CN104514763A - Improved servo control valve and control method thereof - Google Patents
Improved servo control valve and control method thereof Download PDFInfo
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- CN104514763A CN104514763A CN201410848983.4A CN201410848983A CN104514763A CN 104514763 A CN104514763 A CN 104514763A CN 201410848983 A CN201410848983 A CN 201410848983A CN 104514763 A CN104514763 A CN 104514763A
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- 238000000034 method Methods 0.000 title claims description 10
- 238000006073 displacement reaction Methods 0.000 claims description 15
- 230000001276 controlling effect Effects 0.000 claims description 14
- 230000008859 change Effects 0.000 claims description 10
- 230000000694 effects Effects 0.000 claims description 9
- 238000007789 sealing Methods 0.000 claims description 9
- 210000004907 gland Anatomy 0.000 claims description 8
- 230000000452 restraining effect Effects 0.000 claims description 8
- 238000009434 installation Methods 0.000 claims description 6
- 230000000903 blocking effect Effects 0.000 claims description 4
- 230000009471 action Effects 0.000 claims description 3
- 239000000203 mixture Substances 0.000 claims description 3
- 230000001105 regulatory effect Effects 0.000 claims description 3
- 230000007704 transition Effects 0.000 claims description 3
- 238000003780 insertion Methods 0.000 claims 1
- 230000037431 insertion Effects 0.000 claims 1
- 230000009977 dual effect Effects 0.000 abstract 1
- 238000005086 pumping Methods 0.000 abstract 1
- 230000007246 mechanism Effects 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 239000012636 effector Substances 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
Classifications
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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
- F15B13/023—Excess flow valves, e.g. for locking cylinders in case of hose burst
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Servomotors (AREA)
Abstract
The invention relates to an improved servo control valve. The servo control valve comprises a valve body, wherein a valve sleeve and a valve core are arranged on the valve body, and the valve core and the valve sleeve are mounted and arranged in a misplacement manner; an inner hole of a valve seat is mounted on the valve core in a sleeving manner, and an excircle at the lower part is mounted in a mounting hole of the valve sleeve; a pull rod is mounted on the excircle of the valve core in a sleeving manner, a spacing pin is mounted in a positioning pin hole formed in the valve core in a transitional manner, one end of the spacing pin is sunk in the valve core, and the other end of the spacing pin is protruded outside the excircle of the valve core and is inserted in a spacing groove formed in the valve seat; an adjusting screw is combined with the valve body in a screwed manner, and the middle part of a feedback rod is mounted in the adjusting screw in a sleeving manner; a ball head at the left end of the feedback rod is fit with a radial hole formed in the valve sleeve, and a ball head at the right end is mounted in a feedback groove of a servo cylinder; a reset spring seat is mounted in the valve body; in addition, an oil path in the valve body is divided into three parts of oil feeding, oil controlling and oil returning, which are mutually communicated. According to the invention, the valve core is controlled to rotate in different directions, so that the purpose that the servo cylinder operates in different directions is realized, and swash plates oblique by corresponding angles; therefore, the purpose of oil pumping in dual directions is realized, and the output discharge capacity of a pump is changed.
Description
Technical field
The present invention relates to servo variable mechanism technical field, particularly relate to a kind of modified model pilot valve and controlling method thereof.
Background technique
Pilot valve is as the core control unit of servo-system, miscellaneous part is all integrated on valve body, the performance of valve body directly affects the precision and stability of whole control system, by being installed on the pump housing by valve body, by pilot pressure oil and then hydraulic control pump displacement.Spool and valve pocket are set in valve body, the connection of oil circuit control, thus after pilot valve, are delivered to by pilot pressure oil operation and the fixed point stopping that variable oil cylinder controls oil cylinder, play the effect of hydraulic control pump displacement.The spool of current use does not arrange positioning device, cause spool its angle in rotary course uncontrolled, cause the damage of Partial Variable components and parts, and then affect pump delivery, cause whole pump out of control, and pull bar is arranged on spool cylindrical, when pulling pull bar drive Spool rotating under outside Effector effect, easily cause the relative sliding of pull bar and spool, the fixed point stop position of remote-effects oil cylinder, after resetting, servo-system can not accurately be in zero-bit state; Simultaneously the control end that arranges of valve pocket and spool is unreasonable, causes hydraulic system not realize servocylinder by control valve core and runs along different direction, and then drive oil hydraulic pump swash plate to do different direction inclination, realize two-way pump oil, and pump output discharge capacity can not change in real time.
