CN1026189C - Multi-function floating proportional pressure controlling valve - Google Patents
Multi-function floating proportional pressure controlling valve Download PDFInfo
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- CN1026189C CN1026189C CN 91102121 CN91102121A CN1026189C CN 1026189 C CN1026189 C CN 1026189C CN 91102121 CN91102121 CN 91102121 CN 91102121 A CN91102121 A CN 91102121A CN 1026189 C CN1026189 C CN 1026189C
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Abstract
The present invention relates to a force-induced hydraulic chamber-amplified downdraught engine which belongs to the field of hydraulic drive mechanisms. Staged energy amplification is carried out through a multi-stage machine set composed of a hydraulic motor and an oil pump which have the same power. After energy diffluence, a part of energy enters the hydraulic motor to do work to as to convert pressure energy into mechanical energy, the other part flows back to an energy accumulator and uses the energy of the energy accumulator as a power source to start the engine so that the engine can continuously output energy and do work on a working surface. The engine can substitute various resources and other engines in a wide range and is an energy-saving product.
Description
The present invention relates to a kind of multi-function floating proportional pressure controlling valve, its International Classification of Patents position is IPC
5F15B13/043.This valve belongs to type pilot proportional pressure valve class, promptly partly form by electrical-controller, linear electromagnet, pressure valve body etc., it be carry out in the hydraulic system continuous control, telecontrol and the control of open and close ring compression indispensable critical elements.
Existing proportional pressure valve is the hand-operated pressure regulation appliance with linear electromagnetic replacement usual pressure valve mostly, therefore the dead band of electromagnet, stagnate ring and a series of shortcomings such as non-linear all show in proportional pressure valve, and the keying error of Manual pressure valve also exists in proportional pressure valve equally, and therefore every index of existing proportional pressure valve is difficult to satisfy the needs of engineering development.In addition, also have in the recent period a class to adopt the proportional pressure valve of closed loop control to come out, though performance increase owing to be that poor system is arranged, thus static difference still exist, especially to the receptance of flow.
Existing Proportional valve is also the same with the Manual pressure valve of a great variety, and only main type is six kinds of proportional relief valve, ratio Fixed pressure reducing valve, ratio Fixed differential reducing valve, ratio Proprutioning pressure reducing valve, ratio internal control sequence valve and ratio external control sequence valves etc.These valves structurally have nothing in common with each other, and give technology and produce to make troubles.
In sum, existing proportional pressure valve still has two an open questions, and the monotony of first valve function does not have multi-functional characteristics, and the valve of difference in functionality structurally has nothing in common with each other, and does not have interchangeability therebetween; It two is that various proportional pressure valves all are that poor system is arranged, because dead band, the ring that stagnates, receptance non-linear and the pressure versus flow amount all are the performances of static difference.
Task of the present invention is, a kind of multi-functional and astatic proportional pressure valve that has is proposed, make this valve structurally have bigger applicability, the position that only needs to change several hydraulic pressure and electric switch just can constitute required function, and this all is very favourable to technology, production and use; Make this valve have high precision and the high stability of opening and closing simultaneously, promptly have astatic character, its pilot pressure is not subjected to the influence of changes in flow rate.
The technical measures of implementing task of the present invention are, by means of a kind of special electrical-controller and two micro pressure sensors and according to a kind of new control theory structure are set.
Adopt a kind of double input network in the electrical-controller of the present invention, one of input and the differentiating amplifier that is in series with it, valve body and pressure transducer are formed the little closed-loop system of rapid-action, are equivalent to the equivalent open loop part of whole system; Two and pressure transducer output signal of input are subtracted each other, and by being defeated by above-mentioned equivalent open loop behind the integrating amplifier integration again, constitute 1 type closed loop negative feedback system.Two input circuits are worked in coordination and can be made system have the feature of 2 type astatic systems, promptly also can accomplish floating under the ramp function effect.
