CN110805583B - Piezoelectric sheet driven nozzle blocking disc pressure servo valve with main valve core hydraulic compensation - Google Patents
Piezoelectric sheet driven nozzle blocking disc pressure servo valve with main valve core hydraulic compensation Download PDFInfo
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- CN110805583B CN110805583B CN201910978608.4A CN201910978608A CN110805583B CN 110805583 B CN110805583 B CN 110805583B CN 201910978608 A CN201910978608 A CN 201910978608A CN 110805583 B CN110805583 B CN 110805583B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/04—Special measures taken in connection with the properties of the fluid
- F15B21/041—Removal or measurement of solid or liquid contamination, e.g. filtering
Abstract
The invention discloses a piezoelectric ring driving nozzle blocking disc pressure servo valve with main valve core hydraulic compensation, which comprises an upper shell, an adjusting component, a first nozzle, a second nozzle, a lower shell, a valve core, a first return spring, a second return spring, an oil filter, a first shuttle valve and a second shuttle valve. The invention utilizes the piezoelectric sheet to drive the baffle disc to replace the original torque motor electro-mechanical mode, avoids the defects of complex structure, high installation requirement, poor reliability and the like of the traditional torque motor, replaces the baffle with the baffle, avoids the occurrence of high-frequency flutter and squeal of a thin and long metal plate, improves the system stability, and is also favorable for reducing the volume weight of the servo valve body to a certain extent. Meanwhile, the piezoelectric plate drive has higher endurance to severe environments such as high temperature and strong magnetic field interference than a torque motor; the valve core can be greatly compensated for the steady-state hydrodynamic force which changes along with the opening degree and the load pressure during the movement of the valve core, and the static precision of the pressure servo valve is obviously improved.
Description
Technical Field
The invention relates to an electro-hydraulic servo control element of an airplane, in particular to a piezoelectric plate driven nozzle blocking disc pressure servo valve with a main valve core for hydraulic compensation.
Background
The electro-hydraulic servo valve realizes the conversion and accurate control of electric and hydraulic signals through a hydraulic technology and an automatic control technology, is a core element in an electro-hydraulic servo control system, and directly influences and determines the performance of the whole control system. The double-nozzle baffle servo valve has the advantages of high response speed, good linearity, compact structure and the like, has good static and dynamic characteristics, and is most widely used in the industrial field. However, the torque motor of the double-nozzle baffle servo valve is complex in structure and is easy to vibrate and squeal, and the reliability and the service life of the double-nozzle baffle servo valve are seriously influenced. Meanwhile, the torque motor has slow response speed and poor anti-interference capability, and the application range of the torque motor is limited. The piezoelectric patch is a novel electro-mechanical conversion structure and has the advantages of compact structure, fast response, strong anti-interference capability and the like. However, the displacement of the piezoelectric sheet is small, and the piezoelectric sheet is not easy to be used as an actuating mechanism of a large flow valve. The invention utilizes the characteristic that the pressure servo valve works in a small opening range, utilizes the new driving technology as a driving mechanism, and designs a hydraulic compensation mechanism to improve the linearity of the servo valve when the oil supply pressure is high.
Disclosure of Invention
The invention aims to solve the technical problem of providing a piezoelectric sheet driven nozzle baffle disc pressure servo valve with main valve core hydraulic compensation aiming at the defects in the background technology.
The invention adopts the following technical scheme for solving the technical problems:
the piezoelectric ring driving nozzle blocking disc pressure servo valve with the main valve core hydraulic compensation comprises an upper shell, an adjusting component, a first nozzle, a second nozzle, a lower shell, a valve core, a first return spring, a second return spring, an oil filter, a first shuttle valve and a second shuttle valve;
the adjusting assembly comprises a fixed cylinder, N annular piezoelectric patches, N + 1O-shaped nitrile rings, a first baffle disc and a second baffle disc;
the outer diameter of the O-shaped nitrile ring is larger than that of the piezoelectric sheet, and the inner diameter of the O-shaped nitrile ring is smaller than that of the piezoelectric sheet; the N + 1O-shaped nitrile rings and the N piezoelectric plates are stacked in a staggered mode and are coaxial, and a driving piece with O-shaped nitrile rings on two sides is formed;
the second baffle plate comprises a second baffle plate and a connecting rod, one end of the connecting rod is vertically and fixedly connected with the second baffle plate, and the other end of the connecting rod is provided with a thread; the first baffle disc comprises a first baffle plate and a connecting part, the connecting part is fixedly connected with the first baffle plate, and a threaded hole matched with the thread on the connecting rod is formed in the connecting part; one end of the connecting rod with the threads penetrates through the through hole in the center of the driving piece and then is in threaded connection with the connecting part, and the driving piece is clamped between the second baffle and the connecting part; the first baffle and the second baffle are arranged in parallel;
the fixed cylinder is a hollow cylinder, and through holes for the first baffle and the second baffle to pass through are respectively arranged on two end faces of the fixed cylinder; the driving piece is arranged in the fixed cylinder, the outer wall of each O-shaped nitrile ring on the driving piece is abutted against the inner wall of the fixed cylinder, and two end faces of the fixed cylinder clamp two sides of the driving piece;
a cavity is arranged in the upper shell; the fixed cylinder is fixed in the cavity of the upper shell, so that the first baffle and the second baffle are vertically arranged; through holes for the driving wires of the N piezoelectric patches to extend out are arranged on the side walls of the upper shell and the fixed cylinder in a matched manner;
the first nozzle and the second nozzle are arranged on two sides of the upper shell, the first nozzle and the second nozzle extend into the cavity of the upper shell and respectively face the first baffle and the second baffle, and the distance between the first nozzle and the first baffle and the distance between the second nozzle and the second baffle are equal when the N piezoelectric patches are not driven;