Summary of the invention
Technical problem solved by the invention is to provide a kind of modified model pilot valve and controlling method thereof, to solve the shortcoming in above-mentioned background technology.
Technical problem solved by the invention realizes by the following technical solutions:
Modified model pilot valve, comprises valve body, wherein, valve body is provided with the valve pocket mounting hole for installing valve pocket and the spool installation bottom outlet for installing spool, and spool is installed in spool installation bottom outlet through valve pocket bottom, arranges in arranged in dislocation; For preventing sealing from producing air pressure, at spool, bottom outlet sidepiece being installed and offering balance pressure passage, to balance the external and internal pressure of die cavity; Valve seat inner hole sleeve is loaded on spool, and its underpart cylindrical is installed in valve pocket mounting hole, and when loading valve pocket mounting hole, sealing load is unloaded by balance pressure passage; Drag link sleeve is loaded on spool cylindrical, position limit pin transition is installed in positioning pin hole that spool is arranged, its one end is sunken in spool, the other end protrudes from spool cylindrical and inserts in the restraining groove that valve seat is arranged, when Spool rotating, move in the restraining groove of valve seat with position limit pin, when moving to restraining groove edge, position limit pin is restricted, thus the angle of swing of restriction spool; Adjustment screw is installed internal thread by the adjustment screw that the adjustment screw outside thread of outer installment and valve body are arranged and is screwed, be set on the bias adjustment circle of adjustment screw in the middle part of feedback rod, and its left end bulb coordinates with the radial hole that valve pocket is arranged, right-hand member bulb is installed in the feedback groove of servocylinder, by rotating adjustment screw, eccentric adjustment circle is driven to swing, thus the relative position of adjustment feedback rod, allow servo-system be in zero-bit state; Return spring holder is installed in valve body, and on return spring holder, be provided with the plug screw for sealing blocking; In addition, in valve body, oil circuit is divided into oil-feed, control oil and oil return three parts, oil-feed part is provided with the first oil inlet passage, the second oil inlet passage, the 3rd oil inlet passage and the 4th oil inlet passage, oil controlling portion divide be provided with first on the left of control to control on the left of oil duct, second to control on the right side of oily passage and second on the right side of oil duct, first and control oily passage, oil return part is provided with drainback passage, and oil inlet passage, control oil duct are communicated with each other with drainback passage; And have left side V-type groove and right side V-type groove spool gyration center line is symmetrical.
In the present invention, pull bar lock onto on spool cylindrical by fastening screw trip bolt, and coupling mechanism force effectively can ensure that external control device drives Spool rotating when pulling pull bar, and does not cause the relative sliding of pull bar and spool.
In the present invention, adjustment screw is provided with location, top cylindrical and bottom and locate cylindrical, and top is located cylindrical and coordinated with the adjustment screw top positioning hole that valve body is arranged, bottom is located cylindrical and is coordinated with the adjustment screw bottom positioning hole that valve body is arranged.
In the present invention, adjust on screw and secure gland nut is installed, by screwing secure gland nut with fit sealing.
In the present invention, counterbore seal groove secured fit secure gland nut and valve body arranged.
In the present invention, precompressed Returnning spring is provided with between plug screw and return spring holder.
In the present invention, the front end of return spring holder is inserted in reset seat breach that spool is arranged.
In the present invention, the angle rotatable of spool is 3 ° ~ 35 °.
In the present invention, valve pocket is symmetrically set with left oil canal and right oil canal about valve pocket gyration center, for input and the off-load of pressure oil.
In the present invention, the control oil inlet passage of spool and valve pocket composition is provided with input end and output terminal, and external pressure oil flows into servo variable displacement cylinder, through output terminal oil return unloading through input end.
