CN106089454A - Electronic combined supercharging variable compression ratio gasoline engine system - Google Patents

Electronic combined supercharging variable compression ratio gasoline engine system Download PDF

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Publication number
CN106089454A
CN106089454A CN201610486612.5A CN201610486612A CN106089454A CN 106089454 A CN106089454 A CN 106089454A CN 201610486612 A CN201610486612 A CN 201610486612A CN 106089454 A CN106089454 A CN 106089454A
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CN
China
Prior art keywords
compression ratio
supercharging
gasoline engine
working condition
engine system
Prior art date
Legal status (The legal status 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 status listed.)
Pending
Application number
CN201610486612.5A
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Chinese (zh)
Inventor
张力
陈斌
罗求顺
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Chongqing University
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Chongqing University
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Filing date
Publication date
Application filed by Chongqing University filed Critical Chongqing University
Priority to CN201610486612.5A priority Critical patent/CN106089454A/en
Publication of CN106089454A publication Critical patent/CN106089454A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D15/00—Varying compression ratio
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
    • F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0223—Variable control of the intake valves only
    • F02D13/0226—Variable control of the intake valves only changing valve lift or valve lift and timing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0223—Variable control of the intake valves only
    • F02D13/0234—Variable control of the intake valves only changing the valve timing only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D23/00—Controlling engines characterised by their being supercharged
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2700/00—Mechanical control of speed or power of a single cylinder piston engine
    • F02D2700/03—Controlling by changing the compression ratio
    • F02D2700/035—Controlling by changing the compression ratio without modifying the volume of the compression space, e.g. by changing the valve timing
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Abstract

The invention discloses a kind of electronic combined supercharging variable compression ratio gasoline engine system.These main function of system parts include: admission line, bypass valve, electric booster, charge air cooler, VVT gear, variable air valve lift range mechanism, engine block, discharge duct, turbocharger.This petrol engine uses the design of big geometrical compression ratio structure.Run with natural aspiration, big compression ratio mode at middle small load condition, the fuel consumption under small load condition in being conducive to improving.At high load working condition, by reducing inlet valve lift, preadmission door close moment, it is changed to small reduction ratio mode and runs；Utilizing the combined supercharging of electronic supercharging and exhaust gas turbocharge, the height of formation quickly response, than boosting capability, meets the high load working condition requirement to charge by height than supercharging in the case of inlet valve negotiability reduces simultaneously；Small reduction ratio, height contribute to the suppression of Engine Knock burning under high load working condition than super charge throttling refrigeration effect.

