CN203627366U - High-flow and high-frequency-response digital valve capable of being controlled through parallel rotation - Google Patents
High-flow and high-frequency-response digital valve capable of being controlled through parallel rotation Download PDFInfo
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- CN203627366U CN203627366U CN201320690312.0U CN201320690312U CN203627366U CN 203627366 U CN203627366 U CN 203627366U CN 201320690312 U CN201320690312 U CN 201320690312U CN 203627366 U CN203627366 U CN 203627366U
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Abstract
The utility model discloses a high-flow and high-frequency-response digital valve capable of being controlled through parallel rotation. The digital valve comprises components such as a valve body, a valve sleeve, a left servo motor, a right servo motor and the like, wherein the valve sleeve is rotatably mounted in the valve body, and a valve core is rotatably mounted in the valve sleeve; valve holes allowing high pressure oil or low pressure oil to pass are formed in two ends of the valve core and matched with spiral grooves formed in corresponding positions of two sides of the valve sleeve, and axial movement of the valve core is realized through pressure control of accommodating cavities on the right side and the left side of the valve core; the right servo motor drives the valve core to rotate, the left servo motor drives the valve sleeve to rotate, bidirectional rotation is realized through parallel control of the valve core and the valve sleeve, and frequency limitation caused by the fact that only the valve core rotates conventionally is broken through; the spiral groove mechanisms with different helix angles are formed in the valve sleeve, rotation of the valve core is changed into axial movement, and the multistage gain function is realized; high flow and high frequency response of the servo valve and accurate control of the terminal position are realized by means of the spiral groove array structure with the multistage gain function through digital control realized by parallel rotation of the valve core and the valve sleeve.
Description
Technical field
The utility model relates to the electrohydraulic control of Fluid-transmission and control field, relates in particular to a kind of high frequency large flow amount digital servo valve that can 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 has significantly promoted 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 has restricted the further lifting of system control accuracy.Along with the development of digital control technology, antijamming capability strengthens rapidly, and computer and bus are participated in directly to control becomes possibility, and this development for digitizing servovalve provides technical support; In addition, the fast development of high-end equipment, has proposed harsh requirement to large flow, high frequency sound, the antipollution of servovalve, simultaneously also provides the wide market space for developing large flow, high frequency sound, digital, resistant to pollution servovalve.
The design of current electrohydraulic control, mainly launches round high frequency sound two aspects that realize under digitizing and large flow.(1) aspect digitizing: drive ball screw and main valve plug to realize the movement of spool by actuating motor, rotatablely moving of ball screw become to moving axially of spool, by the digital control digitizing (as referenced patent 201110332448.X) that realizes servovalve of actuating motor; Or adopt servo screw device that the pilot stage of valve and main are merged, lead control one to realize, after Spool rotating, produce hydraulic driving and try hard to recommend moving self movement, digital control actuating motor drives Spool rotating to realize digitizing (as referenced patent 200910153014.6); Or adopt the pilot stage control main mode of high-speed switch valve, realize the servocontrol of main valve by controlling the make-and-break time of high-speed switch valve, digital control high-speed switch valve is realized digitizing (as referenced patent WO2012112292A1).(2) aspect the high frequency sound under large flow: adopt super magnetostriction material to make electromechanical transducer as pilot stage, this electromechanical transducer frequency range is large, controls main and can realize the high frequency sound (as referenced patent 201310149224.4) under large flow; Or for large flow 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 realize the digitizing of large-capacity valve, improves its frequency response simultaneously, but has following some shortcomings, and main manifestations is:
1) frequency response of digital servovalve promotes and runs into bottleneck.In the design of digital servovalve, generally adopt actuating motor to drive Spool rotating, realize the control to main valve.In order to improve resolution or the precision of control, require corner corresponding to each pulse of actuating motor the smaller the better.But along with corner corresponding to each pulse diminishes, causing actuating motor to rotate the required step number of equal angular increases, the speed of response that this has reduced spool, has limited 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 the also gain of raising driving main of through-current capability that valve core diameter can promote main valve, are suitable for the spool as large flow digital valves.The monolateral gain control mode (as referenced patent 200910153014.6) adopting in such servo screw mechanism at present, fail the controlled area of full use spool, farthest promote the gain of pilot stage driving main, further to promote the speed of response of main valve plug action.