Modified model pilot valve controlling method, concrete steps are as follows:
Pressure oil is delivered to the control oil inlet passage input end of spool and valve pocket composition through oil-feed part, oil controlling portion is divided a road to control on the left of right oil canal, second to control oily passage on the right side of oil duct and first and is delivered on the left of servo variable displacement cylinder, another road is controlled and is controlled oily passage on the left of oil duct and first and be delivered on the right side of servo variable displacement cylinder on the right side of left oil canal, second, and when oil controlling portion divides a road incoming pressure oil, another Lu Zewei oil return, and final through output terminal and drainback passage oil return unloading; When servovalve is in relative normally off with valve pocket without spool during external control under return spring holder effect; When pull bar is along when being rotated counterclockwise, spool and valve pocket are staggered positions, connect oil circuit, left passage walked by pressure oil, promotes servocylinder right lateral, oil now on the right side of servocylinder returns through right wing and is discharged by output terminal and drainback passage off-load, servocylinder drives motional feedback bar to rotate around adjustment screw simultaneously, and feedback rod is stirred valve pocket and is rotated counterclockwise around spool, impels the oil circuit of connection to trend towards closing, servocylinder rests on current location, and whole hydraulic system is in dynamic balance state; Equally, when pull bar rotates clockwise, spool and valve pocket are staggered positions, connect oil circuit, right wing passage walked by pressure oil, promote servocylinder left lateral, the oil now on the left of servocylinder returns through left and is discharged by output terminal and drainback passage off-load, and servocylinder drives motional feedback bar to rotate around adjustment screw simultaneously, feedback rod is stirred valve pocket and is turned clockwise around spool, impel the oil circuit of connection to trend towards closing, servocylinder rests on current location, and whole hydraulic system is in dynamic balance state; Rotate along different direction by handling spool, run along different direction to realize servocylinder, and then drive oil hydraulic pump swash plate to do different direction, thus realize two-way pump oil, and along with the angle of Spool rotating different, the operation stop position of servocylinder is also different, and the angle of inclination that swash plate is corresponding also changes thereupon, thus realizes the change that pump exports discharge capacity.
Spool is stepless regulated, and export with the stepless change realizing pump displacement, spool angle rotatable is 3 ° ~ 35 °, and it is 3 ° ~ 35 ° that actual logical oil promotes servocylinder operation angle, and the motion mode that hydraulic system is in dynamic balance state is as follows:
When spool is without external control, the distance between the top of left side V-type groove and right side V-type groove is greater than the diameter dimension of the input end passage that valve pocket is arranged, therefore oil circuit is cut off, and is in normally off, and input end pressure oil is through the off-load of system relief valve, the output terminal channel diameter size that valve pocket is arranged is greater than input end channel diameter size, and the distance between the top of left side V-type groove and right side V-type groove is less than the diameter dimension of the output terminal passage that valve pocket is arranged, namely right oil canal is by right side V-type groove, left oil canal is all in normally open by left side V-type groove and output terminal, when spool turns clockwise from reset mode, and angle of swing is when being less than 3 °, left side V-type groove and input end are from closed condition to progressively opening, and the aperture of left side V-type groove now and output terminal will reduce gradually, right side V-type groove and input end are still in closed condition, the aperture of right side V-type groove and output terminal will increase gradually, when left side V-type groove and input end aperture are less than the aperture of left side V-type groove and output terminal, input end flows through the oil of left oil canal directly through output terminal off-load, now be not enough at left oil canal build-up pressure, servocylinder is in zero-bit state under the effect of preloading spring power, swash plate is without inclination, pump delivery is zero, when spool progressively rotates, when impelling the aperture of left side V-type groove and input end to be greater than the aperture of left side V-type groove and output terminal, now at left oil canal build-up pressure, and when the active force of the action of hydraulic force that left oil canal is set up on servocylinder is greater than preloading spring power, servocylinder will be pushed operation, and this when building pressure the critical angle of swing of spool be 3 °, namely left side V-type groove is connected with input end and is also connected with output terminal, the pressure oil part that input end pumps into is leaked for making up servo cylinder system, and part is through output terminal off-load, when Spool rotating crosses β ° (3 ° of < β <35 °), now on the left of moment, V-type groove is only connected with left oil canal, left oil canal builds pressure rapidly, servocylinder is pushed, meanwhile servocylinder motional feedback bar is stirred valve pocket and is turned clockwise, the aperture of left side V-type groove and input end is progressively impelled to reduce, impel the aperture of left side V-type groove and output terminal to increase gradually simultaneously, when left side V-type groove and input end aperture by pressure oil just make up system leak and output terminal off-load time, servocylinder is out of service, servo feedback system is now in hydraulic pressure dynamic balance state, after pilot valve, the fixed point stop position that variable oil cylinder controls oil cylinder is delivered to, to realize hydraulic control pump displacement by pilot pressure oil.
