WO2013166626A1 - Précompresseur séquentiel parallèle à double entraînement - Google Patents

Précompresseur séquentiel parallèle à double entraînement Download PDF

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Publication number
WO2013166626A1
WO2013166626A1 PCT/CN2012/000713 CN2012000713W WO2013166626A1 WO 2013166626 A1 WO2013166626 A1 WO 2013166626A1 CN 2012000713 W CN2012000713 W CN 2012000713W WO 2013166626 A1 WO2013166626 A1 WO 2013166626A1
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WO
WIPO (PCT)
Prior art keywords
compressor
air inlet
impeller
flow channel
dual
Prior art date
Application number
PCT/CN2012/000713
Other languages
English (en)
Chinese (zh)
Inventor
王航
李永泰
朱智富
李延昭
袁道军
王艳霞
宋丽华
Original Assignee
Wang Hang
Li Yongtai
Zhu Zhifu
Li Yanzhao
Yuan Daojun
Wang Yanxia
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, Li Yongtai, Zhu Zhifu, Li Yanzhao, Yuan Daojun, Wang Yanxia, Song Lihua filed Critical Wang Hang
Publication of WO2013166626A1 publication Critical patent/WO2013166626A1/fr
Priority to US14/535,344 priority Critical patent/US20150063989A1/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0253—Surge control by throttling
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0246—Surge control by varying geometry within the pumps, e.g. by adjusting vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
    • F04D27/02—Surge control
    • F04D27/0269—Surge control by changing flow path between different stages or between a plurality of compressors; load distribution between compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/284—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors
    • F04D29/286—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for compressors multi-stage rotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
    • F04D29/4213—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps suction ports
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/44—Fluid-guiding means, e.g. diffusers
    • F04D29/46—Fluid-guiding means, e.g. diffusers adjustable
    • F04D29/462—Fluid-guiding means, e.g. diffusers adjustable especially adapted for elastic fluid pumps
    • 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
    • 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
    • F05D2240/00—Components
    • F05D2240/40—Use of a multiplicity of similar components
    • 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
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/51—Inlet
    • 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
    • F05D2250/00—Geometry
    • F05D2250/50—Inlet or outlet
    • F05D2250/52—Outlet
    • 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
    • F05D2260/00—Function
    • F05D2260/60—Fluid transfer
    • 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
    • F05D2270/00—Control
    • F05D2270/01—Purpose of the control system
    • F05D2270/10—Purpose of the control system to cope with, or avoid, compressor flow instabilities
    • F05D2270/101—Compressor surge or stall

Definitions

  • the present invention relates to a supercharged compressor, and more particularly to a dual-pass compressor casing 1 single-pressure air compressor impeller double-drive parallel-stage supercharged compressor, which belongs to the field of internal combustion engine supercharging. Background technique:
  • the turbocharger uses the exhaust energy of the engine to drive the turbine to rotate, thereby driving the compressor impeller coaxial with the turbine to rotate at a high speed.
  • the compressor pushes the compressed air into the engine cylinder, increasing the air volume of the engine, under pressure and
  • the flow rate is promoted to make the combustion more fully, which increases the power of the engine and reduces the fuel consumption. At the same time, it reduces the emission of harmful substances and reduces the noise.
  • turbochargers with a wider range of available flow rates are essential for improving engine power and improving current engine power performance.
  • the conventional turbocharger basically adopts a single impeller single-channel compressor, and the supercharger surge phenomenon is prone to occur in the low-speed working condition range of the engine, and the supercharger flow congestion phenomenon is likely to occur in the high-speed working condition range of the engine, and The higher pressure ratio, flow range and efficiency level that the turbocharger needs to meet cannot be effectively met. As a result, many engine applications are forced to use a two-stage turbocharging system.
  • the two-stage turbocharging system has many advantages, but compared to the conventional single-wheel turbocharger, the two-stage turbo is added.
  • the pressure system is bulky and complicated in layout, and the design and production technology is difficult and the manufacturing cost is high.
  • the two-stage turbocharging system is suitable for high-end engines and is difficult to promote.
  • the problem to be solved by the present invention is to provide a double-drive parallel-stage supercharging compressor which is mainly used for improving the surge effect of the small flow range of the turbocharger and the blocking effect of the large flow range, and effectively widening the flow range of the turbocharger. .
