CN203114432U - Variable valve time control system - Google Patents
Variable valve time control system Download PDFInfo
- Publication number
- CN203114432U CN203114432U CN2013200004840U CN201320000484U CN203114432U CN 203114432 U CN203114432 U CN 203114432U CN 2013200004840 U CN2013200004840 U CN 2013200004840U CN 201320000484 U CN201320000484 U CN 201320000484U CN 203114432 U CN203114432 U CN 203114432U
- Authority
- CN
- China
- Prior art keywords
- valve
- control unit
- control
- electronic
- moment
- 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.)
- Expired - Fee Related
Links
Images
Classifications
-
- 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 utility model provides a variable valve time control system which comprises an actuator, an actuating reversing valve, an electronic control unit and a displacement sensor. The electronic control unit is electronically connected with the actuating reversing valve. The displacement sensor is electronically connected with the electronic control unit. According to the variable valve time control system, factors for affecting valve time control are removed, and precise control over the opening/ closing time of a variable valve is guaranteed.
Description
Technical field
The utility model relates to a kind of control technique of actuator, and particularly relevant for a kind of changeable air valve moment control system, its moment error Control for postponing at actuator movements to cause.
Background technique
Because the engine variable-valve system has higher requirement to control validity constantly, but the core of electrohydraulic control system is the control of rapid reversal valve, the accurate control of rapid reversal valve is subjected to temperature, voltage change, for example the impedance of coil changes along with variation of temperature, operating voltage is opened what and situations such as variation of electrical equipment along with automobile, cause the real work electric current possibility of control rapid reversal valve under the same control signal different, the solenoid valve action is inaccurate.Simultaneously, rapid reversal valve and the influence that the oil cylinder motion also is subjected to system oil pressure, the oil viscosity of working changes along with temperature have influence on the solenoid valve action thereby cause resistance to motion to change.
The immediate problem that this kind variation causes is that engine variable-valve is opened the influence that is subjected to above-mentioned various factors constantly, this influence causes the changeable air valve actual motion to have certain retard time corresponding to reference signal, and also change along with the variation of various external factors retard time.
By eliminating factors vary such as system oil pressure, working medium viscosity and voltage or fluctuation effectively to Correction and Control between the calculating of the switching time of changeable air valve and circulation to the influence of changeable air valve switching time, reaching the engine variable-valve system had higher requirement to control validity constantly.Wherein, above-mentioned circulation refers to the motor [thermodynamic.
In present related system, the methods of closed loop control of using solve changeable air valve switching time conformity and repeated problem more, closed loop control is to the requirements for hardware height, such as the displacement transducer that needs highi degree of accuracy and high response, cost is higher, big, the poor robustness of control difficulty, and these directly influence the industrialization of engine variable-valve system.
The model utility content
At the problems referred to above, the purpose of this utility model provides a kind of changeable air valve control system constantly, and it is the accurate control of the moment error that delay causes at actuator movements.
The utility model proposes a kind of changeable air valve control system constantly, comprise actuator, actuated valve, electronic control unit and displacement transducer.Described electronic control unit and actuated valve electrically connect.Described displacement transducer is connected with described electronic control unit.
In an embodiment of the present utility model, described changeable air valve control system constantly also comprises the startup selector valve, and described electronic control unit is electrically connected to and starts selector valve driving output.
In an embodiment of the present utility model, described electronic control unit also comprises engine control electronic unit and valve control unit; Described engine control electronic unit is connected with described displacement transducer; Described valve control unit is connected to the engine control electronic unit, and described valve control unit is connected to and starts selector valve driving output simultaneously.
In an embodiment of the present utility model, described changeable air valve control system constantly also comprises electric hydraulic pump, and described electronic control unit is electrically connected to the electric hydaulic pumping source and drives output.
In an embodiment of the present utility model, described electronic control unit also comprises engine control electronic unit and valve control unit; Described engine control electronic unit is connected with described displacement transducer; Described valve control unit is connected to the engine control electronic unit, and described valve control unit is connected to the electric hydaulic pumping source and drives output simultaneously.
In an embodiment of the present utility model, described electronic control unit also comprises engine control electronic unit and valve control unit; Described engine control electronic unit is connected with described displacement transducer; Described valve control unit is connected to the engine control electronic unit, and described valve control unit is connected to actuated valve and drives output simultaneously.
