CN1397719A - Flexible time cross-section controller - Google Patents
Flexible time cross-section controller Download PDFInfo
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- CN1397719A CN1397719A CN01114591.9A CN01114591A CN1397719A CN 1397719 A CN1397719 A CN 1397719A CN 01114591 A CN01114591 A CN 01114591A CN 1397719 A CN1397719 A CN 1397719A
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- 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
- F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
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- 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
- F01L1/28—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of coaxial valves; characterised by the provision of valves co-operating with both intake and exhaust ports
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- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
A flexible time cross-section controller for the pump or valve in the air inlet-exhaust system and fuel supply system of IC engine is composed of throttle valve, fluid channel, throttle control valve and relative drive mechanism. The effective open/close phase, working period, effective lifting distance and eddy intensity can be flexibly controlled. Its advantages are better dynamic behaviour, low noise, less exhaust and direct EGR control.
Description
The present invention is applicable to fluid throttling control field, (time cross-section of indication is defined as among the present invention: Ω=∫ fdt to relate generally to flexible time cross-section controller, f is the fluid passage sectional area, dt is a time diffusion unit), particularly (" valve " is identical concept with " valve " to air gate type herein, down together.) in the inlet and exhaust system of internal-combustion engine the inlet and outlet door (" inlet and outlet door " be identical concept with " throttle valve " herein, and be same down.); Pump in the fuel supply system and valve, and other valve type fluid throttle control device.The effective phase place of the valve of motor, operating time, net lift and fluid vortex intensity are carried out Flexible Control, can make motor obtain optimal performance index.
At present, adopt fixing valve timing, phase place and lift in the engine valve control mechanism mostly, definite compromise design proposal that adopts usually of corresponding cam profile parameter.It has only represented the optimized project on some specific limited operating point, and most of motors all must be worked in the scope of speed and load broadness, thereby it can not take into account the integrated performance index of universe operating mode, cause existing economy, the power performance of internal-combustion engine not good, problems such as the cold-starting temperature influence is big, toxic emission serious environment pollution, accelerating process burning are bad.In numerous experimental study work, enter, arrange geometric parameter, employing 4 Valves Technology, the reasonable Arrangement valve position of passage and ventilation mechanism except optimizing, outside the optimized combustion cell structures etc., improving performance by changing air valve phase, variable working hours and variable lift is an important channel.
In China and foreign countries' patent documentation, have manyly to valve-control, operating time and lift one of them or whole examples of changes, comprise Mechanical Driven mode, electromagnetic drive mode, hydraulic driving mode and other hybrid mode etc.Compare with traditional valve timing, changeable air valve timing (VVT) mechanism obviously improves engine power performance and fuel economy has great potential, and economic performance improves about 16%, and power improves about 20%.The internal combustion engine person has proposed and has implemented many schemes, be intended to optimize flow process, improve fluid dynamic properties, but it is all multifactor to be limited to the complexity of manufacture cost, operational reliability, mechanism, the Applicable scope of system etc., has only the simple system applies of a few functions at present in the internal-combustion engine product.
In No. 970251 (1997) paper of SAE (SAE), people such as Germany BergM have designed " the complete flexible valve control machanism of Δ control-machinery ", it realizes valve lift, opening time and phase angle are adjusted continuously by an additional triangular cam and draw-bar or tappet mechanism and locking cam etc. at the valve top.Obtained gratifying effect in the test, simultaneously, noise obviously reduces under the low speed.But mechanism and control thereof are complicated: the versatility of its triangular cam and drive controlling mechanism thereof is relatively poor, can not dynamically adjust its control mode of mechanism of determining geometric parameter; And because additional mechanism providing additional operation is stressed big and complicated, it is serious to cause setting up parts wear; The driving wasted work is big; The factor that obviously influences this mechanism's regulating effect is more, and it comprises: camshaft holder and oil temperature and engine speed are to the negative factors such as influence of the regulating action of oblique guiding valve.
