CN100441887C - Hydraulic pressure servo valve - Google Patents
Hydraulic pressure servo valve Download PDFInfo
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- CN100441887C CN100441887C CNB2006101248870A CN200610124887A CN100441887C CN 100441887 C CN100441887 C CN 100441887C CN B2006101248870 A CNB2006101248870 A CN B2006101248870A CN 200610124887 A CN200610124887 A CN 200610124887A CN 100441887 C CN100441887 C CN 100441887C
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- spool
- valve body
- filter
- left end
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Abstract
A servo valve of water pressure consists of permanent magnet torque motor, pre-amplification unit and sliding valve power unit. It is featured as arranging filter stopper at two ends of filtering screen end to form concentric circular seam between said stopper and valve body, opening valve body fixed damping hole at valve body between said stopper and valve bush, using water contained in gap between spool and valve bush to form fixed liquid resistance and spool static pressure support of pre -amplification unit.
Description
Technical field
The invention belongs to the hydraulic pressure servo control element, be specifically related to a kind of hydraulic pressure servo valve.
Background technique
The mechanical development in the meeting of Japanese oily pneumatics association on July 8th, 1993, the pure a kind of employing servovalve of water as medium from the beginning of having introduced in mountain pass of Japan Yokohama national university, overall structure and structure of the present invention are roughly suitable, torque motor partly adopts the permanent magnetism moving-iron type, the displacement of spool is mainly regulated by the equalising torque at feedback rod and spool two ends, just spool travel mainly is to measure by displacement transducer, feed back to torque motor then so that regulate by feedback rod, from the filter to the spray nozzle front end, adopt the one-level throttling, spool and valve pocket adopt tightening seal, and the zero-bit distance of nozzle and baffle plate reaches 0.3mm.According to the test report, mainly there are following problems in this kind scheme: stability is not very good, and the characteristic of low aperture is bad, and the viscosity of water is low to cause decay not enough, the servovalve control characteristic is bad, and it is too serious to cavitate, and leakage rate is big, life-span is too short, and response frequency is not too high, has only 25Hz.And general servovalve mainly is to work near zero aperture, cavitation erosion be servovalve work to avoid as far as possible, so this servovalve does not have great actual utility.
No matter be domestic or external on the whole, the research of doing about hydraulic pressure servo valve at present is not a lot, and the result is not very desirable.
Summary of the invention
The invention provides a kind of hydraulic pressure servo valve, purpose is the leakage rate that reduces hydraulic pressure servo valve, reduces the wearing and tearing of spool and valve pocket, reduces cavitation phenomenon, improves servovalve working stability and response frequency.
A kind of hydraulic pressure servo valve of the present invention, form by permanent magnetic torque motor, preposition enlarged portion and guiding valve power section, the armature component of permanent magnetic torque motor is made up of feedback rod, baffle plate, armature, bourdon tube, the bourdon tube upper end is built in the armature mesopore, the baffle plate upper end is fixed in the bourdon tube mesopore, the feedback rod upper end is fixed in the baffle plate mesopore, and the coil that is wrapped on the armature is connected with extraneous power supply by power cord connector; Preposition enlarged portion comprises the filter that is fixed in the valve body, filter screen termination, left end nozzle and the right-hand member nozzle at filter two ends; The guiding valve power section comprises valve body, valve pocket, spool, and spool is built in valve pocket, and valve pocket is fixed in the valve body, and valve body has front cover and rear end cover, and spool interrelates by described feedback rod and armature component; It is characterized in that:
(1), filter retaining head is housed at the two ends, filter screen termination of filter, form concentric gap between filter retaining head and the valve body; Have fixedly damping hole of valve body on the valve body between valve pocket and the filter retaining head;
(2), have the gap between spool and the valve pocket, existing aqueous medium constitutes the fixer resistance of preposition enlarged portion and the hydrostatic support of spool in this gap.
Described hydraulic pressure servo valve is characterized in that: the zero-bit distance between described preposition enlarged portion left end nozzle, right-hand member nozzle and the baffle plate is 0.15～0.2mm; The material of described spool is a pottery, and the material of valve pocket is engineering plastics.
