CN1863993B - Method for optimizing the operation of a charged reciprocating internal combustion engine in the lower engine speed range - Google Patents

Method for optimizing the operation of a charged reciprocating internal combustion engine in the lower engine speed range Download PDF

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Publication number
CN1863993B
CN1863993B CN2004800292108A CN200480029210A CN1863993B CN 1863993 B CN1863993 B CN 1863993B CN 2004800292108 A CN2004800292108 A CN 2004800292108A CN 200480029210 A CN200480029210 A CN 200480029210A CN 1863993 B CN1863993 B CN 1863993B
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China
Prior art keywords
valve
engine
cylinder
intake valve
scavenging
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CN2004800292108A
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Chinese (zh)
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CN1863993A (en
Inventor
沃尔博格·赖纳
马丁·霍普
奥利弗·朗
乔斯·盖格
安德里斯·泽尔
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FEV Co Ltd
FEV Europe GmbH
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FEV Co Ltd
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    • 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
    • F02D13/0203—Variable control of intake and exhaust valves
    • F02D13/0215—Variable control of intake and exhaust valves changing the valve timing only
    • 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
    • F02B25/00—Engines characterised by using fresh charge for scavenging cylinders
    • F02B25/14—Engines characterised by using fresh charge for scavenging cylinders using reverse-flow scavenging, e.g. with both outlet and inlet ports arranged near bottom of piston stroke
    • F02B25/145—Engines characterised by using fresh charge for scavenging cylinders using reverse-flow scavenging, e.g. with both outlet and inlet ports arranged near bottom of piston stroke with intake and exhaust valves exclusively in the cylinder head
    • 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
    • F02B37/12—Control of the pumps
    • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
    • 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
    • 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
    • F02D13/0261—Controlling the valve overlap
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/0002—Controlling intake air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/0002—Controlling intake air
    • F02D41/0007—Controlling intake air for control of turbo-charged or super-charged engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • 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
    • F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
    • F02B2275/14—Direct injection into combustion chamber
    • 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
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • 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
    • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
    • F02B33/32—Engines with pumps other than of reciprocating-piston type
    • 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
    • F02D13/0253—Fully variable control of valve lift and timing using camless actuation systems such as hydraulic, pneumatic or electromagnetic actuators, e.g. solenoid valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/0002—Controlling intake air
    • F02D2041/001—Controlling intake air for engines with variable valve actuation
    • 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
    • F02D23/02—Controlling engines characterised by their being supercharged the engines being of fuel-injection type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/04—Injectors peculiar thereto
    • F02M69/042—Positioning of injectors with respect to engine, e.g. in the air intake conduit
    • F02M69/044—Positioning of injectors with respect to engine, e.g. in the air intake conduit for injecting into the intake conduit downstream of an air throttle valve
    • 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
    • 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
    • Y02T10/40—Engine management systems

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)

Abstract

The invention relates to a method for operating a piston type internal combustion engine. The engine comprises a fuel-injected device and each cylinder comprises at least one outlet valve communicated with a gas exhaust gas system, and at least one inlet valve connected with an air inlet system. The engine also comprises a means for increasing the boost pressure in the air inlet system. A control device for variably adjusting at least the opening times of the inlet valves is provided. The inlet opening times of the inlet valves within the lower engine speed range can be adjusted via the control device in such a manner that there is a valve overlap with the closing time of the corresponding outlet valves. Therefore, the cylinder is scavenged with fresh charge air before and/or during charge exchange in the area of top dead center. The ratio of residua gas in the cylinder that has been scavenged is at least up to 95 %. When the rotating speed of the internal combustion engine is up to 2000 revolutions per minute, the opening/closing times of the valves is adjusted.