a feedback cavity D1, a compensation cavity A1, a main cavity, a compensation cavity A2 and a feedback cavity D2 are sequentially arranged in the lower shell from left to right, and an auxiliary cavity for installing an oil filter is arranged below the main cavity of the lower shell; the lower shell is also provided with an oil inlet, a first control oil port and a second control oil port which are communicated with the outside;
the two ends of the valve core are provided with coaxial connecting rods, and the valve core is sequentially provided with a first convex ring, a second convex ring and a third convex ring from left to right; the first convex ring, the second convex ring, the third convex ring and the fourth convex ring of the valve core are arranged in a main cavity of the lower shell, two ends of the first convex ring, the second convex ring and the third convex ring respectively extend into a compensation cavity A1 and a compensation cavity A2, and connecting rods at two ends of the first convex ring and the third convex ring respectively extend into a feedback cavity D1 and a feedback cavity D2; the main cavity of the lower shell is divided into a control cavity B1, an oil through cavity C1, an oil through cavity C2 and a control cavity B2 from left to right by the first convex ring to the third convex ring, an oil supply cavity E1 is formed between the right side of the outer wall surface of the first convex ring and the inner wall of the lower shell, an oil supply cavity E2 is formed between the left side of the outer wall surface of the third convex ring and the inner wall of the lower shell, and an oil return cavity is formed between the outer wall surface of the second convex ring and the inner wall of the lower shell; a groove is formed in the left side of the outer wall surface of the first convex ring, a throttling groove F1 is formed between the groove in the left side of the outer wall surface of the first convex ring and the inner wall of the lower shell, a groove is formed in the right side of the outer wall surface of the third convex ring, and a throttling groove F2 is formed between the groove in the right side of the outer wall surface of the third convex ring and the inner wall of the lower shell;
when the valve core slides rightwards, the throttling groove F1 is communicated with the oil supply cavity E1, and the oil through cavity C1 is communicated with the oil return cavity; when the valve core slides leftwards, the throttling groove F2 is communicated with the oil supply cavity E2, and the oil through cavity C2 is communicated with the oil return cavity;
the first return spring is arranged in the feedback cavity D1, one end of the first return spring is fixedly connected with the lower shell, and the other end of the first return spring is fixedly connected with a connecting rod at one end of the valve core; the second return spring is arranged in the feedback cavity D2, one end of the second return spring is fixedly connected with the lower shell, and the other end of the second return spring is fixedly connected with the connecting rod at the other end of the valve core; the first return spring and the second return spring are used for providing pretightening force, and the pretightening force provided by the first return spring and the pretightening force provided by the second return spring are equal when the N piezoelectric patches are not driven;
the nozzle cavity of the first nozzle is communicated with the control cavity B1 through a pipeline; the nozzle cavity of the second nozzle is communicated with the control cavity B2 through a pipeline; the bottom of the upper shell cavity is communicated with the oil return cavity through a pipeline;
the auxiliary cavity is respectively communicated with the control cavity B1, the oil supply cavity E1, the oil supply cavity E2, the control cavity B2 and the oil inlet through pipelines; the oil filter is arranged in the auxiliary cavity and used for filtering impurities in oil and protecting the nozzle, the outer wall of the oil filter and the inner wall surface of the auxiliary cavity of the lower shell form a cavity, and the oil flows into the oil filter from the oil inlet, flows into the control cavity B1 and the control cavity B2 after being filtered, and flows into the oil supply cavity E1 and the oil supply cavity E2 through the cavity;
fixed throttling elements are arranged in pipelines between the auxiliary cavity and the control cavity B1 and between the auxiliary cavity and the control cavity B2;
an oil return port is formed in the oil return cavity;
the first shuttle valve and the second shuttle valve are symmetrically arranged in the lower shell and respectively comprise a first oil inlet interface, a second oil inlet interface and an oil outlet interface; a first oil inlet interface of the first shuttle valve is respectively communicated with the oil return port and the throttling groove F1 through pipelines, a second oil inlet interface is communicated with the first control oil port through a pipeline, and an oil outlet interface is communicated with the compensation cavity A1 through a pipeline; a first oil inlet interface of the second shuttle valve is respectively communicated with the oil return port and the throttling groove F2 through pipelines, a second oil inlet interface is communicated with the second control oil port through a pipeline, and an oil outlet interface is communicated with the compensation cavity A2 through a pipeline;
fixed throttling elements are arranged in pipelines among the first oil inlet interface of the first shuttle valve, the first oil inlet interface of the second shuttle valve and the oil return port and are used for ensuring that the oil pressure of the first oil inlet interfaces of the first shuttle valve and the second shuttle valve is a preset pressure threshold;
the first control oil port is also respectively communicated with the oil through cavity C1 and the feedback cavity D2 through pipelines; the second control oil port is also respectively communicated with the oil through cavity C2 and the feedback cavity D1 through pipelines.
As a further optimization scheme of the piezoelectric ring driven nozzle baffle disc pressure servo valve with the main valve core hydraulic compensation, a nozzle oil return restrictor is arranged in a pipeline between the bottom of the upper shell cavity and the oil return cavity to prevent oil in the oil return cavity from flowing into the upper shell cavity.
As a further optimization scheme of the piezoelectric ring driving nozzle baffle disc pressure servo valve with the main valve core hydraulic compensation, through holes are formed in the bottoms of the two side end faces of the fixed cylinder, so that accumulated liquid in the fixed cylinder flows into a cavity of the upper shell.
As a further optimization scheme of the piezoelectric ring driving nozzle baffle disc pressure servo valve with the main valve core hydraulic compensation, a metal film is arranged on the outer side of the piezoelectric sheet, so that the piezoelectric sheet is isolated from oil, and the service life of the piezoelectric sheet is prolonged.