  • the present invention adopts the following technical solutions:
  • a double-drive parallel-stage supercharging compressor comprises a compressor casing, a compressor impeller is arranged in the compressor casing, a compressor flow passage is arranged in the compressor casing, and the compressor casing is respectively connected with the compressor flow passage Compressor inlet and compressor outlet;
  • the compressor impeller is provided with an impeller inlet flow passage, and the impeller inlet flow passage is respectively connected with the compressor inlet and the compressor flow passage.
  • the compressor flow path includes a compressor inner flow passage and a compressor outer side disposed on the compressor casing; the ratio of the inlet width of the compressor inner passage to the inlet width of the compressor outer passage is 0.;! ⁇ 10.
  • a compressor diffuser is arranged at the inlet of the flow passage in the compressor.
  • the compressor air outlet comprises a compressor inner runner air outlet communicating with the compressor inner flow passage and a compressor outer runner air outlet communicating with the compressor outer runner, the compressor inner runner outlet 1 ⁇ 10 ⁇
  • the ratio of the width of the air outlet of the compressor is 0. 1 ⁇ 10.
  • the impeller inlet is provided with an impeller inlet and an impeller outlet
  • the compressor impeller is provided with a partition plate arranged at a position between the impeller inlet and the impeller outlet, the partition plate
  • the impeller inlet flow passage is divided into an impeller intake inner passage communicating with the inner passage of the compressor and an impeller intake outer passage communicating with the outer passage of the compressor.
  • a partition wall is disposed in the air inlet passage between the compressor impeller and the air inlet of the compressor, and the partition wall is arranged in an axial direction and is arranged in an entire circumference, the partition wall and the compressor impeller Pressure
  • the air inlet passage between the air inlets of the machine is the inner passage of the compressor inlet and the outer passage of the compressor inlet.
  • the outer passage of the compressor inlet is located on the outward side of the passage in the inlet of the compressor.
  • the inner passage of the compressor inlet is corresponding to and communicates with the inner flow passage of the impeller
  • the outer passage of the inlet of the compressor corresponds to and communicates with the outer flow passage of the impeller
  • the distance between the end of the partition wall near the inlet of the compressor and the inlet of the impeller is 60 ⁇ : 100mrn, the partition wall is close to the end of the inlet of the compressor and the inlet of the compressor The distance is 5 ⁇ 20mm.
  • a plurality of fixed guide vanes are evenly arranged in the outer passage of the compressor inlet.
  • the outer passage of the inlet of the compressor, the outer flow passage of the impeller, and the outer flow passage of the compressor are normally open flow passages.
  • a butterfly valve is arranged in the inner passage of the compressor inlet near the inlet of the compressor, and a butterfly valve is matched with the passage in the inlet of the compressor, and the butterfly valve is provided with a valve shaft connected to one body
  • the valve shaft drive is connected with a control mechanism, and the butterfly valve rotates around the valve shaft under the driving of the control mechanism, thereby opening or closing the inner passage of the compressor air inlet.
  • An adjustable valve is arranged at a position of the inner flow passage of the compressor near the air outlet of the compressor inner passage, a valve shaft is connected to one end of the adjustable valve, a control mechanism is connected to the valve shaft drive, and the adjustable valve is in the control mechanism. The rotation of the valve shaft is driven to realize the opening or closing of the flow passage in the compressor.
  • each adjustable guide vane is rotatably connected to a shifting fork, and the shifting fork is rotatably connected to the fork disc, and the shifting fork disc is rotated by the control mechanism to realize the rotation of the adjustable guide vane, thereby The opening or closing of the flow passage in the compressor is realized.
  • the inner passage of the compressor inlet, the inner passage of the impeller inlet, and the inner passage of the compressor are normally open channels. Further improvement:
  • each of the adjustable guide vanes respectively corresponds to a gear matched with the gear, and the corresponding arrangement of the gears A gear disc, which can be rotated by the control mechanism to realize the rotation of the adjustable guide vane, thereby opening or closing the outer passage of the compressor inlet.
  • An adjustable valve is arranged in the outer flow passage of the compressor near the air outlet of the compressor outer flow passage, and one end of the adjustable valve is connected with a valve shaft, and the wide door shaft drive is connected with a control mechanism, and the adjustable valve is driven by the control mechanism
  • the lower shaft is rotated around the valve shaft to open or close the outer flow passage of the compressor.
