CN200968336Y - New type two-stage electrohydraulic servo valve - Google Patents
New type two-stage electrohydraulic servo valve Download PDFInfo
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- CN200968336Y CN200968336Y CN 200620123532 CN200620123532U CN200968336Y CN 200968336 Y CN200968336 Y CN 200968336Y CN 200620123532 CN200620123532 CN 200620123532 CN 200620123532 U CN200620123532 U CN 200620123532U CN 200968336 Y CN200968336 Y CN 200968336Y
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Abstract
A novel two-stage electro-hydraulic servo valve relates to a hydraulic servo control system. Giant magnetostrictive force motor is connected with the valve body of the hydraulic amplifier by the force motor connection part. Under the pre-compression force action of the pre-stage slide valve resetting springs, The force motor drive pole of the giant magnetostrictive force motor keep contact with the pre-stage slide valve of the hydraulic amplifier. A seal ring is arranged between the force motor connection part and the valve body. Displacement mechanical feedback agency is installed in the corresponding hole on the valve body of the hydraulic amplifier, under the pre-compression action of the feedback spring, the feedback pole of the displacement mechanical feedback agency keeps contact with the cone section on the power stage slide valve of the hydraulic amplifier. Under the pre-compression action of the pre-stage valve sleeve resetting spring, the pre-stage valve sleeve of the hydraulic amplifier keeps contact with the cone section on the feedback pole of the displacement mechanical feedback agency. The response speed of the utility model is fast and the output flow can basically meet the requirements of all power stage hydraulic servo systems.
Description
Technical field
The utility model relates to a kind of electrohydraulic control that hydraulic servo control system uses.
Background technique
Electrohydraulic control is made up of force motor (or torque motor), hydraulic amplifier, feedback mechanism three parts usually as crucial control unit in the hydraulic servo control system.Present various types of electrohydraulic control, its force motor (or torque motor) all is according to electromagnetic principle, the electric control signal of input is converted to the power or the moment output of machinery, driving hydraulic amplifier generation hydraulic signal output is flow and pressure, and control oil hydraulic cylinder or fluid motor-driven load are according to the work that requires of hydraulic servo control system.The speed of response of this force motor (or torque motor) that utilizes electromagnetic principle work is than very fast, and generally its natural frequency can reach hundreds of Kilohertzs of going up, and directly drives the electrohydraulic control that hydraulic amplifier constitutes by it and is called the single-stage electrohydraulic control.The speed of response of single-stage electrohydraulic control can reach up to a hundred hertz.Because the intrinsic defect of this force motor (or torque motor) is that ouput force is smaller, generally be tens newton to the maximum, so the hydraulic pressure output power of single-stage electrohydraulic control is also very little, can only use at the small-power special occasions.For the big occasion of hydraulic pressure demanded power output, present electrohydraulic control generally adopts the scheme that increases hydraulic pressure preamplifier stage (abbreviation prestage), the output of force motor (or torque motor) after amplifying, prestage is removed to control hydraulic power amplifier stage (abbreviation power stage) again, to realize the high-power output of electrohydraulic control.Constitute secondary and three-stage electrical fluid servo valve thus, also be referred to as the multi-stage electro-hydraulic servovalve.Though by increasing prestage the output power of electrohydraulic control is improved, reduces the speed of response of electrohydraulic control simultaneously.So the bigger multi-stage electro-hydraulic servovalve of current power output, its response frequency is generally tens hertz, and maximum arrives up to a hundred hertz.
In recent years, along with a class has the development of the rare earth functional material of ultra-magnetic telescopic performance, a kind of ultra-magnetic telescopic force motor that is called has appearred.Compare with the force motor (or torque motor) of present electrohydraulic control, the major advantage of this ultra-magnetic telescopic force motor is: its speed of response is fast, and its natural frequency can reach thousands of hertz; Output drive strength is big, can reach hundreds of newton to thousands of newton.But because following technical problem underlying, make this ultra-magnetic telescopic force motor on electrohydraulic control, not obtain practical application as yet: the firstth, the big heat that the control coil winding of this ultra-magnetic telescopic force motor can produce at work, these heats are if can not effectively be controlled, to make the super magnetostriction material of ultra-magnetic telescopic force motor produce very big thermal deformation, may be suitable when thermal deformation is maximum with the mechanical displacement output magnitude of ultra-magnetic telescopic force motor, the technical requirements that makes the mechanical displacement output accuracy of ultra-magnetic telescopic force motor not reach electrohydraulic control far away.The secondth, this ultra-magnetic telescopic force motor its output mechanical displacement in certain range of structures is less, on electrohydraulic control, use and generally only be fit to be used for directly driving prestage, need to increase power stage and constitute the two-stage electrohydraulic control, to satisfy the requirement of the big output power of electrohydraulic control.The feedback mechanism of the electrohydraulic control of this use ultra-magnetic telescopic force motor is if adopt electric reaction type scheme, and the structure of electrohydraulic control is very complicated and huge with making, and functional reliability also will be affected; If adopt machine feedback formula scheme, because the output drive strength of ultra-magnetic telescopic force motor is very big, for electrohydraulic control organization plan commonly used at present, known various forms of machine feedback structures all can't realize.
