CN103541943B - A kind of large-flow high-frequency of rotatable Parallel Control rings digital valve - Google Patents
A kind of large-flow high-frequency of rotatable Parallel Control rings digital valve Download PDFInfo
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- CN103541943B CN103541943B CN201310539974.2A CN201310539974A CN103541943B CN 103541943 B CN103541943 B CN 103541943B CN 201310539974 A CN201310539974 A CN 201310539974A CN 103541943 B CN103541943 B CN 103541943B
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Abstract
The large-flow high-frequency that the invention discloses a kind of rotatable Parallel Control rings digital valve, and be made up of parts such as valve body, valve pocket, left actuating motor and right actuating motors, valve pocket is rotatable to be arranged in valve body, and spool is rotatable to be arranged in valve pocket; Poppet shaft two ends all have the valve opening of logical high pressure oil or low pressure oil, coordinate with valve pocket both sides spiral chute that corresponding position is opened, and are moved axially by spool left and right side chamber pressure control realization spool; Right actuating motor drives Spool rotating, and left actuating motor drives valve pocket to rotate, and realizes bidirectional rotation by the Parallel Control of spool and valve pocket, breaches the frequency limitation that tradition only has Spool rotating to cause.Valve pocket has the spiral chute mechanism of different lead angle, valve core rotation is become move axially that there is multistage gain function.The present invention controls, has the spiral chute array structure of multistage gain function by the rotary digital in parallel of spool and valve pocket, reaches the accurate control of servovalve large discharge, high frequency sound and end position.
Description
Technical field
The present invention relates to the electrohydraulic control of Fluid-transmission and control field, particularly relate to a kind of can the high frequency large flow amount digital servo valve of Parallel Control.
Background technique
Electrohydraulic servo system is widely used in the numerous areas such as Aero-Space, metallurgy, boats and ships and military heavy industry, and its core parts are electrohydraulic controls.The high frequency sound feature of electrohydraulic control significantly improves the control performance of high-end equipment (as large-scale composite material press, friction-welding machine, high-frequency electrohydraulic vibrating table, electro-hydraulic servo commutator and space simulator etc.).Traditional electrohydraulic control generally adopts prestage driving power guiding valve level, and input signal is analogue signal, and the feature of its analogue signal poor anti jamming capability constrains the further lifting of Systematical control precision.Along with the development of digital control technology, antijamming capability strengthens rapidly, and computer and bus participate in control directly becomes possibility, and this is that the development of digitizing servovalve provides technical support; In addition, the fast development of high-end equipment, proposes harsh requirement to the large discharge of servovalve, high frequency sound, antipollution, simultaneously also for development large discharge, high frequency sound, digital, resistant to pollution servovalve provide the wide market space.
The design of current electrohydraulic control, mainly launches round high frequency sound two aspect realized under digitizing and large discharge.(1) in digitizing: drive ball screw and main valve plug to realize the movement of spool by actuating motor, the rotary motion of ball screw is become moving axially of spool, by the digital control digitizing (as referenced patent 201110332448.X) realizing servovalve of actuating motor; Or adopt servo screw device the pilot stage of valve and main to be merged, to realize leading control one, produce hydraulic driving after Spool rotating and try hard to recommend dynamic self movement, digital control actuating motor drives Spool rotating to realize digitizing (as referenced patent 200910153014.6); Or adopt the pilot stage of high-speed switch valve to control main mode, realized the servocontrol of main valve by the make-and-break time controlling high-speed switch valve, namely digital control high-speed switch valve realizes digitizing (as referenced patent WO2012112292A1).(2) in the high frequency sound under large discharge: adopt super magnetostriction material to make electromechanical transducer as pilot stage, this electromechanical transducer frequency range is large, and control main can realize the high frequency sound (as referenced patent 201310149224.4) under large discharge; Or for large discharge cartridge valve, control as pilot stage with two servovalves, to improve the dynamic response (as referenced patent 200810061616.4) of main.Existing Patent design contributes to the digitizing realizing large-capacity valve, improves its frequency response simultaneously, but there are following some shortcomings, and main manifestations is:
1) frequency response of digital servovalve promotes and runs into bottleneck.In the design of digital servovalve, the general actuating motor that adopts drives Spool rotating, realizes the control to main valve.In order to improve resolution or the precision of control, the corner requiring each pulse of actuating motor corresponding is the smaller the better.But diminish along with the corner that each pulse is corresponding, the step number causing actuating motor to rotate needed for equal angular increases, and it reduces the speed of response of spool, limits the further lifting of servovalve frequency response in highi degree of accuracy situation.