The invention also discloses a hydraulic compensation method of the piezoelectric ring driven nozzle baffle disc pressure servo valve with the main valve core hydraulic compensation, which comprises the following steps:
step 1), adjusting the control voltage of each piezoelectric plate to a zero position, wherein the distances from the first nozzle to the first baffle and the distances from the second nozzle to the second baffle are the same, the nozzle cavity pressures of the first nozzle and the second nozzle are equal, the pressures of the lower shell control cavities B1 and B2 are the same, the valve core is in a middle position at the moment, the oil supply cavity E1 is sealed by the first convex ring of the valve core, and the oil supply cavity E2 is sealed by the third convex ring of the valve core;
step 2), adjusting the control voltage of each piezoelectric plate to a preset voltage threshold, wherein the preset voltage threshold is a positive value, at this time, the N annular piezoelectric plates synchronously deform rightward, the first baffle and the second baffle synchronously move rightward along with the deformation of the N annular piezoelectric plates, the distance from the first baffle to the first nozzle is increased, the distance from the second nozzle to the second baffle is reduced, the pressure of the control cavity B1 is reduced, the pressure of the control cavity B2 is increased, and the main valve core slides leftward; the oil inlet is communicated with an oil through cavity C1 through a lower shell auxiliary cavity and an oil supply cavity E1, and oil flows out of the first control oil port through a control cavity C1; the first control oil port is communicated with the oil return cavity; the oil inlet is communicated with the throttling groove F2 through the lower shell auxiliary cavity and the oil supply cavity E2, and oil flows into the oil return port; the throttling groove F1 is closed, oil does not pass through a first oil inlet interface of the first shuttle valve, a second oil inlet interface of the first shuttle valve is communicated with a first control oil port, and the oil flows into the compensation cavity A1 through the second oil inlet interface; the first oil inlet interface of the second shuttle valve is communicated with the oil inlet, the second oil inlet interface is communicated with the second control oil port, and the oil pressure of the first oil inlet interface is higher, so that the oil flows into the compensation cavity A2 through the auxiliary cavity, the oil supply cavity E2, the throttling groove F2 and the first oil inlet interface of the second shuttle valve; the feedback cavity D1 is communicated with a second control oil port; the feedback cavity D2 is communicated with the first control oil port; the compression amount of the first return spring is increased, and the compression amount of the second return spring is decreased;
step 3), restoring the control voltage of each piezoelectric plate to a zero position, wherein the N annular piezoelectric plates return to the initial positions, the distances from the first nozzle to the first baffle and the distances from the second nozzle to the second baffle are the same, the pressure of the nozzle cavities of the first nozzle and the second nozzle are equal, and the pressure of the lower casing control cavities B1 and B2 is the same; and the valve core returns to the neutral position under the action of the return spring.
Compared with the prior art, the invention adopting the technical scheme has the following technical effects:
1. the piezoelectric sheet is used for driving the blocking disc to replace the original torque motor electro-mechanical mode, so that the defects of complex structure, high installation requirement, poor reliability and the like of the traditional torque motor can be avoided. Meanwhile, the piezoelectric plate drive has higher endurance to severe environments such as high temperature and strong magnetic field interference than a torque motor;
2. the baffle is replaced by the baffle, so that the high-frequency flutter and squeal of the thin and long metal plate are avoided, the stability of the system is improved, and the volume and weight of the servo valve body are reduced to a certain extent;
3. the piezoelectric sheet structure has small output force compared with the conventional stacking structure, but has large displacement and compact structure, and is an ideal driver of the nozzle blocking disc type jet flow hydraulic valve. The driving and pre-stage hydraulic amplifier has quick response and wide adjusting range;
4. the hydraulic compensation design of the main valve core can greatly compensate the steady-state hydraulic power which changes along with the opening and the load pressure in the movement of the valve core, and has obvious effect on improving the static accuracy of the pressure servo valve. Therefore, the pressure servo valve has good linearity.
Drawings
FIG. 1 is a structural cross-sectional view of the present invention;
FIG. 2 is a schematic view of the structure of the piezoelectric plate and its outer metal film;
FIG. 3 is a schematic view of the valve core of the present invention in its operating state and fluid flow direction as it moves from zero to left;
FIG. 4 is a schematic view of the valve core of the present invention in its operating state and fluid flow direction as it moves from zero to the right;
FIG. 5 is a schematic view showing the variation curve of the valve core hydraulic force and the compensating force with the opening degree of the valve core.
In the figure, 1-upper shell, 2-fixed cylinder, 3-upper shell and fixed cylinder are provided with through holes for extending leads of each piezoelectric plate, 4-first baffle, 5-O-shaped nitrile ring, 6-piezoelectric plate, 7-first nozzle, 8-second nozzle, 9-second baffle, 10-throttling groove F2, 11-oil supply cavity E2, 12-second shuttle valve, 13-oil filter, 14-second control oil port, 15-oil return port, 16-oil inlet port, 17-first control oil port, 18-fixed throttling element in a pipeline between the second oil inlet port and the oil return port of the first shuttle valve, 19-fixed throttling element in a pipeline between the auxiliary cavity and the control cavity B1, 20-oil supply cavity E1, 21-reset spring, 22-second convex ring on the valve core, 23-lower shell, 24-through holes on two side end faces of the fixed cylinder, 25-metal film.
Detailed Description
The technical scheme of the invention is further explained in detail by combining the attached drawings:
the present invention may be embodied in many different forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the invention to those skilled in the art. In the drawings, components are exaggerated for clarity.