The patent relevant with this ultra-magnetic telescopic force motor is: application number is that 200420021147 Chinese patent is a kind of utility model patent, and the model utility name is called the ultra-magnetostriction microdisplacement actuator.The driver that this patent provides is owing to be a kind of principle scheme, and for the heat that influences giant magnetostrictive rod output displacement accuracy by drive coil and bias coil produced, this driver has adopted a kind of phase-change material that is called to control, therefore in actual applications, reach the real coupling of parameter and need carry out the designing and calculating more complicated, also may cause activation configuration too complicated simultaneously, therefore on electrohydraulic control, be difficult to obtain practical application.
The model utility content
(1) technical problem that will solve
In order to solve the defective in the middle of the prior art, the purpose of this utility model is to provide a kind of speed of response faster, the novel two-stage electrohydraulic control that range of flow is wide.
(2) technological scheme
For achieving the above object, the scheme of the novel two-stage electrohydraulic control that the utility model provides is:
Novel two-stage electrohydraulic control of the present utility model comprises ultra-magnetic telescopic force motor, hydraulic amplifier, displacement mechanical feedback mechanism, wherein the ultra-magnetic telescopic force motor is connected with the valve body of hydraulic amplifier by the force motor link, be provided with seal ring between force motor link and the valve body, the displacement mechanical feedback mechanism is installed on the valve body of hydraulic amplifier.
The novel two-stage electrohydraulic control that the utility model provides, the scheme of its ultra-magnetic telescopic force motor has solved three technical problem underlying: the firstth, the heat control problem that coil winding produces; The secondth, the hot shape compensation problem that giant magnetostrictive rod produces; The 3rd is the inhomogeneous problem that influences the giant magnetostrictive rod displacement output ability of ultra-magnetic telescopic force motor controlling magnetic field and bias magnetic field.Ultra-magnetic telescopic force motor of the present utility model is by the force motor link, loaded spring, force motor driveshaft, the thermal distortion compensation sleeve pipe, giant magnetostrictive rod, coil rack, coil winding, the coil location nut, the force motor cover member, prestage zero adjusting screw, force motor coolant drain screw, Sealing, compositions such as bolt assembly.The utility model provides hydraulic medium to the cooling that circulates of ultra-magnetic telescopic force motor by hydraulic amplifier, thereby realized coil winding is produced the control of heat, the operating temperature of ultra-magnetic telescopic force motor inside is remained unchanged substantially, so the thermal deformation amount of giant magnetostrictive rod does not change substantially.For the thermal deformation that giant magnetostrictive rod produces, ultra-magnetic telescopic force motor of the present utility model mainly adopts the thermal distortion compensation sleeve pipe to become to carry out real-Time Compensation, makes the displacement output accuracy of ultra-magnetic telescopic force motor can satisfy the requirement of electrohydraulic control.Ultra-magnetic telescopic force motor of the present utility model only is provided with a coil winding, required controlling magnetic field and bias magnetic field are produced by same coil winding, bias magnetic field is provided by the normal value electrical signal that is added on the coil winding, and controlling magnetic field is provided by the control electrical signal that is superimposed upon normal value biased electrical signal.This scheme can make the coil winding internal diameter reach minimum substantially, help coil winding and on the giant magnetostrictive rod rod, produce controlling magnetic field uniformly, thereby the displacement output ability of giant magnetostrictive rod is fully used, has also simplified the structure and the volume of power ultra-magnetic telescopic motor simultaneously.
The novel two-stage electrohydraulic control that the utility model provides, the scheme of its hydraulic amplifier has solved three technical problem underlying: the firstth, because that the ultra-magnetic telescopic force motor has an output displacement is little and ouput force is big, how prestage output hydraulic power satisfies the problem that electrohydraulic control output hydraulic power wide variation is from small to large brought; The secondth since the ultra-magnetic telescopic force motor to have ouput force big, when realizing the power stage guiding valve to the displacement machine feedback of prestage, feedback element can't directly drive the problem of prestage guiding valve; The 3rd is that hydraulic amplifier provides the problem of cooling with hydraulic medium to the ultra-magnetic telescopic force motor.Hydraulic amplifier of the present utility model adopts the two poles of the earth slide-valve structure scheme, by valve body, and the prestage valve pocket, prestage guiding valve Returnning spring, prestage guiding valve, prestage valve pocket Returnning spring, power stage housing screw A, power stage guiding valve zero adjusting screw, power stage slide valve spring supporting element, power stage guiding valve centralizing spring, the power stage guiding valve, power stage valve pocket, power stage housing screw B, Sealing, compositions such as plug.Because the prestage of the utility model hydraulic amplifier adopts flow gain and the high slide-valve structure of Pressure gain, so the output hydraulic power scope of prestage is bigger, can satisfy the electrohydraulic control small-power and arrive the requirement that power changes on a large scale.The power stage guiding valve is provided with a conical section, drive the feedback rod that is in contact with it by this conical section, the displacement of power stage guiding valve is reduced into displacement on the feedback rod axial direction according to a certain percentage, can realizes a size and Orientation conversion of power stage spool displacement; Be provided with a conical section on the feedback rod, the prestage valve pocket that is in contact with it by this conical section driving, the displacement of feedback rod is reduced into displacement on the prestage valve pocket axial direction according to a certain percentage, can realizes the secondary size and Orientation conversion of power stage spool displacement.Because when the displacement of feeding back is added in when making itself and prestage sliding valve movement direction in the same way on the prestage valve pocket, this feedback effect and power stage guiding valve are equivalent to the reverse feedback of prestage guiding valve, therefore the utility model adopts the Displacement Feedback of the power stage guiding valve scheme to the prestage valve pocket, solved because of the output drive strength of ultra-magnetic telescopic force motor is very big, directly feedback drives the problem that the prestage guiding valve is difficult to realization.The utility model outputs to the ultra-magnetic telescopic force motor with the oil return hydraulic medium of hydraulic amplifier prestage, can realize the cooling to the ultra-magnetic telescopic force motor.