3) adaptability that end position is accurately controlled has to be strengthened.Because servovalve has been taken into account large flow and high frequency sound in the time designing, flow gain is large, be difficult to realize accurately and controlling on servo-system end position, restrict thus its application in the equipments such as large-scale composite material press, friction-welding machine, limit the lifting of its highi degree of accuracy control performance, reduced the engineering adaptability of this valve.
Summary of the invention
The large-flow high-frequency that the utility model object is to provide a kind of rotatable Parallel Control rings digital valve, realize the digital control and high frequency sound of large serving volume valve 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 flow, high frequency sound and end position.
In order to achieve the above object, the technical solution adopted in the utility model 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 actuating 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 in right actuating motor output shaft.
The bearing that passes on left of valve body and valve pocket is connected, and fixed cover is fixedly connected on valve pocket right side and is placed in valve body, and valve body is connected by bearing with fixed cover.
The left side of valve body and valve pocket is connected with left tapered roller bearing, between valve body and fixed cover, connects 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, on the second from left spool shaft part, have upper left spool bore and lower-left spool bore, valve pocket inner side outside the second from left spool shaft part has left hand screw groove, left hand screw groove is communicated with left control cavity volume, and left hand screw groove is between upper left spool bore and lower-left spool bore; Right side, the valve pocket of the right side two spool shaft parts on spool form right control cavity volume, on right two spool shaft parts, have upper right spool bore and bottom right spool bore, valve pocket inner side outside right two spool shaft parts has right spiral, right spiral is communicated with right control cavity volume, and right spiral is between upper right spool bore and bottom right spool bore.
The left bearing being provided with between left end cap and valve body for regulating left tapered roller bearing pretension amount is adjusted pad, and the right bearing being provided with between right end cap and valve body for regulating right tapered roller bearing pretension amount regulates pad.
Left tapered roller bearing and right tapered roller bearing are installed face-to-face.
Spool two ends are provided for left belleville spring and the right belleville spring of centering.
Spool two ends are provided for calibrating left spool adjustment pad and the right spool adjustment pad of zero-bit.
Along the circumferential direction uniform 1～5 of left hand screw groove, each spiral chute lead angle difference, along the circumferential direction uniform 1～5 of right spiral, each spiral chute lead angle difference.
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 utility model possesses is:
1) by designed spool valve pocket rotating machinery in parallel, break through the bottleneck that large flow digital valves frequency response promotes.The synchronous bidirectional rotation of spool and valve pocket is controlled, and has broken away from the frequency limitation that tradition only has Spool rotating to cause, and has not only guaranteed the control accuracy of servovalve, effectively promotes with respect to its frequency response of conventional digital valve.
2) utilize bilateral gain control structure, improve and change Spool rotating motion into axially movable speed of response.By all having control valve opening at spool two ends, make two on the same axial direction of spool control valve opening and connect respectively high low pressure mouth and be used in conjunction with, thereby the pressure of spool both sides sensitive cavity is changed simultaneously, improve thus its dynamic response.
3), by the servo screw mechanism of multiple coil lift angle, the multistage gain of realizing servovalve switches.Have several spiral chutes with different lead angles in valve pocket inner side, thereby it is different to make Spool rotating motion change axially movable gain into, realizes thus multistage gain.This mechanism can the large flow in control procedure and high-precision different requirement according to control system, rationally switch the ride gain of servovalve, both guaranteed large flow and high frequency sound that control procedure is required, guaranteed again the precision of end position control, and made this valve possess stronger engineering adaptability.
Accompanying drawing explanation
Fig. 1 is the schematic diagram of the utility model internal structure.
Fig. 2 is position relationship and the spool bore structural representation that characterizes valve pocket spiral chute and spool bore.
Fig. 3 is the hydraulic control bridge road schematic diagram that represents spool and valve port that valve pocket forms.
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 is the hydraulic control bridge road that characterizes spool and valve port that valve pocket forms.