In an embodiment of the present utility model, described startup selector valve is two position three-way valve.
In an embodiment of the present utility model, described actuated valve is two-position four-way valve.
The changeable air valve described in the utility model control system target that can guarantee valve opening/close constantly drops to minimum with the actual moment difference of valve opening/close constantly, the factor that the valve of eliminating the effects of the act is controlled constantly, thus the accurate control constantly of changeable air valve On/Off guaranteed.
Above-mentioned explanation only is the general introduction of technical solutions of the utility model, for can clearer understanding technological means of the present utility model, and can be implemented according to the content of specification, and for above-mentioned and other purpose, feature and advantage of the present utility model can be become apparent, below especially exemplified by embodiment, and conjunction with figs., be described in detail as follows.
Description of drawings
Fig. 1 is the control system schematic representation of the hydraulic actuator of the utility model preferred embodiment.
Fig. 2 is the structural representation of spring control oil cylinder when high-lift operating mode valve opening arrives maximum of hydraulic actuator shown in Figure 1.
Fig. 3 is the structural representation of spring control oil cylinder when high-lift operating mode valve is in closed condition of hydraulic actuator shown in Figure 1.
Fig. 4 calculates principle schematic retard time for controlling with changeable air valve.
Fig. 5 is for using changeable air valve trunon delay time algorithm block diagram.
Fig. 6 is for using changeable air valve turn-off delay time algorithm block diagram.
Embodiment
Below in conjunction with accompanying drawing preferred embodiment of the present utility model is described in detail, protection domain of the present utility model is not limited with this embodiment so that advantage of the present utility model and feature can be easier to be it will be appreciated by those skilled in the art that.
See also Fig. 1 to Fig. 3, the described pneumatic door control system of the utility model embodiment comprises: actuator 10, displacement transducer 961, electronic control unit 90, actuated valve 81, startup selector valve 82, high pressure liquid potential source 70, low-pressure hydraulic source (not shown).
Described first piston bar 410 with near the order of described power piston 300 namely along first direction, on the direction at bottom to top, comprise first piston bar first neck 411, first piston bar first shaft shoulder 412, first piston bar second neck 413 and first piston bar second shaft shoulder 414 successively in the accompanying drawings.Described second piston rod 420 namely comprises second piston rod, first neck 421, second piston rod, first shaft shoulder 422, second piston rod, second neck 423 and second piston rod, second shaft shoulder 424 along second direction in the accompanying drawings successively with the order near described power piston 300 on the direction of top to bottom.
In actuation-cylinder 230, have the first fluid space that is limited by actuation-cylinder first end 231 and power piston first surface 310 and second fluid space that is limited by actuation-cylinder the second end 232 and power piston second surface 320.
Be to be fluid bypass 240 between actuation-cylinder 230, the first edges 241 and second edge 242 between first end 231 and the second end 232, fluid bypass 240 provides the hydraulic pressure short circuit at big minister's degree of actuation-cylinder 230.By this hydraulic pressure short circuit, fluid can flow with very low basically resistance between first fluid space and second fluid space, and whole actuation-cylinder 230 is in the pressure that equates basically.When power piston 300 first surfaces 310 surpass bypass first edge 241 at first direction, perhaps power piston 300 second surfaces 320 are when second direction surpasses bypass second edge 242, and the hydraulic pressure short circuit is all inoperative.Longitudinal space between bypass first edge 241 and the actuation-cylinder first end 231 is first effective oil pressure chamber.Longitudinal space between bypass second edge 242 and the actuation-cylinder the second end 232 is second effective oil pressure chamber, when power piston 300 not with first effective oil pressure chamber and second effective oil pressure chamber in during one of any joint, fluid bypass 240 is effective.