As shown in fig. 1, the invention discloses a piezoelectric ring driven nozzle plate pressure servo valve with main valve core hydraulic compensation, which comprises an upper shell, an adjusting component, a first nozzle, a second nozzle, a lower shell, a valve core, a first return spring, a second return spring, an oil filter, a first shuttle valve and a second shuttle valve;
the adjusting assembly comprises a fixed cylinder, N annular piezoelectric patches, N + 1O-shaped nitrile rings, a first baffle disc and a second baffle disc;
the outer diameter of the O-shaped nitrile ring is larger than that of the piezoelectric sheet, and the inner diameter of the O-shaped nitrile ring is smaller than that of the piezoelectric sheet; the N + 1O-shaped nitrile rings and the N piezoelectric plates are stacked in a staggered mode and are coaxial, and a driving piece with O-shaped nitrile rings on two sides is formed;
the second baffle plate comprises a second baffle plate and a connecting rod, one end of the connecting rod is vertically and fixedly connected with the second baffle plate, and the other end of the connecting rod is provided with a thread; the first baffle disc comprises a first baffle plate and a connecting part, the connecting part is fixedly connected with the first baffle plate, and a threaded hole matched with the thread on the connecting rod is formed in the connecting part; one end of the connecting rod with the threads penetrates through the through hole in the center of the driving piece and then is in threaded connection with the connecting part, and the driving piece is clamped between the second baffle and the connecting part; the first baffle and the second baffle are arranged in parallel;
the fixed cylinder is a hollow cylinder, and through holes for the first baffle and the second baffle to pass through are respectively arranged on two end faces of the fixed cylinder; the driving piece is arranged in the fixed cylinder, the outer wall of each O-shaped nitrile ring on the driving piece is abutted against the inner wall of the fixed cylinder, and two end faces of the fixed cylinder clamp two sides of the driving piece;
a cavity is arranged in the upper shell; the fixed cylinder is fixed in the cavity of the upper shell, so that the first baffle and the second baffle are vertically arranged; through holes for the driving wires of the N piezoelectric patches to extend out are arranged on the side walls of the upper shell and the fixed cylinder in a matched manner;
the first nozzle and the second nozzle are arranged on two sides of the upper shell, the first nozzle and the second nozzle extend into the cavity of the upper shell and respectively face the first baffle and the second baffle, and the distance between the first nozzle and the first baffle and the distance between the second nozzle and the second baffle are equal when the N piezoelectric patches are not driven;
a feedback cavity D1, a compensation cavity A1, a main cavity, a compensation cavity A2 and a feedback cavity D2 are sequentially arranged in the lower shell from left to right, and an auxiliary cavity for installing an oil filter is arranged below the main cavity of the lower shell; the lower shell is also provided with an oil inlet, a first control oil port and a second control oil port which are communicated with the outside;
the two ends of the valve core are provided with coaxial connecting rods, and the valve core is sequentially provided with a first convex ring, a second convex ring and a third convex ring from left to right; the first convex ring, the second convex ring, the third convex ring and the fourth convex ring of the valve core are arranged in a main cavity of the lower shell, two ends of the first convex ring, the second convex ring and the third convex ring respectively extend into a compensation cavity A1 and a compensation cavity A2, and connecting rods at two ends of the first convex ring and the third convex ring respectively extend into a feedback cavity D1 and a feedback cavity D2; the main cavity of the lower shell is divided into a control cavity B1, an oil through cavity C1, an oil through cavity C2 and a control cavity B2 from left to right by the first convex ring to the third convex ring, an oil supply cavity E1 is formed between the right side of the outer wall surface of the first convex ring and the inner wall of the lower shell, an oil supply cavity E2 is formed between the left side of the outer wall surface of the third convex ring and the inner wall of the lower shell, and an oil return cavity is formed between the outer wall surface of the second convex ring and the inner wall of the lower shell; a groove is formed in the left side of the outer wall surface of the first convex ring, a throttling groove F1 is formed between the groove in the left side of the outer wall surface of the first convex ring and the inner wall of the lower shell, a groove is formed in the right side of the outer wall surface of the third convex ring, and a throttling groove F2 is formed between the groove in the right side of the outer wall surface of the third convex ring and the inner wall of the lower shell;
when the valve core slides rightwards, the throttling groove F1 is communicated with the oil supply cavity E1, and the oil through cavity C1 is communicated with the oil return cavity; when the valve core slides leftwards, the throttling groove F2 is communicated with the oil supply cavity E2, and the oil through cavity C2 is communicated with the oil return cavity;
the first return spring is arranged in the feedback cavity D1, one end of the first return spring is fixedly connected with the lower shell, and the other end of the first return spring is fixedly connected with a connecting rod at one end of the valve core; the second return spring is arranged in the feedback cavity D2, one end of the second return spring is fixedly connected with the lower shell, and the other end of the second return spring is fixedly connected with the connecting rod at the other end of the valve core; the first return spring and the second return spring are used for providing pretightening force, and the pretightening force provided by the first return spring and the pretightening force provided by the second return spring are equal when the N piezoelectric patches are not driven;
the nozzle cavity of the first nozzle is communicated with the control cavity B1 through a pipeline; the nozzle cavity of the second nozzle is communicated with the control cavity B2 through a pipeline; the bottom of the upper shell cavity is communicated with the oil return cavity through a pipeline;
the auxiliary cavity is respectively communicated with the control cavity B1, the oil supply cavity E1, the oil supply cavity E2, the control cavity B2 and the oil inlet through pipelines; the oil filter is arranged in the auxiliary cavity and used for filtering impurities in oil and protecting the nozzle, the outer wall of the oil filter and the inner wall surface of the auxiliary cavity of the lower shell form a cavity, and the oil flows into the oil filter from the oil inlet, flows into the control cavity B1 and the control cavity B2 after being filtered, and flows into the oil supply cavity E1 and the oil supply cavity E2 through the cavity;
fixed throttling elements are arranged in pipelines between the auxiliary cavity and the control cavity B1 and between the auxiliary cavity and the control cavity B2;
an oil return port is formed in the oil return cavity;
the first shuttle valve and the second shuttle valve are symmetrically arranged in the lower shell and respectively comprise a first oil inlet interface, a second oil inlet interface and an oil outlet interface; a first oil inlet interface of the first shuttle valve is communicated with the throttling groove F1 through a pipeline, a second oil inlet interface is respectively communicated with the oil return port and the first control oil port through pipelines, and an oil outlet interface is communicated with the compensation cavity A1 through a pipeline; the first oil inlet interface of the second shuttle valve is communicated with the throttling groove F2 through a pipeline, the second oil inlet interface is respectively communicated with the oil return port and the second control oil port through pipelines, and the oil outlet interface is communicated with the compensation cavity A2 through a pipeline;
fixed throttling elements are arranged in pipelines among the first oil inlet interface of the first shuttle valve, the first oil inlet interface of the second shuttle valve and the oil return port and are used for ensuring that the oil pressure of the first oil inlet interfaces of the first shuttle valve and the second shuttle valve is a preset pressure threshold;
the first control oil port is also respectively communicated with the oil through cavity C1 and the feedback cavity D2 through pipelines; the second control oil port is also respectively communicated with the oil through cavity C2 and the feedback cavity D1 through pipelines.