Description

Electronic combined supercharging variable compression ratio gasoline engine system
Technical field
The present invention relates to technical field of internal combustion engines, particularly relate to a kind of electronic combined supercharging variable compression ratio petrol engine System.
Background technology
Changeable compression ratio technique i.e. VCR (VariableCompressionRatio) is that one can be greatly improved gasoline and sends out The key technology of fuel economy under motivation sub-load.Under partial load condition, big compression ratio can be used, be effectively improved vapour The oil turbine thermal efficiency；Under high load working condition, in order to avoid detonating combustion, small reduction ratio can be used, it is to avoid gasoline engine is not Normal combustion.
The VCR system occurred so far mainly by component structurals such as cylinder cap, cylinder body, piston and crank companies can Degeneration designs, and changes petrol engine compression ratio.Such as: patent CN102937052A, Great Wall Automobile proposes to be changed by hydraulic cylinder Become the cumulative volume of combustor；Patent CN102953845A, Hyundai Motor Corporation discloses one with double bias even Variable compression ratio device；Patent CN104937238A, BorgWarner Inc discloses a kind of variable compressive for electromotor The piston system of ratio.But these structures are complex, reliability is difficult to fully ensure that, the most still lists without volume production type.
Summary of the invention
In view of this, it is an object of the invention to provide a kind of variable compression ratio gasoline engine system, main function components Including: admission line, bypass valve, electric booster, charge air cooler, variable air valve lift range mechanism, engine block, discharge duct, whirlpool Wheel supercharger.This gasoline engine system regulates the IC Intake Valve Closes moment by VVT gear；When inlet valve is entering When gas is closed the most in advance, can obtain actual compression ratio less than geometrical compression ratio, expansion ratio more than actual compression ratio etc. Effect effect；Therefore along with the change in IC Intake Valve Closes moment, actual compression ratio can change.This petrol engine uses the most several What compression ratio structured design.Run with natural aspiration, big compression ratio mode at middle small load condition, Smaller load in being conducive to improving Fuel consumption under operating mode.At high load working condition, by reducing inlet valve lift, preadmission door close moment, it is changed to Small reduction ratio mode is run, to suppress detonating combustion；Utilize the combined supercharging of electronic supercharging and exhaust gas turbocharge simultaneously, formed Quickly the height of response is than boosting capability, meets high load working condition pair by height than supercharging in the case of inlet valve negotiability reduces The requirement of charge.
The electronic combined supercharging variable compression ratio gasoline engine system of the present invention, uses big compression at middle small load condition Ratio；Making inlet valve close the most in advance in air inlet at high load working condition by VVT gear, gasoline engine is actual Compression ratio is less than geometrical compression ratio, and petrol engine runs under small reduction ratio pattern.
Further, using big geometrical compression ratio structure to design, geometrical compression ratio can be more than 15.
Further, high load working condition uses high ratio supercharging, compensates because the reduction of inlet valve lift and opening angle is caused Inlet flow capacity loss, meet the high load working condition requirement to charge.
Further, the combined pressurizing system using electric booster to cooperate with exhaust-driven turbo-charger exhaust-gas turbo charger, there is realization Quickly the height of response is than the ability of supercharging, can control pressure ratio flexibly.
Further, variable intake valve lift mechanisms it is integrated with；Middle-low load working condition uses big valve stroke, high load working condition Use little valve stroke；Valve stroke under middle-low load working condition is more than the valve stroke under high load working condition.
Further, under high load working condition, the high supercharging pressure level that combined supercharging is formed coordinates little valve stroke, can be at inlet valve Place forms throttling refrigeration effect, again cools down air inlet after charge air cooler.
Further, systematicness integration electric supercharger, charge air cooler, variable air valve lift range mechanism, engine block, turbocharging Device.