Two micro pressure sensors of the present invention place the import and the outlet of valve respectively, and both are through amplifying and subtract each other afterwards as the unified system that feeds back to.This feedback cooperatively interacts with several electricity, liquid switch and has constituted the multifunctionality of valve.When using as proportional pressure control valve, the outlet pressure sensor signal of valve is disconnected, and the regulated variable of system is the inlet pressure P1 of valve; When as the ratio Fixed pressure reducing valve, the inlet pressure sensor signal of valve is disconnected, and the regulated variable of system is the outlet pressure P2 of valve; When using as Fixed differential reducing valve, two feedback signals are fed back simultaneously, and obviously the regulated variable of system is the inlet/outlet pressure difference P1-P2 of valve at this moment; When as Proprutioning pressure reducing valve, answer the command signal of parting system, and make the input end grounding of system.This moment, the feedback signal of system was adjusted into zero automatically.Because string has a potentiometer that coefficient gamma is variable on the output channel of the inlet pressure sensor of valve, so the time γ P1-P2=0, i.e. γ=P2/P1.Should be noted that in other states of valve γ=1 of ordering.Should be identical when using with the state of proportional pressure control valve as the ratio sequence valve, just the hydraulic switch with a rotation communicates the inlet pressure sensor of valve successively with the filler opening or the external control hydraulic fluid port of valve, thus the internal control or the external control ratio sequence valve that constitute.
Another characteristics of the present invention are less demanding to the body portion of valve, and its pilot valve both can be cylindrical bilateral three-way valve or cylindrical monolateral Twoway valves, also can be cone valves; Both open loops promptly come the position of balance and control guide spool with spring and electromagnetic force, also can be closed loop, promptly come balance with the pressure of guide's spool one end and the other end electromagnetic force and control the position of guide's spool.
Below in conjunction with embodiment shown in the drawings, multi-function floating proportional pressure valve of the present invention is further described.Wherein:
Fig. 1 (a) is that pilot valve of the present invention is the multi-function floating proportional pressure valve structural representation of cylindrical bilateral three-way valve.
Fig. 1 (b) is by the electrical-controller circuti diagram of multi-function floating proportional pressure valve shown in Fig. 1 (a) (three embodiments are general).
Fig. 2 is the sectional view along A-A line shown in Fig. 1 (a).
Fig. 3 is that pilot valve of the present invention is the structural representation of the multi-function floating proportional pressure valve of cone valve.
Fig. 4 is that pilot valve of the present invention is the structural representation of the multi-function floating proportional pressure valve of monolateral Twoway valves.
By Fig. 1 (a) and Fig. 1 (b) as can be known, proportional pressure valve of the present invention is made up of an electrical-controller 14, a linear electromagnet 21 and a valve body 15.Wherein electrical-controller 14 by fan-in network 16, group amplifier 2,7,8, derivative unit assembly 3,4, power amplifier 5, integrating amplifier 6, pressure transducer power supply 13, data amplifier 9,10 and relay B with and 13 parts such as control wiring 17 form.Wherein fan-in network 16 is made up of status switch f, a, diode L and opposite sign device 1 respectively; The normally opened contact of relay B is b, and its control wiring is made up of variable coefficient parts α, β and amplifier 18 respectively.In addition, in electrical-controller 14, be used in addition the dynamic and static quality of regulating system variable coefficient parts W1, W2, W3 and W4 and be used for the feedback signal that on-off valve outlet pressure sensor 12 sent switch C and be used for determining the variable coefficient parts γ of proportional pressure reducing value.
Valve body part 15 is made up of three parts such as main valve 19, pilot valve 20 and pressure transducers 11,12, and wherein main valve 19 has a cylindrical main valve plug 22, and it slides up and down in main valve housing 23, in the upper end of main valve plug 22 cavity volume 49 main spool spring 24 is housed.Main valve housing 23 is arranged in the main valve body 25, and tapered window is arranged in its lower end, the following and top filler opening 26 of main valve and the oil outlet 27 of main valve be arranged to respectively of this window.Main valve filler opening 26 has two oil circuits 28 and 29, and wherein oil circuit 28 passes to the upper surface of main valve body 25, so that lead to pilot valve, starts to control to make and uses; Oil circuit 29 leads to pressure transducer 11 by throw over switch e.What communicate with throw over switch e also has an outside control mouth 30, (is called e when throw over switch e is in position shown in Fig. 1 (a)
1Put), what sensor 11 was experienced is main valve filler opening pressure P 1; When throw over switch e (is called e when position shown in Fig. 1 (a) rotates counterclockwise 90 °