Fig. 7 is that the angle of swing and the axial displacement that characterize servo screw mechanism are related to schematic diagram.
Fig. 8 is that Fig. 7 characterizes the angle of swing of servo screw mechanism and the M1 position view of axial displacement relation.
Fig. 9 is that Fig. 7 characterizes the angle of swing of servo screw mechanism and the M2 position view of axial displacement relation.
Figure 10 is that Fig. 7 characterizes 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 that Figure 11 characterizes the valve pocket spiral chute of secondary variable-gain and the schematic diagram of 0-180 ° of spool bore position relationship.
Figure 13 is that Figure 11 characterizes the valve pocket spiral chute of secondary variable-gain and the schematic diagram of 180-360 ° of spool bore position relationship.
Figure 14 is valve pocket spiral chute and the spool bore position relationship that characterizes three grades of variable-gains.
Figure 15 is that Figure 14 characterizes the valve pocket spiral chute of three grades of variable-gains and the schematic diagram of 0-120 ° of spool bore position relationship.
Figure 16 is that Figure 14 characterizes the valve pocket spiral chute of three grades of variable-gains and the schematic diagram of 120-240 ° of spool bore position relationship.
Figure 17 is that Figure 14 characterizes the valve pocket spiral chute of three grades of variable-gains and the schematic diagram of 240-360 ° of spool bore position relationship.
In figure: 1, valve body, 2, valve pocket, 2A, the first hole, 2B, the second hole, 2C, the first hole plug screw, 2D, the 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, 8, right end cap, 9, right actuating motor, 9A, right actuating motor output shaft, 10, right spool is adjusted 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 actuating motor output shaft, 16, left end cap, 17, left bearing is adjusted pad, 18, left tapered roller bearing, 19, left spool is adjusted pad, 20 left belleville springs, 21, spool plug screw.
Embodiment
Below in conjunction with drawings and Examples, embodiment of the present utility model is described.
Fig. 1 has schematically shown the schematic diagram of the internal structure of the utility model embodiment.
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 actuating 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 in right actuating motor output shaft 9A.
The bearing that passes on left of valve body 1 and valve pocket 2 is connected, and fixed cover 4 is fixedly connected on valve pocket 2 right sides and is placed in valve body 1, and valve body 1 is connected by bearing with fixed cover 4.
The left side of valve body 1 and valve pocket 2 is connected with left tapered roller bearing 18, between valve body 1 and fixed cover 4, connects 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, on the second from left spool shaft part 3G, have upper left spool bore 3P1 and lower-left spool bore 3T1, valve pocket 2 inner sides outside the second from left spool shaft part 3G have left hand screw groove 2X, 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, on right two spool shaft part 3H, have upper right spool bore 3T2 and bottom right spool bore 3P2, valve pocket 2 inner sides outside right two spool shaft part 3H have right spiral 2Y, 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.
The left bearing being provided with between left end cap 16 and valve body 1 for regulating left tapered roller bearing 18 pretension amounts is adjusted pad 17, and the right bearing being provided with between right end cap 8 and valve body 1 for regulating right tapered roller bearing 6 pretension amounts regulates pad 7.
Left tapered roller bearing 18 and right tapered roller bearing 6 are installed face-to-face.
Spool 3 two ends are provided for left belleville spring 20 and the right belleville spring 11 of centering, and make left belleville spring 20 and right belleville spring 11 all in compressive state, spool 3 and valve pocket 2 cooperation position that mediates while realizing initial position, and 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 and the second hole 2B.
Along the circumferential direction uniform 1～5 of left hand screw groove 2X, each spiral chute lead angle difference, along the circumferential direction uniform 1～5 of right spiral 2Y, each spiral chute lead angle difference.
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.