Beneficial effect: in the present invention, spool is installed in spool installation bottom outlet through valve pocket bottom, arrange in arranged in dislocation, pull bar lock onto on spool cylindrical by fastening screw trip bolt, pass through rotating rod, connect oil circuit, handle spool to rotate along different direction, run along different direction to realize servocylinder, and then drive oil hydraulic pump swash plate to do different direction, thus realize two-way pump oil, and along with the angle of Spool rotating different, the operation stop position of servocylinder is also different, the angle of inclination also and then change that swash plate is corresponding, thus realize the change of the output discharge capacity of pump, after pilot valve, the fixed point stop position that variable oil cylinder controls oil cylinder is delivered to realize pilot pressure oil, and then control pump discharge capacity, control accuracy is high, and spool is provided with in positioning pin hole, position limit pin one end is sunken in spool, and the other end protrudes from spool cylindrical and inserts in the restraining groove that valve seat is arranged, thus the angle of swing of restriction spool, the limit discharge capacity of control pump.
Accompanying drawing explanation
Fig. 1 is the assembling front view of preferred embodiment of the present invention.
Fig. 2 is the assembling plan view of preferred embodiment of the present invention.
Fig. 3 is the assembling right elevation of preferred embodiment of the present invention.
Fig. 4 is the main sectional view of valve body in preferred embodiment of the present invention.
Fig. 5 is that valve pocket mounting hole in Fig. 4 and spool install bottom outlet sectional view.
Fig. 6 is the adjustment screw plan view in preferred embodiment of the present invention.
Fig. 7 is the spool plan view in preferred embodiment of the present invention.
Fig. 8 is the principle schematic of preferred embodiment of the present invention.
Fig. 9 ~ Figure 12 is that the servo feedback system in preferred embodiment of the present invention is in hydraulic pressure transient equiliblium time-state method.
Figure 13 is Spool rotating angle in preferred embodiment of the present invention and pump displacement relation schematic diagram.
Embodiment
The technological means realized to make the present invention, creation characteristic, reaching object and effect is easy to understand, below in conjunction with concrete diagram, setting forth the present invention further.
See the modified model pilot valve of Fig. 1 ~ Fig. 7, comprise pull bar 1, valve seat 2, O RunddichtringO 1, position limit pin 4, O RunddichtringO 25, fastening screw trip bolt 1, secure gland nut 7, adjustment screw 8, throttling pad 9, O RunddichtringO 3 10, feedback rod 11, O RunddichtringO 4 12, O RunddichtringO 5 13, O RunddichtringO 6 14, O RunddichtringO 7 15, valve body 16, spool 17, sealing screw plug 18, valve pocket 19, plug screw 20, return spring holder 21, Returnning spring 22, O RunddichtringO 8 23, fastening screw trip bolt 2 24, and adjust screw 8 and comprise adjustment screw outside thread 8-1, location, top cylindrical 8-2, eccentric adjustment circle 8-3, location, bottom cylindrical 8-4, valve body 16 comprises fastening screw nail 16-1, oily passage 16-2 is controlled on the left of in the of first, oily passage 16-3 is controlled on the right side of in the of first, drainback passage 16-4, balance pressure passage 16-5, first oil inlet passage 16-6, feedback rod swings breach 16-8, valve pocket mounting hole 16-9, second oil inlet passage 16-10, 3rd oil inlet passage 16-11, spool installs bottom outlet 16-12, 4th oil inlet passage 16-13, adjustment screw bottom positioning hole 16-14, adjustment screw top positioning hole 16-15, internal thread 16-16 installed by adjustment screw, counterbore seal groove 16-17, oil duct 16-18 is controlled on the left of in the of second, oil duct 16-19 is controlled on the right side of in the of second, spool 17 comprises positioning pin hole 17-1, left side V-type groove 17-2, spool cylindrical 17-3, right side V-type groove 17-4, reset seat breach 17-5, input end P, output terminal T, right oil canal A and left oil canal B.