The invention has the beneficial effects as follows: the electronic combined supercharging variable compression ratio gasoline engine system of the present invention, can wait Effect realizes petrolic variable compression ratio and runs.Under middle small load condition, the design of big geometrical compression ratio structure and big compression The ratio method of operation, can improve petrol engine fuel economy.Under high load working condition, small reduction ratio, height throttle than super charge Cold effect contributes to the suppression of detonating combustion；The height of combined supercharging can help to improve petrolic dynamic property than supercharging. The application of electronic combined supercharging, the height possessing quickly response compares boosting capability, it is possible to meet vehicle gasoline engine variable parameter operation Use requirement.
Accompanying drawing explanation
Fig. 1 is the present invention electronic combined supercharging variable compression ratio gasoline engine system structure chart
Fig. 2 is that small load condition natural aspiration big compression ratio operational mode constant volume heats Ideal Cycle figure
Fig. 3 is that moderate duty operating mode plenum big compression ratio operational mode constant volume heats Ideal Cycle figure
Fig. 4 is that high load working condition plenum small reduction ratio operational mode constant volume heats Ideal Cycle figure
Fig. 5 is that high load working condition is high heats Ideal Cycle figure than supercharging small reduction ratio operational mode constant volume
Fig. 6 is small load condition natural aspiration big compression ratio operational mode inlet valve lift and is effectively compressed angle schematic diagram
Fig. 7 is moderate duty operating mode plenum big compression ratio operational mode inlet valve lift and is effectively compressed angle signal Figure
Fig. 8 is high load working condition plenum small reduction ratio operational mode inlet valve lift and is effectively compressed angle schematic diagram
Fig. 9 is that high load working condition height than supercharging small reduction ratio operational mode inlet valve lift and is effectively compressed angle schematic diagram
Figure 10 is moderate duty operating mode exhaust gas turbocharge gasoline engine inlet-air view
Figure 11 is high load working condition electronic combined supercharging gasoline engine inlet-air view
Figure 12 is high than supercharging small reduction ratio operational mode air inlet initial point moment and air inlet restriction cooling schematic diagram
Figure 13 is high than supercharging small reduction ratio operational mode IC Intake Valve Closes moment schematic diagram
Figure 14 is high than supercharging small reduction ratio operational mode air inlet lower dead center moment schematic diagram
Figure 15 is high than supercharging small reduction ratio operational mode compression ignition moment schematic diagram
Figure 16 is high than supercharging small reduction ratio operational mode compression top center moment schematic diagram
Figure 17 is high than supercharging small reduction ratio operational mode aerofluxus initial point schematic diagram at quarter
Detailed description of the invention
Fig. 1 is the present invention electronic combined supercharging variable compression ratio gasoline engine system structure chart.As it is shown in figure 1, this vapour Oil turbine system mainly by admission line 4, bypass valve 6, electric booster 7, charge air cooler 8, variable air valve lift range mechanism 1, send out Motivation body 10, discharge duct 9, turbocharger 3, VVT gear 11 form；By VVT gear 11 Control the IC Intake Valve Closes moment in real time, make inlet valve close the most in advance in air inlet；According to petrol engine load condition Difference, the effective compression ratio in petrol engine running can be adjusted；Engine block 10 uses geometrical compression ratio Big geometrical compression ratio structure more than 15 can design, make gasoline engine use big compression ratio at middle small load condition, in big load work Condition petrol engine runs under small reduction ratio pattern, and i.e. gasoline engine compression ratio under middle small load condition is more than at big load Compression ratio under operating mode.
Fig. 2 is that small load condition natural aspiration big compression ratio operational mode constant volume heats Ideal Cycle figure；Admission pressure is low In environment atmospheric pressure p0, equivalent compress ratio is equal to geometrical compression ratio (V3/V1).Fig. 3 is the moderate duty big pressure of operating mode plenum Contract and heat Ideal Cycle figure than operational mode constant volume；Admission pressure is higher than environment atmospheric pressure p0, equivalent compress ratio is equal to geometry Compression ratio (V3/V1).Fig. 4 is that high load working condition plenum small reduction ratio operational mode constant volume heats Ideal Cycle figure；Air inlet increases In pressure pressure relatively Fig. 3 higher；Due to inlet valve d in the drawings3Point is closed in advance, curve d3c3Section is the section of being effectively compressed, V4For effectively Minimum cylinder volume, effective compression ratio (V4/V1) less than geometrical compression ratio (V3/V1).Fig. 5 is that high load working condition is high less compression than supercharging Ideal Cycle figure is heated than operational mode constant volume；Use high supercharging pressure level plenum；Inlet valve d in the drawings4Point is closed in advance, bent Line d4c4Section is the section of being effectively compressed, V5For being effectively compressed volume, effective compression ratio (V5/V1) less than geometrical compression ratio (V3/V1)；Figure Volume V it is effectively compressed in 55Relatively Fig. 4 is effectively compressed volume V4Less, therefore effective compression ratio is minimum.