  • the invention adopts the above technical solution.
  • the butterfly valve scheme disposed near the inlet of the compressor is arranged! :
  • the process of adjusting the valve arranged in the air outlet of the compressor inner passage and the working process of setting the adjustable flow vane on the compressor diffuser are the same.
  • the adjustable guide vane provided on the butterfly valve or the adjustable valve or the compressor diffuser is rotated by the control mechanism, and the inner passage of the compressor inlet or the compressor is The air outlet of the flow passage is closed, and the inner flow passage of the impeller and the inner passage of the compressor are connected with the inner passage of the air inlet of the compressor, so that the inner flow passage of the impeller and the inner flow passage of the compressor are also closed.
  • the fresh air is driven by the centrifugal force generated by the rotation of the compressor impeller, it is only sucked into the outer passage of the compressor inlet, and then enters the engine to participate in combustion through the impeller inlet flow passage and the compressor outer passage compression acceleration.
  • the adjustable guide vane provided on the butterfly valve or the adjustable valve or the compressor diffuser rotates around the valve shaft under the control mechanism, and the inner passage of the compressor inlet Or open the air outlet of the compressor inner passage to open the inner flow passage of the impeller and the inner flow passage of the compressor at the same time.
  • the fresh air is sucked into the compressor by the centrifugal force generated by the compressor impeller.
  • the fresh air entering the passage of the intake port of the compressor enters the engine and participates in combustion through the centrifugal force of the impeller in the inner flow passage of the impeller and the inner passage of the compressor.
  • the fresh air entering the outer passage of the inlet of the compressor enters the engine and participates in combustion through the centrifugal force and the external flow passage of the impeller and the external flow passage of the compressor to accelerate the work. Since the cross-sectional area of the intake passage of the compressor casing becomes larger, the intake flow rate in the engine under high working conditions is effectively widened, and the engine performance is improved.
  • the working process of the adjustable guide vane arrangement disposed near the inlet of the impeller is arranged close to the compression
  • the working process of the adjustable valve solution at the air outlet of the machine is the same.
  • the adjustable guide vane and the adjustable valve are rotated by the control mechanism, and the outer passage of the compressor inlet or the outlet of the compressor outer passage is closed, due to the outer flow passage of the impeller.
  • the outer flow passage of the compressor is connected to the outer passage of the inlet of the compressor, so the outer flow passage of the impeller and the outer flow passage of the compressor are also closed.
  • the fresh air is only driven by the centrifugal force generated by the rotation of the compressor impeller. It is sucked into the inner passage of the compressor inlet, and then enters the engine to participate in combustion through the impeller intake inner passage and the compressor inner passage compression acceleration. Since the cross-sectional area of the intake passage of the compressor casing becomes smaller, the compressor surge under low-speed engine conditions can be effectively improved.
  • the adjustable guide vane and the adjustable valve are rotated by the control mechanism, and the outer passage of the compressor inlet or the outlet of the compressor outer passage is opened, thereby injecting the impeller.
  • the outer flow passage and the outer flow passage of the compressor are simultaneously opened.
  • the fresh air is sucked into the inner passage of the compressor inlet and the outer passage of the compressor inlet by the centrifugal force generated by the compressor impeller.
  • the fresh air entering the passage of the intake port of the compressor enters the engine and participates in combustion through the centrifugal force of the impeller in the inner flow passage of the impeller and the inner passage of the compressor.
  • the fresh air entering the outer passage of the air inlet of the compressor enters the engine after the centrifugal force is applied to the external flow passage of the impeller and the external flow passage of the compressor to accelerate the work.
  • the machine is involved in the burning. Since the cross-sectional area of the intake passage of the compressor casing becomes larger, the intake flow rate in the engine under high working conditions is effectively widened, and the engine performance is improved.
  • the present invention adopts the above scheme, can effectively improve the compressor surge under the low speed condition of the engine, and can effectively widen the intake air flow under the high working condition of the engine and improve the engine performance.
  • the compressor casing and the compressor impeller structure of the present invention have good inheritance and are easy to realize engineering quickly. The invention will be further described below in conjunction with the drawings and embodiments.