Description

Be used for the method that the running of the internal-combustion piston engine of supercharging optimized at low engine speed range
Background technique
In so-called charged piston internal-combustion engine, required combustion air is sent to cylinder via a pressurized machine with the pressure that is higher than external pressure.When the time comes, boost and can carry out via a so-called exhaust-gas turbocharger, in this exhaust-gas turbocharger, a turbine press machine is driven by a turbine that links to each other with vent systems, and this turbocompressor is on the pressure side linking to each other with gas handling system.But, boosting and also can carry out through a so-called mechanical supercharger, the driving energy of this mechanical supercharger extracts from the bent axle of internal-combustion piston engine.Fuel oil or through spraying the gas-entered passageway that corresponding amount of fuel is admitted to each cylinder respectively, or be admitted in the cylinder through spraying directly.In order to take a breath, each cylinder is respectively equipped with at least one exhaust valve and at least one intake valve, and said exhaust valve correspondingly links to each other with gas handling system with vent systems with intake valve.
Confirm now, in the low engine speed range of internal-combustion piston engine and in (promptly exhaust-gas turbocharger and mechanical supercharger) low transfer rate of consequent pressurized machine, during when starting operation with at low cruise, the bearer properties deficiency.
Summary of the invention
Task of the present invention is, when starting operation and when moving with the slow-speed of revolution, improves the performance characteristic of the internal-combustion piston engine of the above-mentioned type when particularly in 1000 and 1300 rev/mins speed range, moving.
Task of the present invention is achieved in that promptly the present invention provides a kind of method that is used to operate an internal-combustion piston engine; This internal-combustion engine has fuel injection apparatus, has the ventilation door, and each cylinder has at least one exhaust valve that is connected with a vent systems and at least one intake valve that is connected with a gas handling system; And the device with the boost pressure that is used for improving gas handling system wherein, is provided with a control gear that is used for adjusting changeably the point of opening time at least of intake valve; And time point is opened in the air inlet of ventilation door and/or the exc. time point is so adjusted through control gear in low engine speed range; Make to have a valve overlap, and, it is characterized in that in view of the above taking a breath before and/or in gas exchange process, with fresh pressurized air cylinder being carried out scavenging in the scope at upper dead center; Have only enough when existing in the sucking pipe that joins with intake valve at, when being used for pressure to cylinder scavenging and raising; Intake valve and exhaust valve just are unlocked, and thus, exist the scavenging pressure in a front poor; Wherein be pressurized the air that device is sent to gas handling system and have the pressure higher than the back pressure in the vent systems; Reached at least 95% by the residual gas cleared away in the cylinder, wherein, when 2000 rev/mins of the turn ups of internal-combustion piston engine, the valve switch time is adjusted.
Have fueling injection equipment, particularly direct injection device; Has the ventilation door; Each cylinder has at least one exhaust valve that links to each other with vent systems and at least one intake valve that links to each other with gas handling system respectively; And have in the internal-combustion piston engine of device of the boost pressure that is used for improving gas handling system; Above task solves through following measure; Promptly be provided with an opening time point that is used for adjusting at least changeably intake valve control gear and the air inlet of low engine speed range ventilation door open time point and/or exc. time point through said control gear by so adjustment, make exist one with the valve overlap of the shut-in time point of corresponding exhaust valve and make in view of the above cylinder ventilation before and/or in gas exchange process in the scope at upper dead center with fresh air feed by scavenging.The advantage of this working method is; On the one hand; Residual gas as much as possible from cylinder by cleaning and in view of the above after IC Intake Valve Closes is in the cylinder, the temperature levels that is introduced into air is reduced slightly, the air consumption level can greatly be improved when the slow-speed of revolution in view of the above.Tendency to detonate is reduced through clearing away residual gas to a great extent.
Particularly with situation that direct injection combines under, through engine air capacity since the cooling of the mixing in the firing chamber be improved.In view of the above, compare with the reciprocating engine of adjusting exhaust valve and intake valve correct time, can be particularly when starting running and when operating, be significantly improved with low speed in the torque of extracting on the internal-combustion piston engine.In order to improve the scavenging to cylinder, advantageously, the opening time of exhaust valve point and shut-in time point also are variable.In addition, advantageously, have only enough when existing in the sucking pipe that joins with intake valve at, when being used for pressure to cylinder scavenging and raising, intake valve and exhaust valve just are unlocked.Particularly strive for clearing away at least the residual gas of at least 95% in the cylinder.