Fig. 6 is small load condition natural aspiration big compression ratio operational mode inlet valve lift and is effectively compressed angle signal Figure；Curve l in figure1For valve lift curve, valve-opening time section is θIO1；Curve pc1For in-cylinder pressure curve, admission pressure For pk1, maximum combustion pressure is pz1, θc1For being effectively compressed angle.Fig. 7 is that the moderate duty big compression ratio of operating mode plenum runs Pattern inlet valve lift and be effectively compressed angle schematic diagram, curve l2For valve lift curve, valve-opening time section is θIO2； Curve pc2For in-cylinder pressure curve, admission pressure is pk2, maximum combustion pressure is pz2, θc2For being effectively compressed angle；Gas in Fig. 7 Door lifting curve is identical with valve lift curve in Fig. 6, is effectively compressed angle, θ in Fig. 7c2With Fig. 6 is effectively compressed angle, θc1Phase With.
Fig. 8 is high load working condition plenum small reduction ratio operational mode inlet valve lift and is effectively compressed angle signal Figure；Curve l3For valve lift curve, valve-opening time section is θIO3；Curve pc3For in-cylinder pressure curve, admission pressure is pk3, maximum combustion pressure is pz3, θc3For being effectively compressed angle；In Fig. 8, the IC Intake Valve Closes moment is in advance, therefore valve-opening time Section θIO3Less than the θ in Fig. 7 and Fig. 6IO2And θIO1, in Fig. 8, valve lift curve is less than the valve lift curve in Fig. 7 and Fig. 6, Fig. 8 is effectively compressed angle, θc3Less than the θ in Fig. 7 and Fig. 6c2And θc1.Fig. 9 is that high load working condition is high to be transported than supercharging small reduction ratio Row mode inlet valve lift and be effectively compressed angle schematic diagram；Curve l4For valve lift curve, valve-opening time section is θIO4；Curve pc4For in-cylinder pressure curve, admission pressure is pk4, maximum combustion pressure is pz4, θc4For being effectively compressed angle；Institute Having in operational mode, lifting curve, valve-opening time section in Fig. 9, to be effectively compressed angle the most minimum, and admission pressure is the highest.
Figure 10 is moderate duty operating mode exhaust gas turbocharge gasoline engine inlet-air view, now my supercharger list Being solely engine compresses air inlet, boost pressure is relatively low.Figure 11 is high load working condition electronic combined supercharging gasoline engine inlet-air shape State schematic diagram, now electric booster and turbocharger are engine booster jointly, and boost pressure is higher.
High less pressure than supercharging with the high load working condition of the present invention electronic combined supercharging variable compression ratio gasoline engine system As a example by contracting is than operational mode, details are as follows for its thermodynamics work process: electric booster 7 is with turbocharger 3 cooperation also Compression air inlet, high temperature, high pressure admission after compression are cooled down with water-cooled charge air cooler 8 by air-cooled intercooler 5；Inlet valve 14 exists The least lift condition open, in cold after high pressure admission flow through valve produce throttling refrigeration effect, subsequently enter cylinder； VVT gear 1 makes inlet valve 14 close in piston lower dead center in advance, produces the expansion ratio equivalence effect more than compression ratio Should, as shown in figure 13, now cylinder internal volume is V5；Piston 13 continues traveling downwardly to air inlet bottom dead center position shown in Figure 14, complete into Gas stroke, now cylinder internal volume reaches maximum V3；Afterwards, piston start to move upward from bottom dead center position be compressed punching Journey, when piston 13 runs to position shown in Figure 15, plug ignition burns；Piston continues to go upward to compression top center, cylinder Internal volume minimizes value V1, in-cylinder combustion pressure drastically raises, and as shown in figure 16, actually active minimum cylinder volume is V5-V1；It After, expansion stroke starts, and expansion work is to position shown in Figure 17 under cylinder inner high voltage gas push for piston 13, and expansion stroke is tied Bundle, actually active allowance for expansion is V2, therefore effectively expansion ratio is more than effective compression ratio；Meanwhile, exhaust valve 12 has turned on, aerofluxus Stroke starts, and the waste gas after piston 13 continues up burning discharges cylinder.