  • Figure 1 is a schematic view showing the structure of a double-drive parallel-stage supercharging compressor in the engine in a high-speed working condition range according to the first embodiment of the present invention
  • FIG. 2 is a schematic structural view of an air outlet of a double-drive parallel-stage supercharging compressor according to Embodiment 1 of the present invention
  • FIG. 3 is a schematic cross-sectional view of a compressor impeller of a dual-drive parallel-stage supercharged compressor according to Embodiment 1 of the present invention
  • Figure 4 is a schematic view showing the structure of a compressor impeller of a double-drive parallel-stage supercharging compressor in Embodiment 1 of the present invention
  • Figure 5 is a schematic view showing the structure of the double-drive parallel-stage supercharging compressor in the low-speed operating condition range of the engine in the first embodiment of the present invention
  • FIG. 6 is a schematic structural view of a double-drive parallel-stage supercharging compressor in Embodiment 2 of the present invention
  • FIG. 7 is a schematic structural view of a compressor casing of a double-drive parallel-stage supercharging compressor in Embodiment 2 of the present invention
  • FIG. 8 is a schematic structural view of a double-drive parallel-stage supercharging compressor in Embodiment 3 of the present invention
  • FIG. 9 is a perspective view of a dual-drive parallel-stage supercharging compressor in an engine and a high-speed working condition range according to Embodiment 3 of the present invention; Schematic;
  • Figure 10 is a compressor casing and control of a double-drive parallel-stage supercharging compressor in Embodiment 3 of the present invention. Schematic diagram of the structure of the institution;
  • Figure 11 is a schematic view showing the structure of a double-drive parallel-stage supercharging compressor in the low-speed operating range of the engine in Embodiment 3 of the present invention.
  • Figure 12 is a schematic view showing the structure of the double-drive parallel-stage supercharging compressor in the low-speed operating range of the engine in the fourth embodiment of the present invention.
  • Figure 13 is a structural schematic view showing the double-drive parallel-stage supercharging compressor of the embodiment 4 of the present invention in the middle and high operating conditions of the engine.
  • Figure 14 is a structural schematic view showing a compressor casing and a control mechanism of a double-drive parallel-stage supercharging compressor in Embodiment 5 of the present invention
  • Figure 15 is a graph showing the characteristics of a compressor in Examples 1-5 of the present invention.
  • a double-drive parallel-stage supercharging compressor includes a compressor casing 1, a compressor impeller 2 is installed in the compressor casing 1, and a compressor gas is provided in the compressor casing 1
  • the compressor flow passage 1 is provided with a compressor air inlet 3 and a compressor air outlet respectively connected to the compressor flow passage
  • the compressor impeller 2 is provided with an impeller intake flow passage, and the impeller intake flow passage respectively It is in communication with the compressor inlet 3 and the compressor flow passage.
  • the compressor flow path includes a compressor inner flow passage 7 and a compressor outer flow passage 8 which are arranged side by side on the compressor casing 1; an intake port width W1 of the compressor inner flow passage 7 and an intake air of the compressor outer flow passage 8 1 ⁇ 10 ⁇
  • the mouth width W2 ratio is 0. 1 ⁇ 10.
  • a compressor diffuser 4 is provided at the helium port of the flow passage 7 in the compressor.
  • the compressor air outlet includes a compressor inner runner air outlet 9 communicating with the compressor inner flow passage 7 and a compressor outer runner air outlet 10 communicating with the compressor outer runner 8, the compressor inner runner air outlet 1 ⁇ : 10 ⁇
  • the ratio of the ratio of the width W3 of the air outlet of the air outlet 10 is 0. 1 ⁇ : 10.
  • the ratio of the ratio of the inlet width W1 of the compressor inner passage 7 to the inlet width W2 of the compressor outer passage 8 and the width W3 of the compressor inner passage outlet 9 and the compressor outer passage outlet 10 The ratio of the width W4 is not the same.
  • the compressor impeller 2 is provided with an impeller inlet port 5 and an impeller outlet port 6, and the compressor impeller 2 is provided with a full circumference at a position between the impeller inlet port 5 and the impeller outlet port 6. a partitioning plate 11 that divides the impeller inlet flow passage into an impeller intake inner passage 12 that communicates with the compressor inner passage 7 and an impeller intake outer passage that communicates with the compressor outer passage 8 13.
  • a partition wall 14 is disposed in the intake passage between the compressor impeller 2 and the compressor inlet 3, and the partition wall 14 is disposed in the axial direction and in the entire circumference.