Michael .B. relies the China Patent No. 94193867.0 of sharp invention, and " lift device of the used variable valve of internal-combustion engine " realized with the pivot location that changes rocking arm and finger-like driven member.Pivot and rocking arm or finger-like driven member all have the teeth pivot rolling of mating with this pivot to stride across a stationary rack to change the ratio of valve lift and cam lift.The adjusting play is all constant for all positions of pivot, or can change with the position of pivot.By the pivoting action track of the fixing tooth bar delineation of pivot suspension guide plate and, can be an annular or near this annular arc.Change the relation of regulating between gap and the pivot location and produce controlled phase change and operating time variation.These device additional zero parts are more, mechanism's complexity etc., there is following defective: because the mode of certain supporting point of dependence change rocking arm realizes dwindling of displacement or amplifies, thereby change with the motion of supporting point for the stressed big young pathbreaker that overcomes valve spring power rocking arm, thereby cause the wearing and tearing of tooth bar inhomogeneous, especially wearing and tearing are the most serious when the valve maximum lift; Because the variation of rocker-arm ratio causes that the valve clearance changes thereupon; For rocking arm and the driving cam determined, its rocker-arm ratio and valve lift ratio are subject to the geometric parameter of part, thereby limit its regulating action scope; Owing to the additional zero parts stressed big, resistance to motion is big, transmission link is many etc. influences its dynamic response characteristic.
Hara.S. U.S. Pat 5452694, " port timing modifier "; The German patent DE 4404145 of Haas M., the U.S. Pat 5431133 of " port timing modifier " and Spath MJ., the common feature of " valve lift modifier " etc. is to have disposed two groups or three groups of cams for driving each valve on camshaft, correspond respectively to the motor distribution requirement in high, medium and low when speed, can satisfy the part requirement in practice, obtain good effect.But because regulating action is that segmented is carried out, thereby its adaptability is restricted, can not reach best and need set up corresponding mechanism in universe operating mode scope and be used to finish the transition mechanism from a cam to another cam and cause the gap to change the lash compensation device of setting up because the motion link increases, the while is owing to the discontinuous performance output-index that influences of input quantity.
The another kind of implementation of changeable air valve control mechanism is to seek the optimal valve control strategy by hydraulic system, and in the method, cam follower makes the hydraulic oil of sealing or flows out through a fixing aperture or through a controlled aperture.For the passive type mode of structure, consequently valve when low engine speed, open not quite or the time not long, and the liquid deficiency that flows out when high speed is so that the motion of valve is different from conventional system.Positive control mode can make lift and operating time precisely controlled, and consequently owing to be that valve motion just can be controlled intake process completely singly, conventional throttling will go out of use.This system was described in No. 930820 paper of SAE (SAE) (Urata and other people etc.).The defective of this system comprises: the valve opening functional reliability is relatively poor, and the viscosity variation causes machine operation change, system complex because fluid is with temperature.Although torque obviously improves when the motor of this system being installed demonstrating low speed, be installed in conservation of fuel 7% on the automobile.Yet mechanical system is conspicuous for the advantage of a series of requirements.
The something in common of the changeable air valve timing mechanism that patent of more than enumerating and document are related is: the lift of valve is absolute change value (promptly being valve actual motion displacement); Cause that the power that maximum lift changes still acts directly on the valve stem top, stressed big, easy to wear; Because the kinematic pair that increases will cause that in adjustment process the valve clearance changes, thereby influence engine performance thereupon; Need set up lash compensation device; Mechanism's complexity, cost height.
The purpose of this invention is to provide flexible time cross-section controller, this device can open and close phase place, operating time, lift and fluid vortex intensity and carry out Flexible Control to the valve of motor, thereby improves the cold starting performance of internal-combustion engine; Reduce fuel consumption; Reduce pollutant emission; Improve power, moment of torsion; Reduce noise and vibration; Make internal-combustion engine have good performance index at full speed and in the full load scope.