In the present embodiment, all O type circles be installed on valve body are all used for leak-tight seal, valve pocket 19 is installed in the valve pocket mounting hole 16-9 of setting on valve body 16, spool 17 is installed on through valve pocket 19 bottom the spool that valve body 16 is arranged and installs in bottom outlet 16-12, valve seat 2 inner hole sleeve is loaded on spool 17, and bottom cylindrical is installed in valve pocket mounting hole 16-9, when loading valve pocket mounting hole 16-9, sealing load is unloaded by balance pressure passage 16-5, all cooperations are Spielpassung, and valve seat 2 is installed on valve body 16 by fastening screw trip bolt 2 24 is fastening, pull bar 1 is set on spool cylindrical 17-3, and locked by fastening screw trip bolt 1, coupling mechanism force effectively can ensure that external control device is with movable valve plug 17 to rotate when pulling pull bar 1, and do not cause the relative sliding of pull bar 1 and spool 17, position limit pin 4 transition is installed in the positioning pin hole 17-1 of setting on spool 17, one end is sunken in spool 17, the other end protrudes from spool 17 cylindrical and inserts in the restraining groove of valve seat 2, when spool 17 rotates, move in the restraining groove of valve seat 2 with position limit pin 4, when moving to restraining groove edge, position limit pin 4 is restricted, thus the angle of swing of restriction spool 17,
Adjustment screw 8 is installed internal thread 16-16 by the adjustment screw that the adjustment screw outside thread 8-1 of outer installment and valve body 16 are arranged and is screwed, and location, top cylindrical 8-2 coordinates with adjustment screw top positioning hole 16-15, location, bottom cylindrical 8-4 coordinates with adjustment screw bottom positioning hole 16-14, and by screwing secure gland nut 7 fit sealing on adjustment screw 8, now secure gland nut 7 and counterbore seal groove 16-17 secured fit, be set on eccentric adjustment circle 8-3 in the middle part of feedback rod 11, left end bulb coordinates with the radial hole that valve pocket 19 is arranged, right-hand member bulb on feedback rod 11 is installed in the feedback groove of servocylinder, by rotating adjustment screw 8, eccentric adjustment circle 8-3 is driven to swing, thus the relative position of adjustment feedback rod 11, servo-system is allowed to be in zero-bit state, return spring holder 21 is installed in valve body 16, and seals blocking by plug screw 20, and is provided with precompressed Returnning spring 22 between plug screw 20 and return spring holder 21, and the front end of return spring holder 21 is inserted in the reset seat breach 17-5 of spool 17, sealing screw plug 18 is for blocking technique runner hole.
Shown in Figure 8, oil circuit is divided into oil-feed, control oil and oil return three parts, oil-feed part is through the 4th oil inlet passage 16-13, first oil inlet passage 16-6, the input end P place of the 3rd oil inlet passage 16-11 and the second oil inlet passage 16-10 valve pocket, oil controlling portion divides a road through right oil canal A, control on the left of in the of second and control oily passage 16-3 on the right side of oil duct 16-18 and first and be delivered on the left of servo variable displacement cylinder, another road is through left oil canal B, control on the right side of in the of second and control oily passage 16-2 on the left of oil duct 16-19 and first and be delivered on the right side of servo variable displacement cylinder, and when oil controlling portion divides a road incoming pressure oil, another road then becomes oil return part around, and it is final through output terminal T and drainback passage 16-4 oil return unloading, when servovalve is in relative normally off with valve pocket 19 without spool during external control 17 under return spring holder 21 acts on, as shown in Figure 2, when pull bar 1 is along when being rotated counterclockwise, spool 17 and valve pocket 19 staggered positions, connect oil circuit, left passage walked by pressure oil, promote servocylinder right lateral, oil now on the right side of servocylinder returns through right wing and is discharged by output terminal T and drainback passage 16-4 off-load, servocylinder drives motional feedback bar 11 to rotate around adjustment screw 8 simultaneously, now feedback rod 11 will be stirred valve pocket 19 and will be rotated counterclockwise around spool 17, the oil circuit of connection is impelled to trend towards closing, servocylinder is allowed to rest on current location, whole hydraulic system is in dynamic balance state, equally, when pull bar 1 rotates clockwise, spool 17 and valve pocket 19 staggered positions, connect oil circuit, right wing passage walked by pressure oil, promote servocylinder left lateral, oil now on the left of servocylinder returns through left and is discharged by output terminal T and drainback passage 16-4 off-load, servocylinder drives motional feedback bar 11 to rotate around adjustment screw 8 simultaneously, now feedback rod 11 will be stirred valve pocket 19 and turn clockwise around spool 17, impel the oil circuit of connection to trend towards closing, allow servocylinder rest on current location, whole hydraulic system is in dynamic balance state, rotate towards different directions by handling spool 17, realize servocylinder to run towards different directions, and then drive oil hydraulic pump swash plate to do different direction inclinations, thus realize two-way pump oil, and the angle rotated along with spool 17 is different, the operation stop position of servocylinder is also different, the angle of inclination also and then change that swash plate is corresponding, thus realizes the change of the output discharge capacity of pump.
