CN105822795A - Inclined trough type 2D electro-hydraulic high-speed switching valve with variable transmission ratio transmission mechanism - Google Patents
Inclined trough type 2D electro-hydraulic high-speed switching valve with variable transmission ratio transmission mechanism Download PDFInfo
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- CN105822795A CN105822795A CN201610339755.3A CN201610339755A CN105822795A CN 105822795 A CN105822795 A CN 105822795A CN 201610339755 A CN201610339755 A CN 201610339755A CN 105822795 A CN105822795 A CN 105822795A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K11/00—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves
- F16K11/02—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit
- F16K11/06—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements
- F16K11/065—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members
- F16K11/07—Multiple-way valves, e.g. mixing valves; Pipe fittings incorporating such valves with all movable sealing faces moving as one unit comprising only sliding valves, i.e. sliding closure elements with linearly sliding closure members with cylindrical slides
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
- F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
- F16K31/0603—Multiple-way valves
- F16K31/061—Sliding valves
- F16K31/0613—Sliding valves with cylindrical slides
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
- F16K31/00—Actuating devices; Operating means; Releasing devices
- F16K31/44—Mechanical actuating means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Servomotors (AREA)
- Magnetically Actuated Valves (AREA)
Abstract
An inclined trough type 2D electro-hydraulic high-speed switching valve with a variable transmission ratio transmission mechanism comprises a valve body, the transmission mechanism for driving the valve body to be opened and a zero position keeping mechanism for driving the valve body to be closed. An oil inlet cavity communicates with an oil inlet in the valve body and communicates with a valve element through an oil passing hole in the valve element. High-pressure holes communicate with the valve element, and a sensitive cavity communicates with the oil inlet cavity through the oil passing hole, the high-pressure holes and inclined troughs. The sensitive cavity communicates with an oil outlet cavity through low-pressure troughs and the inclined troughs, and the oil outlet cavity communicates with an oil outlet in the valve body. The length, in the axial direction, of a second circular bead is larger than the diameter of the oil outlet, and the oil outlet is located in the motion track of the second circular bead. The lower half part of an upper lifting lever extends into a U-shaped fork of a lower shifting fork, a rotating shaft of rotating equipment is fixedly connected with the upper lifting lever, and a reset spring of the upper lifting lever enables the upper lifting lever to abut against the interior of the lower shifting fork in an inclined manner. The zero position keeping mechanism for forcing the valve body to be kept at the zero position is arranged on the right side of the valve body.
Description
Technical field
The present invention relates to a kind of switch valve, particularly relate to the electro-hydraulic high-speed switch valve of chute type 2D of band variable ratio drive mechanism.
Background technology
High-speed switch valve has become the important directions of Electro hydraulic Digital Control technology development, is widely used in the purposes such as aerospace field, hydraulic locking, engineering machinery and military affairs.In recent years, high-speed switch valve is as a pith of Electro hydraulic Digital Control technology, and as realizing the key element of Electro hydraulic Digital Control, it is had higher requirement, i.e. must have the advantages such as high pressure resistant, fast response time, flow big, good seal performance.
At present, high-speed switch valve is frequently with ball-valve type, side valve type and cone valve type valve core structure form.Ball-valve type valve core structure is simple, processing performance good, action is sensitiveer, stroke is short and dynamic property preferable, but spool is easily affected by hydraulic power, can only make little latus rectum valve.Side valve type spool easily obtains flow force compensation and hydro-cushion, but spool stroke is short, low-response, processing technique and assembly precision is low, poor sealing performance, can only require to select under low occasion to flow, pressure and sealing property at some.Relatively both compare cone valve type spool, the problems such as the short leakage rate of side valve type spool stroke is big can be overcome, the problem such as the hydraulic power of ball-valve type spool can also be overcome uneven, and there is the features such as fast response time, oil filling capacity is strong, good seal performance, contamination resistance are strong.But when being used in the special environment such as high pressure, high frequency sound for this type of valve, should ensure that reliable sealing property ensures that spool is not stuck again, high to requirement on machining accuracy, processing technique difficulty is big, and manufacturing cost is high, it is unfavorable for the extensive application of this type of valve.
In recent years, the electro-hydraulic high-speed switch valve of 2D utilizing servo screw mechanism principle to work has spool radial rotating and the double freedom moved axially, control is flexible, precision is high, frequency response is fast, low-hysteresis, leakage rate are little, advantages of simple structure and simple, currently mainly it is used in Aero-Space, the military field such as guided missile and mostly being under extreme environment.When being energized to the controller of the electro-hydraulic high-speed switch valve of 2D, utilize electromechanical converter to convert the electrical signal to mechanical signal, and pass to mechanical transmission mechanism, the driving moment that electromechanical converter exports is amplified and driven valve core rotation.But, relatively big to the spool difficulty of processing of this type of valve, the through hole that spool is provided with impact to spool under high pressure, high vibration is relatively big, reduces the rigidity of spool, easily fractures in through hole；And the plug of spool afterbody is easily rushed out in the case of hypertonia, cause destruction integrally-built to valve body.And under high pressure, " clamping " phenomenon of spool is easily caused flow and cannot rise.