The object of the present invention is achieved like this: set up throttling control valve and control corresponding mechanism etc. at conventional engine inlet and outlet door (throttle valve) and air valve seat ring place.Throttling control valve and inlet and outlet door and air valve seat ring have a common axis (annotate: herein " common axis " is equal to " axis "); The inlet and outlet door can be about common axis (annotate: definition herein: towards the motion of closing every direction for " on "; Towards the motion of opening every direction is D score) motion, throttling control valve also can move up and down along common axis; Have independently axially relative movement separately between inlet and outlet door and the throttling control valve because the particularity of its relative position, make it to have formed flexible time cross-section controlled in the universe (for valve-controlled internal combustion engine:
, f is the fluid passage sectional area; N is an engine speed; Dt is a time diffusion unit; D is a crank angle differential unit), can obtain the effective phase place of inlet and outlet, operating time, net lift and fluid vortex intensity continuous variable in its whole range of movement, thereby obviously improve the engine performance index.
The present invention has the following advantages compared with the prior art:
1) throttling control is convenient, and it is little to drive consumed power;
2) valve opening and close phase place and can flexible adjust;
3) the valve net lift can be adjusted continuously;
4) valve opening and shut-in time can flexiblely be adjusted;
5) fluid vortex intensity can flexiblely be adjusted;
6) be convenient to implement programming control in real time.
The present invention changes valve-control, operating time, lift and fluid vortex intensity by the independently relative movement mode between inlet and outlet door (throttle valve) and the throttling control valve.Valve and driving mechanism motion thereof still keep former mode, throttling control valve and control corresponding mechanism have been set up, its working principle is different from the principle of existing changeable air valve timing mechanism fully, for valve-controlled internal combustion engine, can implement Flexible Control ventilation (or fluid motion) process in the universe operating mode, the present invention has following characteristics:
1) design proposal can be applicable to traditional tappet mode, overhead camshaft type and other mode and drives valve-controlled internal combustion engine;
2) design proposal can be applicable to single intake valve of each cylinder and/or exhaust valve, or a plurality of intake valves of each cylinder and/or exhaust valve;
3) mechanical structure is simple, and it is few to increase part number;
4) hardware and software control process dynamically realize in engine operation process, and can implement universe control;
5) independently relative movement mode changes the effective phase place of valve, operating time, net lift and fluid vortex intensity flexibly between throttle valve and the throttling control valve, can implement hardware programming control, can bring into play simultaneously the superiority of software control to greatest extent, it is little to make the mode of operation of motor have more diversity, alternative, driving consumed power;
6) cold starting performance can be improved significantly, can realize sequential firing, the starting wasted work reduce significantly; Because the technical bottleneck of cold-starting is broken, thereby other correlated performance is significantly improved;
7) noise and the vibration can be improved significantly;
8) exhaust index can improve, and is convenient to EGR (exhaust gas recirculation) control;
9) partial load condition and declared working condition all have good economic performance;
10) can cancel butterfly valve type solar term (plate) door of existing motor, power, moment of torsion are further enhanced;
11) acceleration performance further improves; Engine idle is low, good stability;
12) the present invention is suitable for making in the time cross-section and flexible other design proposal that changes of fluid vortex intensity of throttling control valve action with different modes.
Below be controlled to be example design accompanying drawing with the valve-controlled internal combustion engine inlet and exhaust system:
Fig. 1 is the existing internal-combustion engine inlet and exhaust system structure diagram that generally adopts;
Fig. 2 is internal-combustion engine inlet and exhaust system of the present invention structure diagram when closing;
Fig. 3 is an inlet and outlet door place structure diagram in the internal-combustion engine cold-starting process of the present invention;
Fig. 4 is an inlet and outlet door place structure diagram in the internal combustion engine operation process of the present invention;
Fig. 5 is the throttling control valve first example structure sketch of the present invention;
Fig. 6 is the plan view of Fig. 5;
Fig. 7 is the throttling control valve second example structure sketch of the present invention;
Fig. 8 is the plan view of Fig. 7;
Fig. 9 is throttling control valve the 3rd an example structure sketch of the present invention;
Figure 10 is the plan view of Fig. 9;
Figure 11 is that valve net lift Δ H of the present invention equals valve actual lift H
1The time plotted curve;
Figure 12 is that valve net lift Δ H of the present invention is 0 o'clock a plotted curve;
Figure 13 is valve net lift Δ H=valve actual lift H of the present invention
1-throttling control valve
Lift H
2The time plotted curve.