Fig. 2, Fig. 3, Fig. 4 and Fig. 5 are position relationship and the spool bore structures that characterizes valve pocket spiral chute and spool bore.Adopt servo screw mechanism, realize rotatablely moving of spool 3 is converted into and moved axially.Valve pocket 2 has left hand screw groove 2X with the position that the second from left spool shaft part 3G matches, and left hand screw groove 2X communicates with left control cavity volume 3D, and valve pocket 2 has right spiral 2Y with the position that right two spool shaft part 3H match, 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.It is different with upper right spool bore 3T2 institute oil-collecting hole that two holes on same axial direction are upper left spool bore 3P1, lower-left spool bore 3T1 and bottom right spool bore 3P2 institute oil-collecting hole are also different, so that the pressure size variation trend of left control cavity volume 3D and right control cavity volume 3E is contrary, thereby improve ride gain.In Fig. 2, upper left spool bore 3P1 and bottom right spool bore 3P2 meet high pressure hydraulic fluid port P, and lower-left spool bore 3T1 and upper right spool bore 3T2 take back respectively hydraulic fluid port T1 and T2.
In conjunction with Fig. 1 and Fig. 2-5, the utility model working principle is as follows: the servo screw mechanism that spool 3 and valve pocket 2 form, by the left control cavity volume 3D of rotary control valve core 3 both sides and the pressure of right control cavity volume 3E of spool 3, realize moving axially of spool 3, realize and lead control one.When after spool 3 rotations, corresponding hydraulic fluid port is connected, and makes left control cavity volume 3D and right control cavity volume 3E pressure generation respective change, moves axially thereby promote spool 3, until the oil circuit of the spiral chute on valve pocket 2 and spool bore disconnects, finally realize rotatablely moving of spool 3 and change into and move axially.Spool 3 and valve pocket 2 coordinate formation four-side structure, by increasing spool 3 diameters, increase the area gradient of working connection, thereby make valve possess large flow through-current capability.Dwindle as far as possible the volume of left control cavity volume 3D and right control cavity volume 3E, can effectively improve the frequency of the natural hydraulic mode of main valve plug.Right actuating motor 9 adopts digital form control that spool 3 is rotated, and left actuating motor 15 adopts digital form to control valve pocket 2 is rotated, in conjunction with the bidirectional rotation control of spool 3 and valve pocket 2.For example, in the time that spool 3 turns clockwise, valve pocket 2 is rotated counterclockwise, with respect to the situation that only has spool 3 to rotate, the bidirectional rotation of spool 3 and valve pocket 2 increases valve opening and the spiral fluted opening on spool 3, spool 3 rotates and becomes axially movable speed of response increase, do not reducing under the prerequisite of control accuracy, can further improve frequency response and the dynamic characteristic of this valve.
Right actuating motor output shaft 9A adopts the modes such as spline or flat key to be connected with a right spool shaft part 3C, and in the process of rotating with movable valve plug 3 at right actuating motor 9, spool 3 also can be realized and moving axially; Left actuating motor output shaft 15A is fixedly connected with valve pocket shaft part 2E, and valve pocket 2 only can be realized and rotatablely moving under the drive of left actuating motor 15.
Right tapered roller bearing 6 and left tapered roller bearing 18 adopt face-to-face to be installed, and can bear larger thrust load, regulates the thickness of pad 7 or the length of right axle sleeve 5, pretension and the location of realizing right tapered roller bearing 6 by changing right bearing; Adjust the length of pad 17 or left axle sleeve 14 by changing left bearing, pretension and the location of realizing left tapered roller bearing 18.
The centering that adopts right belleville spring 11 and left belleville spring 20 to realize spool 3, regulates right spool to adjust pad 10 and left spool is adjusted the initial zero-bit of pad 19 adjustable.
Pilot control valve port is formed by the upper spiral chute of valve pocket 2 and the circular hole of spool 3, this structure to fluid require low, suitable with common valve member, therefore effectively promoted the contamination resistance of servovalve.
Fig. 6 is the hydraulic control bridge road that characterizes spool and valve port that valve pocket forms.Owing to all having valve opening on the second from left spool shaft part 3G on spool 3 and right two spool shaft part 3H, two hole institute oil-collecting hole differences on same axial direction, and match with the spiral chute on valve pocket 2, the left control cavity volume 3D that this makes 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 now the pilot pressure of the left control cavity volume of the state representation in Fig. 3 3D increases, and the pilot pressure of right control cavity volume 3E reduces.Therefore, the control cavity volume pressure size at spool 3 two ends is contrary trend and changes, and the speed of response that pressure changes is faster than single control cavity volume pattern, has further improved thus the speed of response that is converted to axial motion by rotatablely moving.