Described first spring system comprises driving spring 512, spring seat 514, spring control cylinder block 513 and plunger 514, the described driving spring 512 of going up connects described spring seat 514 and spring control cylinder block 513, described spring seat 514 is connected with described first piston bar 410, between can be fixing by semi-ring 515, in the described spring control cylinder block 513 oil pocket 5133 is arranged, described plunger 514 is installed in the described oil pocket 5133, has a runner 5141 to be communicated with described oil pocket and its enable port 260 in the described plunger 514.Driving spring 512 overheads and concentric with first piston bar 410 are gone up in design in this real example, plunger 514 fixing and in runner 5141 is arranged, the to-and-fro motion when going up driving spring 512 for 513 compressions of spring control cylinder block realizes guiding, joins oil.This structure has the following advantages: when avoiding the overlapping arranged concentric of driving spring 512 and first piston bar 410, because of the spring control gear, for example the spring seat in the accompanying drawing 511 is long with the first piston bar 410 that the effective working stroke of spring causes; Shortened the length of first piston bar 410, corresponding the reducing of first piston bar 410 diameters energy, quality is light, has effectively reduced whole actuator movements part quality, has improved actuator movements speed, has reduced energy consumption.Last driving spring control structure compactness, it is reliable and stable to lead, and avoids driving spring 512 to produce lateral force when compression.Adopt two ends and the housing supporting structure of piston rod; Obtain maximum effective bearing length when making piston rod movement, reduced the side direction moment on the piston rod to greatest extent, improved the stability of actuator movements.
Described second spring system comprises cotter seat 521, valve return 522, valve guide 524 and cylinder body 523, cotter seat 521 is connected with valve stem 730 1 ends, valve stem 730 the other ends are connected with engine valve head 710, described cylinder body 523 is between cotter seat 521 and engine valve head 710, on the valve guide 524 suit cylinder bodies, valve stem 710 passes from valve guide cover, and described valve return 522 is sleeved on the valve stem 730 and contacts with cotter seat 521 with cylinder body 523 simultaneously.
Second upper end-hole 212 is connected with first buffer, and described first buffer comprises first one-way valve 612 arranged side by side, first segment head piece 613 and first relief valve 614; Second lower end mouth 222 is connected with second buffer, and described second buffer comprises second one-way valve 622 arranged side by side, second restriction 623 and second relief valve 624.Wherein, the effect of one-way valve is that forward is for pressure oil, oppositely by oil return formation buffer cavity; The effect of restriction is the buffering throttling, and the restriction of reasonable orifice size is set, and makes piston rod seating velocity when the last braking of buffer stage little, stable, and cushioning effect is subjected to influence of temperature change little.The effect of relief valve is to limit the buffering surge pressure, regulates buffer time.The adjustable relief valve of the oil pressure relief that relief valve preferably adopts, the buffering surge pressure can be regulated and control according to the difference of loading condition, avoided too high surge pressure to the influence of system, its high response speed makes the relief valve dynamic performance good simultaneously, can effectively regulate the movement velocity when piston rod has just entered buffer stage.
For simplified design, also can first relief valve 614 and second relief valve 624, described like this first buffer includes only first one-way valve 612 and first segment head piece 613 arranged side by side, and described like this second buffer includes only second one-way valve 622 arranged side by side and second restriction 623.
Described first piston bar first shaft shoulder 412 has at least one first throttle skewed slot 4121 near on the end face of first piston bar second neck 413, and described first throttle skewed slot 4121 is the variable throttling area, diminishes gradually along the first direction area.Described second piston rod, first shaft shoulder 422 has at least one second throttling skewed slot 4221 near on the end face of second piston rod, second neck 423, and the described second throttling skewed slot 4221 is the variable throttling area, diminishes gradually along the second direction area.Described first throttle skewed slot 4121 cooperates described first buffer, makes first piston bar 410 obtain buffering course stably when moving termination along first direction.The described second throttling skewed slot 4221 cooperates described second buffer, makes second piston rod 420 obtain buffering course stably when moving termination along second direction.
High pressure liquid potential source 70 comprises oil hydraulic pump 71, septum valve 73, high pressure accumulator 74, high pressure supply line 75 and fuel tank 72.High pressure liquid potential source 70 is provided at the flow of pressurized of the necessity under high pressure P _ H.Oil hydraulic pump 71 makes hydraulic fluid be passed to all the other places of this system from fuel tank 72 by high pressure supply line 75.High pressure P _ H controls by high pressure control valve 73.The fluctuation minimizing that high pressure accumulator 74 helps to make pressure and flows, and according to total power system capacity or elasticity, flow equilibrium and/or function needs, this high pressure accumulator can be accepted or rejected.Oil hydraulic pump 71 can be to become discharge capacity or the fixing discharge capacity that becomes, and the former provides better energy efficient.High pressure control valve 73 can change high-voltage value according to function needs and/or energy efficiency.