2) pilot stage drives the gain of main to have much room for improvement.The pilot stage of servo screw mechanism and main, with being integrated, increase valve core diameter and can promote the through-current capability of main valve and improve the gain driving main, be comparatively suitable for the spool as large discharge digital valve.The unilateral gain control mode (as referenced patent 200910153014.6) adopted in such servo screw mechanism at present, fail the controlled area of full use spool, maximum lifting pilot stage drives the gain of main, to promote the speed of response of main valve plug action further.
3) adaptability that end position accurately controls has to be strengthened.Because servovalve has taken into account large discharge and high frequency sound when designing, flow gain is large, be difficult to realize accurately controlling on servo-system end position, constrain its application in the equipment such as large-scale composite material press, friction-welding machine thus, limit the lifting of its highi degree of accuracy control performance, reduce the engineering adaptability of this valve.
Summary of the invention
The large-flow high-frequency that the object of the invention is to provide a kind of rotatable Parallel Control rings digital valve, the digital control of large discharge servovalve and high frequency sound is realized by the parallel connection rotation of spool and valve pocket, adopt the spiral chute array structure of valve pocket simultaneously, form multistage gain to realize the accurate control of large discharge, high frequency sound and end position.
In order to achieve the above object, the technical solution used in the present invention is as follows:
The large-flow high-frequency of rotatable Parallel Control rings a digital valve, comprises valve body, valve pocket, spool, left actuating motor, right actuating motor, left end cap, right end cap; Valve pocket is rotatable to be arranged in valve body, and spool is rotatable to be arranged in valve pocket.
Left actuating motor is arranged on valve body by left end cap, and left servo motor output shaft is fixedly connected on valve pocket, and right actuating motor is arranged on valve body by right end cap, and spool is connected to right servo motor output shaft.
Valve body is connected with the bearing that passes on left of valve pocket, and fixed cover to be fixedly connected on the right side of valve pocket and to be placed in valve body, and valve body is connected by bearing with fixed cover.
Valve body is connected with left tapered roller bearing with the left side of valve pocket, connects between valve body and fixed cover with right tapered roller bearing.
Left side, the valve pocket of the second from left spool shaft part on spool form left control cavity volume, the second from left spool shaft part has upper left spool bore and lower-left spool bore, left hand screw groove is had inside valve pocket outside the second from left spool shaft part, left hand screw groove is communicated with left control cavity volume, and left hand screw slot is between upper left spool bore and lower-left spool bore; Right side, the valve pocket of the right side two spool shaft part on spool form right control cavity volume, right two spool shaft parts have upper right spool bore and bottom right spool bore, right spiral is had inside valve pocket outside right two spool shaft parts, right spiral is communicated with right control cavity volume, and right spiral is between upper right spool bore and bottom right spool bore.
Being provided with the left bearing adjustment pad for regulating left tapered roller bearing pretension amount between left end cap and valve body, being provided with between right end cap and valve body for regulating the right bearing of right tapered roller bearing pretension amount to regulate pad.
Left tapered roller bearing and right tapered roller bearing are installed face-to-face.
Spool two ends arrange the left belleville spring and right belleville spring that are used for centering.