Summary of the invention
For overcoming the problems referred to above, the present invention provides the electro-hydraulic high-speed switch valve of chute type 2D of a kind of band variable ratio drive mechanism.
The technical scheme is that
With the electro-hydraulic high-speed switch valve of chute type 2D of variable ratio drive mechanism, including valve body, drive the drive mechanism that valve body is opened and the Zero maintaining mechanism driving valve body to close；
Valve body includes the servo screw mechanism being made up of valve body and spool, spool is rotatably arranged in valve body, spool is sequentially provided with first shoulder, the second shoulder and the 3rd shoulder from left to right, airtight for body cavity enclosure is become sensitive cavity with first shoulder by the left end cap of valve body, airtight for body cavity enclosure cyclization is gone out oil pocket around the annular of spool by first shoulder and the second shoulder, the second shoulder and the 3rd shoulder by airtight for body cavity enclosure cyclization around the annular oil suction chamber of spool；
Oil suction chamber connects with the oil-in on valve body, and oil suction chamber is connected by the oil through on spool with spool；A pair axisymmetric pressure hole and a pair axisymmetric trough is had in first shoulder, and pressure hole and trough are arranged alternately, pressure hole connects with spool, the inwall of valve body is provided with a pair axisymmetric skewed slot, one end of skewed slot connects with sensitive cavity, the other end of skewed slot is positioned on the movement locus of pressure hole and the movement locus of trough, and sensitive cavity is connected with oil suction chamber with skewed slot by oil through, pressure hole；
Sensitive cavity is connected with going out oil pocket by trough, skewed slot, and goes out oil pocket and connect with the oil-out on valve body；Second shoulder length vertically is more than the diameter of oil-out, so that the second shoulder fully seals oil-out when spool is positioned at closed mode, and oil-out is positioned on the movement locus of the second shoulder；
It is arranged on the drive mechanism on the right side of valve body and includes directly on top upper driving lever and lower shift fork located directly below, the lower half ovalize of upper driving lever, the first half of lower shift fork is the U-shaped fork of opening upwards, the lower half of upper driving lever extends in the U-shaped fork of lower shift fork, the rotary shaft of rotating machinery is fixing with upper driving lever to be connected, to drive upper driving lever to drive lower shift fork to rotate, and the bottom of lower shift fork is fixed with the right-hand member of spool and is connected, with band movable valve plug synchronous axial system；The top of upper driving lever is slidably disposed on horizon bar, and one end of horizon bar is arranged with the upper driving lever back-moving spring that upper driving lever is pushed against zero-bit, and upper driving lever is tilted to be pushed against in lower shift fork by upper driving lever back-moving spring；
The right-hand member of spool runs through valve body, and the right side of valve body is provided with the Zero maintaining mechanism forcing valve body to keep zero-bit, described Zero maintaining mechanism includes the valve core reseting spring being set on spool, one end of valve core reseting spring is pushed against on the right flank of the 3rd shoulder, forcing the second shoulder to be positioned at above oil-out and seal hydraulic fluid port, the other end is pushed against on the jump ring being solidly set on spool.
Further, described rotating machinery is rotary magnet.
Further, being provided with high-pressure trough at the port of export of described pressure hole, pressure hole is connected with skewed slot by high-pressure trough, and the distance between trough with high-pressure trough is equal with the width of skewed slot.
Further, the right side of valve body is provided with connection seat, and Zero maintaining mechanism is arranged in connection seat, and drive mechanism is arranged on the connecting plate connected above seat, and described connection seat is tightly connected with valve body by the first sealing ring.
Further, the right-hand member of spool is tightly connected with being connected seat by the second sealing ring；Left end cap is tightly connected with valve body by the 3rd sealing ring.
Further, the left end of valve core reseting spring is pushed against on the right flank of the 3rd shoulder by spring base, and the right-hand member end of valve core reseting spring is pushed against on jump ring by spring pad, and spring base and the equal fixed cover of spring pad are located on spool.
Further, upper driving lever back-moving spring is pushed against on upper driving lever by pad, and described pad is slidably disposed on described horizon bar.
Further, the electro-hydraulic high-speed switch valve of chute type 2D of band variable ratio drive mechanism as claimed in claim 6, it is characterised in that: described connection seat and connecting plate are furnished with lid.
Further, described rotary magnet is arranged on the top of valve body, and is furnished with protective cover.
Further, described upper driving lever is by the first screws clamp on the output shaft of rotary magnet, and described lower shift fork passes through the second screws clamp on spool.
The technology of the present invention is contemplated that:
In order to make the electro-hydraulic high-speed switch valve of 2D have big flow, high frequency sound characteristic, in addition to except electromechanical converter to be ensured, i.e. rotary magnet has fast response characteristic, also should ensure that the axial displacement of spool of servo screw mechanism to having the characteristic of quickly response between rotational angle displacement, mechanical transmission mechanism also to meet the relatively large driving force square provided needed for spool operating in addition.
Servo screw mechanism be realize switch valve spool corner and axial straight-line displacement conversion lead control structure.Valve interior wall left end has skewed slot, and skewed slot g communicates with sensitive cavity f, the first shoulder of spool has two to axisymmetric high-pressure trough 1311 and trough b.High-pressure trough 1311 and trough b be all cross section be the groove of irregular parallelogram like, high-pressure trough 1311 and trough b are positioned at the both sides of skewed slot g, and the distance of high-pressure trough 1311 and trough b is equal with skewed slot width, to increase area gradient, meet the 2D big flow of electro-hydraulic high-speed switch valve, the requirement of high frequency sound.Spool is rotatably mounted in valve body, and one end of skewed slot g communicates with sensitive cavity f, and the other end constitutes resistance half-bridge with high-pressure trough 1311 and trough b, and resistance half-bridge controls the pressure in sensitive cavity f by skewed slot g.
In order to ensure that the electro-hydraulic high-speed switch valve of 2D has the characteristic of big flow, high frequency sound, must assure that rotational angle displacement can be made quickly response by the axial displacement of spool of hydraulic servo screw mechanism, hydraulic servo screw mechanism natural frequency depends on spool end sensitive cavity f volume and spool quality, it is the least that the construction features of the electro-hydraulic high-speed switch valve of 2D determines that its sensitive cavity f can design, thus its hydraulic natural frequency is the highest, about 104～105Hz.The highest hydraulic natural frequency makes order Oscillating not interfere with the dynamic response of spool, and the axially-movable of spool does not results in impact to the response of the angular signal of input, and order Oscillating can be simplified to inertial element.
Because the natural frequency of hydraulic servo screw mechanism is the highest, high-pressure trough 1311 and the trough b of design use plus lap mode with skewed slot, covering amount 0.003～0.007mm, can ensure that lead control level zero leakage amount the least, improve the conversion accuracy between spool corner displacement and axial displacement, and poppet shaft can be made very big to rigidity, be effectively improved the reliability and stability during work of 2D electro-hydraulic high-speed switch valve.
Chute type hydraulic servo screw mechanism has the highest automatically cleaning ability.As long as the one side in the parallelogram region that high-pressure trough 1311 and trough b are constituted with skewed slot is blocked, so dynamic balance of spool will be destroyed, and spool just carries out axially-movable, and in motor process, blocking area increases, can effective removing obstacles thing, contamination resistance is strong.
In order to improve the response speed of the present invention, it is necessary to improve the driving moment driving valve core rotation.The drive mechanism of design can make spool obtain infinitely-great driving moment when starting working.Gear ratio between the shift fork driving lever of design is infinitely great, output torque after rotary magnet energising, by shift fork driving lever drive mechanism, driving moment amplified infinite times and drive spool rapidly radially rotate and move axially, to overcome hydraulic card clamping force, improve the contamination resistance of valve, reduce spool machining accuracy.This drive mechanism may be equally applied to the electro-hydraulic high-speed switch valve of 3-position 4-way 2D.
The invention has the beneficial effects as follows:
1, have employed chute type hydraulic servo screw mechanism, high-pressure trough and trough with irregular parallelogram are simple with area increased gradient, fast response time and processing；
2, use the drive mechanism of variable ratio, effectively amplify the driving moment of spool, to overcome the hydraulic card clamping force at spool, reduce the input torque requirement to electromechanical converter simultaneously；
3, frequency response is fast, and dynamic property is good；
4, it is little that Zero maintaining mechanism rotary inertia is little, zero-bit leads control leakage rate, and precision is high；
5, simple in construction, processing cost is low；
6, low to oil filtrating required precision, contamination resistance is strong.
Accompanying drawing explanation
Fig. 1 is the structural principle schematic diagram of the present invention.
Fig. 2 is the enlarged diagram of high-pressure trough and trough.
Fig. 3 is the structural representation of spool.
Fig. 4 is servo screw mechanism principle schematic.
Fig. 5 be in Fig. 4 E-E to sectional view.
Fig. 6 is drive mechanism structural representation.
Detailed description of the invention
As it can be seen, the electro-hydraulic high-speed switch valve of chute type 2D of band variable ratio drive mechanism, including valve body, drive the drive mechanism that valve body is opened and the Zero maintaining mechanism driving valve body to close；
Valve body includes the servo screw mechanism being made up of valve body 22 and spool 13, spool 13 is rotatably arranged in valve body 22, spool 13 is sequentially provided with first shoulder the 131, second shoulder 132 and the 3rd shoulder 133 from left to right, the valve body 22 airtight enclosure of inner chamber is become sensitive cavity f with first shoulder 131 by the left end cap 24 of valve body 22, valve body 22 inner chamber airtight enclosure cyclization is gone out oil pocket m, the second shoulder 132 and the 3rd shoulder 133 by valve body 22 inner chamber airtight enclosure cyclization around the annular oil suction chamber n of spool 13 around the annular of spool 13 by first shoulder 131 and the second shoulder 132；
Oil suction chamber n connects with the oil inlet P on valve body 22, and oil suction chamber n is connected by the oil through c on spool 13 with spool 13；A pair axisymmetric pressure hole a and a pair axisymmetric trough b is had in first shoulder 131, and pressure hole and trough are arranged alternately, pressure hole a connects with spool 13, the inwall of valve body 22 is provided with a pair axisymmetric skewed slot g, one end of skewed slot g connects with sensitive cavity f, the other end of skewed slot g is positioned on the movement locus of pressure hole a and the movement locus of trough b, and sensitive cavity f is connected with oil suction chamber n with skewed slot g by oil through c, pressure hole a；
Sensitive cavity f is connected with going out oil pocket m by trough b, skewed slot g, and goes out oil pocket m and connect with the oil-out A on valve body 22；The second shoulder 132 length vertically diameter more than oil-out A, so that the second shoulder 132 fully seals oil-out A when spool 13 is positioned at closed mode, and oil-out A is positioned on the movement locus of the second shoulder 132；
It is arranged on the drive mechanism on the right side of valve body and includes directly on top upper driving lever 10 and lower shift fork 12 located directly below, the lower half ovalize of upper driving lever 10, the first half of lower shift fork 12 is the U-shaped fork of opening upwards, the lower half of upper driving lever 10 extends in the U-shaped fork of lower shift fork 12, the rotary shaft of rotating machinery is fixing with upper driving lever 10 to be connected, to drive upper driving lever 10 to drive lower shift fork 12 to rotate, and the bottom of lower shift fork 12 is fixed with the right-hand member of spool 13 and is connected, with band movable valve plug 13 synchronous axial system；The top of upper driving lever 10 is slidably disposed on horizon bar 2, and one end of horizon bar 2 is arranged with the upper driving lever back-moving spring 5 that upper driving lever 10 is pushed against zero-bit, and upper driving lever 10 is tilted to be pushed against in lower shift fork 12 by upper driving lever back-moving spring 5；
The right-hand member of spool 12 runs through valve body 22, and the right side of valve body 22 is provided with the Zero maintaining mechanism forcing valve body 22 to keep zero-bit, described Zero maintaining mechanism includes the valve core reseting spring 19 being set on spool 12, one end of valve core reseting spring 19 is pushed against on the right flank of the 3rd shoulder 133, forcing the second shoulder 132 be positioned at above oil-out A and seal hydraulic fluid port A, the other end is pushed against on the jump ring 17 being solidly set on spool 13.
Described rotating machinery is rotary magnet 9.
Being provided with high-pressure trough 1312 at the port of export of described pressure hole a, pressure hole a is connected with skewed slot by high-pressure trough, and the distance between trough 1311 with high-pressure trough 112 is equal with the width of skewed slot g.
The right side of valve body 22 is provided with connection seat, and Zero maintaining mechanism is arranged in connection seat, and drive mechanism is arranged on the connecting plate 1 connected above seat, and described connection seat is tightly connected with valve body 22 by the first sealing ring 21,
The right-hand member of spool 13 is tightly connected with being connected seat by the second sealing ring 16.
The left end of valve core reseting spring 19 is pushed against on the right flank of the 3rd shoulder 133 by spring base 20, and the right-hand member end of valve core reseting spring 19 is pushed against on jump ring 17 by spring pad 18, and spring base 20 and the equal fixed cover of spring pad 18 are located on spool 13.
Upper driving lever back-moving spring 5 is pushed against on driving lever 10 by pad 4, and described pad 4 is slidably disposed on described horizon bar 2.
Left end cap 24 is tightly connected with valve body 22 by the 3rd sealing ring 23.
Described connection seat and connecting plate are furnished with lid 11.
Described rotary magnet 9 is arranged on the top of valve body 22, and is furnished with protective cover 26.
Described upper driving lever 10 is clamped on the output shaft of rotary magnet 9 by the first screw 8, and described lower shift fork 12 is clamped on spool 13 by the second screw 14.
Rotary magnet 9 is connected with controller.
Described rotary magnet 9 is as the electromechanical converter of the present invention; it is positioned at above valve body 22; and be connected with connecting plate 1 by the first screw 28; protective cover 26 is connected with connecting plate 1 by the second screw 27; lid 11 is connected on protective cover 26 by the 3rd screw 3 simultaneously; the support 7 of horizon bar 2 is fixed on connecting plate 1 by the 3rd screw 6, and left end cap 24 is fixed on valve body 22 by the 4th screw 25.
(1) servo screw mechanism:
Servo screw mechanism is the Dao Kong mechanism realizing switch valve spool corner with axial straight-line displacement conversion, it includes valve body 22 and spool 13, spool 13, valve body 22 and left end cap 24 coordinate composition sensitive cavity f, the cross section of high-pressure trough 1311 and trough b is irregular parallelogram, high-pressure trough 1311 and trough b lay respectively at the both sides of skewed slot, and the distance between high-pressure trough 1311 and trough b is equal with the width of skewed slot g, to increase area gradient, reduce processing technique difficulty, realization meets the 2D big flow of electro-hydraulic high-speed switch valve, the requirement that frequency response is fast.One end of skewed slot g communicates with sensitive cavity f, and the other end constitutes resistance half-bridge with high-pressure trough 1311 and trough b, and resistance half-bridge controls the pressure in sensitive cavity f by skewed slot g.
When spool 13 is positioned at zero-bit (when the present invention is positioned at closed mode), the side of the second shoulder 132 fully seals oil-out A, one end of skewed slot g covers high-pressure trough 1311 and trough b simultaneously, and both area coverages are equal, and the other end of skewed slot g connects with sensitive cavity f.
Fluid is in oil inlet P enters oil suction chamber n, and the pressure in oil suction chamber n is p1null，Fluid in oil suction chamber n is in oil through c enters spool 22，And spill in high-pressure trough 1311 from pressure hole a，Fluid in high-pressure trough 1311 is in skewed slot g enters sensitive cavity f，Fluid in sensitive cavity f is in skewed slot g enters trough b，And enter out in oil pocket m from trough b，Owing to oil-out A seals，Fluid will not outflow，If do not consider frictional force and the impact of valve port hydraulic power when static state，High-pressure trough 1311、The area equation that trough b intersects respectively with skewed slot g，Pressure in sensitive cavity f only has the half of the pressure (system pressure) in oil suction chamber n，But the cross section setting sensitive cavity f is 2 times of the cross section of oil suction chamber n，The pressure at the two in then spool 13 lays respectively at sensitive cavity f and in oil suction chamber n is equal，Spool 13 axially retains static balance，Switch valve is in zero-bit state.
If spool 13 rotates, then on spool 13, high-pressure trough 1311 and trough b change with the area that intersects of skewed slot g on valve body 22, thus cause the pressure of sensitive cavity f to change, and the stress balance of spool 13 is destroyed, and spool 13 produces axially-movable therewith.
As shown in Figure 4, when drive mechanism drives spool 13 to rotate clockwise, the area that high-pressure trough 1311 intersects with skewed slot g reduces, the area that trough b and skewed slot g intersects increases, the pressure causing sensitive cavity f reduces, and spool 13 is to left movement, then the second shoulder 132 is removed from oil-out A, valve is opened, and fluid flows out.If spool 13 continues to rotate counterclockwise, high-pressure trough 1311 is gradually increased again with the area that intersects of skewed slot g, the area that intersects of trough b and skewed slot g is gradually reduced, until high-pressure trough 1311 and skewed slot g intersect area, trough b and skewed slot g crossing area the most equal time, spool 13 axial force balance, spool 13 stop motion, reenters poised state；Otherwise, when spool 13 counterclockwise rotates, above change procedure is just the opposite.Therefore, the present invention is to have the two-stage high-speed switch valve of double freedom of motion, it is linear relationship between spool angular displacement and axially displacement, the present invention utilizes rotary magnet and drive mechanism to drive spool to rotate, realize pilot valve function, spool is promoted to move axially under the effect of oil liquid pressure difference, it is achieved the high-speed opening and closing of valve port.
(2) drive mechanism
The rotation amplitude of rotary magnet 9 is 21 °, rotary magnet 9 drives upper driving lever 10 to rotate counterclockwise, then going up driving lever 10 drives lower shift fork 12 and spool 13 to rotate clockwise, and the area that high-pressure trough 1311 intersects with skewed slot g reduces, and the area that trough b and skewed slot g intersects increases, the pressure causing sensitive cavity f reduces, spool 13 is to left movement, then the second shoulder 132 is removed from oil-out A, and oil-out A is unimpeded, fluid flows out, thus the present invention is in open mode.
But frictional force, hydraulic power, greasy dirt and spool valve body machining accuracy etc. all can produce bigger resistance in the moment of valve core rotation, hydraulic pressure " clamping stagnation " phenomenon easily occurs, in order to make the present invention occur without hydraulic pressure " clamping stagnation " phenomenon, drive mechanism must have bigger moment in startup moment.
The drive mechanism of the present invention can realize torque-variable, the lower half ovalize of upper driving lever 10, to realize variable ratio, owing to the rotation amplitude of rotary magnet 9 is 21 °, assemble for convenience, and realize the symmetric design of upper driving lever 10, driving lever 10 and lower shift fork 12 center of rotation line 21 ° in initial makeup location (the i.e. zero-bit state) deviation of upper driving lever 10, upper driving lever 10 coordinates for linear contact lay between lower shift fork 12, and upper driving lever 10 intersects at R point and S point, as shown in Figure 5 respectively with lower shift fork 12.Now, the normal of contact point R is just past the center of rotation of upper driving lever 10, according to " Kennedy-Aronhold the-orem ", upper driving lever 10 overlaps with the relative instantaneous center of lower shift fork 12, the instantaneous transmission ratio of drive mechanism is infinitely great, lower shift fork 12 is equivalent to a shock response to the response of upper driving lever 10, and output torque is the biggest, it is sufficient to overcome hydraulic pressure " clamping stagnation " phenomenon.
Along with the continuation campaign of upper driving lever 10, relative instantaneous center is close to the center of rotation of lower shift fork 12.From instantaneous theorem, upper driving lever 10 is the respective center of rotation inverse ratio to instantaneous distance with the gear ratio of lower shift fork 12, and therefore gear ratio reduces therewith, but is sufficient for rotating torque required after spool 13 starts.
Compared with existing stable drive ratio drive mechanism, the drive mechanism of the present invention initially will produce infinitely-great moment, with hydraulic pressure " clamping stagnation " phenomenon overcoming the electro-hydraulic high-speed switch valve of 2D easily to be produced spool by problems such as frictional force, hydraulic power, greasy dirt and spool valve body machining accuracies in motion.
For ensureing to make spool 13 remain to be in zero-bit in the case of the controller of switch valve is not powered on or lost efficacy, installing shift fork back-moving spring 5 on horizon bar 2, back-moving spring 5, horizon bar 2 and pad 4 constitute the position-limit mechanism of upper shift fork.Upper shift fork can rotate counterclockwise upon actuation, and oppress upper shift fork back-moving spring 5 by pad 4, after upper shift fork turns to maximum position and stops operating, upper shift fork and back-moving spring 5 are in resting state, when controller power-off, shift fork back-moving spring 5 drives upper shift fork to reset.
In order to improve the job stability of the present invention, balance inertial force, need to be by the center superposition of the center of gravity of upper driving lever 10 and the first screw 8 Yu the armature spindle of rotary magnet 9, and spool 13 central shaft overlaps with the center of gravity of lower shift fork 12 and the second screw 14.
(3) Zero maintaining mechanism
Equipped with jump ring 17, spring pad 18, valve core reseting spring 19 and spring base 20 on spool 13, to prevent switch valve spool 13 play inside valve body 22 in transportation, when ensureing zeroing, spool 13 does stable axially-movable, prevent from colliding with valve body 22, and ensure that spool is in absolute zero position in the case of controller is not powered on simultaneously.
The moment that valve body is opened, spool is moved to the left, and oppresses valve core reseting spring 19, and when controller power-off, back-moving spring 19 drives spool 13 to move right and recovers zero-bit, and the present invention is closed.
In Fig. 1, T is oil return opening.
Content described in this specification embodiment is only enumerating of the way of realization to inventive concept; protection scope of the present invention is not construed as being only limitted to the concrete form that embodiment is stated, protection scope of the present invention also include those skilled in the art according to present inventive concept it is conceivable that equivalent technologies means.
Claims (10)
1. the electro-hydraulic high-speed switch valve of chute type 2D of band variable ratio drive mechanism, it is characterised in that: include valve body, the drive mechanism driving valve body to open and the Zero maintaining mechanism driving valve body to close；
Valve body includes the servo screw mechanism being made up of valve body and spool, spool is rotatably arranged in valve body, spool is sequentially provided with first shoulder, the second shoulder and the 3rd shoulder from left to right, airtight for body cavity enclosure is become sensitive cavity with first shoulder by the left end cap of valve body, airtight for body cavity enclosure cyclization is gone out oil pocket around the annular of spool by first shoulder and the second shoulder, the second shoulder and the 3rd shoulder by airtight for body cavity enclosure cyclization around the annular oil suction chamber of spool；
Oil suction chamber connects with the oil-in on valve body, and oil suction chamber is connected by the oil through on spool with spool；A pair axisymmetric pressure hole and a pair axisymmetric trough is had in first shoulder, and pressure hole and trough are arranged alternately, pressure hole connects with spool, the inwall of valve body is provided with a pair axisymmetric skewed slot, one end of skewed slot connects with sensitive cavity, the other end of skewed slot is positioned on the movement locus of pressure hole and the movement locus of trough, and sensitive cavity is connected with oil suction chamber with skewed slot by oil through, pressure hole；
Sensitive cavity is connected with going out oil pocket by trough, skewed slot, and goes out oil pocket and connect with the oil-out on valve body；Second shoulder length vertically is more than the diameter of oil-out, so that the second shoulder fully seals oil-out when spool is positioned at closed mode, and oil-out is positioned on the movement locus of the second shoulder；
It is arranged on the drive mechanism on the right side of valve body and includes directly on top upper driving lever and lower shift fork located directly below, the lower half ovalize of upper driving lever, the first half of lower shift fork is the U-shaped fork of opening upwards, the lower half of upper driving lever extends in the U-shaped fork of lower shift fork, the rotary shaft of rotating machinery is fixing with upper driving lever to be connected, to drive upper driving lever to drive lower shift fork to rotate, and the bottom of lower shift fork is fixed with the right-hand member of spool and is connected, with band movable valve plug synchronous axial system；The top of upper driving lever is slidably disposed on horizon bar, and one end of horizon bar is arranged with the upper driving lever back-moving spring that upper driving lever is pushed against zero-bit, and upper driving lever is tilted to be pushed against in lower shift fork by upper driving lever back-moving spring；
The right-hand member of spool runs through valve body, and the right side of valve body is provided with the Zero maintaining mechanism forcing valve body to keep zero-bit, described Zero maintaining mechanism includes the valve core reseting spring being set on spool, one end of valve core reseting spring is pushed against on the right flank of the 3rd shoulder, forcing the second shoulder to be positioned at above oil-out and seal hydraulic fluid port, the other end is pushed against on the jump ring being solidly set on spool.
2. the electro-hydraulic high-speed switch valve of chute type 2D of band variable ratio drive mechanism as claimed in claim 1, it is characterised in that: described rotating machinery is rotary magnet.
3. the electro-hydraulic high-speed switch valve of chute type 2D of band variable ratio drive mechanism as claimed in claim 2, it is characterized in that: at the port of export of described pressure hole, be provided with high-pressure trough, pressure hole is connected with skewed slot by high-pressure trough, and the distance between trough with high-pressure trough is equal with the width of skewed slot.
4. the electro-hydraulic high-speed switch valve of chute type 2D of band variable ratio drive mechanism as claimed in claim 3, it is characterized in that: the right side of valve body is provided with connection seat, Zero maintaining mechanism is arranged in connection seat, drive mechanism is arranged on the connecting plate connected above seat, and described connection seat is tightly connected with valve body by the first sealing ring.
5. the electro-hydraulic high-speed switch valve of chute type 2D of band variable ratio drive mechanism as claimed in claim 4, it is characterised in that: the right-hand member of spool is tightly connected with being connected seat by the second sealing ring；Left end cap is tightly connected with valve body by the 3rd sealing ring.
6. the electro-hydraulic high-speed switch valve of chute type 2D of band variable ratio drive mechanism as claimed in claim 5, it is characterized in that: the left end of valve core reseting spring is pushed against on the right flank of the 3rd shoulder by spring base, and the right-hand member end of valve core reseting spring is pushed against on jump ring by spring pad, spring base and the equal fixed cover of spring pad are located on spool.
7. the electro-hydraulic high-speed switch valve of chute type 2D of band variable ratio drive mechanism as claimed in claim 6, it is characterised in that: upper driving lever back-moving spring is pushed against on upper driving lever by pad, and described pad is slidably disposed on described horizon bar.
8. the electro-hydraulic high-speed switch valve of chute type 2D of band variable ratio drive mechanism as claimed in claim 7, it is characterised in that: described connection seat and connecting plate are furnished with lid.
9. the electro-hydraulic high-speed switch valve of chute type 2D of band variable ratio drive mechanism as claimed in claim 8, it is characterised in that: described rotary magnet is arranged on the top of valve body, and is furnished with protective cover.
10. the electro-hydraulic high-speed switch valve of chute type 2D of band variable ratio drive mechanism as claimed in claim 9, it is characterised in that: described upper driving lever is by the first screws clamp on the output shaft of rotary magnet, and described lower shift fork passes through the second screws clamp on spool.
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| CN201610339755.3A CN105822795B (en) | 2016-05-23 | 2016-05-23 | The electro-hydraulic high-speed switch valves of chute type 2D with variable ratio transmission mechanism |
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| CN201610339755.3A CN105822795B (en) | 2016-05-23 | 2016-05-23 | The electro-hydraulic high-speed switch valves of chute type 2D with variable ratio transmission mechanism |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106194879A (en) * | 2016-08-25 | 2016-12-07 | 浙江工业大学 | Direct Action Type 2D Electric hydraulic pressure servo valve |
| CN106438551A (en) * | 2016-08-25 | 2017-02-22 | 浙江工业大学 | Bourdon tube force feedback type 2D electrical-hydraulic pressure servo valve |
| CN107061796A (en) * | 2017-05-19 | 2017-08-18 | 浙江工业大学 | One kind rotation fork shift formula Multi-oil circuit hydraulic control switch |
| CN111102259A (en) * | 2018-10-25 | 2020-05-05 | 浙江工业大学 | Two-dimensional pulse width modulation mechanism |
| CN112555441A (en) * | 2020-10-30 | 2021-03-26 | 湖州职业技术学院 | Large-flow proportional throttle valve |
| CN115750902A (en) * | 2022-11-29 | 2023-03-07 | 富阳通力机械制造有限公司 | Two-dimensional electro-hydraulic proportional valve manual unloading structure for quick self-locking jack |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3517299B2 (en) * | 1995-03-14 | 2004-04-12 | 富士重工業株式会社 | Control device for continuously variable transmission |
| JP2012087854A (en) * | 2010-10-19 | 2012-05-10 | Nsk Ltd | Valve and toroidal continuously variable transmission |
| CN104455651A (en) * | 2014-10-25 | 2015-03-25 | 哈尔滨理大晟源科技开发有限公司 | Pneumatic high-speed switching valve and working method thereof |
| CN104896141A (en) * | 2014-03-08 | 2015-09-09 | 温州益坤电气有限公司 | High-oil-pressure and large-drift-diameter combined reversing valve for electric high-voltage switch hydraulic mechanism |
| CN105545852A (en) * | 2015-12-30 | 2016-05-04 | 浙江大学 | High-speed switch pilot proportioning valve |
| CN205781059U (en) * | 2016-05-23 | 2016-12-07 | 浙江工业大学 | The electro-hydraulic high-speed switch valve of chute type 2D with variable ratio drive mechanism |
-
2016
- 2016-05-23 CN CN201610339755.3A patent/CN105822795B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3517299B2 (en) * | 1995-03-14 | 2004-04-12 | 富士重工業株式会社 | Control device for continuously variable transmission |
| JP2012087854A (en) * | 2010-10-19 | 2012-05-10 | Nsk Ltd | Valve and toroidal continuously variable transmission |
| CN104896141A (en) * | 2014-03-08 | 2015-09-09 | 温州益坤电气有限公司 | High-oil-pressure and large-drift-diameter combined reversing valve for electric high-voltage switch hydraulic mechanism |
| CN104455651A (en) * | 2014-10-25 | 2015-03-25 | 哈尔滨理大晟源科技开发有限公司 | Pneumatic high-speed switching valve and working method thereof |
| CN105545852A (en) * | 2015-12-30 | 2016-05-04 | 浙江大学 | High-speed switch pilot proportioning valve |
| CN205781059U (en) * | 2016-05-23 | 2016-12-07 | 浙江工业大学 | The electro-hydraulic high-speed switch valve of chute type 2D with variable ratio drive mechanism |
Non-Patent Citations (1)
| Title |
|---|
| 江海兵等: "2D电液高速开关阀设计与实验", 《农业机械学报》 * |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106194879A (en) * | 2016-08-25 | 2016-12-07 | 浙江工业大学 | Direct Action Type 2D Electric hydraulic pressure servo valve |
| CN106438551A (en) * | 2016-08-25 | 2017-02-22 | 浙江工业大学 | Bourdon tube force feedback type 2D electrical-hydraulic pressure servo valve |
| CN106438551B (en) * | 2016-08-25 | 2018-01-05 | 浙江工业大学 | Bourdon tube force feedback type 2D Electric hydraulic pressure servo valves |
| CN106194879B (en) * | 2016-08-25 | 2018-01-05 | 浙江工业大学 | Direct Action Type 2D Electric hydraulic pressure servo valves |
| CN107061796A (en) * | 2017-05-19 | 2017-08-18 | 浙江工业大学 | One kind rotation fork shift formula Multi-oil circuit hydraulic control switch |
| CN107061796B (en) * | 2017-05-19 | 2023-01-10 | 浙江工业大学 | Rotary gear shifting type multi-oil-way hydraulic control switch |
| CN111102259A (en) * | 2018-10-25 | 2020-05-05 | 浙江工业大学 | Two-dimensional pulse width modulation mechanism |
| CN111102259B (en) * | 2018-10-25 | 2024-06-07 | 浙江工业大学 | Two-dimensional pulse width modulation mechanism |
| CN112555441A (en) * | 2020-10-30 | 2021-03-26 | 湖州职业技术学院 | Large-flow proportional throttle valve |
| CN112555441B (en) * | 2020-10-30 | 2022-06-17 | 湖州职业技术学院 | Large-flow proportional throttle valve |
| CN115750902A (en) * | 2022-11-29 | 2023-03-07 | 富阳通力机械制造有限公司 | Two-dimensional electro-hydraulic proportional valve manual unloading structure for quick self-locking jack |
| CN115750902B (en) * | 2022-11-29 | 2023-06-09 | 富阳通力机械制造有限公司 | Two-dimensional electro-hydraulic proportional valve manual unloading structure for quick self-locking jack |
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Effective date of registration: 20221021 Address after: 9th Floor, R&D Center, No. 399, Mingli South Road, Zhengzhou Economic and Technological Development Zone, 450000 Henan Province Patentee after: Henan Aerospace Fluid Control Technology Co.,Ltd. Address before: 310005 No. 1, Wuyi lane, Hushu South Road, Gongshu District, Hangzhou, Zhejiang Patentee before: Hangzhou Diwei Electrohydraulic digital control technology Co.,Ltd. |