According to first form of implementation, for example have only intake valve or have only exhaust valve to be adjusted.According to second form of implementation, intake valve and exhaust valve are adjusted.According to the 3rd form of implementation, have only the part of intake valve and/or exhaust valve to be adjusted.
Among the present invention, when 2000 rev/mins of the rotating speed up of internal-combustion piston engine, valve is adjusted.But another form of implementation regulation is preferably no longer carried out this adjustment in order to sweep residual gas when surpassing this rotating speed.According to a form of implementation, in accelerating process, particularly in start-up course, maximum engine load 30% and 100% between scope in carry out adjustment to the valve switch time.Internal-combustion piston engine is preferably pressed the diesel engine principle work and is operated through an injection regulating device.
Produce the enthalpy of a rising based on the cylinder air feed that has improved, the enthalpy of this rising when adopting exhaust-gas turbocharger, cause the quick raising of boost pressure and cause in view of the above stipulating effect improved.
The higher pressurized machine power of same generation in the mechanical supercharger that the driving energy extracts from bent axle; This is because from the working stroke to the working stroke, cause a useful scavenging pressure poor continuously very soon, and makes final torque be able to soon increase based on the cylinder air feed that increases through higher supercharging in view of the above much.
Exist the variation of for example passing through suction system in low engine speed range, to influence the possibility of scavenging pressure difference in addition for residual gas is carried out scavenging.Can influence suction system in the following manner; For example: to the stepless adjustment of an oscillator tube length; Conversion between the different oscillator tube length; In compound oscillator tube,, be transformed on the different accumulator volumes and/or the conversion between the different oscillator tube diameters to the selectable disconnection of a single pipe of each cylinder.For example can adopt single oscillator tube, wherein, in low engine speed range, adopt oscillator tube than used vibration pipe range in higher rotation speed.
Particularly there is the possibility that different, as to be used to influence scavenging pressure difference measures is mutually combined.
The function mode of invention can be caused by a kind of internal-combustion piston engine on the one hand, in this internal-combustion piston engine, is that intake valve has at least the valve device variable along the part area at least, and these variable valve devices can be handled via control gear.This valve device can for example be the structure of so-called electromagnetic valve device.In these electromagnetic valve devices, between two electromagnet, an armature that links to each other with valve is according to importing closed position and enable possition to valve respectively through the given in advance circulation of control gear.When the time comes, opening time point and shut-in time put given in advance by control gear.Other electromechanics or electromagnetic air valve regulating device also may be utilized.
Variable or the complete variable mechanical valves transmission device of the also available part of function mode of invention carries out.In these valve devices, between the fixing distribution shaft cam of camshaft and valve, be provided with additional, adjustable control cam.The function mode of invention is particularly advantageous as far as internal-combustion piston engine traditional, that have the ventilation door of controlling via camshaft especially.At least be that the camshaft that is used for intake valve and advantageously also is used for exhaust valve has corresponding adjustable, the cam that is used for adjusting at least the opening time point.Cam regulator links to each other with camshaft and is handled by a control gear.But, but the system of other mechanical adjustment also can be used on the valve device so that guarantee that ventilation door open-interval necessity is overlapping.These mechanical systems can for example have a bowl-type pushrod control device, a drawbar control gear or a lever controller or also can have a rocking bar control gear.In addition, also there is the possibility that different systems is mutually combined.
Advantageously regulation in an operating range of not sweeping residual gas, in order in low engine speed range, to generate valve overlap, provides exhaust gas recirculation via handling the ventilation door changeably.Exhaust gas recirculation can and/or use an exhaust gas recirculation valve to carry out through in-engine rectification circuit.For example this exhaust gas recirculation can be through just not carrying out in clearing away the operating range of residual gas through the regulation of the valve overlap in low speed range a this moment.