Left spool adjustment pad and right spool that spool two ends are arranged for calibrating zero-bit adjust pad.
Left hand screw groove along the circumferential direction uniform 1 ~ 5, each spiral chute lead angle is different, right spiral along the circumferential direction uniform 1 ~ 5, and each spiral chute lead angle is different.
Upper left spool bore connects high pressure oil, and lower-left spool bore connects low pressure oil, and upper right spool bore connects high pressure oil, and bottom right spool bore connects low pressure oil.
The spiral fluted lead angle number of degrees are 10 ~ 80 degree.
The beneficial effect that the present invention possesses is:
1) by designed spool valve pocket rotating machinery in parallel, the bottleneck that the frequency response of large discharge digital valve promotes is broken through.The synchronous bidirectional of spool and valve pocket rotates and controls, and has broken away from the frequency limitation that tradition only has Spool rotating to cause, not only ensure that the control accuracy of servovalve, effectively promote relative to its frequency response of conventional digital valve.
2) utilize bilateral gain control structure, improving Spool rotating movement transition is the speed of response moved axially.By all having control valve opening at spool two ends, make on the same axial direction of spool two control valve openings connect high low pressure mouth respectively and with the use of, thus the pressure of spool both sides sensitive cavity is changed simultaneously, which thereby enhances its dynamic response.
3) by the servo screw mechanism of multiple coil lift angle, the multistage gain realizing servovalve switches.Inside valve pocket, have several spiral chute with different lead angle, thus make Spool rotating movement transition be the gain difference moved axially, realize multistage gain thus.This mechanism can according to the large discharge of control system in control procedure and high-precision different requirement, the ride gain of reasonable switching servovalve, both ensure the large discharge needed for control procedure and high frequency sound, ensure again the precision that end position controls, this valve is possessed stronger engineering adaptability.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of internal structure of the present invention.
Fig. 2 is the position relationship and the spool bore structural representation that characterize valve pocket spiral chute and spool bore.
Fig. 3 is that Fig. 2 characterizes the position relationship of valve pocket spiral chute and spool bore and the transverse sectional view of spool bore structure.
Fig. 4 is that Fig. 2 characterizes the position relationship of valve pocket spiral chute and spool bore and the C-C direction sectional view of spool bore structure.
Fig. 5 is that Fig. 2 characterizes the position relationship of valve pocket spiral chute and spool bore and the D-D direction sectional view of spool bore structure.
Fig. 6 be characterize spool and valve pocket form the hydraulic control bridge road of valve port.
Fig. 7 is the angle of swing and the axial displacement relation schematic diagram that characterize servo screw mechanism.
Fig. 8 is Fig. 7 is characterize the angle of swing of servo screw mechanism and the M1 position view of axial displacement relation.
Fig. 9 is Fig. 7 is characterize the angle of swing of servo screw mechanism and the M2 position view of axial displacement relation.
Figure 10 is Fig. 7 is characterize the angle of swing of servo screw mechanism and the M3 position view of axial displacement relation.
Figure 11 characterizes the valve pocket spiral chute of secondary variable-gain and the schematic diagram of spool bore position relationship.
Figure 12 is the schematic diagram that Figure 11 characterizes the valve pocket spiral chute of secondary variable-gain and 0-180 ° of spool bore position relationship.
Figure 13 is the schematic diagram that Figure 11 characterizes the valve pocket spiral chute of secondary variable-gain and 180-360 ° of spool bore position relationship.
Figure 14 is valve pocket spiral chute and the spool bore position relationship of sign three grades of variable-gains.
Figure 15 is the schematic diagram that Figure 14 characterizes the valve pocket spiral chute of three grades of variable-gains and 0-120 ° of spool bore position relationship.
Figure 16 is the schematic diagram that Figure 14 characterizes the valve pocket spiral chute of three grades of variable-gains and 120-240 ° of spool bore position relationship.