The present invention compares with the pure hydraulic pressure servo valve of studying in mountain pass: the mountain pass is pure has only a filter screen termination damping hole, is equivalent to the one-level throttling; The present invention forms concentric gap and filter screen termination damping hole composition two-step throttle at the two ends of filter between filter retaining head and the valve body, therefore have stronger anti-cavitation erosion ability.The high pressure water of input port P of the present invention can be guided to the two ends of spool by the gap between spool and the valve pocket, like this when spool when move on the left side, the formed low pressure of spool right-hand member cavity just can be entered by high pressure water and wherein play pressure compensated effect, and pure spool and the valve pocket in mountain pass adopts tightening seal, all there is not high pressure water to replenish even form lower pressure at the spool two ends, the water at spool two ends is owing to low pressure causes cavitation phenomenon like this, and therefore structure of the present invention has better anti-cavitation erosion ability.The present invention has fixedly damping hole of valve body on the valve body between valve pocket and the filter retaining head, can suppress cavitation phenomenon greatly, because the enhancing of anti-cavitation erosion ability, drift is little just littler with the impact shock acceleration action so, will improve the control accuracy of hydraulic pressure servo valve like this, the material with spool makes pottery into simultaneously thereupon, and the material of valve pocket makes engineering plastics into, help to reduce the frictional force of valve pocket and spool like this, reduce wearing and tearing.Zero-bit distance between left end nozzle of the present invention, right-hand member nozzle and the baffle plate is reduced to 0.15～0.2mm, helps reducing leakage rate.Because above-mentioned improvement, the result of test shows: the characteristic linearity of the pressure-flow of system of the present invention is better, thereby improved the dynamic performance of hydraulic pressure servo valve on the whole, advantage such as have system works pressure height (14Mp), flow big (100L/min), anti-cavitation erosion ability is strong, wear extent is little, leakage rate is little, efficient is high, the linearity is good, drift is little, the influence of impact shock acceleration is little.
Description of drawings
Fig. 1 is the schematic perspective view of one embodiment of the invention;
Fig. 2 is the stereogram of valve body;
Fig. 3 is the right elevation that Fig. 1 removes two end cap;
Fig. 4 is the schematic representation of the A-A section of Fig. 3;
Fig. 5 is the enlarged view of first part 7 among Fig. 4;
Fig. 6 is the enlarged view of second part 16 among Fig. 4;
Fig. 7 is the right elevation that Fig. 1 removes torque motor and coil case part;
Fig. 8 is the B-B sectional drawing of Fig. 7;
Fig. 9 is the C-C sectional drawing of Fig. 7;
Figure 10 is the D-D sectional drawing of Fig. 7;
Figure 11 is the schematic representation of the spool that shifts out from embodiment, valve pocket, sealing retaining head;
Figure 12 is the schematic representation of the E-E section half-twist of Figure 11;
Figure 13 is the stereogram of permanent magnetic torque motor;
Figure 14 is the right elevation of Figure 13;
Figure 15 is the schematic representation of the F-F section half-twist of Figure 14;
Figure 16 is the schematic representation of left and right end nozzle;
Figure 17 is the G-G generalized section of Figure 16;
Figure 18 is the schematic representation of filter retaining head;
Figure 19 is the left view of Figure 18.
Being designated among the figure: front cover 1, power cord connector 2, coil case 3, rear end cover 4, valve body 5, coil 6, first partial enlarged drawing 7, magnet 8, valve pocket 9, spool retaining 10, spool 11, left end first cavity volume 12, left end second cavity volume 13, right-hand member first cavity volume 14, right-hand member second cavity volume 15, second partial enlarged drawing 16, feedback groove 17, sealing retaining 18, filter retaining 19, filter screen termination 20, left end nozzle 21, elongated hole 22, filter 23, filter screen termination damping hole 24, a filter retaining recess 25, solid of rotation cavity volume 26, concentric gap 27, a filter retaining cavity volume 28, gross porosity 29, valve body rectangular window 30, cylinder type passage 31, feedback rod 32, baffle plate 33, armature 34, bourdon tube 35, left end nozzle exocoel 36, nozzle circular channel 37, left end nozzle ante-chamber 38, left end nozzle 39, right-hand member nozzle 40, right-hand member nozzle ante-chamber 41, valve body is damping hole 42 fixedly, right-hand member first rectangular window 43, valve pocket right-hand member cavity volume 44, right-hand member circular channel 45, right-hand member second rectangular window 46, left end second rectangular window 47, left end circular channel 48, valve pocket left end cavity volume 49, left end is damping hole 50 fixedly, spool left end cavity 51, left end first rectangular window 52, spool right-hand member cavity 53.