2Put), sensor 11 impression be external control pressure P ou in the outside control mouth 30.Pressure transducer 12 is arranged on the oil circuit of main valve outlet 27, is used for measuring main valve outlet pressure P2.Pressure transducer 11 and 12 bridge circuit two ends are by power supply 13 power supplies, and amplify the back as the pressure feedback signal logistics through data amplifier 9,10 respectively by the electrical signal of bridge circuit other two ends output.Also have a vertical draining through hole 31 on the right side of main valve body 25, its lower end communicates with oil return, and the upper end communicates with pilot valve by damping hole 41.Between the outlet 27 of main valve and draining through hole 31, a throw over switch d is arranged, the on-off between its control main valve outlet 27 and the draining through hole 31.Pilot valve 20 has a guide valve core 32, and this spool is provided with two convex shoulders 33 and 34, and can slide in corresponding guide valve bushing 35, and 35 of guide valve bushings are arranged in the pilot valve body 36.The left end of guide valve core 32 is equipped with spring 37, and right-hand member contacts with the iron core of electromagnet 21.By Fig. 1 (a) and Fig. 2 as can be known, be respectively arranged with on guide valve bushing 35, the oil return window, their each free one manholes that vertically passes guide valve bushing 35 axis constitute.Through-hole diameter is 2.0～3.0 millimeters.The outer survey of above-mentioned through hole is respectively arranged with annular collecting tray 38 and 44, and they communicate with oil circuit 39 and 40 separately.Wherein oil circuit 39 communicates with oil circuit 28 on the main valve body; Oil circuit 40 communicates with draining through hole 31 by damping hole 41.Guide valve bushing 35 communicates with the epicoele 49 of main valve plug 22 by oil circuit G, damping hole 46 with the formed cavity volume 45 of neck of guide valve core 32 centres.The cavity volume of guide valve core 32 left ends communicates with pilot valve intermediate cavity 45 by oil circuit 42, and the cavity volume of guide valve core 32 right-hand members communicates with the epicoele 49 of main valve plug 22 by the oil circuit 43 of tiltedly wearing guide valve bushing 35 and pilot valve body 36, thereby constitutes the dynamic pressure feedback loop of guide valve core 32.The control coil of electromagnet 21 is connected by the output terminal of the power amplifier 5 in latch 47, socket 48 and the electrical-controller, and the latter can provide the electric current of 0～800mA.
The control principle of the electrical-controller shown in Fig. 1 (b) can be summarized as follows: when command signal V successively by the switch f in the fan-in network 16, diode L, switch a and opposite sign device 1(or without opposite sign device 1) after divide the two-way logistics.Lead up to variable coefficient parts W1, group amplifier 2, differentiating amplifier 2 assemblies 3,4, power amplifier 5, electromagnet 21, valve body 15, pressure transducer 11,12, data amplifier 9,10, after the links such as variable coefficient parts γ, on-off switch C and operational amplifier 8, form with negative sign feeds back to group amplifier 2, constitute a little closed-loop system, be referred to as the equivalent open loop networks of system.This network has two effects, and the first improves the rapidity of system, and it two is check valve body integrating effects that main valve plug 22 is produced when being open loop, otherwise double integral system is difficult to stablize.Though for closed loop but under some state, have when just presenting effect, also can be suppressed by this little closed loop for valve body.Another road of the command signal V that process fan-in network 16 is imported is by group amplifier 7, import equivalent open loop networks by group amplifier 2 again after variable coefficient parts W4, the integrating amplifier 6, and pressure feedback signal is defeated by group amplifier 7 with the negative sign form, compare with given command signal, thereby constitute 1 type floating close loop negative feedback control pressurer system of the present invention.By adjusting the coefficient of W1, W4, the result of above-mentioned two input signal system interactions can make the present invention have the character of 2 type astatic systems again, i.e. floating under the ramp function effect.
The function of electrical-controller repeat circuit B shown in Fig. 1 (b) is to prevent the mistake integration of integrating amplifier under system's runaway condition, because when system changes normal state over to by runaway condition, the integrating amplifier output terminal perhaps is compression shock because the mistake voltage that integration obtained will make system moment a very big pressure overshoot occur.State when so-called system runaway condition is meant and makes valve can't produce required pressure or required pressure to be lower than the pressure minimum of valve owing to underfed.Under normal state, between the delivery pressure Vt and instruction signal V of group amplifier 2 function relation, i.e. a V are arranged
t=f(V) determine, and can obtain by test.This curve useable linear function V
t=α V+ δ covers, α in the formula=max(σ V
t/ σ V), δ is for making linear function cover the needed minimum cut square of original value.Obviously, δ＞V under the normal state
t-α V, δ≤V under the runaway condition
t-α V.If the starting resistor of relay is △, then the condition that starts of relay is δ=10 △/β, can determine the β value thus, i.e. β=10 △/δ, K Ω.Relay B starts back contact b closure, and at this moment integrating amplifier 6 becomes inertial element, thereby stops integration.When because the flow boost pressure can reach setting value or because setting value during no longer less than the minimum pressure of valve, normal state is got back to by system, thereby Vt-α V＜δ, thus relay B discharge, contact b disconnection, integrating amplifier begins integration again.