Figure 17 is the schematic diagram that Figure 14 characterizes the valve pocket spiral chute of three grades of variable-gains and 240-360 ° of spool bore position relationship.
In figure: 1, valve body, 2, valve pocket, 2A, first hole, 2B, second hole, 2C, first hole plug screw, 2D, second hole plug screw, 2X, left hand screw groove, 2Y, right spiral, 3, spool, 3B, the first from left spool shaft part, 3C, a right spool shaft part, 3D, left control cavity volume, 3E, right control cavity volume, 3F, spring chamber, 3G, the second from left spool shaft part, 3H, right two spool shaft parts, 3P1, upper left spool bore, 3T1, lower-left spool bore, 3P2, bottom right spool bore, 3T2, upper right spool bore, 4, fixed cover, 5, right axle sleeve, 6, right tapered roller bearing, 7, right bearing regulates pad, and 8, right end cap, 9, right actuating motor, 9A, right servo motor output shaft, 10, right spool adjustment pad, 11, right belleville spring, 12, seal spool coil array, 13, valve pocket seal ring array, 14, left axle sleeve, 15, left actuating motor, 15A, left servo motor output shaft, 16, left end cap, 17, left bearing adjustment pad, 18, left tapered roller bearing, 19, left spool adjustment pad, 20 left belleville springs, 21, spool plug screw.
Embodiment
Below in conjunction with drawings and Examples, the specific embodiment of the present invention is described.
Fig. 1 schematically illustrates the schematic diagram of the internal structure of embodiment of the present invention.
The large-flow high-frequency of rotatable Parallel Control rings a digital valve, comprises valve body 1, valve pocket 2, spool 3, left actuating motor 15, right actuating motor 9, left end cap 16, right end cap 8; Valve pocket 2 is rotatable to be arranged in valve body 1, and spool 3 is rotatable to be arranged in valve pocket 2.
Left actuating motor 15 is arranged on valve body 1 by left end cap 16, and left servo motor output shaft 15A is fixedly connected on valve pocket 2, and right actuating motor 9 is arranged on valve body 1 by right end cap 8, and spool 3 is connected to right servo motor output shaft 9A.
Valve body 1 is connected with the bearing that passes on left of valve pocket 2, and fixed cover 4 to be fixedly connected on the right side of valve pocket 2 and to be placed in valve body 1, and valve body 1 is connected by bearing with fixed cover 4.
Valve body 1 is connected with left tapered roller bearing 18 with the left side of valve pocket 2, connects between valve body 1 and fixed cover 4 with right tapered roller bearing 6.
Left side, the valve pocket 2 of the second from left spool shaft part 3G on spool 3 form left control cavity volume 3D, the second from left spool shaft part 3G has upper left spool bore 3P1 and lower-left spool bore 3T1, left hand screw groove 2X is had inside valve pocket 2 outside the second from left spool shaft part 3G, left hand screw groove 2X is communicated with left control cavity volume 3D, and left hand screw groove 2X is between upper left spool bore 3P1 and lower-left spool bore 3T1; Right side, the valve pocket 2 of the right side two spool shaft part 3H on spool 3 form right control cavity volume 3E, right two spool shaft part 3H have upper right spool bore 3T2 and bottom right spool bore 3P2, right spiral 2Y is had inside valve pocket 2 outside right two spool shaft part 3H, right spiral 2Y is communicated with right control cavity volume 3E, and right spiral 2Y is between upper right spool bore 3T2 and bottom right spool bore 3P2.
Being provided with the left bearing adjustment pad 17 for regulating left tapered roller bearing 18 pretension amount between left end cap 16 and valve body 1, being provided with between right end cap 8 and valve body 1 for regulating the right bearing of right tapered roller bearing 6 pretension amount to regulate pad 7.
Left tapered roller bearing 18 and right tapered roller bearing 6 are installed face-to-face.