Spool 17 is stepless regulated, the stepless change of the existing pump displacement of historical facts or anecdotes exports, the angle of swing of spool 17 and the relation of pump displacement are as shown in figure 13, the angle rotatable scope of spool 17 is 3 ° ~ 35 °, it is 3 ° ~ 35 ° that actual logical oil promotes servocylinder operation angle scope, clockwise and counterclockwise limit position is as a in Fig. 2, shown in b position, hydraulic system is in dynamic balance state sequential, as shown in Figure 9, when spool 17 is without external control, because the distance between left side V-type groove 17-2 and the top of right side V-type groove 17-4 is greater than the diameter dimension of the input end P channel that valve pocket 19 is arranged, so oil circuit is cut off, be in normally off, input end P pressure oil is through the off-load of system relief valve, the channel diameter size that on valve pocket 19, output terminal T is arranged is greater than the channel diameter size of input end P, and the distance between the top of left side V-type groove 17-2 and right side V-type groove 17-4 is less than the diameter dimension of the output terminal T passage that valve pocket 19 is arranged, namely right oil canal A is by right side V-type groove 17-4, left oil canal B is all in normally open with output terminal T respectively by left side V-type groove 17-2, as shown in Figure 10, with 17 clockwise turn to example, when spool 17 turns clockwise from reset mode, and angle of swing is when being less than 3 °, left side V-type groove 17-2 and input end P is from closed condition to progressively opening, and the aperture of left side V-type groove 17-2 now and output terminal T will reduce gradually, and right side V-type groove 17-4 now and input end P is still in closed condition, the aperture of right side V-type groove 17-4 and output terminal T will increase gradually, because left side V-type groove 17-2 and input end P aperture are less than the aperture of left side V-type groove 17-2 and output terminal T, therefore input end P flows through the oil of left oil canal B directly through output terminal T off-load, now be not enough at left oil canal B build-up pressure, servocylinder is in zero-bit state under the effect of preloading spring power, swash plate is without inclination, pump delivery is zero, when spool 17 progressively rotates, when impelling the aperture of left side V-type groove 17-2 and input end P to be greater than the aperture of left side V-type groove 17-2 and output terminal T, now at left oil canal B build-up pressure, and when the active force of action of hydraulic force on servocylinder that left oil canal B sets up is greater than preloading spring power, servocylinder will be pushed operation, and this when building pressure the critical angle of swing of spool 17 be 3 °, now namely V-type groove 17-2 in left side connects with input end P and also connects with output terminal T, the pressure oil part that input end P pumps into is leaked for making up servo cylinder system, part is through output terminal T off-load, as shown in figure 11, when spool 17 rotates through β ° (this angle is greater than 3 ° and is less than 35 °), now on the left of moment, V-type groove 17-2 only connects with left oil canal B, left oil canal B builds pressure rapidly, servocylinder is pushed, meanwhile servocylinder motional feedback bar is stirred valve pocket 19 and is turned clockwise, the aperture of left side V-type groove 17-2 and input end P is progressively impelled to reduce, impel the aperture of left side V-type groove 17-2 and output terminal T to increase gradually simultaneously, when left side V-type groove 17-2 and input end P aperture by pressure oil just make up system leak and output terminal T off-load time, servocylinder is out of service, as shown in figure 12, servo feedback system is now in hydraulic pressure dynamic balance state.