The novel two-stage electrohydraulic control that the utility model provides, its displacement mechanical feedback mechanism comprises feedback spring adjusting screw, feedback spring, feedback rod.Have following characteristics: prestage is the electrohydraulic control of sliding valve style at present, generally can only take displacement electricity feedback scheme, make the complex structure of servovalve, size increases, and at some thrust vectoring electrohydraulic servo-controlling system to the very big occasion of reliability effect of electrical type device such as guided missile, rocket, the reliability of electricity feedback is difficult to be guaranteed.The utility model adopts the mechanical type feedback scheme that is integrated in the hydraulic amplifier valve body, makes the compact structure of electrohydraulic control and has higher reliability.
The novel two-stage electrohydraulic control that the utility model provides, its working principle is: when the input control electrical signal of novel two-stage electrohydraulic control is zero, the ultra-magnetic telescopic force motor is output as zero to hydraulic amplifier prestage spool displacement, the prestage delivery pressure that is added in power stage guiding valve two ends equates, electrohydraulic control is in the zero-bit state, externally is output as zero.When the input control electrical signal of electrohydraulic control is non-vanishing, the ultra-magnetic telescopic force motor will produce a displacement output driving prestage guiding valve an opening amount, make the prestage delivery pressure that is added in power stage guiding valve two ends that a pressure reduction be arranged, the power stage guiding valve is setting in motion under the driving of this pressure reduction.Under the effect of conical section on the power stage guiding valve and feedback spring, feedback rod will be simultaneously along its axial-movement, the displacement of feedback rod is by the effect of conical section on the feedback rod and prestage valve pocket Returnning spring, driving the prestage valve pocket produces and the displacement in the same way of prestage sliding valve movement direction, prestage slide opening amount is reduced, thereby the prestage output pressure reduction that is added in power stage guiding valve two ends is reduced.When prestage is exported pressure reduction and acted on power stage guiding valve upper spring equilibrium of forces, the power stage guiding valve will stop at a certain position, and electrohydraulic control will have and input control corresponding output flow of electrical signal and pressure.
(3) beneficial effect
The advantage of novel two-stage electrohydraulic control described in the utility model with good effect is: this novel two-stage electrohydraulic control compares with present electrohydraulic control that performance is greatly improved aspect two: the firstth, and speed of response is faster, present electrohydraulic control, the speed of response of small flow be its amplitude-frequency bandwidth generally about 200Hz, big flow be generally tens Hz.The novel two-stage electrohydraulic control that provides of the present utility model, the amplitude-frequency bandwidth of small flow can reach more than the 400Hz, and the amplitude-frequency bandwidth of big flow is more than 100Hz.The secondth, not reducing substantially under the prerequisite of assurance speed of response, the scheme of the novel two-stage electrohydraulic control that the utility model provides can satisfy the requirement of present various power rank Hydrauservo Systems substantially.
Description of drawings
Fig. 1 is a structure principle chart of the present utility model;
Fig. 2 is a ultra-magnetic telescopic force motor structure principle chart of the present utility model;
Fig. 3 is the three-view diagram of force motor link of the present utility model;
Fig. 4 is the three-view diagram of thermal distortion compensation sleeve pipe of the present utility model;
Fig. 5 is a hydraulic amplifier structure principle chart of the present utility model;
Fig. 6 is a valve body structure schematic representation of the present utility model;
Fig. 7 is the three-view diagram of prestage valve pocket of the present utility model;
Fig. 8 is the three-view diagram of power stage guiding valve of the present utility model;
Fig. 9 is a displacement mechanical feedback mechanism structure principle chart of the present utility model;
Figure 10 is the valve body structure schematic representation of feedback rod of the present utility model.
1. ultra-magnetic telescopic force motors among the figure, 2. hydraulic amplifier, 3. displacement mechanical feedback mechanism, 4. valve body, 5. feedback spring adjusting screw, 6. feedback spring, 7. feedback rod, 8. prestage valve pocket, 9. prestage guiding valve Returnning spring, 10. prestage guiding valve, 11. prestage valve pocket Returnning springs, 12. force motor links, 13. loaded spring, 14. the force motor driveshaft, 15. thermal distortion compensation sleeve pipes, 16. giant magnetostrictive rods, 17. coil rack, 18. coil winding, 19. coil location nuts, 20. force motor cover member, 21. prestage zero adjusting screw, 22. power stage housing screw A, 23. power stage guiding valve zero adjusting screws, 24. power stage slide valve spring supporting elements, 25. power stage guiding valve centralizing spring, 26. the power stage guiding valve, 27. power stage valve pockets, 28. power stage housing screw B, 29. force motor coolant drain screw, 30. Sealing, 31. plugs, 32. bolt assemblies.
Embodiment
Below in conjunction with accompanying drawing, further describe the embodiment of novel two-stage electrohydraulic control described in the utility model, but be not used for limiting protection domain of the present utility model.