Spool 3 two ends arrange and are used for the left belleville spring 20 of centering and right belleville spring 11, and make left belleville spring 20 and right belleville spring 11 all be in compressive state, and when realizing initial position, spool 3 and valve pocket 2 mediate cooperation position, and namely spool 3 is in meta.
The pressure of spring chamber 3F is communicated with oil return inlet T 1 by discharge degree by the first hole 2A on valve pocket 2 with the second hole 2B.
Left spool adjustment pad 19 and right spool that spool 3 two ends are arranged for calibrating zero-bit adjust pad 10.When servovalve is designed to zero lap valve, because left belleville spring 20 and right belleville spring 11 realize the centering of spool 3, can not guarantee that valve port is in zero lap position, reach valve port by the adjustment left spool adjustment pad 19 of cooperation and the thickness of right spool adjustment pad 10 and be in zero lap position, thus calibration zero-bit.
Left hand screw groove 2X along the circumferential direction uniform 1 ~ 5, each spiral chute lead angle is different, right spiral 2Y along the circumferential direction uniform 1 ~ 5, and each spiral chute lead angle is different.
Upper left spool bore 3P1 connects high pressure oil, and lower-left spool bore 3T1 connects low pressure oil, and upper right spool bore 3T2 connects high pressure oil, and bottom right spool bore 3P2 connects low pressure oil.
The spiral fluted lead angle number of degrees are 10 ~ 80 degree.
Spool plug screw 21 is fixedly connected in the first from left spool shaft part 3B.
Fig. 2, Fig. 3, Fig. 4 and Fig. 5 are the position relationship and the spool bore structure that characterize valve pocket spiral chute and spool bore.Adopting servo screw mechanism, realizing the convert rotational motion of spool 3 as moving axially.The position that valve pocket 2 matches with the second from left spool shaft part 3G has left hand screw groove 2X, and left hand screw groove 2X communicates with left control cavity volume 3D, and the position that valve pocket 2 matches with right two spool shaft part 3H has right spiral 2Y, and right spiral 2Y communicates with right control cavity volume 3E.The second from left spool shaft part 3G has upper left spool bore 3P1 and lower-left spool bore 3T1, and right two spool shaft part 3H have upper right spool bore 3T2 and bottom right spool bore 3P2.Holes on same axial direction and upper left spool bore 3P1 are different with upper right spool bore 3T2 institute oil-collecting hole, lower-left spool bore 3T1 is also different with bottom right spool bore 3P2 institute oil-collecting hole, to make the pressure size variation trend of left control cavity volume 3D and right control cavity volume 3E contrary, thus improve ride gain.In Fig. 2, upper left spool bore 3P1 and bottom right spool bore 3P2 meets high pressure hydraulic fluid port P, and lower-left spool bore 3T1 and upper right spool bore 3T2 takes back hydraulic fluid port T1 and T2 respectively.
Spool 3 rotates and becomes its specific works process moved axially: in spool 3 is according to Fig. 2, the F direction of C-C view rotates, namely spool 3 turns clockwise, lower-left spool bore 3T1 communicates with left hand screw groove 2X, and the pressure oil of left control cavity volume 3D is introduced oil return inlet T 1 by lower-left spool bore 3T1 and left hand screw groove 2X; Bottom right spool bore 3P2 communicates with right spiral 2Y, and the high pressure oil of P mouth is introduced right control cavity volume 3E by bottom right spool bore 3P2 and right spiral 2Y.Now, left control cavity volume 3D pressure reduces, and the pressure of right control cavity volume 3E raises, and hydraulic action drives spool 3 to be moved to the left, until lower-left spool bore 3T1 and bottom right spool bore 3P2 all disconnect with corresponding spiral fluted oil circuit, spool 3 stops continuation mobile.Spool 3 is rotated counterclockwise as the same.Along with moving axially of spool 3, the four-side working connection that spool 3 and valve pocket 2 are formed is opened, and makes working connection enter working state.