More than show and describe basic principle of the present invention and major character and advantage of the present invention.The technician of the industry should understand; the present invention is not restricted to the described embodiments; what describe in above-described embodiment and specification just illustrates principle of the present invention; without departing from the spirit and scope of the present invention; the present invention also has various changes and modifications, and these changes and improvements all fall in the claimed scope of the invention.Application claims protection domain is defined by appending claims and equivalent thereof.
Claims (10)
1. modified model pilot valve, comprises valve body, it is characterized in that, valve body is provided with the valve pocket mounting hole for installing valve pocket and the spool installation bottom outlet for installing spool, and spool is installed in spool installation bottom outlet through valve pocket bottom, arranges in arranged in dislocation; And offering balance pressure passage at spool installation bottom outlet sidepiece, valve seat inner hole sleeve is loaded on spool, and its underpart cylindrical is installed in valve pocket mounting hole; Drag link sleeve is loaded on spool cylindrical, and position limit pin transition is installed in positioning pin hole that spool is arranged, and its one end is sunken in spool, and the other end protrudes from spool cylindrical and inserts in the restraining groove that valve seat is arranged; Adjustment screw is installed internal thread by the adjustment screw that the adjustment screw outside thread of outer installment and valve body are arranged and is screwed, be set on the bias adjustment circle of adjustment screw in the middle part of feedback rod, and its left end bulb coordinates with the radial hole that valve pocket is arranged, right-hand member bulb is installed in the feedback groove of servocylinder; Return spring holder is installed in valve body, and on return spring holder, be provided with the plug screw for sealing blocking; In addition, in valve body, oil circuit is divided into oil-feed, control oil and oil return three parts, oil-feed part is provided with the first oil inlet passage, the second oil inlet passage, the 3rd oil inlet passage and the 4th oil inlet passage, oil controlling portion divide be provided with first on the left of control to control on the left of oil duct, second to control on the right side of oily passage and second on the right side of oil duct, first and control oily passage, oil return part is provided with drainback passage, and oil inlet passage, control oil duct are communicated with each other with drainback passage; And have left side V-type groove and right side V-type groove spool gyration center line is symmetrical.
2. modified model pilot valve according to claim 1, is characterized in that, pull bar is lock onto on spool cylindrical by fastening screw trip bolt.
3. modified model pilot valve according to claim 1, it is characterized in that, adjustment screw on be provided with top location cylindrical and bottom locate cylindrical, and location, top cylindrical coordinates with the adjustment screw top positioning hole that valve body is arranged, location, bottom cylindrical coordinates with the adjustment screw bottom positioning hole that valve body is arranged.
4. modified model pilot valve according to claim 1, is characterized in that, adjustment screw is provided with secure gland nut.
5. modified model pilot valve according to claim 4, is characterized in that, the counterbore seal groove secured fit that secure gland nut and valve body are arranged.
6. modified model pilot valve according to claim 1, is characterized in that, is provided with precompressed Returnning spring between plug screw and return spring holder.
7. modified model pilot valve according to claim 1, is characterized in that, in the reset seat breach that the front end insertion spool of return spring holder is arranged.
8. modified model pilot valve according to claim 1, is characterized in that, valve pocket is symmetrically set with left oil canal and right oil canal about valve pocket gyration center.