With reference to figure 1,2,5,9.Novel two-stage electrohydraulic control provided by the utility model is made up of ultra-magnetic telescopic force motor 1, hydraulic amplifier 2, displacement mechanical feedback mechanism 3 three parts.When realizing the utility model, ultra-magnetic telescopic force motor 1 is installed on the valve body 4 of two-stage sliding valve style hydraulic amplifier 2 by the screw thread 33 of force motor link 12, in the hole 51 of displacement mechanical feedback mechanism 3 integral installations on the valve body 4 of two-stage sliding valve style hydraulic amplifier 2.
When realizing the utility model, the installation step of novel two-stage electrohydraulic control is:
Assemble ultra-magnetic telescopic force motor 1 according to Fig. 2;
Be assembled to displacement mechanical feedback mechanism 3 other parts except feedback spring adjusting screw 5 on the valve body 4 of hydraulic amplifier 2 according to Fig. 1 and Fig. 9;
Assemble hydraulic amplifier 2 according to Fig. 5;
Be assembled to ultra-magnetic telescopic force motor 1 on the valve body 4 of hydraulic amplifier 2 according to Fig. 1;
The feedback spring adjusting screw 5 of displacement mechanical feedback mechanism 3 is assembled on the valve body 4 of hydraulic amplifier 2 according to Fig. 1 and Fig. 9.
When realizing the utility model, the zero-bit set-up procedure of novel two-stage electrohydraulic control is:
Finish the assembling of novel two-stage electrohydraulic control according to the installation step of novel two-stage electrohydraulic control;
Adjust the zero-bit of the prestage guiding valve 10 of hydraulic amplifier 2, concrete steps are:
Remove the plug 31 of hydraulic amplifier 2, two prestage guiding valve zero-bit adjusting process holes 50 on the valve body 4 join with flow transducer respectively;
Block two delivery outlets 71 of novel two-stage electrohydraulic control with the test frock;
The charge oil pressure of adjusting pilot system is a low pressure for example about 5MPa, and to novel electrohydraulic control input hydraulic pressure working medium;
Ultra-magnetic telescopic force motor 1 input constant direct current biasing electrical signal to novel two-stage electrohydraulic control;
Measure the flow of above-mentioned two flow transducers;
Judge the direction of prestage guiding valve zero drift according to the measured value of flow, thereby determine the direction that prestage guiding valve 10 positions should be adjusted;
Regulate the prestage zero adjusting screw 21 of ultra-magnetic telescopic force motor 1 and the measured value of two flow transducers of Real Time Observation, till it equates, finish the adjustment of prestage guiding valve 10 zero-bits;
The plug 31 of hydraulic amplifier 2 is assembled back novel two-stage electrohydraulic control;
Remove the test frock of the delivery outlet of novel two-stage electrohydraulic control.
Adjust the zero-bit of the power stage guiding valve 26 of hydraulic amplifier 2, concrete steps are:
Two delivery outlets 71 of novel two-stage electrohydraulic control are joined with flow transducer respectively;
The charge oil pressure of adjusting pilot system is for example 5～10MPa of low pressure, and to novel electrohydraulic control input hydraulic pressure working medium;
Ultra-magnetic telescopic force motor 1 input constant direct current biasing electrical signal to novel two-stage electrohydraulic control;
Detect the measured discharge of above-mentioned two flow transducers;
Judge the zero drift direction of the power stage guiding valve 26 of hydraulic amplifier 2 according to the flow measured value, thereby determine the direction that the position of power stage guiding valve 26 should be adjusted;
Regulate the measured value of power stage guiding valve zero adjusting screw 20 and two flow transducers of Real Time Observation, till it equates, finish the adjustment of power stage guiding valve 26 zero-bits.
When realizing the utility model, force motor link 12 should have feature shown in Figure 3: force motor link 12 adopts engage thread to be connected with the valve body 4 of hydraulic amplifier 2, the part that force motor link 12 embeds valve body 4 is provided with outside thread 33, and valve body 4 corresponding mounting holes are tapped hole 34.Seal with seal ring between force motor link 12 and the valve body 4.On force motor link 12 and the end plane that valve body 4 contacts circular groove 36 shown in Figure 4 should be set, be provided with some through holes 37 in the circular groove 36, circular groove 36 is in order to the return line 35 of communicating groove inner via hole 37 with valve body 4.The latus rectum of the physical dimension of circular groove 36 and through hole 37 and quantity should satisfy following condition: the area of passage of circular groove 36 is its sectional area prestage that should be not less than hydraulic amplifier 2 when maximum oil return flow, the area of passage of prestage guiding valve 10 throttling windows; The prestage that the total sectional area of through hole 37 should be not less than hydraulic amplifier 2 when maximum oil return flow, make a slip of the tongue 2 times of flow area of prestage guiding valve 10 throttle window.The part that force motor link 12 is embedded into valve body 4 should be provided with through hole shown in Figure 4 a group 38, in order to link up prestage valve pocket Returnning spring 11 at installation cavity on the valve body 4 39 and loaded spring 13 mounting hole 41 on force motor link 12.The quantity of through hole 38 and latus rectum should satisfy following condition: the prestage that the total sectional area of through hole 38 should be not less than hydraulic amplifier 2 when maximum oil return flow, the area of passage of prestage guiding valve 10 throttling windows.Rectangular flange dish 40 (also can according to circumstances be set to circle) is set on the force motor link 12 to be connected by bolt assembly 32 with thermal distortion compensation sleeve pipe 15, the end face of flange plate 40 is provided with sealing with circular groove 42, is used for installing between force motor link 12 and thermal distortion compensation sleeve pipe 15 Sealing 30.