Low-pressure hydraulic source (not shown) refers to system downstream or oil return part, and its pressure P _ L is because of flow passage resistance force of waterproof or the back pressure a little higher than atmospheric pressure of control or tank pressure.
Actuated valve 81 and startup selector valve 82 are the port fuel feeding of hydraulic actuator 10 by suitable flow supply pipeline.As shown in Figure 1, starting selector valve 82 is two position three-way valve, and it is because it has three external hydraulic line for three-way valve---comprise two intake pipelines and fluid pipe-line 190.Described two intake pipelines are low pressure P_L pipeline and high pressure P _ H pipeline.Starting selector valve 82 is to have two stable control positions because of it for two-position valve, is represented by the left piece among the figure and right-hand.When electromagnet was not switched on, left position was guaranteed by the spring force of return spring, and it is also referred to as nature or default location.Right position guarantees by opening electromagnet.On position, the left and right sides, start selector valve 82 and respectively fluid pipe-line 190 and low pressure P_L pipeline and high pressure P _ H pipeline are coupled together.
Actuated valve 81 is two-position four-way valve, and it has four external hydraulic line low pressure P_L pipelines, high pressure P _ H pipeline, fluid pipe-line 192 and fluid pipe-lines 194.The default location of actuated valve 81 is to guarantee its right position by return spring, and its other position is to left position by the electromagnet application of force.In its acquiescence or right position, actuated valve 81 respectively with fluid pipe- line 192 and 194 and low pressure P_L pipeline and high pressure P _ H pipeline couple together.When actuated valve 81 during in its left position, this order of connection is switched.
90 pairs of actuated valves 81 of electronic control unit, startup selector valve 82 and the control of electric hydaulic pumping source (not shown).Electronic control unit 90 is made up of engine control electronic unit (ECU, Engine Control Unit) 91 gentle door control units 92.Engine control electronic unit 91 is control system of coordinating the whole engine running of control, engine control electronic unit 91 is responsible for the calculation engine valve simultaneously and when is opened and when close, and result of calculation is sent to valve control unit 92 by signal wire harness 931.Valve control unit 92 is responsible for the control signal of engine control electronic unit 91 is converted to driving current or voltage output, the driving output here comprises three the tunnel, one the tunnel is that actuated valve drives output (Output_S1) 951, the second the tunnel is to start selector valve to drive output (Output_S2) 952, and Third Road is that the electric hydaulic pumping source drives output (Output_M1) 953.
In the embodiment of the actuator 10 that does not need to start selector valve, just can save and start selector valve and drive output (Output_S2) 952; In the embodiment who does not need the electric hydaulic pumping source, just can save the electric hydaulic pumping source and drive output (Output_M1) 953.
The function of engine control electronic unit 91 gentle door control units 92 and the boundary of circuit are not absolute, and if desired, valve control unit 92 can be combined in the engine control electronic unit 91 and go.
In the present embodiment, described displacement transducer 961 is sent to valve control unit 92 to detected displacement signal by the electronic control unit entrance, is used for acquiring the actual moment of opening or closing of valve.Displacement transducer 961 can adopt different sensing principles, also can be placed on the different azimuth of actuator.For example, can adopt difference variable-reluctance transducer (DVRT), and detect its change in displacement near being installed in spring seat 511 as shown in Figure 1, spring seat 511 is mobile with valve 700 substantially.Also can put displacement transducer 961 in addition and come the displacement of directly measuring valve stem 730 in position.
Figure does not show in other embodiments, can infer the valve displacement information indirectly by other (being non-displacement type) sensor yet.For example, the pressure that can utilize two pressure transducers to detect the actuator upper and lower port changes, and judges the valve position according to this variation and the relevance of valve displacement, thereby obtains the moment of the actual opening and closing of valve.