In addition, the Proportional valve shown in Fig. 1 (a) and Fig. 1 (b) also has 4 needs explanations:
1) the diode L in the fan-in network 16 guarantees that signal constant for just, enters runaway condition to avoid system;
2) purpose of shunt capacitance is to strobe in the feeder loop of group amplifier 2;
3) effect of damping hole 41 is dampings of raising system, to reduce vibration;
4) damping hole 46 has two effects, the first improves the damping of main valve plug 22, another is to make guide valve core 32 have the effect of dynamic pressure feedback by oil circuit 42 and 43, to improve the damping of pilot valve, obviously, when guide valve core 32 moves right, 49 oil returns of main valve plug epicoele, thereby the pressure in the main valve plug epicoele 49 is greater than the pressure in the pilot valve intermediate cavity 45, so guide valve core 32 produces a hydraulic coupling left, hinder its motion, otherwise,, thereby lead pressure in the intermediate cavity 45 greater than the pressure in the main valve epicoele 49 when guide valve core 32 main valve epicoele 49 oil-feeds during to left movement, so on guide valve core 32, produce a hydraulic coupling to the right, also be the motion that hinders guide valve core 32.
Describe the multi-functional embodiment of proportional pressure valve of the present invention now in detail in conjunction with Fig. 1 (a) and Fig. 1 (b).
(1) proportional pressure control valve
Proportional pressure valve shown in Fig. 1 (a) and Fig. 1 (b) is the working state of proportional pressure control valve, and this moment is by the feedback channel of the pressure transducer 12 of switch C disconnection P2, and the variable coefficient value of the pressure transducer 11 of P1 is transferred to maximum, i.e. γ=1.Hydraulic switch d makes main valve oil outlet 27 communicate with draining through hole 31, and hydraulic switch e makes main valve filler opening 26 communicate with pressure transducer 11.When command signal V imports, through the upper contact a of switch f, diode L and switch a
1Divide two-way to import system into, the first is defeated by electromagnet 21 through W1, group amplifier 2, W2, derivative unit assembly 3,4 and power amplifier 5, then the spring force that iron core overcomes spring 37 with guide valve core 32 push the left side to, high pressure oil will flow to main valve epicoele 49 by left window, intermediate cavity 45, oil circuit G and the damping hole 46 of oil circuit 28,39, guide valve bushing 35.So main valve plug 22 begins to move down, turn down the main valve window, so pressure P 1 begins to rise, pressure transducer 11 is experienced this variation, and by data amplifier 9, group amplifier 8 is defeated by group amplifier 2 with the negative sign form, constitutes little close loop negative feedback control mesh.When guide valve core 32 is got back to meta basically, main valve plug 22 stop motions, at this moment pressure P 1 is basically near setting value.Owing to adopted derivative unit 3,4, can make dynamic process carry out very soon.Meanwhile input instruction signal is again from another passage logistics, promptly be defeated by group amplifier 7, and with subtract each other from the feedback signal of group amplifier 8, error signal after will subtracting each other is defeated by integrating amplifier 6 and is carried out integration, signal behind the integration is defeated by group amplifier 2 again, thereby controlled pressure P 1 is revised, and is zero up to error signal, integrator just stops integration, and this shows that system is an indifference.When the W1 value is transferred to optimum value, can further improves the rapidity of system, and make system near 2 type astatic systems.
(2) ratio internal control sequence valve
If with the throw over switch d half-twist shown in Fig. 1 (a), the present invention promptly constitutes the internal control sequence valve.As main valve inlet pressure P1 during less than setting value P10, guide valve core 32 is pushed to the left side by electromagnetic force, therefore, high pressure oil enters main valve epicoele 49 by the left window of guide valve bushing 35, and main valve plug 22 is pressed on the tapered window of main valve housing 23, therefore, main valve oil outlet 27 does not have fluid to flow out.As pressure P 1=P10, and during slightly greater than P10, guide valve core 32 is got back to meta and deflection the right slightly, so the right side window of main valve epicoele 40 by guide valve bushing 35 communicate with draining through hole 31, so main valve plug 22 moves on beginning, the main valve window is opened.Because this moment, the main valve oil outlet 27 led to load, so P1 does not open and descends owing to the main valve window, so system becomes open loop, relay B startup, and main valve plug 22 will rise to limit position always, thereby the pressure loss is less.
(3) ratio external control sequence valve
If the throw over switch e shown in Fig. 1 (a) is reversed 90 °, then aforementioned proportion internal control sequence valve just makes ratio external control sequence valve into.Its working principle is identical with ratio internal control sequence valve.