When realizing the utility model, force motor link 12 also can adopt the flange mode to be connected with the valve body 4 of hydraulic amplifier 2.With reference to figure 3, should remove and increase structure characteristic flange plate 70 this moment with the structure characteristic screw thread 33 on the force motor link 12, flange plate 70 shapes can be rectangle or circle, size is determined according to actual conditions, connection on the flange plate 70 should evenly be arranged with through hole, be generally 4, can certainly be provided with as the case may be; Corresponding therewith, on valve body 4 and face that the flange plate 70 of force motor link 12 contacts, the position tapped hole identical with quantity should be set.
When realizing the utility model, the thermal distortion compensation sleeve pipe 15 of ultra-magnetic telescopic force motor 1 should have feature shown in Figure 4: thermal distortion compensation sleeve pipe 15 is provided with flange plate 43 with force motor link 12 connecting ends; The shape of flange plate 43 and be used for the position of the through hole of construction bolt assembly 32 should be consistent with quantity with the flange plate 40 of force motor link 12.Thermal distortion compensation sleeve pipe 15 is provided with flange plate 43, and flange plate 43 two sides are provided with a circular groove 44 and 45 respectively, is provided with one group of through hole 46 in the circular groove 44.Circular groove 44 is in order to communicating groove inner via hole 46.The area of passage of circular groove 44 is its sectional area prestage that should be not less than hydraulic amplifier 2 when maximum oil return flow, the area of passage of prestage guiding valve 10 throttling windows; The prestage that the total sectional area of through hole 46 should be not less than hydraulic amplifier 2 when maximum oil return flow, make a slip of the tongue 2 times of flow area of prestage guiding valve 10 throttle window.Circular groove 45 is used for installing Sealing 30 between thermal distortion compensation sleeve pipe 15 and force motor cover member 20.Coil rack 17 is installed on thermal distortion compensation sleeve pipe 15, coil rack 17 left ends contact with the flange plate of thermal distortion compensation sleeve pipe 15, right-hand member contacts with the coil location nut 19 that is installed in thermal distortion compensation sleeve pipe 15 tail ends, coil winding 18 is installed on the coil rack 17, force motor cover member 20 is installed in coil winding 18 outsides, links together by bolt assembly 32 and force motor link 12 and thermal distortion compensation sleeve pipe 15; Force motor coolant drain screw 29 is installed on the force motor cover member 20.The bushing outer surface that thermal distortion compensation sleeve pipe 15 contacts with coil rack 17 is a hierarchic structure 47, forms a circular gap between hierarchic structure 47 and coil rack 17 inner hole surface, for the hydraulic pressure cooling medium of ultra-magnetic telescopic force motor provides passage.Thermal distortion compensation sleeve pipe 15 afterbodys circumferentially evenly are provided with one group of through hole 51 near the ladder position, so that the hydraulic pressure cooling medium flows into the inner space of thermal distortion compensation sleeve pipe 15, the giant magnetostrictive rod 16 that is installed in the thermal distortion compensation sleeve pipe 15 are cooled off.The area of passage of circular gap is its sectional area prestage that should be not less than hydraulic amplifier 2 when maximum oil return flow between hierarchic structure 47 and coil rack 17 inner hole surface, the area of passage of prestage guiding valve 10 throttling windows; The latus rectum of through hole 51 and quantity should satisfy following condition: the prestage that the total sectional area of all through holes should be not less than hydraulic amplifier 2 when maximum oil return flow, make a slip of the tongue 2 times of flow area of prestage guiding valve 10 throttle window.Boots 50 are supported along circumferentially evenly being provided with 4 in the inner space of thermal distortion compensation sleeve pipe 15, the gap of supporting between boots 50 and the giant magnetostrictive rod 16 is less, can realize the passage that forms the hydraulic pressure cooling medium between the boots 50 is supported in the radial location of giant magnetostrictive rod 16 and axially directed.The prestage that the sectional area of passage should be not less than hydraulic amplifier 2 when maximum oil return flow, make a slip of the tongue 2 times of flow area of prestage guiding valve 10 throttle window.On the afterbody multidiameter shaft of thermal distortion compensation sleeve pipe 15 outside thread 48 is set, is used to install coil location nut 19, realize fixing coil rack 17.The afterbody of thermal distortion compensation sleeve pipe 15 is provided with internal thread through hole 49 along axis, is used to install prestage zero adjusting screw 21.