Fig. 7-10 characterize angle of swing and the axial displacement relation of servo screw mechanism.In Fig. 8, M1 represents that spool 3 rotates relative to valve pocket 2, at spool 3 circumferencial directions, and the schematic diagram of spool bore skew spiral chute distance y; In Fig. 9, M2 is illustrated on the basis of state shown in M1, and spool 3 moves axially apart from x, and spool bore and spiral fluted oil circuit are cut off; In Figure 10, M3 represents the synthetic schematic diagram of M1 and M2.
Figure 11, Figure 12 and Figure 13 are valve pocket spiral chute and the spool bore position relationships that characterizes secondary variable-gain.Valve pocket 2 inner sides have spiral chute L1 and the L2 of two different lead angles uniformly, the two 180 degree of being separated by.Valve pocket 2 is flattened and shown with the spiral chute of spool 3 matching surfaces and the cylndrical surface at valve opening place, and in identical spool corner situation, larger its axial displacement of lead angle is less, and its resolution is higher.Therefore for different operating modes, valve pocket Rotate 180 ° is made to different spiral chute participation work, can obtain different resolution is different gains.In actuator motions process, need large flow control, end position to need in all multiple-project application of highi degree of accuracy control, can pass through said structure, in control procedure, make less lead angle participation work, realize large flow control, while approaching terminal, make larger lead angle participation work, further promote the control accuracy of servovalve.The mode of this secondary variable-gain, the adaptability of the further high-precision servo control that improves valve under heavy traffic condition.
Figure 14, Figure 15, Figure 16 and Figure 17 are valve pocket spiral chute and the spool bore position relationships that characterizes three grades of variable-gains.Different requirements according to controlled final controlling element control rate from control accuracy, can further have uniformly more than three n level spiral chutes in valve pocket inner side, n level spiral fluted lead angle difference is set, every rotation 360/n degree, can make the spiral chute participation work of different lead angles, select suitable spiral chute participation work according to the requirement of control rate and precision, this will significantly improve the adaptability of valve.Under common large latus rectum valve core structure, spiral chute too much will increase difficulty of processing and reduce intensity, and therefore the valve pocket inner side spiral chute of opening is no more than 5 grades.
Claims (10)
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 actuating motor output shaft (15A) is fixedly connected on valve pocket (2), it is upper that right actuating motor (9) is arranged on valve body (1) by right end cap (8), and spool (3) is connected in right actuating motor output shaft (9A);
Valve body (1) is connected with the bearing that passes on left of valve pocket (2), and 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).
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 described valve body (1) and the left tapered roller bearing for left side (18) of valve pocket (2) are connected, and connect with right tapered roller bearing (6) between valve body (1) and fixed cover (4).
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 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), on the second from left spool shaft part (3G), have upper left spool bore (3P1) and lower-left spool bore (3T1), outer valve pocket (2) inner side of the second from left spool shaft part (3G) 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), right side, the valve pocket (2) of the right side two spool shaft parts (3H) on spool (3) form right control cavity volume (3E), on right two spool shaft parts (3H), have upper right spool bore (3T2) and bottom right spool bore (3P2), outer valve pocket (2) inner side of right two spool shaft parts (3H) has 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).
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 being provided with the left bearing adjustment pad (17) for regulating left tapered roller bearing (18) pretension amount between described left end cap (16) and valve body (1), the right bearing being provided with between right end cap (8) and valve body (1) for regulating right tapered roller bearing (6) pretension amount regulates pad (7).
5. the large-flow high-frequency of a kind of rotatable Parallel Control according to claim 2 rings digital valve, and left tapered roller bearing (18) and right tapered roller bearing (6) described in it is characterized in that are installed face-to-face.
6. 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 are provided for left belleville spring (20) and the right belleville spring (11) of centering.
7. 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 are provided for calibrating left spool adjustment pad (19) and the right spool adjustment pad (10) of zero-bit.