Below in conjunction with accompanying drawing the present invention is described in further detail:
Shown in Figure 1, be the existing internal-combustion engine inlet and exhaust system structure diagram that generally adopts, mainly by valve actuating mechanism 2, cotter seat 3, valve collet 4, valve spring 5, valve guide bushing 6, cylinder head 7, valve 9, fluid passage 11, valve seat 12 compositions such as grade.Masterpiece from valve actuating mechanism 2 is used in valve 9 tops, and compression valve spring 5 is opened valve 9, because the existence of pressure reduction, fluid is forced to move in the fluid passage 11 cylinder head 7 in, finishes air inlet or exhaust process; After valve actuating mechanism 2 active forces reduced gradually, remove, valve 9 was closed under the effect of valve spring 5 power.Because the geometric parameters number average of valve actuating mechanism 2 and other mechanism is determined, thereby timing, phase place and the lift of valve 9 opening and closing are also fixing, the half-way house of taking into account overall target on some specific operation point has only been represented in its design.
Shown in Figure 2, be internal-combustion engine inlet and exhaust system of the present invention structure diagram when closing, in the existing internal-combustion engine inlet and exhaust system that generally adopts, set up throttling control valve and control corresponding mechanism etc., mainly by throttling control valve driving mechanism 1, valve actuating mechanism 2, cotter seat 3, valve collet 4, valve spring 5, valve guide bushing 6, cylinder head 7, throttling control valve member 8, valve 9, throttling control valve 10, fluid passage 11, valve seat 12 compositions such as grade.Valve guide bushing 6, valve 9, throttling control valve 10, valve seat 12 etc. are installed on the same axis (being common axis); Throttling control valve 10 bottoms cooperate with the skirt section of valve 9, and throttling control valve 10 cylindricals cooperate with fluid passage 11 inwalls and valve seat 12 endoporus; One eccentric opening that is parallel to valve guide bushing 6 axis (common axis) is arranged near the valve guide bushing 6 on the cylinder head 7, and throttling control valve member 8 passes from eccentric opening, and throttling control valve driving mechanism 1 is controlled throttling control valve 10 by throttling control valve member 8; Throttling control valve 10 can be moved up and down in fluid passage 11 inwalls and valve seat 12 along axis by the effect of throttling control valve driving mechanism 1 power, and throttling control valve 10 also can move up and down with the effect from valve 9 power; Valve 9 can move about valve guide bushing 6 axis of the effect lower edge of valve actuating mechanism 2 and valve spring 5 power in (switching); There are independently relative movement in valve 9, throttling control valve 10 with respect to valve guide bushing 6, fluid passage 11 and valve seat 12 endoporus, and its relative movement constitutes effective flexible time cross-section; In valve 9 movement processes, throttling control valve 10 effective phase place, operating time, net lift and the fluid vortex intensity that may command valve 9 opens and closes that moves up and down, its manual or automatic implementation can be: machinery type, hydraulic pressure or pneumatic control mode, electric power Electromagnetic Control mode or alternate manner.
Shown in Figure 3, be inlet and outlet door place structure diagram in the internal-combustion engine cold-starting process of the present invention, act directly on valve 9 tops from the power of valve actuating mechanism 2, by valve collet 4 and cotter seat 3, compression valve spring 5, valve 9 moves downward (unlatching valve) along axis; The power of throttling control valve driving mechanism 1 acts on the throttling control valve 10 by throttling control valve member 8, throttling control valve 10 can move along common axis up and down with valve 9, the position of throttling control valve 10 is by 1 control of throttling control valve driving mechanism, can design throttling passage 13 on the annular canister of throttling control valve 10 bottoms, its position and sectional area draw through optimization; Owing to have draught head with the external world in the cylinder, fluid is forced to motion in the fluid passage 11 cylinder head 7 in, enters, discharges cylinder via throttling passage 13, finishes the gas exchange process when starting; After valve actuating mechanism 2 power reduced gradually, remove, valve 9 was closed under the effect of valve spring 5 power gradually; The annular canister bottom of closing throttling control valve 10 in the closed procedure resets to former initial position under the skirt section of valve 9 moves upward the effect of power, throttling control valve 10 also can reset under 1 control of throttling control valve driving mechanism.In starting process, the movement position of the throttling control valve 10 at valve 9 places increases the inlet and outlet resistance as much as possible, so that with a certain amount of not combustion in the last circulation or fired mixed gas and reside in the cylinder, improve next circuit and fire environment, until smooth starting.