When realizing the utility model, the valve body 4 of hydraulic amplifier 2 should have feature shown in Figure 6: hole 54 axis of axis, power stage valve pocket 27 that the hole 52 of prestage valve pocket 8 is installed on the valve body 4 are parallel to each other, the hole 56 with displacement mechanical feedback mechanism 3 is a step hole respectively, and the axis in hole 56 should vertical mutually and coplane; The oil feed line 57 of prestage guiding valve 10 communicates with the oil feed line 58 of power stage guiding valve 26 in valve body 4.The return line 35 of prestage guiding valve 10 should be provided with separately, does not allow to communicate with the return line 59 of power stage guiding valve 26, in order to avoid the oil return of power stage guiding valve 26 influences the cooling of the oil return of prestage guiding valve 10 to ultra-magnetic telescopic force motor 1 because of its pressure is higher.Valve body 4 is provided with two prestage guiding valve zero-bit adjusting process holes 55, and this hole is a tapped hole, communicate with two output tubes 60 tunnel of prestage guiding valve 10 respectively, and during electrohydraulic control work, these two prestage guiding valve zero-bit adjusting process holes plug 31 shutoff.When force motor removes screw thread 33 and when increasing flange plate 70, the tapped hole 34 on the valve body 4 should be unthreaded hole.Valve body 4 can be designed to monolithic construction shown in Figure 6, also can according to circumstances be designed to split formula structure, promptly is made up of two-part up and down.For example can be by shown in Figure 6, along the A-A face separately, upper part is used to install prestage hydraulic amplifier, ultra-magnetic telescopic force motor 1 and displacement mechanical feedback mechanism 3, is called upper valve body; Lower part installation power level hydraulic amplifier is called valve body down.Upper valve body can be connected with screw with following valve body; Install on the surface of contact seal arrangement should be set, sealing means is generally end face seal.When valve body 4 was made up of upper valve body and following valve body two-part, aforementioned prestage guiding valve zero-bit adjusting process hole should be arranged on the upper valve body.
When realizing the utility model, the prestage valve pocket 7 of hydraulic amplifier 2 should have feature shown in Figure 9: prestage valve pocket 8 is the pipe fitting of an end opening one end sealing, closed end is provided with the minor axis 62 that contacts with conical section 53 on the feedback rod 7, and the minor axis end is a smooth sphere 61.Prestage valve pocket 8 time move in work, and in order to reduce the friction of its motion, under the situation of physical dimension permission, the structure that other positions on its external cylindrical surface outside the throttling window should be designed to step type as far as possible is to reduce the area of contact with valve body 4.Between prestage valve pocket 8 and the valve body 4 Sealing is not set, in order to avoid influence the kinematic dexterity of prestage valve pocket 8.
When realizing the utility model, the power stage guiding valve 26 of hydraulic amplifier 2 should have feature shown in Figure 8: power stage guiding valve 26 is provided with four steps 63, is provided with smooth conical section 64 between two steps of left end; The external cylindrical surface of each step of power stage guiding valve 26 is provided with the annular balancing slit 65 that 3～5 sections are rectangle; Power stage guiding valve 26 two ends are provided with the minor axis 66 that power stage guiding valve centralizing spring 25 is led.Power stage valve pocket 27 is installed in the hole 54 of valve body 4, two ends, the left and right sides compress the location by power stage housing screw B28 and power stage housing screw A22 respectively, power stage guiding valve 26 is installed in the power stage valve pocket 27, two ends, the left and right sides contact with power stage guiding valve centralizing spring 25 respectively, centralizing spring 25 is supported by power stage slide valve spring supporting element 24, and power stage slide valve spring supporting element 24 is supported by the power stage guiding valve zero adjusting screw 23 that is installed in its right-hand member.
When realizing the utility model, the feedback rod 7 of displacement mechanical feedback mechanism 3 should have feature shown in Figure 10: the end that the conical section 64 on the power stage guiding valve 26 of feedback rod 7 paths part and hydraulic amplifier 2 contacts is a sphere 67; Feedback rod 7 large-diameter portion branches are provided with between 68, two steps of two steps and are provided with smooth conical section 53; Feedback rod 7 tops are provided with the minor axis 69 that feedback spring 6 is led, and the monolateral gap of minor axis and feedback spring 6 should be not less than 0.2mm, when avoiding feedback rod 7 motion may and feedback spring 6 between produce friction.
When realizing the utility model, with reference to figure 8 and Figure 10, the cone angle of conical section 53 is α on the feedback rod 3
1, the cone angle of conical section 64 is α on the power stage guiding valve 26
2α
1, α
2Setting method be: suppose that power stage guiding valve 26 to the Displacement Feedback coefficient of prestage guiding valve 10 is K
Fb, α then
1, α
2Should satisfy following formula:
tgα
1·tgα
2＝K
fb
According to following formula α can be set
1, α
2The time, generally should make α
2＜α
1
When realizing the utility model, with reference to figure 1 and Fig. 5, the prestage guiding valve 10 of hydraulic amplifier 2 is except keeping the reliable mode that contacts with the force motor actuator 14 of ultra-magnetic telescopic force motor 1 by the pre-compression force of prestage guiding valve Returnning spring 9, also can adopt directly fixing mode such as thread connecting mode, interference fit etc., link together with force motor actuator 14, prestage guiding valve Returnning spring 9 can remove at this moment.When adopting directly fixing mode to be connected with force motor actuator 14, should be before being installed in ultra-magnetic telescopic force motor 1 on the valve body 4, earlier prestage guiding valve 10 is installed on the force motor actuator 14 of ultra-magnetic telescopic force motor 1, then ultra-magnetic telescopic force motor 1 is installed on the valve body 4.
More than be preferred forms of the present utility model, according to the disclosed content of the utility model, some identical, replacement schemes that those of ordinary skill in the art can expect apparently all should fall into the scope that the utility model is protected.