8. the large-flow high-frequency of a kind of rotatable Parallel Control according to claim 3 rings digital valve, it is characterized in that along the circumferential direction uniform 1～5 of described left hand screw groove (2X), each spiral chute lead angle difference, along the circumferential direction uniform 1～5 of right spiral (2Y), each spiral chute lead angle difference.
9. the large-flow high-frequency of a kind of rotatable Parallel Control according to claim 3 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.
10. the large-flow high-frequency of a kind of rotatable Parallel Control according to claim 8 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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| Application Number | Priority Date | Filing Date | Title |
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| CN201320690312.0U CN203627366U (en) | 2013-11-05 | 2013-11-05 | High-flow and high-frequency-response digital valve capable of being controlled through parallel rotation |
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| CN201320690312.0U CN203627366U (en) | 2013-11-05 | 2013-11-05 | High-flow and high-frequency-response digital valve capable of being controlled through parallel rotation |
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| CN203627366U true CN203627366U (en) | 2014-06-04 |
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| CN (1) | CN203627366U (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103541943A (en) * | 2013-11-05 | 2014-01-29 | 南通锻压设备股份有限公司 | High-flow high-frequency-response digital valve capable of rotating and being controlled in parallel |
| CN104500783A (en) * | 2015-01-12 | 2015-04-08 | 无锡市晟瑞机械电子有限公司 | Valve sleeve type proportional valve |
| CN105156386A (en) * | 2015-08-20 | 2015-12-16 | 武汉科技大学 | High-flow and high-frequency-response proportional servo valve |
| CN105570222A (en) * | 2016-02-17 | 2016-05-11 | 武汉市航天汉诺优科技有限公司 | Numerical-control spinning-core type proportional cartridge valve |
| WO2019010591A1 (en) * | 2017-07-12 | 2019-01-17 | 王亚娟 | Rotatable, parallel control, high flow rate, high frequency response digital valve |
| CN110319242A (en) * | 2019-08-05 | 2019-10-11 | 安徽理工大学 | A kind of rotary spool switching mechanism based on bidirectional torsion spring |
-
2013
- 2013-11-05 CN CN201320690312.0U patent/CN203627366U/en not_active Withdrawn - After Issue
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103541943A (en) * | 2013-11-05 | 2014-01-29 | 南通锻压设备股份有限公司 | High-flow high-frequency-response digital valve capable of rotating and being controlled in parallel |
| CN103541943B (en) * | 2013-11-05 | 2015-12-16 | 南通锻压设备股份有限公司 | A kind of large-flow high-frequency of rotatable Parallel Control rings digital valve |
| CN104500783A (en) * | 2015-01-12 | 2015-04-08 | 无锡市晟瑞机械电子有限公司 | Valve sleeve type proportional valve |
| CN105156386A (en) * | 2015-08-20 | 2015-12-16 | 武汉科技大学 | High-flow and high-frequency-response proportional servo valve |
| CN105156386B (en) * | 2015-08-20 | 2017-04-12 | 武汉科技大学 | High-flow and high-frequency-response proportional servo valve |
| CN105570222A (en) * | 2016-02-17 | 2016-05-11 | 武汉市航天汉诺优科技有限公司 | Numerical-control spinning-core type proportional cartridge valve |
| CN105570222B (en) * | 2016-02-17 | 2017-09-22 | 武汉市汉诺优电控有限责任公司 | Core type proportional cartridge valve is revolved in a kind of numerical control |
| WO2019010591A1 (en) * | 2017-07-12 | 2019-01-17 | 王亚娟 | Rotatable, parallel control, high flow rate, high frequency response digital valve |
| CN110319242A (en) * | 2019-08-05 | 2019-10-11 | 安徽理工大学 | A kind of rotary spool switching mechanism based on bidirectional torsion spring |
| CN110319242B (en) * | 2019-08-05 | 2024-03-26 | 安徽理工大学 | Rotary valve core switching mechanism based on bidirectional torsion spring |
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| C14 | Grant of patent or utility model | ||
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| AV01 | Patent right actively abandoned |
Granted publication date: 20140604 Effective date of abandoning: 20151216 |
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| C25 | Abandonment of patent right or utility model to avoid double patenting |