Composition graphs 1 and Fig. 2-5, working principle of the present invention is as follows: the servo screw mechanism that spool 3 and valve pocket 2 are formed, by the left control cavity volume 3D of rotary control valve core 3 both sides of spool 3 and the pressure of right control cavity volume 3E, realize moving axially of spool 3, namely realize leading control one.After spool 3 rotates, corresponding hydraulic fluid port is connected, and makes left control cavity volume 3D and right control cavity volume 3E pressure generation respective change, thus promotion spool 3 moves axially, until the oil circuit of spiral chute on valve pocket 2 and spool bore disconnects, finally realize the converting rotary motion of spool 3 for moving axially.Spool 3 and valve pocket 2 coordinate formation four-side structure, by increasing spool 3 diameter, increasing the area gradient of working connection, thus making valve possess large discharge through-current capability.Reduce the volume of left control cavity volume 3D and right control cavity volume 3E as far as possible, effectively can improve the frequency of the natural hydraulic mode of main valve plug.Right actuating motor 9 adopts digital form to control spool 3 is rotated, and left actuating motor 15 adopts digital form to control and valve pocket 2 is rotated, and the bidirectional rotation in conjunction with spool 3 and valve pocket 2 controls.Such as when spool 3 turns clockwise, valve pocket 2 is rotated counterclockwise, relative to the situation only having spool 3 to rotate, the bidirectional rotation of spool 3 and valve pocket 2 makes the valve opening on spool 3 and spiral fluted opening increase, then spool 3 rotates the speed of response increase becoming and move axially, under the prerequisite not reducing control accuracy, can further improve frequency response and the dynamic characteristic of this valve.
Right servo motor output shaft 9A adopts the mode such as spline or flat key to be connected with a right spool shaft part 3C, and in the process that right actuating motor 9 rotates with movable valve plug 3, spool 3 also can realize moving axially; Left servo motor output shaft 15A is fixedly connected with valve pocket shaft part 2E, and valve pocket 2 only can realize rotary motion under the drive of left actuating motor 15.
Right tapered roller bearing 6 and left tapered roller bearing 18 adopt face-to-face installation, can bear larger thrust load, regulating the thickness of pad 7 or the length of right axle sleeve 5, realizing pretension and the location of right tapered roller bearing 6 by changing right bearing; By changing the length of left bearing adjustment pad 17 or left axle sleeve 14, realize pretension and the location of left tapered roller bearing 18.
Adopt right belleville spring 11 and left belleville spring 20 to realize the centering of spool 3, regulate right spool to adjust pad 10 and left spool adjustment pad 19 adjustable initial zero position.
Pilot control valve port is formed by the upper spiral chute of valve pocket 2 and the circular hole of spool 3, and the requirement of this structure to fluid is low, suitable with common valve member, therefore effectively improves the contamination resistance of servovalve.
Fig. 6 be characterize spool and valve pocket form the hydraulic control bridge road of valve port.Due to the second from left spool shaft part 3G on spool 3 and right two spool shaft part 3H having valve opening, holes institute oil-collecting hole on same axial direction is different, and match with the spiral chute on valve pocket 2, this makes the left control cavity volume 3D at spool 3 two ends and right control cavity volume 3E form two hydraulic half-bridges.Filled arrows shown in Fig. 3 represents that this position liquid resistive is large, and hollow arrow represents that this position liquid resistive is little, and the pilot pressure of the left control cavity volume of the state representation now in Fig. 3 3D increases, and the pilot pressure of right control cavity volume 3E reduces.Therefore, the control chamber pressure size at spool 3 two ends is opposite trend change, and the speed of response of pressure change is faster than single control cavity volume pattern, further increases speed of response rotary motion being converted to axial motion thus.