For multiple cylinder engine, on throttling control valve 10 annular canister of some, be provided with throttling passage 13, and be not provided with throttling passage 13 on all the other throttling control valves 10; Like this, do not have cylinder ventilation volume in starting process of throttling control valve 10 of throttling passage 13 few, the cylinder that is provided with the throttling control valve 10 of throttling passage 13 can be got angry continuously; Also can control and obtain different cross sections working lipe and be worth and reach corresponding target by the movement position of throttling control valve 10 that throttling passage is not established in control, like this, because the compression wasted work reduces, thereby the starting resistance square reduces, it is easier to start, and can realize that hardware programming or software control get angry in proper order.
The present invention then availablely realizes it at low cost when only being used to improve cold-starting.In starting process, the throttling control valve in the inlet and outlet mechanism 10 is set in the appropriate location according to enviromental parameter, to reach optimum efficiency, internal-combustion engine is started smoothly, after starting finishes, throttling control valve 10 is controlled at inoperative state (position), does not quite have this device this moment and exist.
The present invention is owing to broken through the technical bottleneck of internal-combustion engine cold-starting, and (as: fuel consumption rate, discharging, noise, vibration etc.) bring obvious improvement to other performance index simultaneously.
Shown in Figure 4, it is inlet and outlet door place structure diagram in the internal combustion engine operation process of the present invention, manually or automatically control (comprising rotating speed, load, temperature and enviromental parameter etc.) motion state of throttling control valve 10 by throttling control valve driving mechanism 1 according to the status parameter of motor, throttling control valve 10 moves up and down, effective phase place, operating time, net lift and fluid vortex intensity that may command valve 9 is opened; When in rated load and overload operation, throttling control valve 10 bottoms do not contact with valve 9 skirt sections, do not play throttling action; When moving under being lower than rated load, throttling control valve 10 can move up and down along axis, with cross section working lipe that control valve 9 is opened, corresponding control inlet and outlet amount.Greatly then working lipe, the cross section was big for load, otherwise then little; For motor when dynamic load moves, the movement position of gradable manual control throttling control valve 10, or should otherwise control the motion of throttling control valve 10, automatically seek optimum working state, have very big flexibility, can realize multi-mode operation (originate mode, economic model, low emission pattern, overburdening pattern etc.).For many intake valves, many exhaust valves motor, in same cylinder, can control the motion of each throttling control valve 10 according to the needs of different fluid strength of vortex and inlet and outlet amount.
In the multiple cylinder engine, on throttling control valve 10 annular canister of some, be provided with throttling passage 13, and do not establish throttling passage 13 on all the other throttling control valves 10; Like this, do not have cylinder ventilation volume in starting process of throttling control valve 10 of throttling passage 13 few, the cylinder that is provided with the throttling control valve 10 of throttling passage 13 can be got angry continuously; Also can control and obtain different cross sections working lipe and be worth and reach corresponding target by the movement position of throttling control valve 10 that throttling passage is not established in control, like this, because the compression wasted work reduces, and in the time of can being implemented in underrun, closes the working cylinder of some.The multicylinder engine that this scheme is used for electronic fuel injection system has clear superiority.
Rectifier plate (fly valve) in the suction tude of the desirable carburetor engine that disappears of the application of throttling control valve 10, Electronic Fuel Injection (EFI) motor or other engine fuel, under equal conditions significantly reduced restriction loss, improved the pressure at each intake valve place, thereby improved the air inlet quality, improve power, improve performances such as economy, power, it is low to obtain engine idle simultaneously, indexs such as good stability.This scheme is particularly remarkable for the supercharged engine effect.
The present invention is applied in the exhaust valve, and the position of throttling control valve 10 in exhaust process directly influences exhaust resistance, remains in exhausted air quantity in the cylinder by control, utilizes waste gas to improve the exhaust quality, realizes directly EGR control in the cylinder; In the cold-starting process, sectional area working lipe of control throttling control valve 10 and valve 9 is with a certain amount of not combustion in the last circulation or fired mixed gas and force to reside in the cylinder, so that improve next circuit compression temperature, make it to satisfy continuous ignition condition, realize that starting smoothly.