And a nozzle oil return restrictor is arranged in a pipeline between the bottom of the upper shell cavity and the oil return cavity to prevent oil in the oil return cavity from flowing into the upper shell cavity.
The bottom of solid fixed cylinder both sides terminal surface is equipped with the through-hole for the hydrops in the solid fixed cylinder flows in the cavity of last casing.
As shown in fig. 2, a metal film is disposed outside the piezoelectric sheet, so that the piezoelectric sheet is isolated from oil, and the service life of the piezoelectric sheet is prolonged.
The distances from the first nozzle to the first baffle plate and from the second nozzle to the second baffle plate can be controlled by changing the excitation voltage applied to the piezoelectric sheet, namely the input voltage of the servo valve. When the input voltage is zero, the distances from the first nozzle to the first baffle and from the second nozzle to the second baffle are equal, the pressures in the two nozzle cavities are equal, the axial hydraulic pressure applied to the valve core is zero, the slide valve is in a zero position, and no hydraulic signal is output from the servo valve. At the moment, the hydraulic force applied to the valve core is zero; the pressures of the compensation cavities A1 and A2 are equal, and the hydraulic compensation force applied to the valve core is zero.
When positive excitation voltage is input to the piezoelectric sheet, the piezoelectric sheet can generate a rightward bulge deformation to push the first baffle and the second baffle to move rightward synchronously. Therefore, the distance from the second nozzle to the second baffle plate is reduced, the distance from the first nozzle to the first baffle plate is increased, the pressure of the nozzle chamber of the second nozzle is increased, the pressure of the nozzle chamber of the first nozzle is reduced, namely the pressure of the control chamber B2 is increased, the pressure of the control chamber B1 is reduced, so that the valve core moves leftwards under the action of the hydraulic pressure and overcomes the resistance such as spring force (generated by the first return spring and the second return spring), and the flowing direction of the oil liquid is shown in FIG. 3.
The oil supply cavity E1 is communicated with the first control oil port, and the oil flows into the first control oil port from the oil supply cavity E1, so that hydraulic force which is rightward along the axial direction of the valve core is generated at the valve core, and the size of the hydraulic force changes along with the opening degree of the valve core; the oil supply chamber E2 is in a closed state, and the second control port is communicated with the oil return port.
For the compensation chamber A1, the valve core moves left to close the rectangular throttling groove F1, and the oil inlet channel of the first shuttle valve is only communicated with the first control oil port. Therefore, the pressure of the compensation cavity A1 and the pressure value p of the first control oil port1The same is true. For the compensation chamber a2, it communicates with the oil supply chamber E2 through a rectangular throttle groove F2. The pressure drop occurs after the oil flows through the restriction F2. Because the volume change of the oil in the compensation cavities A1 and A2 is small in steady state, most of the oil is fixedThe throttling element returns oil. The hydraulic bridge circuit composed of the throttling groove F2 (equivalent to variable hydraulic resistance) and the fixed throttling element analyzes that the throttling hole can ensure that the pressure of the valve core right compensation cavity is changed along with the displacement of the valve core, so as to meet the hydraulic compensation requirement. The hydraulic compensation chambers A1 and A2 on both sides of the valve core have pressure difference, so that hydraulic compensation force towards the left in the axial direction of the valve core (opposite to the direction of the hydraulic force) is generated.
When the input voltage returns to zero from a certain value, the piezoelectric sheet returns to a near-initial state to drive the baffle disc to return to a middle position, the pressure of the first nozzle is equal to that of the first baffle, the pressure of the second nozzle is equal to that of the second baffle, and the pressure of the nozzle cavity of the first nozzle and the pressure of the nozzle cavity of the second nozzle return to zero pressure. At this time, the pressures in the spool control chambers B1 and B2 become equal. The slide valve returns to the zero position again under the action of the return spring, and the servo valve is closed again.
FIG. 4 is a schematic diagram of the operation and fluid flow direction of the servo valve spool of the present invention moving from zero to the right.