According to another design of invention, use one automobile-used, have the direct injection device and have the four-stroke gasoline engine of at least three cylinders.Each cylinder is furnished with at least one intake valve and at least one exhaust valve.A boost pressure in this intake valve and the gas handling system improves device and links to each other.Be provided with one and be used to adjust the opening time point of intake valve and exhaust valve and the regulating device of shut-in time point.This regulating device can activate in order to clear away residual gas in order in a low engine speed range, to reach valve overlap.This petrol engine has an active device; This active device define qualification, generate the signal that regulating device is activated when being used for the condition from cylinder cleaning residual gas; Wherein, Have only enough when existing in the sucking pipe that joins with intake valve at, when being used for pressure to cylinder scavenging and raising, intake valve and exhaust valve just are unlocked.
According to one first form of implementation, this active device has the condition of qualification with depositing, makes when defining enough scavenging pressure differences, and said signal is only and can generates.But in order in cylinder, to generate the condition of the scavenging pressure difference that provides enough earlier, this active device also can be coupled with a forecast module, can determine when according to the parameter that obtains by this forecast module to generate said signal.This active device forecasts the preferably constituent element of a valve control apparatus of module with this, and this valve control apparatus links to each other with device for controlling engine via the control zone network-bus.
According to a form of implementation regulation, said scavenging difference can directly or indirectly obtain by a measuring device.According to another form of implementation regulation, said scavenging difference can obtain from being deposited with replenishing in the operational data the engine controlling unit.These two kinds of ways also can be coupled each other.A form of implementation has secondary injection, so that can utilize the combustion characteristic that has been enhanced thus based on high scavenging.' hysteresis ' adjustment of in low engine speed range, carrying out igniting also is possible.
Particularly one by the diesel engine principle and also stipulate in the internal-combustion piston engine by the petrol engine principle work, average gas pressure was raised before intake valve.This particularly can be used in the four stroke cycle when controlled self ignition.In addition, the increase of torque also can be implemented through following measure, promptly takes measure that add, motor.These measures for example can be following, can be separately or the measure that mutually combines and adopt: or amount of fuel when increasing direct injection grease-added to air inlet; Secondary fuel injection or repeatedly oil spout; Adjustment press machine blade or guide wheel when adopting exhaust-gas turbocharger; ' hysteresis ' adjustment is sprayed in petrol engine, in diesel engine, general adjustment etc. is carried out in injection.
The injection that for example distributes.The injection of this distribution can stipulate, one first amount of fuel comprises the about 50% to 80% of amount of fuel to be sprayed, and the amount of fuel of injection subsequently comprises 20% to 50% amount of fuel.When the time comes, said amount of fuel to be sprayed subsequently can be assigned to one or more courses of injection.The injection that distributes is particularly preferably being carried out in the speed range between 1300 rev/mins and 1500 rev/mins under the approximate at least full-power situation.A form of implementation in the petrol engine of a direct injection has for example stipulated that one is once sprayed and a secondary injection; This once spray with secondary injection in, once spray injection duration with secondary injection than being about 60% to 75% pair 25% to about 40%.
In addition, also there is the possibility that particularly in supercharging gasoline engine, also can in low engine speed range, adopt different combustion processes with direct injection device.This can be a kind of even combustion process or a kind of with different levels combustion process.Can for example use the combustion process that a kind of beam is leading or air is leading.When the time comes, direct injection can be used one or more spargers for each cylinder.Preferably use a kind of spiral hole sparger or a kind of multi-hole injector.The angle of attack of sparger is advantageously in being lower than 70 ° scope, particularly in about 50 ° scope.
Description of drawings
Accompanying drawing by signal specifies the present invention below.The characteristic that illustrates respectively in the accompanying drawings can be with the further feature of accompanying drawing and also can be combined into other form of implementation with above-mentioned characteristic and be unrestricted.Accompanying drawing is depicted as:
Fig. 1 is the circuti diagram with internal-combustion piston engine of exhaust-gas turbocharger.