Fig. 7-10 characterizes angle of swing and the axial displacement relation of servo screw mechanism.In Fig. 8, M1 represents that spool 3 opposing valve sleeves 2 rotates, and at spool 3 circumferencial direction, spool bore offset helical slot pitch is from the schematic diagram of y; In Fig. 9, M2 represents that spool 3 moves axially distance x on the basis of state shown in M1, and spool bore and spiral fluted oil circuit are cut off; In Figure 10, M3 represents the synthesis schematic diagram of M1 and M2.
Valve pocket 2 and spool 3 all rotatable, if valve pocket 2 angle of swing is δ
2, spool 3 counterrotating angle is δ
1, then circumferencial direction spiral chute and valve opening distance y=(δ in relative rotation
1+ δ
2) R, wherein R is spool radius, and after valve pocket 2 rotation relative to spool 3, under Hydraulic bridge effect, generation is moved axially distance x by spool 3, and x=y/tan θ, wherein θ is lead angle.Therefore lead angle is larger, under the identical corner of spool 3, spool 3 to move axially distance x less, namely the resolution of servo screw mechanism will obtain and promote further, more be conducive to high precision and control.
Figure 11, Figure 12 and Figure 13 are the valve pocket spiral chute and the spool bore position relationship that characterize secondary variable-gain.Have spiral chute L1 and L2 of two different lead angles inside valve pocket 2 uniformly, the two is separated by 180 degree.Flattened with the spiral chute of spool 3 matching surface and the cylndrical surface at valve opening place by valve pocket 2 and show, in identical spool corner situation, lead angle its axial displacement larger is less, and namely its resolution is higher.Therefore for different operating mode, valve pocket is rotated 180 ° and make different spiral chute participation work, different resolution and different gains can be obtained.Need in many engineer applied that large discharge controls, end position needs highi degree of accuracy to control in actuator motions process, by said structure, less lead angle participation work is made in control procedure, realize large discharge to control, during close to terminal, make larger lead angle participation work, promote the control accuracy of servovalve further.The mode of this secondary variable-gain, the adaptability that the further high-precision servo improving valve controls under heavy traffic condition.
Figure 14, Figure 15, Figure 16 and Figure 17 are valve pocket spiral chute and the spool bore position relationship of sign three grades of variable-gains.According to the different requirements of controlled final controlling element control rate from control accuracy, the n level spiral chute of more than three can be had further uniformly inside valve pocket, it is different that n level spiral fluted lead angle is set, often rotate 360/n degree, the spiral chute participation work of different lead angle can be made, suitable spiral chute participation work is selected in requirement according to control rate and precision, and this will significantly improve the adaptability of valve.Under common big orifice valve core structure, spiral chute too much will increase difficulty of processing and reduce intensity, and therefore inside valve pocket, spiral chute of opening is no more than 5 grades.
Claims (8)
1. the large-flow high-frequency of rotatable Parallel Control rings a digital valve, it is characterized in that it comprises valve body (1), valve pocket (2), spool (3), left actuating motor (15), right actuating motor (9), left end cap (16), right end cap (8); Valve pocket (2) is rotatable to be arranged in valve body (1), and spool (3) is rotatable to be arranged in valve pocket (2);
Left actuating motor (15) is arranged on valve body (1) by left end cap (16), left servo motor output shaft (15A) is fixedly connected on valve pocket (2), right actuating motor (9) is arranged on valve body (1) by right end cap (8), and spool (3) is connected to right servo motor output shaft (9A);
Valve body (1) is connected with the bearing that passes on left of valve pocket (2), fixed cover (4) is fixedly connected on valve pocket (2) right side and is placed in valve body (1), and valve body (1) is connected by bearing with fixed cover (4);
Described valve body (1) is connected with left tapered roller bearing (18) with the left side of valve pocket (2), connects between valve body (1) and fixed cover (4) with right tapered roller bearing (6); Being provided with left bearing adjustment pad (17) for regulating left tapered roller bearing (18) pretension amount between described left end cap (16) and valve body (1), being provided with between right end cap (8) and valve body (1) for regulating the right bearing of right tapered roller bearing (6) pretension amount to regulate pad (7).