Fig. 5～8th, 10 two kinds of example structure sketches of throttling control valve of the present invention, part or all of throttling control valve 10 circularizes tubular, is installed in fluid passage 11 in the valve 9, cylinder head 7, the valve seat 12 formed spaces; There are independently relative movement in throttling control valve 10, valve 9 with respect to valve guide bushing 6 and fluid passage 11 and valve seat 12 endoporus, and its relative movement constitutes effective flexible time cross-section; Throttling control valve 10 moves up and down, effective phase place, operating time, net lift and fluid vortex intensity that control inlet and outlet door 9 opens and closes.
Fig. 5 is the throttling control valve first example structure sketch of the present invention, and Fig. 6 is the plan view of Fig. 5; Shown in Fig. 5,6, throttling control valve 10 circularizes drum, an outstanding entity part on the inner circumference, be used for being connected with throttling control valve member 8, throttling control valve 10 bottoms cooperate with valve 9 skirt sections, throttling control valve 10 cylindricals and fluid passage 11 inwalls and valve seat 12 endoporus Spielpassung, throttling passage 13, throttling passage 13 are arranged is closed type or open in design on the throttling control valve 10 lower annular tubes; Also can not establish throttling passage 13 on the throttling control valve 10 lower annular tubes.Throttling control valve 10 can be made one or discrete with throttling control valve member 8.
Fig. 7 is the throttling control valve second example structure sketch of the present invention, and Fig. 8 is the plan view of Fig. 7; Shown in Fig. 7,8, throttling control valve 10 circularizes drum, an outstanding entity part on the excircle, be used for being connected with throttling control valve member 8, outstanding entity part can be assemblied in the eccentric opening on the cylinder head 7 on the excircle, and throttling control valve 10 bottoms cooperate with valve 9 skirt sections, throttling control valve 10 cylindricals and fluid passage 11 inwalls and valve seat 12 endoporus Spielpassung, throttling passage 13, throttling passage 13 are arranged is closed type or open in design on the throttling control valve 10 lower annular tubes; Also can not establish throttling passage 13 on the throttling control valve 10 lower annular tubes.Throttling control valve 10 can be made one or discrete with throttling control valve member 8.
Fig. 9 is throttling control valve the 3rd an example structure sketch of the present invention, and Figure 10 is the plan view of Fig. 9; Shown in Fig. 9,10, throttling control valve 10 circularizes drum, and throttling control valve member 8 directly is fixed on throttling control valve 10 circumference, throttling control valve member 8 axis and throttling control valve 10 parallel axes; Throttling control valve 10 bottoms cooperate with valve 9 skirt sections, throttling control valve 10 cylindricals and fluid passage 11 inwalls and valve seat 12 endoporus Spielpassung, throttling passage 13, throttling passage 13 are arranged is closed type or open in design on the throttling control valve 10 lower annular tubes; Also can not establish throttling passage 13 on the throttling control valve 10 lower annular tubes.Throttling control valve 10 can be made one or discrete with throttling control valve member 8.
Shown in Figure 11～13, be valve net lift of the present invention with the crank angle change curve, effectively the phase control scope is: (0, θ), θ is a valve timing angle to φ ∈; The time control range: t ∈ (0, θ/6n); Net lift Δ H=valve actual lift H
1-throttling control valve lift H
2, the net lift control range: Δ H ∈ (0, H
Max), H
MaxBe valve 9 maximum actual lifts.
Figure 11 is that valve net lift Δ H of the present invention equals valve actual lift H
1The time plotted curve, this moment throttling control valve 10 lift H
2Be 0, controlled time cross-section zone also is 0, and motor operates in high load or overload state.Throttling control valve this moment 10 pairs of effective phase places, operating time and net lifts do not start to control making usefulness, but may command fluid eddy current (rolling stream) intensity.
Figure 12 is that valve net lift Δ H of the present invention is 0 o'clock a plotted curve, at this moment throttling control valve 10 lift H
2Equal the actual lift H of valve 9
1, whole interval is controlled time cross-section zone, motor operates in low-load or cold-starting state.10 pairs of effective phase places of throttling control valve this moment, operating time, net lift and fluid vortex intensity are started to control to make and are used.