The outlet of the first shuttle valve is communicated with the compensation cavity A1, the outlet of the second shuttle valve is communicated with the compensation cavity A2, each shuttle valve is provided with two oil inlets, and one of the two oil inlets with higher pressure is selected (the other one is closed). For example, for a first shuttle valve, the outlet of the first shuttle valve is connected with a main valve core compensation cavity A1, and one of two oil inlets of the first shuttle valve is a first control port pressure p1One path is the supply pressure pSThe compensation pressure (slightly less than p) is reduced through a rectangular throttling groove F1 on a first convex ring of the valve coreS). When the valve core moves left from the zero position, the rectangular throttling groove F1 is not communicated with psThen the oil pressure in the compensation chamber A1 is p1. At this time, the rectangular throttle groove F2 on the third collar is energized by the supply pressure psAnd a first oil inlet interface of the second shuttle valve. Due to the pressure p after throttlingxWhich is slightly less than the supply pressure and the spool second control port pressure p2Lower (slightly greater than oil return pressure p)0) Whereby the second shuttle valve spool moves downward, opening compensation chamber a2 to a pressure px. Thus, the valve core moves from zero position to left xvThe hydraulic compensation is Ac(px-p1) Wherein p isxAnd p1Are all following xvAnd changes accordingly. On the contrary, when the main valve core moves from zero position to right, the scheme can be obtainedThe obtained hydraulic force is compensated as Ac(px-p2). The direction is always opposite to the hydraulic force so as to form cancellation and ensure the precision of the opening amount.
The effective acting area of the hydraulic power compensation cavity can be determined according to the hydraulic power. The calculation formula of the hydrodynamic force applied to the valve core is as follows:
Fs＝0.43W1xv(ps-pL)
wherein, W1Is the area gradient, x, of the valvevFor displacement of the spool, pSSupply pressure of the servo valve, pLThe load pressure of the servo valve is the pressure difference between the first control oil port and the second control oil port.
When the valve core moves leftwards, the oil supply cavity E1 is communicated with the first control oil port, the oil supply cavity E2 is closed, and the second control oil port is communicated with the oil return port. For compensation chamber A1The valve core moves left to close the rectangular throttling groove F1, and the first shuttle valve is only communicated with the first control oil port. Thus, the compensation chamber A1Oil pressure in the chamber is p1. For compensation chamber A2It communicates with the oil supply chamber E2 through a rectangular throttle groove F2, assuming that its pressure is represented by psReduced to px。
Because the second control oil port is communicated with the oil return port, the pressure p of the second control oil port is2Value close to tank pressure p0(actual valve port pressure drop, p, due to oil flow2Is slightly larger than p0) At this time p2Compared with pSAnd p1Smaller, it can be said that pL＝p1-p2≈p1. Therefore, the total hydraulic power of the two series-connected valve ports of the main valve core is as follows:
FL＝0.43W1xv(pS-pL)≈0.43W1xv(pS-p1)
the oil flows into the first oil inlet port of the second shuttle valve from the oil supply cavity E2 through a rectangular throttling groove F2, the rectangular throttling groove F2 is a variable hydraulic resistance which is in direct proportion to the displacement of the valve core, and the outlet pressure p of the rectangular throttling groove isxRelated to the fixed throttling element partial pressure (obtained by the hydraulic half-bridge partial pressure consisting of the variable hydraulic resistance of the rectangular throttling groove and the fixed throttling element).
The method can be obtained by the following steps:
the pressure drop of the oil from the oil supply cavity E2 is generated through the rectangular throttling groove F2, and the flow rate of the oil flowing through the throttling groove E2 is as follows:
wherein, Cd1Is the flow coefficient of a rectangular throttling groove, W2Is its area gradient, ρ is the oil density, pxRectangular throttle slot outlet pressure. Because of the small amount of change in the fluid in the compensation chamber a2, most of the oil returns through the fixed restriction before entering the second shuttle valve. The flow through the throttling element is:
wherein, Cd2To fix the flow coefficient of the throttling element, AhTo fix the flow area of the restriction element. Since the flow at the outlet of the second shuttle valve, namely the compensation chamber A2, is extremely small and zero, q is providedcin＝qc0Namely:
can be simplified into:
the total hydrodynamic compensation force that the compensation chambers a1, a2 can provide is:
where A isCTo compensate the effective active area of the cavity spool. To compensate for the entire hydrodynamic force, the hydrodynamic force and the compensating force need to be satisfiedEqual, i.e.:
FS＝FC
after substitution, the equation can be written as:
in the formula, p1With xvAnd (4) changing. To simplify the analysis, p can be represented by an approximate relationship1. The pressure characteristic of the cylindrical slide valve shows that the load pressure is satisfied in a small opening range
p1＝Kp0xv(pL＝Kp0xvAs mentioned above, p is a small openingL≈p1)
In the formula, Kp0Zero pressure gain for zero opening valve. In general calculation, Kp0Can be taken as follows:
therefore, p is1Substituting the approximate expression of (a), the hydraulic force compensation can be simplified as:
further simplification of the above formula yields:
wherein the content of the first and second substances,
so far, the design can be reasonably designed AC、k1And k2Let both sides of the above formula be at xvApproximately equal in the interval of (0-0.2) mm. FIG. 5 shows a set of equations obtained by design and optimizationThe relationship of the edge force. Fig. 5 shows that the total compensation force generated by the hydraulic compensation cavity is approximately equal to the hydraulic force, and the hydraulic force borne by the valve core can be fully compensated in each opening within the range, so that the control precision of the load pressure of the servo valve is improved.
N annular piezoelectric patches with the same specification are arranged in the piezoelectric sleeve, and the same excitation voltage is applied. The outer periphery of the piezoelectric sheet is fixed by a large-diameter O-shaped nitrile ring, and the inner periphery of the piezoelectric sheet is fixed by a small-diameter O-shaped nitrile ring. The inner periphery of the piezoelectric sheet outputs force and displacement under the action of excitation voltages with different magnitudes and polarities so as to drive the blocking disc and bear certain impact force.
And two ends of the valve core are provided with return springs, so that the main valve core can return to a zero position after the excitation voltage is cancelled.
It will be understood by those skilled in the art that, unless otherwise defined, all terms (including technical and scientific terms) used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. It will be further understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the prior art and will not be interpreted in an idealized or overly formal sense unless expressly so defined herein.