2. the large-flow high-frequency of a kind of rotatable Parallel Control according to claim 1 rings digital valve, it is characterized in that the left side of the second from left spool shaft part (3G) on described spool (3), valve pocket (2) forms left control cavity volume (3D), the second from left spool shaft part (3G) has upper left spool bore (3P1) and lower-left spool bore (3T1), the second from left spool shaft part (3G) valve pocket outward (2) inner side has left hand screw groove (2X), left hand screw groove (2X) is communicated with left control cavity volume (3D), left hand screw groove (2X) is positioned between upper left spool bore (3P1) and lower-left spool bore (3T1), the right side on the right side two spool shaft part (3H) on spool (3), valve pocket (2) form right control cavity volume (3E), right two spool shaft parts (3H) have upper right spool bore (3T2) and bottom right spool bore (3P2), right two spool shaft part (3H) valve pocket outward (2) inner sides have right spiral (2Y), right spiral (2Y) is communicated with right control cavity volume (3E), and right spiral (2Y) is positioned between upper right spool bore (3T2) and bottom right spool bore (3P2).
3. the large-flow high-frequency of a kind of rotatable Parallel Control according to claim 1 rings digital valve, it is characterized in that described left tapered roller bearing (18) and right tapered roller bearing (6) are installed face-to-face.
4. the large-flow high-frequency of a kind of rotatable Parallel Control according to claim 1 rings digital valve, it is characterized in that described spool (3) two ends arrange the left belleville spring (20) and right belleville spring (11) being used for centering.
5. the large-flow high-frequency of a kind of rotatable Parallel Control according to claim 1 rings digital valve, it is characterized in that left spool adjustment pad (19) and right spool that described spool (3) two ends are arranged for calibrating zero-bit adjust pad (10).
6. the large-flow high-frequency of a kind of rotatable Parallel Control according to claim 2 rings digital valve, it is characterized in that described left hand screw groove (2X) along the circumferential direction uniform 1 ~ 5, each spiral chute lead angle is different, right spiral (2Y) along the circumferential direction uniform 1 ~ 5, each spiral chute lead angle is different.
7. the large-flow high-frequency of a kind of rotatable Parallel Control according to claim 2 rings digital valve, it is characterized in that described upper left spool bore (3P1) connects high pressure oil, lower-left spool bore (3T1) connects low pressure oil, upper right spool bore (3T2) connects high pressure oil, and bottom right spool bore (3P2) connects low pressure oil.
8. the large-flow high-frequency of a kind of rotatable Parallel Control according to claim 6 rings digital valve, it is characterized in that the described spiral fluted lead angle number of degrees are 10 ~ 80 degree.
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| CN104500782B (en) * | 2014-05-28 | 2016-09-21 | 苏州雷姆斯汽车工程有限公司 | A kind of multistage hydraulic regulating slide valve core body |
| CN104454730B (en) * | 2014-11-29 | 2017-03-22 | 南京萨伯工业设计研究院有限公司 | Servo valve element and machining method thereof |
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| WO2019010591A1 (en) * | 2017-07-12 | 2019-01-17 | 王亚娟 | Rotatable, parallel control, high flow rate, high frequency response digital valve |
| CN112664500A (en) * | 2020-12-23 | 2021-04-16 | 苏州宏腾液压机电科技有限公司 | Rotary valve assembly for digital hydraulic oil cylinder and corresponding mechanical feedback digital hydraulic oil cylinder |
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Effective date of registration: 20180813 Address after: 226503 Jiangsu Nantong Rugao North Road Park North Road (economic and Technological Development Zone Forging Industry Park) Patentee after: Nantong forging equipment Rugao Co., Ltd. Address before: 226503 Jiangsu Nantong Rugao Economic Development Zone Forging Industry Park Patentee before: Nantong Forging Equipment Co., Ltd. |