Fig. 2 is the circuti diagram of internal-combustion piston engine shown in Figure 1, that have mechanical supercharger.
Fig. 3 is the internal-combustion piston engine for engine driven supercharging, air feed coefficient and residual gas content and rotating speed and open-interval graph of relation.
Fig. 4 is for turbo charged internal-combustion piston engine, the graph of relation of boost pressure and air feed coefficient and the opening time point in when ventilation in the scope of upper dead center.
Fig. 5 is used for clearing away at low engine speed range the schematic views of the internal-combustion piston engine of residual gas for another.
Embodiment
Internal-combustion piston engine with four cylinder I, II, III, IV has been shown in Fig. 1, and each cylinder has an intake valve 2 and an exhaust valve 3 respectively.Said intake valve 2 links to each other with a gas handling system 4, and said exhaust valve 3 links to each other with a vent systems 5.
In addition, shown internal-combustion piston engine also has one for example for being total to the direct injection device of road injection system 6 structures.Fuel oil is sent to common road injection system 6 via a pump 7.
In order to handle intake valve, regulation has a camshaft 8, and the cam of this camshaft 8 is adjustable structure and can adjusts through a cam regulator 9 about the opening process of intake valve 2.This cam regulator 9 links to each other with a control gear 10, and the given in advance load of fueling injection equipment and the bases such as ignition mechanism that are not shown specifically is in the drawings handled via this control gear 10 through throttle control 11.
In the embodiment shown in this figure, exhaust valve 3 is handled through a camshaft 12, and the cam of this camshaft 12 has a given in advance regularly control profile.But, a cam setting device and/or a camshaft phase regulating device of exhaust valve also can be proposed.These two camshafts 8 and 12 the crank-driven of mode through not being shown specifically in the figure with routine.
Vent systems 5 links to each other with the air pressurizing unit 13.1 of a turbocharger arrangement, and the exhaust turbine 14 of this air pressurizing unit 13.1 is exerted pressure by waste gas and its exhaust gas turbine press machine 15 is on the pressure side linking to each other with gas handling system 4.Can also can be located at petcock 16 in the outlet pipe 6, controlled through one avoids increasing for the disabled boost pressure of operating range at that time through reducing the exhaust gas flow that turbo machine is exerted pressure.
Structure at the internal-combustion piston engine shown in Fig. 2 is substantially similar to the structure by the described equipment of Fig. 1, therefore can quote it.Its difference only is that a kind of mechanical supercharger 13.2 is as air pressurizing unit, and the driving energy of this mechanical supercharger 13.2 extracts from the bent axle 1.1 of internal-combustion piston engine 1.
For both of these case; For the manipulation of the intake valve 2 of each cylinder is regulation like this; Promptly in low engine speed range; The distribution shaft cam of intake-side camshaft 8 is adjusted towards " air inlet is in advance opened " direction via cam regulator 9, and intake valve 2 was opened respectively before exhaust valve closing.Air pressurizing unit 13.1 or 13.2 must so be placed; When making the slow-speed of revolution in the startup scope and for example exist the scavenging pressure in a front poor in 1300 rev/mins the operating range, promptly guarantee to be pressurized the air that device is sent to gas handling system 4 and have the pressure higher than the back pressure in the vent systems 5.
To the high rotational speed transition time, the adjustment controlled device 10 that the opening time of intake valve is put rotates back into the time point into the normal operation defined via cam regulator 9.
Substitute described turbosupercharger or mechanical supercharger, can be supercharging a kind of equipment that is used for so-called pulse pressure-charging is provided.When the time comes, in order to increase air demand, utilize the pressure reduction between gas handling system and the cylinder.When having this pressure reduction, pressurized air under the suitable differential pressure conditions can through the automatic and controlled sealing medium pulsed in gas-entered passageway at that time be sent to cylinder.When correspondingly adjusting valve overlap, the air demand that can realize cleaning residual gas in short-term and improve in view of the above.