(4) ratio Fixed differential reducing valve
If the switch C shown in Fig. 1 (b) is closed, just composition Fixed differential reducing valve.Therefore the feedback signal the time is (P1-P2) K
fK in the formula
fBe the pressure transducer coefficient.For astatic system, V=(P1-P2 during stable state) K
fSo, △ P=P1-P2=V/K
f
(5) ratio Proprutioning pressure reducing valve
If with the switch f ground connection shown in Fig. 1 (b), switch C closes and variable coefficient γ is transferred to a certain value, then just composition Proprutioning pressure reducing valve of the present invention.Because be input as zero this moment, then set up, i.e. (γ P1-P2) K according to establishing an equation under the floating principle
f=0, so γ=P2/P1.Obviously, the pressure ratio of a correspondence is promptly arranged whenever for a γ value.
(6) ratio Fixed pressure reducing valve
If with the switch a plate shown in Fig. 1 (b) to lower contact a
2, the C and variable coefficient γ transferred to zero of closing a switch, then the present invention is the composition Fixed pressure reducing valve.Because this moment, command signal V became negative value by opposite sign device 1, and from the signal of pressure transducer 12 be on the occasion of, so still be negative feed back control system.The pressure P 2 of main valve oil outlet 27 is proportional to command signal V at this moment.
The above is first embodiment that the present invention proposes, and now second embodiment of the present invention is illustrated in down:
Shown in Fig. 3 and Fig. 1 (b) second embodiment of the present invention.Comparison diagram 3 and Fig. 1 (a), it is basic identical except that pilot valve to be not difficult to find both.For valve body 64, if replace the electromagnet 21 on pilot valve 66 right sides, and remove pressure transducer 11,12 and switch e and d with hand-operated pressure regulation appliance, promptly be common relief valve, it is a kind of close loop negative feedback control pressurer system of zero type.When doing the use of proportional pressure control valve of the present invention and ratio sequence valve, come the high pressure oil of autonomous valve filler opening 26 to enter pilot valve ante-chamber 51 by damping hole 56, oil circuit 28, damping hole 50 and oil circuit 40, and the spring force of the spring 54 of the hydraulic coupling that produced on poppet valve core 53 of the window by guide valve seat 52 and poppet valve core 53 back balances each other, and the magnetic force of this spring force and electromagnet balances each other, thereby constitutes the 3rd pressure feedback passage in the proportional pressure valve that the present invention proposes.When doing various proportional pressure-reducing valves and use, above-mentioned oil duct loses feedback effect, thereby only plays the effect of balance electromagnetic force control guide valve core 52 motions.Obviously, above-mentioned second embodiment, the working principle when using as various proportional pressure valves is identical with first embodiment with adjusting method.
Shown in Figure 4 is the 3rd embodiment of the present invention, and its used electrical-controller is identical with the first two embodiment of the present invention, therefore, contrast second with the 3rd embodiment both are basic identical as can be known, just guide valve core is different, the former is a cone valve, the latter is a column valve.This cylindrical two admittance spools 59 are identical with first embodiment again with guide valve bushing 58, only remove the window of guide valve bushing left end among first embodiment, thereby make three-way valve become Twoway valves.This embodiment is than second embodiment's advantage:
1) because guide valve core 59 has two convex shoulders, and control fluid intermediate cavity 60 and guide valve bushing window 61 flow back to fuel tank.Therefore, the axial hydraulic power on the guide valve core 59 of acting on is zero substantially, this moment electromagnetic force by the spring force 57 of guide valve core 59 left ends balance in addition, this has just eliminated the 3rd exclusive among second embodiment pressure feedback passage.Because this passage use basically is little, and when using, reduction valve not only loses negative feedback doing, sometimes even the effect of just presenting occurs;
2) owing to add dynamic pressure feedback channel 62 and 63 on the guide valve core 59, the damping of pilot valve is increased, thereby increase the stability margin of system.
The working principle of the 3rd embodiment when doing six kinds of proportional pressure valves uses is identical with preceding two embodiments with adjusting method.
Tabulate the position of the present invention's pairing each switch under various functions and the state of input instruction now.
Three embodiments of multi-function floating proportional pressure valve of the present invention not only have six kinds of functions, and its dynamic and static precision also is very high.Test shows, this valve do not have the dead band, stagnate ring and non-linear, static difference be less than 0.2%, and its pilot pressure is not subjected to the influence of changes in flow rate.
Do not find out in sum; the multifunctional floating principle of utilizing the present invention to propose can also be further improved on the circuit of electrical-controller or on the structure at valve body, or develops and other embodiments; short of disengaging basic design of the present invention ought to belong to protection scope of the present invention.