Oil hydraulic pump 71 is preferably directly driven by motor, and this can be connected (not shown) by the suitable mechanical transmission with engine output shaft or bent axle and realize.When engine start, just need effective work of oil hydraulic pump 71 with to the oil hydraulic circuit pressurization, if desired, can increase above-mentioned electric hydaulic pumping source.The electric hydaulic pumping source can be that electric power compensation drive unit (not shown) is come auxiliary drive oil hydraulic pump 71, or electricity drives the compensated pump (not shown).Electricity drive compensated pump can with oil hydraulic pump 71 fluid serial or parallel connections.The driving control of electric hydaulic pumping source is the running state according to motor, is calculated by control unit of engine 91.Control unit of engine 91 sends the demand pressure signal by wire harness 931, and valve control unit 92 converts the control signal of input to the electric hydaulic pumping source and drives output (Output_M1) 953, controls the operation of electric hydaulic pumping source.System can carry out dynamic flow control by the electric hydaulic pumping source, to realize system pressure or high pressure P _ H control, can replace septum valve 73 and pressure regulatory function thereof simultaneously.
Actuator 10 can provide the two-stage valve lift, and the little lift operating mode of valve is mainly used in engine start and the little load operation of low speed, and valve high-lift operating mode is mainly used in the middle and high fast high load working condition of motor.Switching between the little lift of valve and the valve high-lift mainly realizes switching by starting selector valve 82.
In conjunction with shown in Figure 1, be in default location when starting selector valve 82, its enable port 260 and low-pressure hydraulic source are communicated with, this moment, actuator 10 was in the little lift operating mode of valve, namely, cylinder body upper surface 5131 contacts with cavity first confined planes 251, last driving spring 512 possesses certain or limited amount of spring compression, the clean spring of stable state of last driving spring 512 and following driving spring 522 is made a concerted effort power piston 300, piston rod 410,420 and engine valve 700 fixing in the position shown in the figure 1 or near this position, engine valve 20 is fixed on its closed position, also gives required valve contact force.
In conjunction with shown in Figure 2, when the engine low load operating mode is switched the high load operating mode, 91 switching signals of control unit of engine are given valve control unit 92, valve control unit 92 sends signal and gives startup selector valve 82, start the position that selector valve 82 switches to the right, its enable port 260 and low-pressure hydraulic source 70 are communicated with, and fluid enters oil pocket 5133 by flowing to 5141, spring is controlled cylinder block 513 press down, switch to valve high-lift operating mode from the little lift operating mode of valve; Cylinder body lower surface 5132 contacts with cavity second confined planes 252, and last driving spring 512 possesses a bigger amount of spring compression.
When engine start, two selector valves 81 and 82 default locations at them.Its enable port 260 is connected to the P_L pipeline, and comprises first upper end-hole 211 and second upper end-hole 212 is connected to the P_L pipeline in interior upper end-hole, comprises first lower end mouth 221 and second lower end mouth 222 is connected to the P_H pipeline in interior lower end mouth.After system had just started, actuator cavity of resorption i.e. second fluid space was in system high pressure P_H, and valve is in closed condition.
See also Fig. 4, the principle of introducing valve opening below and closing.When needing valve opening, control unit of engine 91 detects working state and the power demand of motor, when the engine thermal power cycle needs engine valve 700 to open, determines the unlatching of engine valve 700 constantly.Shown in the control signal 250 among Fig. 4,251 send trigger signal according to changeable air valve moment controlling method constantly in triggering, control unit of engine 91 sends trigger signal by wire harness 931, and valve control unit 92 is from the trigger signal of wire harness 931 and displacement transducer signal (Input_D1) 941 from wire harness 933, ambient temperature signal (Input_T1) 942, working medium temperature signal (Input_T2) 943 and working medium pressure signal (Input_P) 944 convert actuated valve to and drive output Output_S1, start selector valve and drive output (Output_S2) 952 and electric hydaulic pumping source driving output (Output_M1) 953.Actuated valve drives output Output_S1 causes actuated valve 81 to switch to "on" position when high petential, realizes that actuated valve 81 is transformed into left position, and this moment, upper end-hole and high pressure liquid potential source 70 were communicated with, and lower end mouth and low-pressure hydraulic source are communicated with.Displacement transducer signal (Input_D1) 941 is from displacement transducer 961, ambient temperature signal (Input_T1) the 942 environment temperature sensor (not shown) that comes from the outside, working medium temperature signal (Input_T2) 943 is from working medium temperature transducer (not shown), and working medium pressure signal (Input_P) 944 is from working medium pressure sensor (not shown).Working medium pressure can directly be certain compound or mean value of system high pressure P_H or an above different pressures value.The system of described break or the status parameter of environment (comprising ambient temperature, working medium temperature and working medium pressure) are in the response that influences described break in varying degrees or working state, electronic control unit can be considered their influence in control procedure, this also can have selection or emphasis is arranged.