Figure 13 is valve net lift Δ H=valve actual lift H of the present invention
1-throttling control valve lift H
2The time plotted curve, this moment, Δ H was greater than 0, θ
1≤ θ≤θ
2Interval internal upper part area is cross section working lipe, and all the other are controlled time cross-section zone, throttling control valve 10 lift H
2Be subjected to throttling control valve driving mechanism 1 control, during motor operates in, low load condition.10 pairs of effective phase places of throttling control valve this moment, operating time, net lift and fluid vortex intensity are started to control to make and are used.
Claims (11)
1. the flexible time cross-section controller that is used for fluid throttling control, it is characterized in that: mainly by valve actuating mechanism 2, cotter seat 3, valve collet 4, valve spring 5, valve guide bushing 6, cylinder head 7, valve 9, throttling control valve 10, throttling control valve member 8 and corresponding throttling control valve driving mechanism 1 have been set up in the existing internal-combustion engine inlet and exhaust system of compositions such as valve seat 12 in fluid passage 11; Throttling control valve 10 is installed in fluid passage 11 and valve seat 12 and the valve 9 formed spaces in the cylinder head 7, throttling control valve 10 circularizes cylindric, its axis of movement and valve guide bushing 6 axis coaxles or parallel are controlled the sectional area of fluid passage and the strength of vortex of effective phase place, operating time, net lift and fluid motion that valve (valve comprises: engine valve and other fluid valve) is periodically opened and closed by the relative movement between control valve 9 and the throttling control valve 10;
2. device as claimed in claim 1, it is characterized in that: part or all of described throttling control valve 10 made the around shaping drum shape, throttling control valve 10 cylindricals and fluid passage 11 inwalls and valve seat 12 endoporus Spielpassung, its bottom contacts (cooperation) with the umbrella skirt section of valve 9;
3. as claim 1 and 2 described devices, it is characterized in that: throttling control valve 10 can parallel to the axis along valve guide bushing 6 axis and its and move up and down and around rotational;
4. as claim 1 and 2 described devices, it is characterized in that: described throttling control valve 10 circularizes drum, and an interior outstanding entity part is used for being connected with throttling control valve member 8 on its inner circumference;
5. as claim 1 and 2 described devices, it is characterized in that: described throttling control valve 10 circularizes drum, and an outer outstanding entity part is used for being connected with throttling control valve member 8 on its excircle;
6. as claim 1 and 2 described devices, it is characterized in that: described throttling control valve 10 circularizes drum, and throttling control valve member 8 directly is fixed on throttling control valve 10 circumference, throttling control valve member 8 axis and throttling control valve 10 parallel axes;
7. device as claimed in claim 1 is characterized in that: throttling control valve member 8 is for shaft-like, and throttling control valve 10 can be made one or discrete with throttling control valve member 8.