Claims (7)

1. an electronic combined supercharging variable compression ratio gasoline engine system, is characterized in that: pass through VVT gear Control the IC Intake Valve Closes moment in real time, make inlet valve close the most in advance in air inlet, thus realize changing of actual compression ratio Becoming, gasoline engine uses big compression ratio at middle small load condition, transports under small reduction ratio pattern at high load working condition petrol engine OK.
Electronic combined supercharging variable compression ratio gasoline engine system the most according to claim 1, is characterized in that: use big Geometrical compression ratio structure designs, and geometrical compression ratio can be more than 15.
Electronic combined supercharging variable compression ratio gasoline engine system the most according to claim 1, is characterized in that: big load Operating mode uses high ratio supercharging, compensates the inlet flow capacity loss caused because of the reduction of inlet valve lift and opening angle, full The foot high load working condition requirement to charge.
Electronic combined supercharging variable compression ratio gasoline engine system the most according to claim 2, is characterized in that: use electricity The combined pressurizing system that dynamic supercharger cooperates with exhaust-driven turbo-charger exhaust-gas turbo charger, has the height realizing quickly response than the energy of supercharging Power, can control flexibly to pressure ratio.
Electronic combined supercharging variable compression ratio gasoline engine system the most according to claim 1, is characterized in that: be integrated with Variable intake valve lift mechanisms；Middle-low load working condition uses big valve stroke, and high load working condition uses little valve stroke.
Electronic combined supercharging variable compression ratio gasoline engine system the most according to claim 1, is characterized in that: big load Under operating mode, combined supercharging formed high supercharging pressure level coordinate little valve stroke, throttling refrigeration effect can be formed at inlet valve, in After cooler, air inlet is cooled down again.
Electronic combined supercharging variable compression ratio gasoline engine system the most according to claim 1, is characterized in that: systematicness Integration electric supercharger, charge air cooler, variable air valve lift range mechanism, engine block, turbocharger.
CN201610486612.5A 2016-06-28 2016-06-28 Electronic combined supercharging variable compression ratio gasoline engine system Pending CN106089454A (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109458255A (en) * 2017-09-06 2019-03-12 上汽通用汽车有限公司 Gasoline engine combined pressurizing system control method and gasoline engine combined pressurizing system
CN110080889A (en) * 2018-01-25 2019-08-02 丰田自动车株式会社 The control device of internal combustion engine
CN110832184A (en) * 2017-07-05 2020-02-21 本田技研工业株式会社 Peripheral structure of engine
CN112282943A (en) * 2020-10-30 2021-01-29 吉林大学 Effective thermal efficiency-based compression ratio control method for quality-adjusted engine
CN113202628A (en) * 2021-06-02 2021-08-03 北京理工大学 Two-stage low-compression-cycle implementation method, device and detection method

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CN101466933A (en) * 2006-06-15 2009-06-24 丰田自动车株式会社 Spark ignition type internal combustion engine
CN101699040A (en) * 2009-10-26 2010-04-28 清华大学 Two-stage variable compression ratio system of gasoline engine and control method thereof
CN102137993A (en) * 2009-05-01 2011-07-27 丰田自动车株式会社 Spark-ignited internal combustion engine
CN105508029A (en) * 2015-12-28 2016-04-20 重庆大学 Principle and device for electric pressurizing, inlet air compressing and cooling and air valve throttling refrigeration of gasoline engine

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Publication number Priority date Publication date Assignee Title
US5724927A (en) * 1995-04-27 1998-03-10 Yamaha Hatsudoki Kabushiki Kaisha Direct cylinder injected engine and method of operating same
CN101046177A (en) * 2006-03-31 2007-10-03 马自达汽车株式会社 Spark-ignition gasoline engine
CN101466933A (en) * 2006-06-15 2009-06-24 丰田自动车株式会社 Spark ignition type internal combustion engine
CN102137993A (en) * 2009-05-01 2011-07-27 丰田自动车株式会社 Spark-ignited internal combustion engine
CN101699040A (en) * 2009-10-26 2010-04-28 清华大学 Two-stage variable compression ratio system of gasoline engine and control method thereof
CN105508029A (en) * 2015-12-28 2016-04-20 重庆大学 Principle and device for electric pressurizing, inlet air compressing and cooling and air valve throttling refrigeration of gasoline engine

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110832184A (en) * 2017-07-05 2020-02-21 本田技研工业株式会社 Peripheral structure of engine
CN109458255A (en) * 2017-09-06 2019-03-12 上汽通用汽车有限公司 Gasoline engine combined pressurizing system control method and gasoline engine combined pressurizing system
CN110080889A (en) * 2018-01-25 2019-08-02 丰田自动车株式会社 The control device of internal combustion engine
CN110080889B (en) * 2018-01-25 2021-08-20 丰田自动车株式会社 Control device for internal combustion engine
CN112282943A (en) * 2020-10-30 2021-01-29 吉林大学 Effective thermal efficiency-based compression ratio control method for quality-adjusted engine
CN113202628A (en) * 2021-06-02 2021-08-03 北京理工大学 Two-stage low-compression-cycle implementation method, device and detection method

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Application publication date: 20161109