Shown in valve displacement diagram 255 among Fig. 4, valve reaches valve opening moment position threshold X1(at the initial moment t2 of unlatching and is generally, but be not limited to, the valve full lift 1% to 3%), valve close initial moment t4 turn back to valve-closing constantly position threshold X2(be generally, but be not limited to, the valve full lift 99% to 97%).
Killing engine, in fact the opening process with above-mentioned is opposite for valve 700.Start to as shown in Figure 1 acquiescence or right position by conversion braking selector valve 81.After finishing, hydraulic actuator 10 and engine valve 700 turn back to default conditions as shown in Figure 1.
The utility model also discloses a kind of changeable air valve controlling method constantly, it comprises the steps: according to the valve opening moment position threshold X1 and the valve close moment position threshold X2 that set, thereby the judgement initial moment t2 of valve opening and valve are closed moment beginning t4.In Fig. 4, valve motion curve 255 is actual valve motion curves, in the present embodiment, uses displacement transducer 961 to measure this curve, also can use additive method to obtain this location point, thereby judge that valve has been opened or valve has begun to close.
After the valve opening signal sends, owing to the influence of factors such as actuated valve 81 electromagnetic coils and fluid, just can actually open at valve opening reality moment t2 valve, the t1 moment and the time lag of t2 between the moment are valves open late dt1=t2-t1.In like manner, the t3 moment and the time lag of t4 between the moment are valve-closing retard dt2=t4-t3.
Valve is actual open or close before, determine valve opening target t20 or valve-closing target t40 constantly constantly according to the engine charge control algorithm, t20 needs valve to begin to open constantly, t40 needs valve to begin to close constantly.Because the existence of various factors, valve opening move to valve opening constantly general the and target moment t20 in position threshold X1 place certain deviation is arranged, just generally there is certain deviation in valve opening target moment t20 with actual t2 constantly, this deviation is valve opening control deviation ddt1, is calculated as: ddt1=t20-t2.Equally, valve-closing control deviation ddt2 is calculated as: ddt2=t40 – t4.
In the valve opening control algorithm, the changeable air valve input parameter of control algorithm constantly is the target moment t20 of valve opening, calculates valve opening signal t1 constantly.At this moment, the target of valve opening moment t20 and the difference dt10 of valve opening signal t1 between the moment are that valve opening is estimated delay, i.e. dt10=t20-t1.
In the valve-closing control algorithm, the changeable air valve input parameter of control algorithm constantly is the target moment t40 of valve-closing, calculates valve-closing signal t3 constantly.At this moment, the target of valve-closing moment t40 and the difference dt20 of valve-closing signal t2 between the moment are that delay is estimated in valve-closing, i.e. dt20=t40 – t2.Influence retard time dt1 and the principal element of dt2 comprise: the temperature T 2 of ambient temperature T1, working medium and the pressure P of working medium, the variation of these influence factors all be one continuously but not the variation of transient state, the unlatching control deviation ddt1 of the above cycle period of institute or closing control deviation ddt2 can revise the next calculating that circulates.
Fig. 5 and Fig. 6 are respectively valve openings of the present utility model and close algorithm block diagram, and core is respectively valve opening control algorithm 258 and valve-closing control algorithm 259, and their execution is carried out in valve control unit 92.In an embodiment, control algorithm 258,259 is used self-adaptive PID (proportional-integral-differential) control, and PID control is made up of ratio unit (P), integral unit (I) and differentiation element (D).Valve opening and closing control algorithm 258,259 input are respectively valve opening control deviation ddt1 and close moment control deviation ddt2 constantly, output is respectively that valve opening postpones correction value ddt3 constantly and close moment postpones correction value ddt4, and formula is respectively formula (1-1) and reaches (1-2).Interact between ratio unit, differentiation element and the integral unit of control algorithm, passing ratio gain Kp, storage gain Ki and DG Differential Gain Kd adjust response, error and the overshoot performance of control algorithm.