For possible shifting to an earlier date, the control time of invention regulation " air inlet is in advance opened " is restricted through clear passage that exist, between valve and piston in its concrete engine structure.Piston geometry through corresponding firing chamber configuration and/or coupling can make shifting to an earlier date far away prior to LWOT (the boost pressure exchange in the upper dead center), so that can begin scavenging process as early as possible of control time " air inlet is in advance opened ".Another advantage is, particularly when adopting turbosupercharger, produces the reaction to the pressurized machine design through improving pressurization, makes towards the turbosupercharger of power to be selected to and maybe and also can to adopt the small construction unit in view of the above.
With situation that direct injection combines under, detent torque can be enhanced, and rated moment is reached when quite low rotating speed.Less pinking has limited from the minimizing that reaches the circulation air demand that rated moment causes.The better combustion efficiency that is caused has reduced the fuel consume in whole speed range.
Particularly when adopting turbosupercharger, in following influence, produce and improve.
In direct injection, a little has reduced the torque advantage of having set up slow slightly location of peak pressure.This pinking of increasing restriction is to set up through the cylinder air demand that raises in the firing chamber.Higher circulation air demand is directly in the firing chamber, to vaporize and produce owing to fuel oil.This causes mixing cooling and improves air feed density.With respect to the sucking pipe condition, air consumption raises to such an extent that the minimizing of specific torque advantage is strong several percentage points.This effect causes the higher volume flowrate of operation point migration in the pressurized machine characterisitic family.Based on the no-load running condition, this is higher, cause the raising of pressure ratio through the volume flowrate of turbo machine.This boost pressure that is so increased causes the obvious raising of torque subsequently.As a result of, each influences parameter and draws torque and raise about 10%.
The coupling that causes the cylinder air coefficient according to the scavenge effect that caused of invention.If in illustrated embodiment; Total air conditions is brought up to stoichiometric boundary conditions; Make roughly as in the internal-combustion piston engine that does not have the cam regulator, moving with same cylinder air coefficient (microlitre ≈ 0.9); Then this causes EGT to raise, and volume flowrate raises, and therefore causes improving in the energy supply at turbine inlet place.Add the effect of reinforcement voluntarily that exhaust-gas turbocharger occurs, so boost pressure just has been that 1.7 crust are possible when 1300 rev/mins of rotating speeds.Producing torque at full capacity thus raises to about 200 rev/mins more slow-revving displacement.
In addition, the high exhaust gas temperature level in low engine speed range also provides advantage the valve timing that is used for the sub load scope during strategy when the engine thermal machine turns round and corresponding optimization.
In Fig. 3 with the form of line chart be the internal-combustion piston engine of engine driven supercharging under the situation of the trap of design gas handling system 4, show residual gas content and air feed coefficient relation curve promptly with the relation curve of rotating speed.Operational data during test regulation, intake valve action consistent length are 200 ° of KW and 1 millimeter.
When opening travel is 1 millimeter, then when 310 ° of crank angle KW open, produces for 1000 rev/mins rotating speeds and to be lower than 0.6% residual gas content and to produce 0.99 air feed coefficient.Along with the rising of rotating speed, it is constant that residual gas content keeps in reaching about 2500 rev/mins of rotating speeds, and air feed coefficient in this speed range, descend (with the curve of square block sign).
For an opening time point when about 335 ° of crank angle KW best air feed coefficient (curve that identifies with rhombus and triangle down) is arranged along whole illustrated speed range.When the time comes, 1.5% the residual gas content of being to the maximum during 2500 rev/mins of turn ups still keeps lower.