  • the partition wall 14 spaces the inlet passage between the compressor impeller 2 and the compressor inlet 3 into a compressor inlet passage 15 and a compressor inlet passage 16.
  • the compressor inlet passage 16 is located circumferentially outward of the passage 15 in the compressor inlet.
  • the compressor inlet passage 15 is in communication with and communicates with the impeller intake passage 12, and the compressor inlet passage 16 corresponds to and communicates with the impeller intake passage 13 .
  • the compressor inlet passage 16 and the impeller inlet runner 13 and the compressor runner 8 are normally open passages.
  • the distance H between the end of the partition wall 14 adjacent to the intake port 3 of the compressor and the inlet port 5 of the impeller is 60 to 100 mm; the partition wall 14 is close to the end of the intake port 3 of the compressor and the intake of the compressor.
  • the distance h between the ports 3 is 5 to 20 mm.
  • a plurality of fixed guide vanes 17 are arranged uniformly in the outer passage 16 of the compressor inlet.
  • the structural design is mainly used for fixing the connecting partition wall 14 and the compressor casing 1 on the one hand, and effectively guiding the compressor into the compressor on the other hand.
  • the exhaust gas flow from the outer passage 16 of the intake port smoothly enters the outer flow passage 13 of the impeller.
  • a butterfly valve 18 is provided in the inner passage 15 of the compressor inlet near the compressor inlet 3 to cooperate with the compressor inner passage 15 of the compressor.
  • the butterfly valve 18 is provided with a valve shaft 19 connected to a body.
  • the valve shaft 19 is connected with a control mechanism.
  • the butterfly valve 18 rotates around the valve shaft 19 under the control mechanism, thereby pressing the compressor.
  • the air inlet passage 15 is opened or closed.
  • the butterfly valve 18 is rotated about the valve shaft 19 by the control mechanism, and the inner passage 15 of the compressor inlet is closed, due to the inner flow passage 12 of the impeller.
  • the compressor inner flow passage 7 communicates with the compressor inner passage 15 so that the impeller intake inner passage 12 and the compressor inner passage 7 are also closed, and fresh air is rotated at the compressor impeller 2 at this time.
  • the generated centrifugal force is only sucked into the outer passage 16 of the compressor inlet port, and then compressed and accelerated through the impeller intake outer flow passage 13 and the compressor outer flow passage 8 to enter the engine to participate in combustion. Since the cross-sectional area of the intake passage of the compressor casing 1 is small, the compressor surge can be effectively improved under low engine speed conditions.
  • the butterfly valve 18 is rotated around the valve shaft 19 by the control mechanism, and the inner passage 15 of the compressor inlet is opened, thereby injecting the inflow of the impeller.
  • the channel 12 and the internal flow passage 7 of the compressor are simultaneously opened.
  • the fresh air is sucked into the compressor inlet passage 15 and the compressor inlet passage 16 by the force generated by the compressor impeller 2.
  • the fresh air entering the compressor inlet passage 15 is centrifugally driven by the impeller intake inner passage 12, and the compressor internal flow passage 7 is compressed and accelerated to enter the engine for combustion.
  • the fresh air entering the outer passage 16 of the air inlet of the compressor is subjected to the centrifugal force by the outer flow passage of the impeller, and the outer flow passage 8 of the compressor is accelerated to work and then enters the engine to participate in the combustion. Since the cross-sectional area of the intake passage of the compressor casing 1 becomes large, the intake air amount in the engine under high working conditions is effectively widened, and the engine performance is improved.
  • Embodiment 2 as shown in FIG. 6 and FIG. 7, on the basis of Embodiment 1, the butterfly valve 18 disposed in the passage 15 of the compressor intake port is removed, and the flow passage 7 in the compressor is close to the compressor. 9 inner air outlets
  • the position of the adjustable valve 20 is connected with a valve shaft 19, and the valve shaft 19 is driven and connected with a control mechanism, and is driven by the control mechanism to realize the opening of the flow passage 7 in the compressor. Or close.
  • the adjustable valve 20 is closed, the fresh air entering the engine intake pipe through the inner passage 15 of the compressor inlet, the inner passage 12 of the impeller, and the inner passage 7 of the compressor are blocked.