Because actuation of engine valves device 10, actuated valve 81 and start selector valve 82 etc. the temperature T 2, the pressure P of working medium of ambient temperature T1, working medium have higher sensitivity to external world, under the different external environmental conditions, the characteristic of system can change, for the stability of retentive control, in control algorithm 258,259, can add selectively as required according to ambient temperature T1, working medium temperature T 2 or/and working medium pressure P variable effect is revised proportional gain Kp, storage gain Ki and three parameters of DG Differential Gain Kd.The influence degree of all temps and pressure is different, and the less variable of influence degree can be left in the basket or not consider.
As Fig. 5 and shown in Figure 6, parameter tuning in the control algorithm 258 and 259 in the pid algorithm, be to use engineering setting method commonly used to obtain on stream, and revision by experiment, store in advance having revised the parameter adjustment table, in actual conditions, according to the variation of ambient temperature T1, working medium temperature T 2, working medium pressure P, revision ratio, integration and DG Differential Gain parameter.
Use control algorithm 258,259 to calculate under precondition, the valve opening that a last circulation is estimated postpones correction value (or iteration amount) ddt3 close moment delay correction value (or iteration amount) ddt4 constantly.
So can use the method for iterative computation between circulation, valves open late estimated time dt10 is calculated as: dt10 (k+1)=dt10 (k)+ddt3 (k), wherein ddt3 (k) is calculated by control algorithm in the K time computing according to control algorithm 258.Equally, valve-closing retard estimated time dt20 is calculated as: dt20 (k+1)=dt20 (k)+ddt4 (k), wherein ddt4 (k) is calculated by control algorithm in the K time computing according to control algorithm 259.
Thus, knowing valve opening target moment t20 and closing under the situation of target moment t40, can calculate this valve opening signal t1:t1 (k+1)=t20 (k+1)-dt10 (k+1) constantly; And this valve-closing signal moment t3:t3 (k+1)=t40 (k+1)-dt20 (k+1).
In sum, changeable air valve described in the utility model constantly control system and method just can guarantee valve opening to the accurate calculating of valve opening and turn-off delay time and the target of closing (t20 and t40) and valve opening and (t2 and the t4) difference of the actual moment of closing drop to minimum constantly, the factor that the valve of eliminating the effects of the act is controlled constantly, thus guarantee that changeable air valve is opened and the accurate control of close moment.
In addition, actuator 10 in the utility model also is substitutable for US Patent No. 7302920, US7194991, US7156058, US7290509, US7213549, the described variable valve actuator of US7370615 (Variable valve actuator) related embodiment structure, and nearest Chinese patent application number is that 201210095184.5 denominations of invention are " variable valve actuator ", application number is " the switching time method of measurement of variable valve actuator " for the 201210095178.X denomination of invention, and application number is that 201210161831.8 denominations of invention are the actuator related embodiment structure of the Chinese patent application announcement of " Variabale valve actuation system and controlling method thereof ".
The above, only be embodiment of the present utility model, be not that the utility model is done any pro forma restriction, though the utility model discloses as above with embodiment, yet be not in order to limit the utility model, any those skilled in the art, in not breaking away from the technical solutions of the utility model scope, when the technology contents that can utilize above-mentioned announcement is made a little change or is modified to the equivalent embodiment of equivalent variations, in every case be not break away from the technical solutions of the utility model content, any simple modification that foundation technical spirit of the present utility model is done above embodiment, equivalent variations and modification all still belong in the scope of technical solutions of the utility model.
Claims (1)
1. a changeable air valve moment control system comprises actuator and actuated valve, it is characterized in that this changeable air valve control system constantly also comprises:
To the electronic control unit that actuated valve is controlled, described electronic control unit and actuated valve electrically connect; And
For detection of the displacement transducer of valve displacement signal, described displacement transducer is connected with described electronic control unit.
2. changeable air valve moment control system according to claim 1 is characterized in that described changeable air valve control system constantly also comprises the startup selector valve, and described electronic control unit is electrically connected to and starts selector valve driving output.
3. changeable air valve moment control system according to claim 2 is characterized in that described electronic control unit also comprises engine control electronic unit and valve control unit; Described engine control electronic unit is connected with described displacement transducer; Described valve control unit is connected to the engine control electronic unit, and described valve control unit is connected to and starts selector valve driving output simultaneously.