9. modified model pilot valve controlling method, is characterized in that, concrete steps are as follows:
Pressure oil is delivered to the control port place of spool and valve pocket composition through oil-feed part, oil controlling portion is divided a road to control on the left of right oil canal, second to control oily passage on the right side of oil duct and first and is delivered on the left of servo variable displacement cylinder, another road is controlled and is controlled oily passage on the left of oil duct and first and be delivered on the right side of servo variable displacement cylinder on the right side of left oil canal, second, and when oil controlling portion divides a road incoming pressure oil, another road then becomes oil return part, and final through output terminal and drainback passage oil return unloading; When servovalve is without external control, spool is in relative normally off with valve pocket under return spring holder effect; When pull bar is along when being rotated counterclockwise, spool and valve pocket are staggered positions, connect oil circuit, left passage walked by pressure oil, promotes servocylinder right lateral, oil now on the right side of servocylinder returns through right wing and is discharged by output terminal and drainback passage off-load, servocylinder drives motional feedback bar to rotate around adjustment screw simultaneously, and feedback rod is stirred valve pocket and is rotated counterclockwise around spool, impels the oil circuit of connection to trend towards closing, servocylinder rests on current location, and whole hydraulic system is in dynamic balance state; Equally, when pull bar rotates clockwise, spool and valve pocket are staggered positions, connect oil circuit, right wing passage walked by pressure oil, promote servocylinder left lateral, the oil now on the left of servocylinder returns through left and is discharged by output terminal and drainback passage off-load, and servocylinder drives motional feedback bar to rotate around adjustment screw simultaneously, feedback rod is stirred valve pocket and is turned clockwise around spool, impel the oil circuit of connection to trend towards closing, servocylinder rests on current location, and whole hydraulic system is in dynamic balance state; Rotate along different direction by handling spool, run along different direction to realize servocylinder, and then drive oil hydraulic pump swash plate to do different direction, thus realize two-way pump oil, and along with the angle of Spool rotating different, the operation stop position of servocylinder is also different, and the angle of inclination that swash plate is corresponding also changes thereupon, thus realizes the change that pump exports discharge capacity.
10. modified model pilot valve controlling method according to claim 9, it is characterized in that, spool is stepless regulated, export with the stepless change realizing pump displacement, spool angle rotatable is 3 ° ~ 35 °, it is 3 ° ~ 35 ° that actual logical oil promotes servocylinder operation angle, and the motion mode that hydraulic system is in dynamic balance state is as follows:
When spool is without external control, the distance between the top of left side V-type groove and right side V-type groove is greater than the diameter dimension of the input end passage that valve pocket is arranged, therefore oil circuit is cut off, and is in normally off, and input end pressure oil is through the off-load of system relief valve, the output terminal channel diameter size that valve pocket is arranged is greater than input end channel diameter size, and the distance between the top of left side V-type groove and right side V-type groove is less than the diameter dimension of the output terminal passage that valve pocket is arranged, namely right oil canal is by right side V-type groove, left oil canal is all in normally open by left side V-type groove and output terminal, when spool turns clockwise from reset mode, and angle of swing is when being less than 3 °, left side V-type groove and input end are from closed condition to progressively opening, and the aperture of left side V-type groove now and output terminal will reduce gradually, right side V-type groove and input end are still in closed condition, the aperture of right side V-type groove and output terminal will increase gradually, when left side V-type groove and input end aperture are less than the aperture of left side V-type groove and output terminal, input end flows through the oil of left oil canal directly through output terminal off-load, now be not enough at left oil canal build-up pressure, servocylinder is in zero-bit state under the effect of preloading spring power, swash plate is without inclination, pump delivery is zero, when spool progressively rotates, when impelling the aperture of left side V-type groove and input end to be greater than the aperture of left side V-type groove and output terminal, now at left oil canal build-up pressure, and when the active force of the action of hydraulic force that left oil canal is set up on servocylinder is greater than preloading spring power, servocylinder will be pushed operation, and this when building pressure the critical angle of swing of spool be 3 °, namely left side V-type groove is connected with input end and is also connected with output terminal, the pressure oil part that input end pumps into is leaked for making up servo cylinder system, and part is through output terminal off-load, as Spool rotating over-angle β °, 3 ° of < β ° <35 °, now on the left of moment, V-type groove is only connected with left oil canal, left oil canal builds pressure rapidly, servocylinder is pushed, meanwhile servocylinder motional feedback bar is stirred valve pocket and is turned clockwise, the aperture of left side V-type groove and input end is progressively impelled to reduce, impel the aperture of left side V-type groove and output terminal to increase gradually simultaneously, when left side V-type groove and input end aperture by pressure oil just make up system leak and output terminal off-load time, servocylinder is out of service, servo feedback system is now in hydraulic pressure dynamic balance state.
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| CN110657267A (en) * | 2019-11-15 | 2020-01-07 | 黄洪刚 | Unloading valve with overflow function |
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|---|---|
| CN104514763B (en) | 2017-01-18 |
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