  • the adjustable valve 20 is opened under the driving of the control mechanism (as indicated by the dotted line of the adjustable valve in the figure), and the working process of this working condition is the same as that in the engine in the first embodiment. Working process under working conditions.
  • Embodiment 3 as shown in FIG. 8 and FIG. 9, on the basis of Embodiment 2, the adjustable valve 20 disposed near the air outlet 9 of the internal flow passage of the blower is removed, and the compressor diffuser 4 is disposed. 2 ⁇ 6 ⁇
  • the ratio of the number of the number of the adjustable guide vanes 21 is 0. 2 ⁇ 6.
  • each of the adjustable guide vanes 21 is rotatably connected to a shifting fork 22, and the shifting fork 22 is rotatably connected to the fork disc 23, and the shifting fork disc 23 is rotated by the control mechanism to realize The rotation of the flow vane 21 is adjusted to achieve opening or closing of the flow passage 7 in the compressor.
  • control mechanism in this embodiment 3 is not limited to the shift fork control mechanism, and a control mechanism of any configuration can be selected.
  • Adjustable guide vane 21 is in a closed state under the driving of the control mechanism, and the centrifugal force generated by the fresh air rotating in the compressor impeller 2 at this time Under the driving, it is only sucked into the inner passage 15 of the compressor inlet and then compressed by the impeller internal flow passage 12 and the compressor inner flow passage 7 to enter the engine to participate in combustion. Since the cross-sectional area of the intake port of the compressor casing becomes smaller, the compressor surge under low-speed engine conditions can be effectively improved. Adjustable guide vane The sheet 21 is closed to block fresh air entering the engine intake pipe through the compressor inlet passage 16, the impeller inlet runner 13, and the compressor outlet runner 8.
  • the adjustable guide vane 21 is in an open state under the driving of the control mechanism, and the working process of this working condition is the same as the high-speed working condition in the engine in the first embodiment. The working process.
  • Embodiment 4 as shown in FIG. 12 and FIG. 13, different from the above-mentioned Embodiments 1, 2, and 3, the scheme is designed to design the inner passage 15 of the compressor inlet, the inner passage 12 of the impeller, and the internal flow of the compressor.
  • Road 7 is a normally open flow path.
  • the butterfly valve 18 disposed in the inner passage 15 of the compressor inlet is removed, and a plurality of uniformly arranged guide vanes are disposed in the outer passage 16 of the compressor inlet near the impeller port 5 of the impeller.
  • each of the adjustable guide vanes 21 respectively corresponds to a gear 24 matched thereto, and the gear 24 is correspondingly provided with a gear disc 25, and the gear disc 25 can be rotated by the control mechanism to achieve adjustable The rotation of the guide vanes 21 causes opening or closing of the outer passage 16 of the compressor inlet.
  • control mechanism in this embodiment 4 is not limited to the gear control mechanism, and a control mechanism of any configuration can be selected.
  • the adjustable guide vane 21 is rotated by the control mechanism to close the compressor outer passage 16 due to the impeller intake.
  • the outer flow passage 13 and the compressor outer flow passage 8 communicate with the compressor outer passage 16 so that the impeller intake outer flow passage 13 and the compressor outer flow passage 8 are also closed, and fresh air is rotated in the compressor impeller 2 at this time.
  • the generated centrifugal force is only sucked into the inner passage 15 of the compressor intake port, and the shield is accelerated by the impeller intake inner passage 12 and the compressor inner passage 7 to enter the engine to participate in combustion. Since the cross-sectional area of the intake passage of the compressor casing becomes smaller, the compressor surge under the low speed condition of the engine can be effectively improved.
  • the adjustable guide vane 21 is rotated by the control mechanism, and the compressor air inlet outer passage 16 is opened, thereby the impeller xenon outer flow passage 13,
  • the compressor outer flow passage 8 is simultaneously opened, and at this time, the fresh air is sucked into the compressor inlet passage 15 and the compressor inlet passage 16 by the centrifugal force generated by the compressor impeller 2.
  • the fresh air entering the passage 15 in the intake port of the compressor is compressed by the impeller intake inner passage 12 and the compressor inner passage 7 under the action of centrifugal force, and then enters the engine to participate in combustion.
  • the fresh air entering the outer passage 16 of the compressor suffocating port is away Under the action of the heart force, the impeller intake outer flow passage 13 and the compressor outer flow passage 8 are compressed and accelerated to work, and then enter the engine to participate in combustion. Since the cross-sectional area of the intake passage of the compressor casing becomes larger, the intake flow rate in the engine under high working conditions is effectively widened, and the engine performance is improved.