The situation that is used for turbo charged internal-combustion piston engine (petrol engine with direct injection device) has been shown in Fig. 4.Operational data regulation when trying to achieve figure line is carried out the exhaust unlatching and when 351 ° of KW, is carried out exc. when 165 ° of KW.Stroke is 1 millimeter, rotation speed n=1000 rev/min.Constant intake valve action measurement of length value during for 185 ° of KW and 1 millimeter stroke is represented with the square block sign.Import during for 555 ° of KW and 1 millimeter stroke is closed the fixation measuring value and is represented with the circle sign.Can find out that from the figure line of attaching troops to a unit each other the before unlatching of time point " air inlet unlatching " is got over near-earth and is rotated back into upper dead center, then boost pressure and air feed coefficient are low more.Residual gas content with scavenge effect weaken and corresponding increase.
Fig. 5 shows one with the form of view of signal and has the internal-combustion piston engine 18 that is used at the ventilation door 19 of a low engine speed range cleaning residual gas.Regulating device 20 joins with these ventilation doors 19, wherein, this regulating device 20 that is used for intake valve and exhaust valve separably or as illustrate can be integrated existence.This regulating device 20 be with one equally separably or the active device that also can integrally exist 21 couplings.This regulating device 20 and this active device 21 be a constituent element that for example is located in the valve control equipment 22 on the ventilation door 21 preferably.But this valve control equipment 22 also can exist with regulating device 20 at least discretely.This valve control equipment 22 is via a data bus system 23, and particularly a control zone network-bus is coupled with a device for controlling engine 24.The operational data that the quilt of internal-combustion piston engine 18 is tried to achieve can be sent on the valve control equipment 22 and feedback.This valve control equipment 22 and/or this device for controlling engine 24 can have a forecast module 25.At least the opening and closing that are intake valve can forecast that module is by initialization in the lump through this.Operational data can be tried to achieve via a measuring device 26 again, can confirm via these operational datas, but whether reached for example preset, proof makes the correct condition of residual gas initialization of sweeping in a low engine speed range of internal-combustion piston engine.An ejection control device 27 also preferably is integrated in the device for controlling engine 24, and a sparger 28 that is used for the direct injection device can activate via this ejection control device 27.Via this sparger 28, fuel oil at course of injection, emitted dose, also have under the situation of injection duration and at that time operating range coupling, can be sprayed in the firing chamber.This also for example makes secondary injection become possibility when the slow-speed of revolution at least.In addition, also schematically show an ERG 29 among Fig. 5.This ERG 29 is particularly swept residual gas when the time comes at one and is activated in not by the operating range of carrying out.When adopting this internal-combustion piston engine 18; According to a form of implementation; The opening time point that has only intake valve is preferably by so adjustment; Make in order before ventilation, in the scope of upper dead center, to clear away the residual gas in the cylinder, in low engine speed range, have a valve overlap of putting with the shut-in time of a corresponding exhaust valve with fresh pressurized air.

Claims (20)

1. be used to operate the method for an internal-combustion piston engine, this internal-combustion engine has fuel injection apparatus, has the ventilation door; Each cylinder has at least one exhaust valve that is connected with a vent systems and at least one intake valve that is connected with a gas handling system; And the device with the boost pressure that is used for improving gas handling system wherein, is provided with a control gear that is used for adjusting changeably the point of opening time at least of intake valve; And time point is opened in the air inlet of ventilation door and/or the exc. time point is so adjusted through control gear in low engine speed range; Make to have a valve overlap, and, it is characterized in that in view of the above taking a breath before and/or in gas exchange process, with fresh pressurized air cylinder being carried out scavenging in the scope at upper dead center; Have only enough when existing in the sucking pipe that joins with intake valve at, when being used for pressure to cylinder scavenging and raising; Intake valve and exhaust valve just are unlocked, and thus, exist the scavenging pressure in a front poor; Wherein be pressurized the air that device is sent to gas handling system and have the pressure higher than the back pressure in the vent systems; Reached at least 95% by the residual gas cleared away in the cylinder, wherein, when 2000 rev/mins of the turn ups of internal-combustion piston engine, the valve switch time is adjusted.
2. method according to claim 1 is characterized in that, intake valve has the variable valve device of part at least at least, and these valve devices are handled through said control gear.