8. as claim 1 and 2 described devices, it is characterized in that: the wall bottom of the around shaping drum of described throttling control valve 10 is provided with one or above hole 13 or opening;
9. as claim 1 and 2 described devices, it is characterized in that: hole 13 or opening are not established in the wall bottom of the around shaping drum of described throttling control valve 10, can play airtight effect when its bottom contacts (cooperation) with the umbrella skirt section of valve 9;
10. device as claimed in claim 1, it is characterized in that: an eccentric opening that is parallel to valve guide bushing 6 axis is arranged near the valve guide bushing 6 on the described cylinder head 7, throttling control valve member 8 passes from eccentric opening, and throttling control valve driving mechanism 1 is controlled throttling control valve 10 by throttling control valve member 8;
11. device as claimed in claim 1, it is characterized in that: an eccentric hole slot that is parallel to the valve collet axially bored line is arranged on the described cotter seat 3, throttling control valve member 8 passes from eccentric opening, and throttling control valve driving mechanism 1 is controlled throttling control valve 10 by throttling control valve member 8;
Priority Applications (5)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN01114591.9A CN1397719A (en) | 2001-07-18 | 2001-07-18 | Flexible time cross-section controller |
| EA200400493A EA005445B1 (en) | 2001-07-18 | 2002-07-18 | A control device for continuously variable time and cross section |
| EP02752957A EP1422386A1 (en) | 2001-07-18 | 2002-07-18 | A flexible control device for time-section factor |
| US10/489,881 US20040261740A1 (en) | 2001-07-18 | 2002-07-18 | Flexible control device for time-section factor |
| PCT/CN2002/000504 WO2003008769A1 (en) | 2001-07-18 | 2002-07-18 | A flexible control device for time-section factor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN01114591.9A CN1397719A (en) | 2001-07-18 | 2001-07-18 | Flexible time cross-section controller |
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| Publication Number | Publication Date |
|---|---|
| CN1397719A true CN1397719A (en) | 2003-02-19 |
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ID=4661227
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN01114591.9A Pending CN1397719A (en) | 2001-07-18 | 2001-07-18 | Flexible time cross-section controller |
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| Country | Link |
|---|---|
| US (1) | US20040261740A1 (en) |
| EP (1) | EP1422386A1 (en) |
| CN (1) | CN1397719A (en) |
| EA (1) | EA005445B1 (en) |
| WO (1) | WO2003008769A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102797532A (en) * | 2011-05-23 | 2012-11-28 | 邓国峰 | Variable-time cross area control device |
| CN109312642A (en) * | 2016-06-02 | 2019-02-05 | 沃尔沃卡车集团 | Valve gear and valve guiding piece |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3762381A (en) * | 1972-10-30 | 1973-10-02 | S Dave | Variable internal combustion engine valve operating system |
| US3911873A (en) * | 1972-10-30 | 1975-10-14 | Sharad M Dave | Variable internal combustion engine valve operating system |
| JPS521229A (en) * | 1975-06-24 | 1977-01-07 | Toyota Motor Corp | Suction valve having inverse flow prevention mechanism |
| US4836154A (en) * | 1987-08-18 | 1989-06-06 | Bergeron Charles W | Poppet valve assembly with apertures |
| US5358212A (en) * | 1993-10-08 | 1994-10-25 | Copes-Vulcan, Inc. | Poppet valve having external adjustment for a flow restrictor |
| DE4404145A1 (en) | 1994-02-09 | 1995-08-10 | Schaeffler Waelzlager Kg | Switching device in a valve train |
| US5431133A (en) | 1994-05-31 | 1995-07-11 | General Motors Corporation | Low mass two-step valve lifter |
| US6237549B1 (en) * | 1999-04-21 | 2001-05-29 | Acro-Tech, Inc | Vented valve mechanism for internal combustion engines |
| CN1233923C (en) * | 1999-08-24 | 2005-12-28 | 邓国峰 | Flexible time section fluid controller |
-
2001
- 2001-07-18 CN CN01114591.9A patent/CN1397719A/en active Pending
-
2002
- 2002-07-18 WO PCT/CN2002/000504 patent/WO2003008769A1/en not_active Application Discontinuation
- 2002-07-18 US US10/489,881 patent/US20040261740A1/en not_active Abandoned
- 2002-07-18 EA EA200400493A patent/EA005445B1/en not_active IP Right Cessation
- 2002-07-18 EP EP02752957A patent/EP1422386A1/en not_active Withdrawn
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102797532A (en) * | 2011-05-23 | 2012-11-28 | 邓国峰 | Variable-time cross area control device |
| CN109312642A (en) * | 2016-06-02 | 2019-02-05 | 沃尔沃卡车集团 | Valve gear and valve guiding piece |
| CN109312642B (en) * | 2016-06-02 | 2021-06-15 | 沃尔沃卡车集团 | Valve device and valve guide |
| US11143146B2 (en) | 2016-06-02 | 2021-10-12 | Volvo Truck Corporation | Valve arrangement and valve guide |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1422386A9 (en) | 2004-07-28 |
| EP1422386A1 (en) | 2004-05-26 |
| US20040261740A1 (en) | 2004-12-30 |
| EA200400493A1 (en) | 2004-08-26 |
| WO2003008769A1 (en) | 2003-01-30 |
| EA005445B1 (en) | 2005-02-24 |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |