CN102588029A - Method for measuring opening-closing time of variable valve actuator - Google Patents
Method for measuring opening-closing time of variable valve actuator Download PDFInfo
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- CN102588029A CN102588029A CN201210095178XA CN201210095178A CN102588029A CN 102588029 A CN102588029 A CN 102588029A CN 201210095178X A CN201210095178X A CN 201210095178XA CN 201210095178 A CN201210095178 A CN 201210095178A CN 102588029 A CN102588029 A CN 102588029A
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Abstract
The invention discloses a method for measuring opening-closing time of a variable valve actuator. The method includes the steps: providing a system for measuring and determining the opening-closing time of the variable valve actuator; setting valve opening displacement X1 and valve closing displacement X2; setting opening pressure threshold, closing pressure threshold, opening pressure threshold crossing time difference and closing pressure threshold crossing time difference for a pressure sensor; testing a pressure curve through the pressure sensor; finding opening pressure threshold crossing time from the pressure curve and calculating valve opening time t1 by adding the opening pressure threshold crossing time and the opening pressure threshold crossing time difference; and calculating valve closing time t2 by adding closing pressure threshold crossing time and the closing pressure threshold crossing time difference. The method for measuring the opening-closing time of the variable valve actuator can be used for controlling the variable valve actuator without a displacement sensor, and is simple and reliable.
Description
Technical field
The correlation technique and the system that present invention relates in general to actuator and be used to control this actuator particularly accurately judge through pressure signal and control valve switch constantly.
Background technique
Because the engine variable-valve system has higher requirement to control validity constantly; But the core of control system is the control of rapid reversal valve; The accurate control of rapid reversal valve receive temperature (impedance of coil changes along with variation of temperature), voltage (operating voltage along with automobile open electrical equipment what and change) change; Cause the real work electric current possibility of control rapid reversal valve under the same control signal different, the solenoid valve action is inaccurate.Rapid reversal valve and oil cylinder motion simultaneously also receives the influence of system oil pressure, working oil viscosity (along with variation of temperature, the variation of oil viscosity), has influence on the solenoid valve action thereby cause resistance to motion to change.
When the engine variable-valve system is controlled, must obtain the change in displacement situation of engine variable-valve generally speaking.In present related system, all be to use displacement transducer directly to measure the valve change in displacement to the measurement of this change in displacement.But the displacement transducer cost is higher, the installing space demand big, poor robustness.These directly influence the industrialization of engine variable-valve system.
Summary of the invention
The technical problem that the present invention mainly solves provides a kind of switching time method of measurement of variable valve actuator, uses one or two pressure transducer to replace displacement transducer, judges and control the initial moment of valve switch incident.
For solving the problems of the technologies described above, the technological scheme that the present invention adopts is: a kind of switching time method of measurement of variable valve actuator is provided, it is characterized in that, comprising:
(100) control system of a variable valve actuator is provided: comprise the actuator that has upper end-hole pressure measurement district and lower end mouth pressure measurement district at least, pressure transducer, electronic control unit, actuated valve, high pressure liquid potential source, low-pressure hydraulic source and the engine valve that is installed in one of said upper end-hole pressure measurement district and lower end mouth pressure measurement district;
(102) valve opening displacement X1, valve-closing displacement X2 are set;
(104) for said pressure transducer be provided with cracking pressure threshold value, closing pressure threshold value, cracking pressure stride the presentation time poor, that closing pressure is striden the presentation time is poor;
(200) through said pressure transducer test pressure curve;
(202) from said pressure diagram, to find cracking pressure to stride the presentation time and carve, force value surpasses the moment of said cracking pressure threshold value when promptly opening valve;
(300), by said cracking pressure stride that the presentation time carves and said cracking pressure to stride the presentation time poor, calculate valve opening moment t1,
T1=said cracking pressure stride the presentation time carve+that said cracking pressure is striden the presentation time is poor,
This moment, the displacement of valve was valve opening displacement X1;
(302), by said closing pressure stride that the presentation time carves and said closing pressure to stride the presentation time poor, calculate valve-closing moment t2:
T2=said closing pressure stride the presentation time carve+that said closing pressure is striden the presentation time is poor,
This moment, the displacement of valve was valve-closing displacement X2.
In preferred embodiment of the present invention; In the excursion of at least a operating mode of said actuator; Demarcate said cracking pressure respectively and stride presentation time difference and closing pressure to stride the presentation time poor, said cracking pressure stride that the presentation time differs from and closing pressure to stride the presentation time difference respectively be one group of a plurality of data.
In preferred embodiment of the present invention, wherein said cracking pressure threshold value is identical with said closing pressure threshold value.
In preferred embodiment of the present invention, said actuator drives the opening and closing of engine valve, also comprises:
Housing has said upper end-hole and lower end mouth
Actuation-cylinder in said housing, first direction longitudinally and second direction have first end and the second end respectively;
Power piston in said oil cylinder has first surface and second surface, and is removable along vertically;
The first fluid space is limited the first end of said actuation-cylinder and the first surface of said power piston;
Second fluid space is limited the second end of said actuation-cylinder and the second surface of said power piston;
First spring system is along second direction bias voltage power piston;
Second spring system is along first direction bias voltage power piston;
At least one piston rod is connected in first surface and the second surface of said power piston;
Fluid bypass, when said power piston did not have fully near any of the first end of said actuation-cylinder and the second end, said fluid bypass is short circuit said first fluid space and said second fluid space effectively;
First-class actuation mechanism, the fluid of controlling between said first fluid space and said first port is communicated with; With
The second mobile mechanism, the fluid of controlling between said second fluid space and said second port is communicated with; Wherein:
When said fluid bypass was opened basically, at least one in the said first-class actuation mechanism and the said second mobile mechanism closed at least in part;
When said fluid bypass was closed basically, each in the said first-class actuation mechanism and the said second mobile mechanism was opened at least in part;
Said actuated valve is said upper end-hole and lower end mouth fuel feeding through last fluid pipe-line with following fluid pipe-line respectively.
In preferred embodiment of the present invention, said pressure transducer is installed in said upper end-hole pressure measurement district;
Said cracking pressure threshold value be the first cracking pressure threshold value Pt11, said closing pressure threshold value be the first closing pressure threshold value Pt12, said cracking pressure to stride the presentation time difference be that first cracking pressure is striden presentation time difference dt11, said closing pressure to stride presentation time difference be that first closing pressure is striden presentation time difference dt12, said pressure diagram is first pressure diagram, it is that first cracking pressure is striden t11 at quarter presentation time that said cracking pressure strides that the presentation time carves;
Stride by said first cracking pressure that the presentation time is carved t11 and said first cracking pressure is striden presentation time difference dt11, calculate said valve opening t1 constantly:
t1=t11+?dt11，
Stride by said first closing pressure that the presentation time is carved t12 and said first closing pressure is striden presentation time difference dt12, calculate said valve-closing t2 constantly:
t2=t12+?dt12。
In preferred embodiment of the present invention, the wherein said first cracking pressure threshold value Pt11 is identical with the said first closing pressure threshold value Pt12.
5, the switching time method of measurement of variable valve actuator according to claim 1 is characterized in that, said pressure transducer is installed in said lower end mouth pressure measurement district;
Said cracking pressure threshold value be the second cracking pressure threshold value Pt21, said closing pressure threshold value be the second closing pressure threshold value Pt22, said cracking pressure to stride the presentation time difference be that second cracking pressure is striden presentation time difference dt21, said closing pressure to stride presentation time difference be that second closing pressure is striden presentation time difference dt22, said pressure diagram is second pressure diagram, it is that second cracking pressure is striden t21 at quarter presentation time that said cracking pressure strides that the presentation time carves;
Stride by said second cracking pressure that the presentation time is carved t21 and said second cracking pressure is striden presentation time difference dt21, calculate said valve opening t1 constantly:
t1=t21+?dt21，
Stride by said second closing pressure that the presentation time is carved t22 and said second closing pressure is striden presentation time difference dt22, calculate said valve-closing t2 constantly:
t2=t22+?dt22。
In preferred embodiment of the present invention, the wherein said second cracking pressure threshold value Pt21 is identical with the said second closing pressure threshold value Pt22.
In preferred embodiment of the present invention, the control system of said variable valve actuator comprises first pressure transducer and second pressure transducer;
Said first pressure transducer is installed in said upper end-hole pressure measurement district;
Said cracking pressure threshold value be the first cracking pressure threshold value Pt11, said closing pressure threshold value be the first closing pressure threshold value Pt12, said cracking pressure to stride the presentation time difference be that first cracking pressure is striden presentation time difference dt11, said closing pressure to stride presentation time difference be that first closing pressure is striden presentation time difference dt12, said pressure diagram is first pressure diagram, it is that first cracking pressure is striden t11 at quarter presentation time that said cracking pressure strides that the presentation time carves;
Stride by said first cracking pressure that the presentation time is carved t11 and said first cracking pressure is striden presentation time difference dt11, calculate first valve opening t1 ' constantly:
t1′=t11+?dt11，
Stride by said first closing pressure that the presentation time is carved t12 and said first closing pressure is striden presentation time difference dt12, calculate first valve-closing t2 ' constantly:
t2′=t12+?dt12；
Said second pressure transducer is installed in said lower end mouth pressure measurement district;
Said cracking pressure threshold value be the second cracking pressure threshold value Pt21, said closing pressure threshold value be the second closing pressure threshold value Pt22, said cracking pressure to stride the presentation time difference be that second cracking pressure is striden presentation time difference dt21, said closing pressure to stride presentation time difference be that second closing pressure is striden presentation time difference dt22, said pressure diagram is second pressure diagram, it is that second cracking pressure is striden t21 at quarter presentation time that said cracking pressure strides that the presentation time carves;
Stride by said second cracking pressure that the presentation time is carved t21 and said second cracking pressure is striden presentation time difference dt21, calculate that said duaspiracle opens t1 constantly ":
t1″=t21+?dt21，
Stride by said second closing pressure that the presentation time is carved t22 and said second closing pressure is striden presentation time difference dt22, calculate said duaspiracle close moment t2 ":
t2″=t22+?dt22；
Said first valve opening moment t1 ' is opened t1 constantly with said duaspiracle " compare, if both differences in margin of error, then calculate said valve opening t1 constantly; With said first valve-closing moment t2 ' and said duaspiracle close moment t2 " compare, if both differences in margin of error, then calculate said valve-closing t2 constantly.
In preferred embodiment of the present invention; In margin of error; Said valve opening t1 constantly equals said first valve opening t1 ' open t1 constantly with the said duaspiracle mean value of " mean value, said valve-closing t2 constantly equals said first valve-closing t2 ' and said duaspiracle close moment t2 constantly " constantly.Wherein mean value comprises arithmetic mean value, geometrical mean, mean square and weighted mean value etc.
In preferred embodiment of the present invention, valve opening displacement X1 is defined in a numerical value of 1% to 15% scope of valve full lift.
In preferred embodiment of the present invention, close the numerical value that displacement X2 is defined in 85% to 99% scope of valve full lift.
The invention has the beneficial effects as follows: the switching time method of measurement of variable valve actuator of the present invention; Use one or two pressure transducer to replace displacement transducer; Judge and control the initial moment of valve switch incident; Can solve under the situation of not using displacement transducer variable valve actuator is controlled, simple and reliable.
Description of drawings
Fig. 1 is the control system schematic representation of hydraulic actuator one preferred embodiment;
The structural representation that Fig. 2 is a hydraulic actuator valve opening shown in Figure 1 when maximum;
Fig. 3 is a hydraulic actuator high-lift structural representation shown in Figure 1;
Fig. 4 judges that with pressure transducer engine valve displacement changes the schematic representation of principle.
Embodiment
Below in conjunction with accompanying drawing preferred embodiment of the present invention is set forth in detail, thereby protection scope of the present invention is made more explicit defining so that advantage of the present invention and characteristic can be easier to it will be appreciated by those skilled in the art that.
See also Fig. 1 and Fig. 3, the embodiment of the invention comprises:
A kind of pneumatic door control system comprises: actuator 10, be installed in the actuator port first pressure transducer 53 and second pressure transducer 54, electronic control unit 90, actuated valve 81, start selector valve 82, high pressure liquid potential source 70, low-pressure hydraulic source.
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 through high pressure supply line 75.High pressure P _ H controls through high pressure control valve 73.High pressure accumulator 74 helps to make pressure and the fluctuation of flowing to reduce, and can accept or reject according to total power system capacity or elasticity, flow equilibrium and/or this high pressure accumulator of function needs.Oil hydraulic pump 71 can be to become discharge capacity or the fixing discharge capacity that becomes, and the former provides better energy validity.High pressure control valve 73 can change high-voltage value according to function needs and/or energy efficiency.
Actuated valve 81 is the port fuel feeding of hydraulic actuator 10 through suitable flow supply pipeline with starting selector valve 82.Startup selector valve 82 shown in Figure 1 is a two position three-way valve.It is to have three external hydraulic line because of it for three-way valve---comprise two intake pipelines and fluid pipe-line 190, said two intake pipelines are low pressure P_L pipeline and high pressure P _ H pipeline.It is because it has two stable control positions for two-position valve, is represented by left piece 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 through 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 a two-position four-way valve.It has four external hydraulic line: low pressure P_L pipeline, high pressure P _ H pipeline, last fluid pipe-line 192 and following fluid pipe-line 194.Its default location is to guarantee its right position by return spring, and its other position is by the electromagnet application of force to left position.In its acquiescence or right position, actuated valve 81 respectively up and down 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 electric hydraulic pump 71 controls.Electronic control unit 90 is made up of engine control electronic unit 91 gentle door control units 92.Engine control electronic unit 91 is control system of coordinating the whole engine running of control, and engine control electronic unit 91 is responsible for the calculation engine valve simultaneously and when is opened and when close.And be sent to valve control unit 92 to result of calculation through signal wire harness 931.Valve control unit 92 is responsible for converting the control signal of engine control electronic unit 91 to driving current or voltage; The drive circuit here comprises three the tunnel; One the tunnel is the drive circuit 951 that actuated valve 81 is driven; The second the tunnel is the drive circuit 952 that startup selector valve 82 is driven, and Third Road is the drive circuit 953 that electric hydraulic pump 71 is driven.
At least one pressure transducer is installed on the engine variable-valve actuator; (first pressure transducer 53 and/or second pressure transducer 54); Pressure transducer is sent to valve control unit 209 to the inlet of detected pressure signal through electronic control unit, is used for the calculating to the variable valve actuator displacement conversion.
First upper end-hole 211 and second upper end-hole 212 can be commonly referred to as upper end-hole, and upper end-hole will comprise in first upper end-hole 211 and second upper end-hole 212 at least; First lower end mouth 221 and second lower end mouth 222 can be commonly referred to as lower end mouth, and lower end mouth will comprise in first lower end mouth 221 and second lower end mouth 222 at least.
Said first piston bar 410 is promptly to 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 along first direction (in the accompanying drawings from the bottom to the direction at top) near the order of said power piston 300 successively; Said second piston rod 420 is being to comprise 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 on first direction to the second direction direction of top to bottom (in the accompanying drawings from) successively near the order of said power piston 300.
In actuation-cylinder 230, have the first fluid space that limits actuation-cylinder first end 231 and power piston first surface 310 and limit second fluid space 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 on big minister's degree of actuation-cylinder 230.Through this hydraulic pressure short circuit, fluid can flow with very low basically resistance between the 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 on first direction, when perhaps power piston 300 second surfaces 320 surpassed bypass second edge 242 on second direction, the hydraulic pressure short circuit was 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.
Said first spring system comprises driving spring 512, spring seat 511, spring control cylinder block 513 and plunger 514; The said driving spring 512 of going up is placed oneself in the midst of between said spring seat 511 and the spring control cylinder block 513; Said spring seat 511 is connected with said first piston bar 410; Between can be fixing through semi-ring 515, in the said spring control cylinder block 513 oil pocket 5133 is arranged, said plunger 514 is fixedly attached on the said housing 200 and extends in the said oil pocket 5133; Plunger 514 also can be same one in mechanism with housing 200, has a runner 5141 to be communicated with said oil pocket 5133 and its enable port 260 in the said plunger 514.Driving spring 512 overheads and concentric with first piston bar 410 are gone up in design in this real example, and runner 5141 is arranged in the plunger 514, and the to-and-fro motion when going up driving spring 512 for 513 compressions of spring control cylinder block realizes guiding, joins oil.Have the following advantages: avoid driving spring 512 and first piston bar 410 not only concentric but also when axial overlap is arranged, because of the first piston bar 410 that spring control gear (spring seat 511) and the effective working stroke of spring cause long; Shortened the length of first piston bar 410, corresponding the reducing of first piston bar 410 diameters ability, light weight has effectively reduced whole actuator movements part quality, has improved actuator movements speed, has reduced energy consumption.Last driving spring control structure is compact, and it is reliable and stable to lead, and avoids driving spring 512 when compression, to produce lateral force.Adopt the 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.
If the enclosed cavity cavity 250 not necessarily resembles among Fig. 1 in fact produces the image of feeling suffocated in order to prevent when spring control cylinder block 513 moves, should add the passage (representing among Fig. 1) of an assurance cavity 250 and ambient air circulation.The top of housing 200 in addition can be structurally not with housing 200 other partial continuous or directly continuously (expression among Fig. 1), the top of main housing 200 and other part do not have relative movement.
Said second spring system comprises cotter seat 521, following driving spring 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; Said 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 said driving spring 522 down 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 said 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 said second buffer comprises second one-way valve 622 arranged side by side, second restriction 623 and second relief valve 624.The wherein effect of one-way valve: forward supplies pressure oil, oppositely forms buffer cavity by oil return; Restriction effect: buffering throttling; The restriction of reasonable orifice size is set, makes piston rod seating velocity when the last braking of buffer stage little, stable, cushioning effect receives influence of temperature change little.Relief valve effect: limit the buffering surge pressure, regulate 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 of the influence of too high surge pressure to system; Its high response speed makes the relief valve dynamic performance good simultaneously, can effectively regulate the movement velocity when piston rod has just got into buffer stage.
On the end face of said first piston bar first shaft shoulder 412 near first piston bar second neck 413 at least one first segment chute 4121 is arranged, said first segment chute 4121 is the variable throttling area, diminishes gradually along the first direction area; On the end face of said second piston rod, first shaft shoulder 422 near second piston rod, second neck 423 at least one second throttling groove 4221 is arranged, said second throttling groove 4221 is the variable throttling area, diminishes gradually along the second direction area.Throttling groove variable throttling area design makes piston rod obtain buffering course stably.
Start
When engine start, oil hydraulic pump 71 is at first opened to pressurize to oil hydraulic circuit; During automobilism, oil hydraulic pump 71 is preferably directly driven by motor.This just possibly adopt compensates electric device (not illustrating at this) to come primer fluid press pump 71, perhaps increases electricity and drives compensated pump (also not shown).The drive controlling that electricity drives compensated pump is the running state according to motor, and control unit of engine 91 calculates.Control unit of engine 91 sends the demand pressure signal through wire harness 931, and valve control unit 92 converts the control signal of input to drive signal Output_M1, controls the running that electricity drives compensated pump.
Among Fig. 1, two selector valves 81 and 82 default locations at them.Its enable port 260 is connected to the P_L pipeline, and upper end-hole (first upper end-hole and second upper end-hole) is connected to the P_L pipeline, and lower end mouth (first lower end mouth and second lower end mouth) is connected to the P_H pipeline.
Start the voltage supply of back system, the voltage supply of actuator cavity of resorption, valve is in closed condition.
Valve opening
The working state of control unit of engine 91 detection of engine; When the engine thermal power cycle needs engine valve 700 to open; Determine the unlatching moment of engine valve 700; According to factors such as corresponding algorithm and system delays, control unit of engine 91 sends trigger signal through wire harness 931, and valve control unit 92 converts the control signal of input to drive signal Output_S1 and Output_S2.Drive signal Output_S1 makes actuated valve 81 switch to "on" position, 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.The effect that first one-way valve 612 is under pressure is opened, the pressure that makes second upper end-hole 212 after a period of time near or reach high pressure P _ H.The pressure that this moment, first pressure transducer 53 demonstrated second upper end-hole 212 is elevated to the force value of high pressure P _ H from low pressure values, and this variation in pressure can be found out through first pressure diagram 22 among Fig. 4.
Shown in valve displacement diagram 21 among Fig. 4; T1 reaches unlatching displacement X1 (General Definition is at a numerical value of 1% to 15% scope of valve full lift) to valve opening constantly, and valve turns back at close moment t2 and closes displacement X2 (General Definition is at a numerical value of 85% to 99% scope of valve full lift).
Because second lower end mouth 222 is communicated with the low-pressure hydraulic source, pressure descends fast and approaches low pressure P_L.The pressure that is installed in second pressure transducer 54 in second lower end mouth 222 this moment descends and approaches low pressure P_L; Second pressure transducer 54 has shown the variation of this pressure; The decline of this pressure is the process of a variation, and the process of this variation in pressure is illustrated by second pressure diagram 23 in Fig. 2.
Valve-closing
The valve 700 that kills engine is in fact opposite with the opening process of just having described.Start to its acquiescence as shown in Figure 1 or right position through conversion braking selector valve 81.After the completion, hydraulic actuator 10 and engine valve 700 turn back to the default conditions of as shown in Figure 1 they.First pressure diagram in Fig. 4 and second pressure diagram are dropped by height respectively when valve-closing and by low high, and be opposite with pressure changing when the valve opening.
The lift operating mode is switched
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 little lift of valve and the valve high-lift mainly realizes switching through starting selector valve 82.
In conjunction with Fig. 1 and Fig. 3; The valve lift two-stage operating mode is switched: during engine start; Start selector valve 82 and be in default location; Its enable port 260 is communicated with the low-pressure hydraulic source, and this moment, actuator was in the little lift operating mode of valve: cylinder body upper surface 5131 contacts with cavity first confined planes 251, and last driving spring 512 possesses certain amount of spring compression.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, starts the position that selector valve 82 switches to the right, and its enable port 260 is communicated with low-pressure hydraulic source 70; Fluid gets into oil pocket 5133 through 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.
The switching time method of measurement
Can judge or infer valve opening t1 and close moment t2 constantly according to the variation in pressure of first pressure transducer 53 and/or second pressure transducer 54.
Consult Fig. 4, first pressure diagram 22 surpasses the first cracking pressure threshold value Pt11 at moment t11 (t11=t1 – dt11), and returns again at moment t12 (t12=t2 – dt12) and to pass the first closing pressure threshold value Pt12.First cracking pressure is striden presentation time difference dt11 and first closing pressure, and to stride presentation time difference dt12 generally less; And it is relatively stable; Can demarcate down in various operating modes (can comprise oily temperature and system pressure) in advance; So can by moment t11 and constantly t12 infer and open constantly t1 (that is t1=t11+dt11) and close moment t2 (that is t2=t12+dt12),.First cracking pressure stride presentation time difference dt11 and first closing pressure stride presentation time difference dt12 the time sequence status shown in Fig. 4 be on the occasion of, but show concrete design, manufacture process or working conditions change, they also possibly be negative values.For some pressure transducers, it possibly not be a numerical value that its pressure is striden the presentation time poor (dt11 or dt12), but one group data or a matrix relevant with operating mode.The first cracking pressure threshold value Pt11 and the first closing pressure threshold value Pt12 can decide according to concrete design; The robustness of judging with signal is a target; 50%, the first cracking pressure threshold value Pt11 such as being system pressure can select for use identical value also can select different values for use with the first closing pressure threshold value Pt12.
Second pressure diagram 23 surpasses the second cracking pressure threshold value Pt21 at moment t21 (t21=t1 – dt21), and returns again at moment t22 (t22=t2 – dt22) and to pass the second closing pressure threshold value Pt22.Second cracking pressure is striden presentation time difference dt21 and second closing pressure, and to stride presentation time difference dt22 generally less; And it is relatively stable; Can demarcate down in various operating modes (can comprise oily temperature and system pressure) in advance; So can by moment t21 and constantly t22 infer and open constantly t1 (that is t1=t21+dt21) and close moment t2 (that is t2=t22+dt22),.Second cracking pressure stride presentation time difference dt21 and second closing pressure stride presentation time difference dt22 the time sequence status shown in Fig. 4 be on the occasion of, but show concrete design, manufacture process or working conditions change, they also possibly be negative values.For some pressure transducers, it possibly not be a numerical value that its pressure is striden the presentation time poor (dt21 or dt22), but one group data or a matrix relevant with operating mode.The second cracking pressure threshold value Pt21 can select for use identical value also can select different values for use with the second closing pressure threshold value Pt22.
Pressure diagram 22 and 23 among Fig. 4 is Utopian pressure diagrams, in real system, has more fluctuation in the pressure signal.Generally can adopt rational means of filtering, Mathematical treatment and physics to judge and improve the accuracy of differentiating moment t1 and t2.Such as; First pressure diagram 22 is after moment t11 surpasses the first pressure threshold Pt11; Might be because pressure surge and just returning before the moment t12 or low the first pressure threshold Pt12; If but this is to send in system to close before the valve signal or outside the time range of demarcating, just can get rid of it is the possibility of valve-closing incident.
Change, though might influence time difference dt11, dt12, dt21 and dt22 slightly.In principle; First and second pressure transducer 53 and 54 should be tried one's best respectively near second upper end-hole 212 and second lower end mouth 222; They also can be installed in first upper end-hole 211 and first lower end mouth 221 respectively, or are installed in fluid pipe-line 192 and following fluid pipe-line 194 respectively.Can and go up fluid pipe-line 192 second upper end-hole 212 shown in Figure 1, first upper end-hole 211 and be commonly referred to as upper end-hole pressure measurement district; Can second lower end mouth 222 shown in Figure 1, first lower end mouth 221 and down fluid pipe-line 194 be commonly referred to as lower end mouth pressure measurement district.(not shown) in some case study on implementation, first upper end-hole 211 or first lower end mouth 221 can direct external hydraulic reservoirs; In this case study on implementation, first upper end-hole 211 or first lower end mouth 221 do not belong to upper end-hole pressure measurement district or lower end mouth pressure measurement district.
On above-mentioned judgement control valve switch basis constantly, can be according to the error of switching time in a certain engine thermal circulation, the adjustment control signal time or the moment in follow-up circulation are to eliminate or to reduce the error of switching time.
Adopt in first and second pressure transducer 53 and 54 any one just can realize controlling requirement basically.If simultaneously with helping to avoid erroneous judgement and minimizing error constantly.Such as in pressure signal, having the pressure wave that many transient state streams cause; Its crest or ripple be low might to be passed through threshold value and causes erroneous judgement; But the possibility that similar pressure wave appears in two different pressure measurement districts simultaneously can reduce greatly; Therefore can reduce the possibility judged by accident greatly with reference to the signal in two different pressure measurement districts, improve the robustness of control.In addition, the mean value of fetching from two different pressure measurement districts can reduce error constantly.
Be specially: stride by said first cracking pressure that the presentation time is carved t11 and said first cracking pressure is striden presentation time difference dt11; Calculate first valve opening t1 ' (t1 '=t11+ dt11) constantly; Stride by said first closing pressure that the presentation time is carved t12 and said first closing pressure is striden presentation time difference dt12, calculate first valve-closing t2 ' (t2 '=t12+ dt12) constantly; Stride by said second cracking pressure that the presentation time is carved t21 and said second cracking pressure is striden presentation time difference dt21; Calculate that said duaspiracle opens constantly t1 " (t1 "=t21+ dt21); Stride by said second closing pressure that the presentation time is carved t22 and said second closing pressure is striden presentation time difference dt22, calculate said duaspiracle close moment t2 " (t2 "=t22+ dt22); Said first valve opening moment t1 ' is opened t1 constantly with said duaspiracle " compare, if both differences in margin of error, then calculate said valve opening t1 constantly; With said first valve-closing moment t2 ' and said duaspiracle close moment t2 " compare, if both differences in margin of error, then calculate said valve-closing t2 constantly.Said valve opening t1 constantly equals said first valve opening t1 ' open t1 constantly with the said duaspiracle mean value of " mean value, said valve-closing t2 constantly equals said first valve-closing t2 ' and said duaspiracle close moment t2 constantly " constantly.Wherein mean value comprises arithmetic mean value, geometrical mean, mean square and weighted mean value etc.
The above is merely embodiments of the invention; Be not so limit claim of the present invention; Every equivalent structure or equivalent flow process conversion that utilizes specification of the present invention and accompanying drawing content to be done; Or directly or indirectly be used in other relevant technical fields, all in like manner be included in the scope of patent protection of the present invention.
Claims (10)
1. the switching time method of measurement of a variable valve actuator is characterized in that, comprising:
(100) control system of a variable valve actuator is provided: comprise the actuator that has upper end-hole pressure measurement district and lower end mouth pressure measurement district at least, pressure transducer, electronic control unit, actuated valve, high pressure liquid potential source, low-pressure hydraulic source and the engine valve that is installed in one of said upper end-hole pressure measurement district and lower end mouth pressure measurement district;
(102) valve opening displacement X1, valve-closing displacement X2 are set;
(104) for said pressure transducer be provided with cracking pressure threshold value, closing pressure threshold value, cracking pressure stride the presentation time poor, that closing pressure is striden the presentation time is poor;
(200) through said pressure transducer test pressure curve;
(202) from said pressure diagram, to find cracking pressure to stride the presentation time and carve, force value surpasses the moment of said cracking pressure threshold value when promptly opening valve;
(300) stride by said cracking pressure that the presentation time carves and said cracking pressure to stride the presentation time poor, calculate valve opening moment t1,
T1=said cracking pressure stride the presentation time carve+that said cracking pressure is striden the presentation time is poor,
This moment, the displacement of valve was valve opening displacement X1;
(302), by said closing pressure stride that the presentation time carves and said closing pressure to stride the presentation time poor, calculate valve-closing moment t2:
T2=said closing pressure stride the presentation time carve+that said closing pressure is striden the presentation time is poor,
This moment, the displacement of valve was valve-closing displacement X2.
2. the switching time method of measurement of variable valve actuator according to claim 1,
In the excursion of at least a operating mode of said actuator, demarcate said cracking pressure respectively and stride presentation time difference and closing pressure to stride the presentation time poor, said cracking pressure stride that the presentation time differs from and closing pressure to stride the presentation time difference respectively be one group of data.
3. the switching time method of measurement of variable valve actuator according to claim 1 is characterized in that, wherein said cracking pressure threshold value is identical with said closing pressure threshold value.
4. the switching time method of measurement of variable valve actuator according to claim 1,
Said actuator drives the opening and closing of engine valve, also comprises:
Housing has said upper end-hole and lower end mouth
Actuation-cylinder in said housing, first direction longitudinally and second direction have first end and the second end respectively;
Power piston in said oil cylinder has first surface and second surface, and is removable along vertically;
The first fluid space is limited the first end of said actuation-cylinder and the first surface of said power piston;
Second fluid space is limited the second end of said actuation-cylinder and the second surface of said power piston;
First spring system is along second direction bias voltage power piston;
Second spring system is along first direction bias voltage power piston;
At least one piston rod is connected in first surface and the second surface of said power piston;
Fluid bypass, when said power piston did not have fully near any of the first end of said actuation-cylinder and the second end, said fluid bypass is short circuit said first fluid space and said second fluid space effectively;
First-class actuation mechanism, the fluid of controlling between said first fluid space and said first port is communicated with; With
The second mobile mechanism, the fluid of controlling between said second fluid space and said second port is communicated with; Wherein:
When said fluid bypass was opened basically, at least one in the said first-class actuation mechanism and the said second mobile mechanism closed at least in part;
When said fluid bypass was closed basically, each in the said first-class actuation mechanism and the said second mobile mechanism was opened at least in part;
Said actuated valve is said upper end-hole and lower end mouth fuel feeding through last fluid pipe-line with following fluid pipe-line respectively.
5. the switching time method of measurement of variable valve actuator according to claim 1 is characterized in that, said pressure transducer is installed in said upper end-hole pressure measurement district;
Said cracking pressure threshold value be the first cracking pressure threshold value Pt11, said closing pressure threshold value be the first closing pressure threshold value Pt12, said cracking pressure to stride the presentation time difference be that first cracking pressure is striden presentation time difference dt11, said closing pressure to stride presentation time difference be that first closing pressure is striden presentation time difference dt12, said pressure diagram is first pressure diagram, it is that first cracking pressure is striden t11 at quarter presentation time that said cracking pressure strides that the presentation time carves;
Stride by said first cracking pressure that the presentation time is carved t11 and said first cracking pressure is striden presentation time difference dt11, calculate said valve opening t1 constantly:
t1=t11+?dt11，
Stride by said first closing pressure that the presentation time is carved t12 and said first closing pressure is striden presentation time difference dt12, calculate said valve-closing t2 constantly:
t2=t12+?dt12。
6. the switching time method of measurement of variable valve actuator according to claim 1 is characterized in that, said pressure transducer is installed in said lower end mouth pressure measurement district;
Said cracking pressure threshold value be the second cracking pressure threshold value Pt21, said closing pressure threshold value be the second closing pressure threshold value Pt22, said cracking pressure to stride the presentation time difference be that second cracking pressure is striden presentation time difference dt21, said closing pressure to stride presentation time difference be that second closing pressure is striden presentation time difference dt22, said pressure diagram is second pressure diagram, it is that second cracking pressure is striden t21 at quarter presentation time that said cracking pressure strides that the presentation time carves;
Stride by said second cracking pressure that the presentation time is carved t21 and said second cracking pressure is striden presentation time difference dt21, calculate said valve opening t1 constantly:
t1=t21+?dt21，
Stride by said second closing pressure that the presentation time is carved t22 and said second closing pressure is striden presentation time difference dt22, calculate said valve-closing t2 constantly:
t2=t22+?dt22。
7. the switching time method of measurement of variable valve actuator according to claim 1 is characterized in that, the control system of said variable valve actuator comprises first pressure transducer and second pressure transducer;
Said first pressure transducer is installed in said upper end-hole pressure measurement district;
Said cracking pressure threshold value be the first cracking pressure threshold value Pt11, said closing pressure threshold value be the first closing pressure threshold value Pt12, said cracking pressure to stride the presentation time difference be that first cracking pressure is striden presentation time difference dt11, said closing pressure to stride presentation time difference be that first closing pressure is striden presentation time difference dt12, said pressure diagram is first pressure diagram, it is that first cracking pressure is striden t11 at quarter presentation time that said cracking pressure strides that the presentation time carves;
Stride by said first cracking pressure that the presentation time is carved t11 and said first cracking pressure is striden presentation time difference dt11, calculate first valve opening t1 ' constantly:
t1′=t11+?dt11，
Stride by said first closing pressure that the presentation time is carved t12 and said first closing pressure is striden presentation time difference dt12, calculate first valve-closing t2 ' constantly:
t2′=t12+?dt12；
Said second pressure transducer is installed in said lower end mouth pressure measurement district;
Said cracking pressure threshold value be the second cracking pressure threshold value Pt21, said closing pressure threshold value be the second closing pressure threshold value Pt22, said cracking pressure to stride the presentation time difference be that second cracking pressure is striden presentation time difference dt21, said closing pressure to stride presentation time difference be that second closing pressure is striden presentation time difference dt22, said pressure diagram is second pressure diagram, it is that second cracking pressure is striden t21 at quarter presentation time that said cracking pressure strides that the presentation time carves;
Stride by said second cracking pressure that the presentation time is carved t21 and said second cracking pressure is striden presentation time difference dt21, calculate that said duaspiracle opens t1 constantly ":
t1″=t21+?dt21，
Stride by said second closing pressure that the presentation time is carved t22 and said second closing pressure is striden presentation time difference dt22, calculate said duaspiracle close moment t2 ":
t2″=t22+?dt22；
Said first valve opening moment t1 ' is opened t1 constantly with said duaspiracle " compare, if both differences in margin of error, then calculate said valve opening t1 constantly; With said first valve-closing moment t2 ' and said duaspiracle close moment t2 " compare, if both differences in margin of error, then calculate said valve-closing t2 constantly.
8. the switching time method of measurement of variable valve actuator according to claim 7; It is characterized in that; In margin of error; Said valve opening t1 constantly equals said first valve opening t1 ' open t1 constantly with the said duaspiracle mean value of " mean value, said valve-closing t2 constantly equals said first valve-closing t2 ' and said duaspiracle close moment t2 constantly " constantly.
9. the switching time method of measurement of variable valve actuator according to claim 1 is characterized in that, valve opening displacement X1 is defined in a numerical value of 1% to 15% scope of valve full lift.
10. the switching time method of measurement of variable valve actuator according to claim 1 is characterized in that, closes the numerical value that displacement X2 is defined in 85% to 99% scope of valve full lift.
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210095178XA CN102588029A (en) | 2012-03-31 | 2012-03-31 | Method for measuring opening-closing time of variable valve actuator |
| CN201210323412.XA CN102797527B (en) | 2012-03-31 | 2012-09-05 | Method for measuring opening time and closing time of variable valve actuator |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210095178XA CN102588029A (en) | 2012-03-31 | 2012-03-31 | Method for measuring opening-closing time of variable valve actuator |
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| CN102588029A true CN102588029A (en) | 2012-07-18 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201210095178XA Pending CN102588029A (en) | 2012-03-31 | 2012-03-31 | Method for measuring opening-closing time of variable valve actuator |
| CN201210323412.XA Expired - Fee Related CN102797527B (en) | 2012-03-31 | 2012-09-05 | Method for measuring opening time and closing time of variable valve actuator |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104880319A (en) * | 2014-02-28 | 2015-09-02 | 比亚迪股份有限公司 | Variable valve timing phase calibrating method and apparatus |
| CN106647683A (en) * | 2015-11-03 | 2017-05-10 | 北汽福田汽车股份有限公司 | Controller switching value calibration method and device |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103032179A (en) * | 2013-01-04 | 2013-04-10 | 江苏公大动力技术有限公司 | Timing control system and method for variable valve |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7302920B2 (en) * | 2005-06-16 | 2007-12-04 | Zheng Lou | Variable valve actuator |
| US7290509B2 (en) * | 2005-08-01 | 2007-11-06 | Zheng Lou | Variable valve actuator |
| US7591237B2 (en) * | 2006-02-03 | 2009-09-22 | Lgd Technology, Llc | Electromechanical variable valve actuator with a spring controller |
-
2012
- 2012-03-31 CN CN201210095178XA patent/CN102588029A/en active Pending
- 2012-09-05 CN CN201210323412.XA patent/CN102797527B/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104880319A (en) * | 2014-02-28 | 2015-09-02 | 比亚迪股份有限公司 | Variable valve timing phase calibrating method and apparatus |
| CN106647683A (en) * | 2015-11-03 | 2017-05-10 | 北汽福田汽车股份有限公司 | Controller switching value calibration method and device |
| CN106647683B (en) * | 2015-11-03 | 2019-01-18 | 北京宝沃汽车有限公司 | A kind of controller switches amount scaling method and device |
Also Published As
| Publication number | Publication date |
|---|---|
| CN102797527A (en) | 2012-11-28 |
| CN102797527B (en) | 2014-06-25 |
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Application publication date: 20120718 |