Claims (10)
1. novel two-stage electrohydraulic control, comprise ultra-magnetic telescopic force motor (1), hydraulic amplifier (2), displacement mechanical feedback mechanism (3), it is characterized in that: ultra-magnetic telescopic force motor (1) is connected with the valve body (4) of hydraulic amplifier (2) by force motor link (12), be provided with seal ring (31) between force motor link (12) and the valve body (4), displacement mechanical feedback mechanism (3) is installed on the valve body (4) of hydraulic amplifier (2).
2. a kind of novel two-stage electrohydraulic control according to claim 1, it is characterized in that: ultra-magnetic telescopic force motor (1) comprises force motor link (12), loaded spring (13), force motor driveshaft (14), thermal distortion compensation sleeve pipe (15), giant magnetostrictive rod (16), coil rack (17), coil winding (18), coil location nut (19), force motor cover member (20), prestage zero adjusting screw (21), force motor coolant drain screw (29), Sealing (30), bolt assembly (32); Giant magnetostrictive rod (16) is installed in the thermal distortion compensation sleeve pipe (15), loaded spring (13) is being installed between force motor link (12) and the force motor driveshaft (14), force motor driveshaft (14) contacts with giant magnetostrictive rod (16) left end, the prestage zero-bit is adjusted nut (21) and is installed in thermal distortion compensation sleeve pipe (15) afterbody, and contact with the right-hand member of giant magnetostrictive rod (16), coil rack (17) is installed on the thermal distortion compensation sleeve pipe (15), left end contacts with the flange plate of thermal distortion compensation sleeve pipe (15), right-hand member contacts with the coil location nut (19) that is installed in thermal distortion compensation sleeve pipe (15) tail end, coil winding (18) is installed on the coil rack (17), force motor cover member (20) is installed in coil winding (18) outside, links together by bolt assembly (32) and force motor link (12) and thermal distortion compensation sleeve pipe (15); Force motor coolant drain screw (29) is installed on the force motor cover member (20).
3. a kind of novel two-stage electrohydraulic control according to claim 2, it is characterized in that: the interior part of tapped hole (34) that force motor link (12) is installed in the valve body (4) of hydraulic amplifier is provided with outside thread (33), force motor link (12) is provided with a circular groove (36) with the end face that valve body (4) outer surface contacts, be provided with one group of through hole (37) in the circular groove (36) and link up the prestage return tube (35) of hydraulic amplifier (2), one group of through hole (38) is set on the end face of screw thread (33) part links up the installation cavity (39) that the valve body (4) of hydraulic amplifier (2) is gone up prestage Returnning spring (11), force motor link (12) is provided with flange plate (40), force motor link (12) is provided with the mounting hole (41) of loaded spring, and force motor link (12) is provided with sealing circular groove (42) at flange plate (40) end face.
4. a kind of novel two-stage electrohydraulic control according to claim 2, it is characterized in that: thermal distortion compensation sleeve pipe (15) is provided with flange plate (43), flange plate (43) two sides is provided with respectively and is provided with circular groove (44) and (45), circular groove (44) is provided with one group of through hole (46), the bushing outer surface that contacts with coil rack (17) is hierarchic structure (47), thermal distortion compensation sleeve pipe (15) afterbody is provided with outside thread (48), the axis of tail end face upper edge thermal distortion compensation sleeve pipe (15) is provided with an internal thread through hole (49), the internal cavity of thermal distortion compensation sleeve pipe (15) supports boots (50) along circumferentially evenly being provided with 4, and thermal distortion compensation sleeve pipe (15) is provided with one group of through hole (51) in hierarchic structure (47) near outside thread (48) position.
5. a kind of novel two-stage electrohydraulic control according to claim 1, it is characterized in that: hydraulic amplifier (2) comprises valve body (4), prestage valve pocket (8), prestage guiding valve Returnning spring (9), prestage guiding valve (10), prestage valve pocket Returnning spring (11), power stage housing screw A (22), power stage guiding valve zero adjusting screw (23), power stage slide valve spring supporting element (24), power stage guiding valve centralizing spring (25), power stage guiding valve (26), power stage valve pocket (27), power stage housing screw B (28), Sealing (30), plug (31); Prestage valve pocket (8) is installed in the hole (52) of valve body (4), left end contacts with conical section (53) on the feedback rod (7), right-hand member contacts with prestage valve pocket Returnning spring (11), the right-hand member of prestage valve pocket Returnning spring (11) contacts with force motor link (12), prestage guiding valve Returnning spring (9) is installed in prestage valve pocket (8) endoporus, its left end contacts with prestage valve pocket (8) endoporus bottom, right-hand member contacts with prestage guiding valve (10) left end, prestage guiding valve (10) right-hand member contacts with force motor link (12) left end of ultra-magnetic telescopic force motor (1), power stage valve pocket (27) is installed in the hole (54) of valve body (4), two ends, the left and right sides compress the location by power stage housing screw B (28) and power stage housing screw A (22) respectively, power stage guiding valve (26) is installed in the power stage valve pocket (27), two ends, the left and right sides contact with power stage guiding valve centralizing spring (25) respectively, the power stage guiding valve centralizing spring (25) of power stage guiding valve (26) left end is supported by power stage housing screw B (28), the power stage guiding valve centralizing spring (25) of power stage guiding valve (26) right-hand member is supported by power stage slide valve spring supporting element (24), power stage slide valve spring supporting element (24) is supported by the power stage guiding valve zero adjusting screw (23) that is installed in its right-hand member, and plug (31) is installed in the prestage guiding valve zero-bit adjusting process hole (55) on the valve body (4).