The above-mentioned embodiments, objects, technical solutions and advantages of the present invention are further described in detail, it should be understood that the above-mentioned embodiments are only illustrative of the present invention and are not intended to limit the present invention, and any modifications, equivalents, improvements and the like made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (5)
1. The piezoelectric ring driving nozzle blocking disc pressure servo valve with the main valve core hydraulic compensation is characterized by comprising an upper shell, an adjusting component, a first nozzle, a second nozzle, a lower shell, a valve core, a first return spring, a second return spring, an oil filter, a first shuttle valve and a second shuttle valve;
the adjusting assembly comprises a fixed cylinder, N annular piezoelectric patches, N + 1O-shaped nitrile rings, a first baffle disc and a second baffle disc;
the outer diameter of the O-shaped nitrile ring is larger than that of the piezoelectric sheet, and the inner diameter of the O-shaped nitrile ring is smaller than that of the piezoelectric sheet; the N + 1O-shaped nitrile rings and the N piezoelectric plates are stacked in a staggered mode and are coaxial, and a driving piece with O-shaped nitrile rings on two sides is formed;
the second baffle plate comprises a second baffle plate and a connecting rod, one end of the connecting rod is vertically and fixedly connected with the second baffle plate, and the other end of the connecting rod is provided with a thread; the first baffle disc comprises a first baffle plate and a connecting part, the connecting part is fixedly connected with the first baffle plate, and a threaded hole matched with the thread on the connecting rod is formed in the connecting part; one end of the connecting rod with the threads penetrates through the through hole in the center of the driving piece and then is in threaded connection with the connecting part, and the driving piece is clamped between the second baffle and the connecting part; the first baffle and the second baffle are arranged in parallel;
the fixed cylinder is a hollow cylinder, and through holes for the first baffle and the second baffle to pass through are respectively arranged on two end faces of the fixed cylinder; the driving piece is arranged in the fixed cylinder, the outer wall of each O-shaped nitrile ring on the driving piece is abutted against the inner wall of the fixed cylinder, and two end faces of the fixed cylinder clamp two sides of the driving piece;
a cavity is arranged in the upper shell; the fixed cylinder is fixed in the cavity of the upper shell, so that the first baffle and the second baffle are vertically arranged; through holes for the driving wires of the N piezoelectric patches to extend out are arranged on the side walls of the upper shell and the fixed cylinder in a matched manner;
the first nozzle and the second nozzle are arranged on two sides of the upper shell, the first nozzle and the second nozzle extend into the cavity of the upper shell and respectively face the first baffle and the second baffle, and the distance between the first nozzle and the first baffle and the distance between the second nozzle and the second baffle are equal when the N piezoelectric patches are not driven;
a feedback cavity D1, a compensation cavity A1, a main cavity, a compensation cavity A2 and a feedback cavity D2 are sequentially arranged in the lower shell from left to right, and an auxiliary cavity for installing an oil filter is arranged below the main cavity of the lower shell; the lower shell is also provided with an oil inlet, a first control oil port and a second control oil port which are communicated with the outside;
the two ends of the valve core are provided with coaxial connecting rods, and the valve core is sequentially provided with a first convex ring, a second convex ring and a third convex ring from left to right; the first convex ring, the second convex ring, the third convex ring and the fourth convex ring of the valve core are arranged in a main cavity of the lower shell, two ends of the first convex ring, the second convex ring and the third convex ring respectively extend into a compensation cavity A1 and a compensation cavity A2, and connecting rods at two ends of the first convex ring and the third convex ring respectively extend into a feedback cavity D1 and a feedback cavity D2; the main cavity of the lower shell is divided into a control cavity B1, an oil through cavity C1, an oil through cavity C2 and a control cavity B2 from left to right by the first convex ring to the third convex ring, an oil supply cavity E1 is formed between the right side of the outer wall surface of the first convex ring and the inner wall of the lower shell, an oil supply cavity E2 is formed between the left side of the outer wall surface of the third convex ring and the inner wall of the lower shell, and an oil return cavity is formed between the outer wall surface of the second convex ring and the inner wall of the lower shell; a groove is formed in the left side of the outer wall surface of the first convex ring, a throttling groove F1 is formed between the groove in the left side of the outer wall surface of the first convex ring and the inner wall of the lower shell, a groove is formed in the right side of the outer wall surface of the third convex ring, and a throttling groove F2 is formed between the groove in the right side of the outer wall surface of the third convex ring and the inner wall of the lower shell;
when the valve core slides rightwards, the throttling groove F1 is communicated with the oil supply cavity E1, and the oil through cavity C1 is communicated with the oil return cavity; when the valve core slides leftwards, the throttling groove F2 is communicated with the oil supply cavity E2, and the oil through cavity C2 is communicated with the oil return cavity;
the first return spring is arranged in the feedback cavity D1, one end of the first return spring is fixedly connected with the lower shell, and the other end of the first return spring is fixedly connected with a connecting rod at one end of the valve core; the second return spring is arranged in the feedback cavity D2, one end of the second return spring is fixedly connected with the lower shell, and the other end of the second return spring is fixedly connected with the connecting rod at the other end of the valve core; the first return spring and the second return spring are used for providing pretightening force, and the pretightening force provided by the first return spring and the pretightening force provided by the second return spring are equal when the N piezoelectric patches are not driven;
the nozzle cavity of the first nozzle is communicated with the control cavity B1 through a pipeline; the nozzle cavity of the second nozzle is communicated with the control cavity B2 through a pipeline; the bottom of the upper shell cavity is communicated with the oil return cavity through a pipeline;