Switch
State a γ c d e V
Function
Internal control sequence valve a1 1 is e1 ∝ P1 absolutely
External control sequence valve a1 1 is the outer governor pressure of e2 direct ratio absolutely
Fixed differential reducing valve a1 1 is e1 ∝ (P1-P2) all
Proprutioning pressure reducing valve a1=P2/p1 is e1 0 all
Any all ∝ P2 of Fixed pressure reducing valve a2 0
Claims (5)
1, a kind of multi-function floating proportional pressure controlling valve, comprise an electric controller, an electromagnet and a valve body, wherein valve body comprises pressure transducer again, a pilot valve and a main valve, this moment, main valve housing was arranged in the main valve body, tapered window is arranged in its lower end, following and the top main valve filler opening and the main valve oil outlet be arranged to respectively of this window, guide valve core is provided with two convex shoulders, on guide valve bushing, be respectively equipped with into, the oil return window, they respectively are made of a manhole that vertically passes this guide valve bushing axis, the outside of above-mentioned through hole is respectively equipped with annular remittance comb groove, it is characterized in that:
Electrical-controller (14) is by fan-in network (16), group amplifier (2,7,8), derivative unit assembly (3,4), power amplifier (5), integrating amplifier (6), pressure transducer power supply (13), data amplifier (9,10) and relay (B) with and 13 parts such as control wiring (17) form, wherein fan-in network (16) is respectively by status switch (f, a), diode (L) and opposite sign device (1) are formed, the control wiring of relay (B) is respectively by variable coefficient parts (α, β) and amplifier (18) form, it is moving to be used for regulating system in the electrical-controller (14) in addition, variable coefficient parts (the W1 of static quality, W2, W3, W4) and be used for the feedback signal that break-make outlet pressure sensor (12) sent switch (C) and be used for determining the variable coefficient parts (γ) of proportional pressure reducing value;
Valve body (15) is provided with two micro pressure sensors (11,12), wherein main valve filler opening (26) has two oil circuits (28,29), oil circuit (28) passes to the upper surface of main valve body (25), lead to and start to control the pilot valve of making usefulness, oil circuit (29) passes through to pressure transducer (11) by throw over switch (e), with the throw over switch (outside control mouth (30) in addition that e communicates, the position of throw over switch (e) is set as and makes pressure transducer (11) experience main valve filler opening pressure (P1) or experience outer governor pressure (Pou) in the outside control mouth (30), the pressure transducer (12) of measuring main valve outlet pressure (P2) is arranged on the oil circuit of main valve outlet (27), also has a vertical draining through hole (31) on the right side of main valve body (25), its lower end communicates with oil return, the upper end communicates with pilot valve by damping hole (41), between the outlet (27) of main valve and draining through hole (31), there is one to control the throw over switch of on-off (d) therebetween, the left end of guide valve core (32) is equipped with spring (37), right-hand member contacts with the iron core of electromagnet (21), annular collecting tray (38 on the guide valve bushing (35), 44) respectively with oil circuit (39,40) communicate, oil circuit (40) communicates with draining through hole (31) by damping hole (41), the formed cavity volume of neck (45) in the middle of guide valve bushing (35) and the guide valve core (32) is by oil circuit (G), damping hole (46) communicates with the epicoele (49) of main valve plug (22), and guide valve core (32) left end cavity volume communicates with pilot valve intermediate cavity (45) by oil circuit (42).Guide valve core (32) right-hand member cavity volume communicates with the epicoele (49) of main valve plug (22) by the oil circuit (43) of tiltedly wearing guide valve bushing (35) and pilot valve body (36), thereby constitute the dynamic pressure feedback loop of guide valve core (32), the control coil of electromagnet (21) is connected by the output terminal of the power amplifier (5) in latch (47), socket (48) and the electric controller.
Electrical-controller (14) adopts the double input network, one of input and differentiating amplifier assembly (3,4), power amplifier (5), electromagnet (21), valve body (15), pressure transducer (11,12), data amplifier (9,10), variable coefficient parts (γ), on-off switch (C) and the operational amplifier (8) etc. that are in series with it are formed a rapid-action equivalence open loop networks, input two with pressure transducer (11,12) pressure feedback signal input group amplifier (7), compare with given command signal; And import equivalent open loop networks by group amplifier (2) again afterwards by group amplifier (7), variable coefficient parts (W4), integrating amplifier (6),
By being contained in two pressure transducers (11,12) on the valve body (15) and the multifunctionality of three status switches (f, a, c) in two state switch (d, e) and the electrical-controller (14) and variable coefficient parts (γ) composition pressure valve.