3. method according to claim 1; It is characterized in that; At least intake valve is through a camshaft actuated, and this camshaft has corresponding cam and this camshaft adjustable, that be used for adjusting at least the opening time point and links to each other with a cam regulator of being handled by said control gear.
4. according to the described method of one of claim 1 to 3, it is characterized in that, in order to increase opening time point and the shut-in time point that cylinder scavenging is changed exhaust valve.
5. according to the described method of one of claim 1 to 3, it is characterized in that, when rotating speed is higher than 2000 rev/mins, do not carry out for to cylinder scavenging and to the adjustment of valve switch time.
6. according to the described method of one of claim 1 to 3, it is characterized in that, in accelerating process, the engine load of maximum 30% to 100% between scope in carry out adjustment to the valve switch time.
7. according to the described method of one of claim 1 to 3, it is characterized in that a kind of turbosupercharger is used as the device that improves boost pressure.
8. according to the described method of one of claim 1 to 3, it is characterized in that a kind of mechanical supercharger is used as the device that improves boost pressure.
9. according to the described method of one of claim 1 to 3, it is characterized in that a kind of impulse booster is used as the device that improves boost pressure.
10. according to the described method of one of claim 1 to 3, it is characterized in that the change of suction system is used as the means that improve boost pressure.
11., it is characterized in that said internal-combustion piston engine is pressed the diesel engine principle work and operated through an injection regulating device according to the described method of one of claim 1 to 3.
12. have direct injection device and automobile-used four-stroke gasoline engine with at least three cylinders; Wherein, each cylinder is furnished with at least one intake valve and at least one exhaust valve, and this intake valve improves device with a boost pressure in the gas handling system and links to each other; Be provided with one and be used to adjust the opening time point of intake valve and exhaust valve and the regulating device of shut-in time point; This regulating device can activate, and reaching valve overlap in one of this petrol engine speed range low, that be used for clearing away residual gas, and has an active device; It is characterized in that; This active device define qualification, generate a signal when being used for carrying out the condition from cylinder cleaning residual gas, said regulating device is activated through this signal, wherein; Have only enough when existing in the sucking pipe that joins with intake valve at, when being used for pressure to cylinder scavenging and raising, intake valve and exhaust valve just are unlocked.
13. petrol engine according to claim 12 is characterized in that, said active device has the condition of qualification with depositing, said signal is only can generate when defining enough scavenging pressure differences.
14. petrol engine according to claim 12; It is characterized in that; Said active device and the coupling of a forecast module in order in cylinder, to generate the condition of the scavenging pressure difference that provides enough earlier, can determine when that according to the parameter of trying to achieve said signal can be generated by this forecast module.
15. petrol engine according to claim 14 is characterized in that, the constituent element that said active device and said forecast module are valve control equipments, and this valve control equipment links to each other with a device for controlling engine via the control zone network-bus.
16. petrol engine according to claim 13 is characterized in that, said scavenging pressure difference can directly or indirectly be tried to achieve by a measuring device.
17. petrol engine according to claim 13; It is characterized in that; Said scavenging pressure difference can be tried to achieve from be deposited with an operational data the engine controlling unit and can from can replenish an operational data the engine controlling unit, be tried to achieve.
18. petrol engine according to claim 12 is characterized in that, is provided with a secondary injection.
19. petrol engine according to claim 12 is characterized in that, in low engine speed range, is provided with ' hysteresis ' adjustment to igniting.
20. petrol engine according to claim 12; It is characterized in that; Be provided with an ERG; This ERG activates in an operating range of petrol engine, in this operating range, does not activate in low engine speed range, being used to reach the valve overlap of clearing away residual gas.
CN2004800292108A 2003-10-06 2004-10-06 Method for optimizing the operation of a charged reciprocating internal combustion engine in the lower engine speed range Expired - Fee Related CN1863993B (en)

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PCT/EP2004/011164 WO2005035958A1 (en) 2003-10-06 2004-10-06 Method for optimizing the operation of a charged reciprocating internal combustion engine in the lower engine speed range

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