the auxiliary cavity is respectively communicated with the control cavity B1, the oil supply cavity E1, the oil supply cavity E2, the control cavity B2 and the oil inlet through pipelines; the oil filter is arranged in the auxiliary cavity and used for filtering impurities in oil and protecting the nozzle, the outer wall of the oil filter and the inner wall surface of the auxiliary cavity of the lower shell form a cavity, and the oil flows into the auxiliary cavity from the oil inlet, flows into the control cavity B1 and the control cavity B2 after being filtered, and flows into the oil supply cavity E1 and the oil supply cavity E2 through the cavity;
fixed throttling elements are arranged in pipelines between the auxiliary cavity and the control cavity B1 and between the auxiliary cavity and the control cavity B2;
the oil return cavity is communicated with the oil return opening through a pipeline;
the first shuttle valve and the second shuttle valve are symmetrically arranged in the lower shell and respectively comprise a first oil inlet interface, a second oil inlet interface and an oil outlet interface; a first oil inlet interface of the first shuttle valve is respectively communicated with the oil return port and the throttling groove F1 through pipelines, a second oil inlet interface is communicated with the first control oil port through a pipeline, and an oil outlet interface is communicated with the compensation cavity A1 through a pipeline; a first oil inlet interface of the second shuttle valve is respectively communicated with the oil return port and the throttling groove F2 through pipelines, a second oil inlet interface is communicated with the second control oil port through a pipeline, and an oil outlet interface is communicated with the compensation cavity A2 through a pipeline;
fixed throttling elements are arranged in pipelines among the first oil inlet interface of the first shuttle valve, the first oil inlet interface of the second shuttle valve and the oil return port and are used for ensuring that the oil pressure of the first oil inlet interfaces of the first shuttle valve and the second shuttle valve is a preset pressure threshold;
the first control oil port is also respectively communicated with the oil through cavity C1 and the feedback cavity D2 through pipelines; the second control oil port is also respectively communicated with the oil through cavity C2 and the feedback cavity D1 through pipelines.
2. A piezoelectric ring driven nozzle plate pressure servo valve with primary spool hydrodynamic compensation as claimed in claim 1 wherein a nozzle return restrictor is provided in the conduit between the bottom of the upper housing cavity and the return chamber to prevent oil in the return oil chamber from flowing into the upper housing cavity.
3. A piezoelectric ring driven nozzle plate pressure servo valve with main valve core hydraulic compensation as claimed in claim 1, wherein the bottom of the two side end faces of the fixed cylinder is provided with a through hole, so that the accumulated liquid in the fixed cylinder flows into the cavity of the upper shell.
4. A piezoelectric ring driven nozzle plate pressure servo valve with main valve core hydraulic compensation as claimed in claim 1, wherein the outside of the piezoelectric sheet is provided with a metal film, so that the piezoelectric sheet is isolated from oil and the service life of the piezoelectric sheet is prolonged.
5. The method for hydraulically compensating a piezo-electric ring driven nozzle flap pressure servo valve with main valve spool hydraulic compensation of claim 1, comprising the steps of:
step 1), adjusting the control voltage of each piezoelectric plate to a zero position, wherein the distances from the first nozzle to the first baffle and the distances from the second nozzle to the second baffle are the same, the nozzle cavity pressures of the first nozzle and the second nozzle are equal, the pressures of the lower shell control cavities B1 and B2 are the same, the valve core is in a middle position at the moment, the oil supply cavity E1 is sealed by the first convex ring of the valve core, and the oil supply cavity E2 is sealed by the third convex ring of the valve core;
step 2), adjusting the control voltage of each piezoelectric plate to a preset voltage threshold, wherein the preset voltage threshold is a positive value, at this time, the N annular piezoelectric plates synchronously deform rightward, the first baffle and the second baffle synchronously move rightward along with the deformation of the N annular piezoelectric plates, the distance from the first baffle to the first nozzle is increased, the distance from the second nozzle to the second baffle is reduced, the pressure of the control cavity B1 is reduced, the pressure of the control cavity B2 is increased, and the main valve core slides leftward; the oil inlet is communicated with an oil through cavity C1 through a lower shell auxiliary cavity and an oil supply cavity E1, and oil flows out of the first control oil port through a oil through cavity C1; the oil through cavity C2 is communicated with the oil return cavity; the oil inlet is communicated with the throttling groove F2 through the lower shell auxiliary cavity and the oil supply cavity E2, and oil flows into the oil return port; the throttling groove F1 is closed, oil does not pass through a first oil inlet interface of the first shuttle valve, a second oil inlet interface of the first shuttle valve is communicated with a first control oil port, and the oil flows into the compensation cavity A1 through the second oil inlet interface; the first oil inlet interface of the second shuttle valve is communicated with the oil inlet, the second oil inlet interface is communicated with the second control oil port, and the oil pressure of the first oil inlet interface is higher, so that the oil flows into the compensation cavity A2 through the auxiliary cavity, the oil supply cavity E2, the throttling groove F2 and the first oil inlet interface of the second shuttle valve; the feedback cavity D1 is communicated with a second control oil port; the feedback cavity D2 is communicated with the first control oil port; the compression amount of the first return spring is increased, and the compression amount of the second return spring is decreased;
step 3), restoring the control voltage of each piezoelectric plate to a zero position, wherein the N annular piezoelectric plates return to the initial positions, the distances from the first nozzle to the first baffle and the distances from the second nozzle to the second baffle are the same, the pressure of the nozzle cavities of the first nozzle and the second nozzle are equal, and the pressure of the lower casing control cavities B1 and B2 is the same; and the valve core returns to the neutral position under the action of the return spring.
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| CN112253316B (en) * | 2020-10-19 | 2021-10-22 | 中国航发沈阳发动机研究所 | Force compensation type differential pressure oil return valve and force compensation parameter design method |
| CN115614333B (en) * | 2022-09-23 | 2023-04-18 | 燕山大学 | Gas-liquid servo speed regulating device based on piezoelectric type double-nozzle pneumatic valve |
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