2, a kind of multi-function floating proportional pressure controlling valve, comprise an electrical-controller, an electromagnet and a valve body, valve body wherein, wherein valve body comprises pressure transducer, a pilot valve and a main valve again, this moment, main valve housing was arranged in the main valve body, and tapered window is arranged in its lower end, the following and top main valve filler opening and the main valve oil outlet be arranged to respectively of this window, guide valve core is a poppet valve core, it is characterized in that:
Electrical-controller (14) is by fan-in network (16), group amplifier (2,7,8), derivative unit assembly (3,4), power amplifier (5), integrating amplifier (6), pressure transducer power supply (13), data amplifier (9,10) and relay (B) with and 13 parts such as control wiring (17) form, wherein fan-in network (16) is respectively by status switch (f, a), diode (L) and opposite sign device (1) are formed, the control wiring of relay (B) is respectively by variable coefficient parts (α, β) and amplifier (18) form, it is moving to be used for regulating system in the electrical-controller (14) in addition, variable coefficient parts (the W1 of static quality, W2, W3, W4) and be used for the feedback signal that on-off valve outlet pressure sensor (12) sent switch (C) and be used for determining the variable coefficient parts (γ) of proportional pressure reducing value.
Valve body (64) is provided with two micro pressure sensors (11,12), wherein main valve filler opening (26) has two oil circuits (28,29), oil circuit (28) origin or beginning is provided with damping hole (56), terminal is provided with damping hole (50) oil circuit (29) and leads to pressure transducer (11) by throw over switch (e), an outside control mouth (30) in addition that communicates with throw over switch (e), the position of throw over switch (e) is arranged to make pressure transducer (11) to experience main valve filler opening pressure (P1) or is experienced the outer governor pressure (Pou) of outside control mouth (30), the pressure transducer (12) of measuring main valve outlet pressure (P2) is arranged on the oil circuit of main valve outlet (27), also has a vertical draining through hole (31) on the right side of main valve body (64), its lower end communicates with oil return, the upper end communicates with pilot valve by damping hole (41), between the outlet (27) of main valve and draining through hole (31), there is one to control the throw over switch of on-off (d) therebetween, main valve filler opening (26) and damping hole (56), oil circuit (28), damping hole (50) and oil circuit (40) and pilot valve ante-chamber (51) communicate, a spring (54) that is used for its left end hydraulic coupling of balance and its right-hand member electromagnetic force is set between poppet valve core (53) and electromagnet (21), thereby the 3rd pressure feedback passage in the composition pressure valve, electromagnet (21) control coil is by latch (47), the output terminal of the power amplifier (5) in socket (48) and the electrical-controller is connected.
Electrical-controller (14) adopts the double input network, one of input and the differentiating amplifier assembly (3 that is in series with it, 4), power amplifier (5), electromagnet (21), valve body (64), pressure transducer (11,12), data amplifier (9,10), variable coefficient parts (γ), on-off switch (c) and operational amplifier (8) etc. are formed a rapid-action equivalence open loop networks, input two with pressure transducer (11,12) pressure feedback signal input group amplifier (7), compare with given command signal, and by group amplifier (7), variable coefficient parts (W4), integrating amplifier (6) is imported equivalent open loop networks by comprehensive amplify (2) again afterwards.
By being contained in two pressure transducers (11,12) on the valve body (64) and the multifunctionality of three status switches (f, a, c) in two state switch (d, e) and the electrical-controller (14) and variable coefficient parts (γ) composition pressure valve.