4. changeable air valve moment control system according to claim 1 is characterized in that described changeable air valve control system constantly also comprises electric hydraulic pump, and described electronic control unit is electrically connected to the electric hydaulic pumping source and drives output.
5. changeable air valve moment control system according to claim 3 is characterized in that described electronic control unit also comprises engine control electronic unit and valve control unit; Described engine control electronic unit is connected with described displacement transducer; Described valve control unit is connected to the engine control electronic unit, and described valve control unit is connected to the electric hydaulic pumping source and drives output simultaneously.
6. changeable air valve moment control system according to claim 1 is characterized in that described electronic control unit also comprises engine control electronic unit and valve control unit; Described engine control electronic unit is connected with described displacement transducer; Described valve control unit is connected to the engine control electronic unit, and described valve control unit is connected to actuated valve and drives output simultaneously.
7. changeable air valve moment control system according to claim 2 is characterized in that described startup selector valve is two position three-way valve.
8. changeable air valve moment control system according to claim 1 is characterized in that described actuated valve is two-position four-way valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013200004840U CN203114432U (en) | 2013-01-04 | 2013-01-04 | Variable valve time control system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2013200004840U CN203114432U (en) | 2013-01-04 | 2013-01-04 | Variable valve time control system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203114432U true CN203114432U (en) | 2013-08-07 |
Family
ID=48894788
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2013200004840U Expired - Fee Related CN203114432U (en) | 2013-01-04 | 2013-01-04 | Variable valve time control system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203114432U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106368760A (en) * | 2016-08-30 | 2017-02-01 | 中国第汽车股份有限公司 | Engine valve slow seating mechanism |
-
2013
- 2013-01-04 CN CN2013200004840U patent/CN203114432U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106368760A (en) * | 2016-08-30 | 2017-02-01 | 中国第汽车股份有限公司 | Engine valve slow seating mechanism |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103032179A (en) | Timing control system and method for variable valve | |
| CN100451336C (en) | Low idling energy consumption hydraulic power source | |
| JP3785464B2 (en) | Variable valve operating apparatus for internal combustion engine, control method therefor, and hydraulic actuator | |
| CN102472265B (en) | Method for controlling delivery quantity, and reciprocating compressor having delivery quantity control | |
| CN101413522A (en) | Independent electrohydraulic load sensitive energy regeneration hydraulic system of engineering machinery load port | |
| WO2011116702A1 (en) | Tandem hydraulic cylinders and stroke control device and method thereof | |
| CN109630491B (en) | Electric control compensation two-way proportional flow valve | |
| CN102425581B (en) | Pilot flow closed-loop controlled flow valve and control method | |
| CN103882906A (en) | Excavator negative flow system sensitive to load | |
| CN103277163A (en) | Variable-lift driver | |
| Huova et al. | Energy efficiency of digital hydraulic valve control systems | |
| CN101846109B (en) | Two-way flow rate continuous control valve | |
| CN108386398A (en) | A kind of compound hydraulic cylinder position control pump control hydraulic system | |
| Zhong et al. | Dynamic performance and control accuracy of a novel proportional valve with a switching technology-controlled pilot stage | |
| CN203114432U (en) | Variable valve time control system | |
| CN105065361A (en) | Proportional flow unit under compound control of electromagnetic switch valves and proportional throttle valve in parallel | |
| CN102797527B (en) | Method for measuring opening time and closing time of variable valve actuator | |
| CN205918570U (en) | Axial plunger pump device of high accuracy electric proportional control | |
| CN101881289A (en) | Hydraulic cylinder reliability test method and device based on power recovery technology | |
| CN203684314U (en) | Load-sensitive excavator negative flow system | |
| CN215634637U (en) | Damping regulating valve internal characteristic testing equipment for reducing working condition of shock absorber | |
| Gao et al. | Rapid flow measurement for high speed on/off valve based on coil current derivative | |
| CN110296113B (en) | Force application system based on flow electro-hydraulic servo valve and control method thereof | |
| CN209654358U (en) | Electronic type Ioad-sensing control device | |
| CN209892555U (en) | Bidirectional speed regulation hydraulic control system based on hydraulic cylinder negative load oil return cavity |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20130807 Termination date: 20150104 |
|
| EXPY | Termination of patent right or utility model |