6. a kind of novel two-stage electrohydraulic control according to claim 5, it is characterized in that: the parallel axes in the axis in the hole (52) of valve body (4) last installation prestage valve pocket (8) and the hole (54) of installation power level valve pocket (27), and the axis in the hole (56) of the axis of hole (52) and hole (54) and installation position telephone-moving tool feedback mechanism (3) is in same plane, and with the axis normal of hole (56), hole (56) is a step hole, the hydraulic medium input pipeline (57) of prestage guiding valve (10) and the hydraulic medium input pipeline (58) of power stage guiding valve (24) are in valve body (4) internal communication, be respectively arranged with prestage return line (35) and power stage return line (59) on the valve body (4), two pipelines do not allow to link up, valve body (4) is provided with prestage guiding valve zero-bit adjusting process hole (55), communicate with two output pipes (60) of prestage guiding valve (10) respectively, prestage guiding valve zero-bit adjusting process hole (55) is a tapped hole.
7. a kind of novel two-stage electrohydraulic control according to claim 5, it is characterized in that: prestage valve pocket (8) is the pipe fitting of an end opening one end sealing, closed end has the minor axis (61) that contacts with conical section on the feedback rod (7), and the minor axis end is smooth sphere (62).
8. a kind of novel two-stage electrohydraulic control according to claim 5, it is characterized in that: power stage guiding valve (26) is provided with four steps (63), between two steps of left end, be provided with a smooth conical section (64), the external cylindrical surface of step (63) is provided with the annular balancing slit (65) that 3～5 sections are rectangle, and power stage guiding valve (26) two ends are provided with minor axis (66).
9. a kind of novel two-stage electrohydraulic control according to claim 1, it is characterized in that: displacement mechanical feedback mechanism (3) comprises feedback spring adjusting screw (5), feedback spring (6), feedback rod (7); Feedback rod (7) is installed in valve body (4) and goes up in the vertical hole (56) of left end, and feedback rod (7) top is equipped with feedback spring (6), and feedback spring (6) is provided support by the feedback spring adjusting screw (5) of portion mounted thereto.
10. a kind of novel two-stage electrohydraulic control according to claim 9, it is characterized in that: the end that feedback rod (7) contacts with conical section (64) on the power stage guiding valve (26) is smooth sphere (67), feedback rod (7) is provided with two steps (68), be provided with conical section (53) between two steps, feedback rod (7) top is provided with minor axis (69).
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| CN 200620123532 CN200968336Y (en) | 2006-08-04 | 2006-08-04 | New type two-stage electrohydraulic servo valve |
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| Application Number | Priority Date | Filing Date | Title |
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| CN 200620123532 CN200968336Y (en) | 2006-08-04 | 2006-08-04 | New type two-stage electrohydraulic servo valve |
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| CN200968336Y true CN200968336Y (en) | 2007-10-31 |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102242744A (en) * | 2011-07-11 | 2011-11-16 | 南京航空航天大学 | Double-nozzle type giant magnetostrictive jet servo valve and working method |
| CN105090562A (en) * | 2014-05-21 | 2015-11-25 | 株式会社京浜 | Fluid pressure control device |
| CN106415025A (en) * | 2014-04-10 | 2017-02-15 | 伍德沃德有限公司 | Servo valve |
| CN106762925A (en) * | 2017-03-13 | 2017-05-31 | 上海衡拓液压控制技术有限公司 | The integrated jet pipe servo valve of dual master control valve |
| CN107638611A (en) * | 2017-10-31 | 2018-01-30 | 湖南中医药大学 | A kind of electronic infusion device of novel non-contact |
| CN109372813A (en) * | 2018-11-30 | 2019-02-22 | 武汉船用机械有限责任公司 | A kind of electro-hydraulic proportional throttle valve and its control method |
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2006
- 2006-08-04 CN CN 200620123532 patent/CN200968336Y/en not_active Expired - Fee Related
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102242744A (en) * | 2011-07-11 | 2011-11-16 | 南京航空航天大学 | Double-nozzle type giant magnetostrictive jet servo valve and working method |
| CN102242744B (en) * | 2011-07-11 | 2014-01-29 | 南京航空航天大学 | Double-nozzle type giant magnetostrictive jet servo valve and working method |
| CN106415025A (en) * | 2014-04-10 | 2017-02-15 | 伍德沃德有限公司 | Servo valve |
| CN105090562A (en) * | 2014-05-21 | 2015-11-25 | 株式会社京浜 | Fluid pressure control device |
| CN105090562B (en) * | 2014-05-21 | 2018-01-05 | 株式会社京浜 | Hydraulic control device |
| CN106762925A (en) * | 2017-03-13 | 2017-05-31 | 上海衡拓液压控制技术有限公司 | The integrated jet pipe servo valve of dual master control valve |
| CN107638611A (en) * | 2017-10-31 | 2018-01-30 | 湖南中医药大学 | A kind of electronic infusion device of novel non-contact |
| CN109372813A (en) * | 2018-11-30 | 2019-02-22 | 武汉船用机械有限责任公司 | A kind of electro-hydraulic proportional throttle valve and its control method |
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Granted publication date: 20071031 Termination date: 20120804 |