3, a kind of multi-function floating proportional pressure controlling valve, comprise an electrical-controller, an electromagnet and a valve body, wherein valve body comprises pressure transducer, a pilot valve and a main valve again, this moment, main valve housing was arranged in the main valve body, tapered window is arranged in its lower end, following and the top main valve filler opening and the main valve oil outlet be arranged to respectively of this window, guide valve core is provided with two convex shoulders, it is characterized in that;
Electrical-controller (14) is by fan-in network (16), group amplifier (2,7,8), derivative unit assembly (3,4), power amplifier (5), integrating amplifier (6), pressure transducer power supply (13), data amplifier (9,10) and relay (B) with and 13 parts such as control wiring (17) form, wherein fan-in network (16) is respectively by status switch (f, a), diode (L) and opposite sign device (1) are formed, the control wiring of relay (B) is respectively by variable coefficient parts (α, β) and amplifier (18) form, it is moving to be used for regulating system in the electrical-controller (14) in addition, variable coefficient parts (the W1 of static quality, W2, W3, W4) and be used for the feedback signal that on-off valve outlet pressure sensor (12) sent switch (C) and be used for determining the variable coefficient parts (γ) of proportional pressure reducing value;
Two micro pressure sensors (11 are set on the valve body (65), 12), wherein main valve filler opening (26) has two oil circuits (28,29), oil circuit (28) origin or beginning is provided with damping hole (56), terminal is provided with damping hole (50), oil circuit (29) leads to pressure transducer (11) by throw over switch (e), an outside control mouth (30) in addition that communicates with throw over switch (e), the position of throw over switch (e) is arranged to make pressure transducer (11) to experience main valve filler opening pressure (P1) or is experienced the outer governor pressure (Pou) of outside control mouth (30), the pressure transducer (12) of measuring main valve outlet pressure (P2) is arranged on the oil circuit of main valve outlet (27), also has a vertical draining through hole (31) on the right side of main valve body (65), its lower end communicates with oil return, the upper end communicates with pilot valve by damping hole (41), between the outlet (27) of main valve and draining through hole (31), there is one to control the throw over switch of on-off (d) therebetween, guide valve bushing (58) left end is not provided with window, thereby three-way valve is become at Twoway valves, the left end of guide valve core (59) is equipped with spring (57), right-hand member contacts with the iron core of electromagnet (21), control fluid flows back to fuel tank through intermediate cavity (60) and guide valve bushing window (61), therefore the axial hydraulic power that acts on the guide valve core (59) is zero substantially, electromagnetic force is by the spring force balance of different spool (59) left end at this moment, different spool adds dynamic pressure feedback channel (62 on (59), 63), the damping of pilot valve is increased, thereby increase the stability margin of system, the control coil of electromagnet (21) is by latch (47), the output terminal of the power amplifier (5) in socket (48) and the electrical-controller is connected
Electrical-controller (14) adopts the double input network, one of input and the differentiating amplifier assembly (3 that is in series with it, 4), power amplifier (5), electromagnet (21), valve body (65), pressure transducer (11,12), data amplifier (9,10), variable coefficient parts (γ), on-off switch (c) and operational amplifier (8) etc. are formed a rapid-action equivalence open loop networks, input two with pressure transducer (11,12) pressure feedback signal input group amplifier (7), compare with given command signal, and by group amplifier (7), variable coefficient parts (W4), integrating amplifier (6) is imported equivalent open loop networks by group amplifier (2) again afterwards
By being contained in two pressure transducers (11,12) on the valve body (65) and the multifunctionality of three status switches (f, a, c) in two state switch (d, e) and the electrical-controller (14) and variable coefficient parts (γ) composition pressure valve.
4, by each the proportional pressure control valve in the claim 1 to 3, it is characterized in that, two state switch (d, e) on the valve body (15,64,65) respectively are provided with two gears, the switch (C) of electrical-controller (14) is provided with and disconnects and two gears that close, switch (f) is provided with to be connected and two gears of ground connection, and switch (a) is provided with upper contact (a
1) and lower contact (a
2), the variable coefficient value of variable coefficient parts (γ) is adjustable.
5, by the proportional pressure control valve of claim 1 or 3, it is characterized in that the diameter that vertically passes the manhole of its axis on the guide valve bushing (35,38) is 2～3 millimeters.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 91102121 CN1026189C (en) | 1991-04-09 | 1991-04-09 | Multi-function floating proportional pressure controlling valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 91102121 CN1026189C (en) | 1991-04-09 | 1991-04-09 | Multi-function floating proportional pressure controlling valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1065709A CN1065709A (en) | 1992-10-28 |
| CN1026189C true CN1026189C (en) | 1994-10-12 |
Family
ID=4905416
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 91102121 Expired - Fee Related CN1026189C (en) | 1991-04-09 | 1991-04-09 | Multi-function floating proportional pressure controlling valve |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1026189C (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100353097C (en) * | 2004-12-23 | 2007-12-05 | 北京三博中自科技有限公司 | Proportional control valve for lifting height of nozzle |
| CN110425245A (en) * | 2019-07-22 | 2019-11-08 | 成都博仕腾科技有限公司 | A kind of rolling stock half active oil-pressure damper of double oil circuits switching regulator adaptive damping |
| CN111022402B (en) * | 2019-12-04 | 2021-09-17 | 中国直升机设计研究所 | Electromagnetic valve for starting helicopter APU |
-
1991
- 1991-04-09 CN CN 91102121 patent/CN1026189C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CN1065709A (en) | 1992-10-28 |
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