  • Embodiment 5 As shown in Fig. 14, the inner passage 15 of the compressor inlet, the inner passage 12 of the impeller, and the inner passage 7 of the compressor are designed as normally open passages.
  • the butterfly valve 18 disposed in the inner passage 15 of the compressor inlet is removed, and an adjustable valve 20 is disposed in the outer flow passage 8 of the compressor near the outlet port 10 of the compressor outer flow passage.
  • the adjustable valve 20 is connected to the control mechanism and driven by the control mechanism to open or close the compressor outer flow passage 8.
  • the adjustable valve 20 when the engine is in a low speed working condition range, the adjustable valve 20 is in a closed state (shown by the solid line of the adjustable valve) driven by the control mechanism, and the fresh air is generated by the rotation of the compressor impeller 2 at this time.
  • the centrifugal force is only sucked into the inner passage 15 of the compressor inlet and then compressed by the impeller inlet inner passage 12 and the compressor inner passage 7 to enter the engine to participate in combustion. Since the cross-sectional area of the intake passage of the compressor casing becomes smaller, the compressor surge under low-speed engine conditions can be effectively improved.
  • the adjustable valve 20 is closed, the fresh air entering the engine intake pipe through the compressor outer passage 16, the impeller intake outer passage 13 and the compressor outer passage 8 is blocked.
  • the adjustable valve 20 is opened under the driving of the control mechanism (as shown by the dotted line of the adjustable valve), and the working process of this working condition is the same as that in the engine in the fourth embodiment.
  • FIG. 15 when only one small compressor flow path is operated, it is a characteristic diagram of a small compressor (as shown by a broken line), when only one large compressor flow path works.
  • the characteristic map of a large compressor as shown by the solid line
  • the characteristic map of the compressor will cover the characteristic map of the compressor of the large and small flow passages. It can be clearly seen from the figure that after adopting this technical solution, the intake air flow range of the compressor is expanded, and two independent efficiency circles appear at the same time, which improves the performance of the compressor.

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

Abstract

La présente invention concerne un précompresseur séquentiel parallèle à double entraînement, qui comprend un logement (1) de compresseur. Un agitateur (2) de compresseur est installé à l'intérieur du logement (1) de compresseur. Un canal d'écoulement de compresseur est prévu à l'intérieur du logement (1) de compresseur. Une entrée d'air de compresseur et une sortie d'air de compresseur, en communication avec le canal d'écoulement de compresseur respectivement sont prévues sur le logement (1) de compresseur. Un canal d'écoulement d'entrée d'air d'agitateur est prévu sur l'agitateur (2) de compresseur. Le canal d'écoulement d'entrée d'air d'agitateur est en communication avec une entrée d'air (3) de compresseur et le canal d'écoulement de compresseur respectivement. Le compresseur peut atténuer des surtensions du compresseur dans un état de fonctionnement d'un moteur à vitesse réduite et étendre un flux d'entrée d'air dans un état de fonctionnement d'un moteur à grande vitesse, de manière à améliorer les performances du moteur.
PCT/CN2012/000713 2012-05-07 2012-05-22 Précompresseur séquentiel parallèle à double entraînement WO2013166626A1 (fr)

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US14/535,344 US20150063989A1 (en) 2012-05-07 2014-11-07 Compressor of turbocharger

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CN201210137085.9 2012-05-07
CN201210137085.9A CN102720692B (zh) 2012-05-07 2012-05-07 双驱并联顺序增压压气机

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WO2021015814A1 (fr) * 2019-07-23 2021-01-28 Edward Charles Mendler Turbocompresseur électrique hybride
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CN114412828A (zh) * 2021-12-24 2022-04-29 中国北方发动机研究所(天津) 一种拓宽压气机堵塞流量的叶轮结构
WO2024107572A1 (fr) * 2022-11-18 2024-05-23 Johnson Controls Tyco IP Holdings LLP Roue multi-étages utilisable avec un compresseur et compresseur à roue multi-étages
CN116591971A (zh) * 2023-07-17 2023-08-15 西北工业大学 一种高低压比的双流道离心压气机

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CN102720692A (zh) 2012-10-10
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