Appareil d'amplification à écoulement variable du type à buses multiples Download PDF

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Publication number
WO2012100387A1
WO2012100387A1 PCT/CN2011/000598 CN2011000598W WO2012100387A1 WO 2012100387 A1 WO2012100387 A1 WO 2012100387A1 CN 2011000598 W CN2011000598 W CN 2011000598W WO 2012100387 A1 WO2012100387 A1 WO 2012100387A1
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WO
WIPO (PCT)
Prior art keywords
nozzle
flow passage
intake
angle
flow
Prior art date
Application number
PCT/CN2011/000598
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English (en)
Chinese (zh)
Inventor
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 (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wang Hang, Liu Ying, Wang Congcong, Li Yongtai, Song Lihua filed Critical Wang Hang
Publication of WO2012100387A1 publication Critical patent/WO2012100387A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D9/00—Stators
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/026—Scrolls for radial machines or engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2220/00—Application
    • F05D2220/40—Application in turbochargers

Definitions

  • 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.
  • VNT vane variable-section turbocharger
  • VNT tongue-shaped baffle variable-section turbocharger
  • 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:
  • 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.
  • 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.
  • 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.
  • 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. .
  • 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.
  • 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.
  • 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 intermediate partition is disposed along the circumference of the volute.
  • 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.
  • 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.
  • 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.
  • the intake valve 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.
  • 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.
  • the nozzle intermediate flow passage and the outer flow passage of the nozzle are respectively provided with intake valves near the intake port.
  • the angle of the inlet area of the flow passage in the nozzle is any angle between 0 and 360 degrees
  • the angle of the inlet area of the outer flow passage of the nozzle is at any angle between 360 and 0 degrees
  • the intermediate passage of the nozzle The angle of the intake region is any angle between 0 and 360 degrees
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 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.
  • 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.
  • the intake valve 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.
  • 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.
  • 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
  • FIG. 6 is a schematic structural view of a multi-nozzle variable flow turbine in Embodiment 3 of the present invention
  • 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 ⁇ 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.
  • 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.
  • 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 ⁇ 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 ⁇ of the flow path 10 is 30 degrees, and the corresponding intake region angle ⁇ 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 ⁇ of the flow passage 10 in the nozzle At 340 degrees, the angle ⁇ of the intake region of the corresponding nozzle outer flow passage 11 is 20 degrees.
  • 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.
  • the intake valve 9 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 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.
  • 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.
  • ⁇ 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
  • 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 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 ⁇ of the intake region of the flow passage 10 in the nozzle is 35 degrees
  • the angle ⁇ of the intake region of the nozzle intermediate passage 12 is 35 degrees
  • the angle ⁇ 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 ⁇ of the intake region of the nozzle intermediate passage 12 is 90 degrees
  • the angle ⁇ of the intake region of the corresponding nozzle outer passage 11 is 45 degrees. .
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the angle ⁇ of the intake region of the flow passage 10 in the nozzle is an arbitrary angle between 0 and 360 degrees, and the angle ⁇ 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 ⁇ 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.
  • 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.
  • 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.
  • 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.
  • 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

Un appareil d'amplification à écoulement variable du type à buses multiples comprend une volute (2). Une entrée d'air et un passage d'admission d'air en spirale (10-14) communiquant avec l'entrée d'air sont disposés dans la volute (2), et au moins une plaque de séparation (8, 81) est disposée dans le passage d'admission d'air en spirale (10-14). L'appareil peut répondre aux exigences d'amplification dans la plage des conditions de fonctionnement complètes d'un moteur.
PCT/CN2011/000598 2011-01-27 2011-04-06 Appareil d'amplification à écoulement variable du type à buses multiples WO2012100387A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN 201110029166 CN102094704A (zh) 2011-01-27 2011-01-27 多喷管式可变流量增压装置
CN201110029166.2 2011-01-27

Publications (1)

Publication Number Publication Date
WO2012100387A1 true WO2012100387A1 (fr) 2012-08-02

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PCT/CN2011/000598 WO2012100387A1 (fr) 2011-01-27 2011-04-06 Appareil d'amplification à écoulement variable du type à buses multiples

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CN102383877A (zh) * 2011-10-08 2012-03-21 康跃科技股份有限公司 可变几何的脉冲进气涡轮机的蜗壳装置
CN102536435B (zh) * 2012-03-08 2013-09-11 康跃科技股份有限公司 混合式可变流量蜗壳
CN102606233A (zh) * 2012-03-19 2012-07-25 康跃科技股份有限公司 带有叶喷嘴环的可变截面蜗壳
CN103696814B (zh) * 2013-11-14 2016-02-24 汉捷机械部件（常州）有限公司 可变截面的三通道涡壳
CN108267295B (zh) * 2017-12-25 2019-10-18 中国航天空气动力技术研究院 一种流量控制喷管
KR102080666B1 (ko) * 2019-04-12 2020-02-24 박행제 수력발전장치용 임펠라 어셈블리
CN110360155A (zh) * 2019-08-01 2019-10-22 全浩铖 一种多导流通道离心泵或离心风机壳
CN110454240A (zh) * 2019-08-28 2019-11-15 天津大学 一种部分进气轴流式超临界二氧化碳透平膨胀机

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CN101598038A (zh) * 2009-07-03 2009-12-09 寿光市康跃增压器有限公司 涡轮增压器双层流道变截面涡轮机

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CN101936214B (zh) * 2010-08-03 2012-08-08 康跃科技股份有限公司 脉冲可变流道涡轮机装置
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US4384821A (en) * 1981-10-14 1983-05-24 Wallace Murray Corporation Free floating divider wall turbine housing
US5094587A (en) * 1990-07-25 1992-03-10 Woollenweber William E Turbine for internal combustion engine turbochargers
CN101598038A (zh) * 2009-07-03 2009-12-09 寿光市康跃增压器有限公司 涡轮增压器双层流道变截面涡轮机

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