Embodiment
The present invention is made up of permanent magnetic torque motor, preposition enlarged portion and guiding valve power section, Figure 1 shows that front cover 1, rear end cover 4, the valve body 5 of power cord connector 2, coil case 3 and the guiding valve power section of permanent magnetic torque motor.
Fig. 2 is the stereogram of valve body 5, and valve body 5 bottom surfaces have input port P, output port T, left control port A and right control port B.
As Fig. 4, Fig. 7, Fig. 8, shown in Figure 10,9 one-tenth interference fit of valve body 5 and valve pocket, valve pocket 9 is slidingly matched for 11 one-tenth with spool, the spool two ends are by spool retaining 10 and extraneous sealing, spool retaining 10 is fixing by screw and front cover 1, rear end cover 4, has fixedly damping hole 42 of valve body on the valve body 5 between valve pocket 9 and the filter retaining 19, and cylinder type passage 31 usefulness on the valve body 5 seal keeps off 18 and seal, sealing retaining 18 and 5 one-tenth interference fit of valve body, and be screwed with front cover 1.
As Fig. 4, shown in Figure 5, left end nozzle 21 and right-hand member nozzle 40 become the center to be symmetrically distributed with feedback rod 32 axis, left end nozzle 21, right-hand member nozzle 40 all with 5 one-tenth interference fit of valve body.
As the bulb part of Fig. 6 feedback rod 32 lower ends and the feedback groove 17 no gap engagements of spool 11.
As shown in Figure 8, the 5 one-tenth interference fit in filter screen termination 20 and valve body, 20 one-tenth interference fit of filter 23 and filter screen termination, filter retaining 19 front end and filter screen termination 20 1 ends force together, and filter retaining 19 front end center and filter screen termination 20 mesopores are to the heart, filter retaining 19 rear end by bolt in front cover 1 and rear end cover 4, composition concentric gap 27 between filter retaining 19 and the valve body 5.
As shown in figure 12, valve pocket 9 bilateral symmetry have the fixedly fixing damping hole 53 of damping hole 50 and right-hand member of left end; Also have the symmetrical rectangular window of four groups of circle distribution on the valve pocket 9, two groups of left end are respectively left end first rectangular window 52, left end second rectangular window 47, and correspondingly right-hand member is respectively right-hand member first rectangular window 43, right-hand member second rectangular window 46 for two groups; Also have the circular channel of circle distribution on the valve pocket 9 symmetrically, be respectively left end circular channel 48, right-hand member circular channel 45.
As shown in figure 15, the armature component of permanent magnetic torque motor is made up of feedback rod 32, baffle plate 33, armature 34, bourdon tube 35, armature 34 mesopores become interference fit with bourdon tube 35 upper end external diameters, bourdon tube 35 mesopores become interference fit with baffle plate 33 upper end external diameters, and baffle plate 33 mesopores become interference fit with feedback rod 32 upper ends.
Figure 16, Figure 17 shows that left and right end nozzle, is example with the left end nozzle, nozzle circular channel 37, left end nozzle ante-chamber 38, left end nozzle 39.
Specific implementation process of the present invention is as follows: as shown in Figure 5, when not giving the permanent magnetic torque motor signal, be wrapped in coil 6 no electric circuits on the armature 34, magnet 8 makes the suffered power in armature 34 two ends equate, therefore armature 34 does not deflect, baffle plate 33 is in the neutral position of left end nozzle 21 and right-hand member nozzle 40, the pressure of the pressure of left end nozzle ante-chamber 38 and right-hand member nozzle ante-chamber 41 equates, the pressure that with water is carrier passes to as Fig. 4 and spool 11 two ends shown in Figure 12, the pressure of spool left end cavity 51 and spool right-hand member cavity 53 equates, spool 11 mediates motionless, left end first rectangular window 52 on the valve pocket 9, left end second rectangular window 47, right-hand member first rectangular window 43, right-hand member second rectangular window 46 is shut by spool 11, does not have water source output.When giving the permanent magnetic torque motor signal, as shown in Figure 5, coil 6 energisings, when the controlled deflection left of armature 34, the and then deflection left of baffle plate 33 upper ends, the deflection to the right of baffle plate 33 lower ends, cause liquid flowing resistance to strengthen by right-hand member nozzle 40, the liquid flowing resistance of corresponding left end nozzle 21 reduces, then the pressure of the left end nozzle ante-chamber 38 of the right nozzle ante-chamber 41 pressure ratio correspondences is big, pressure is that carrier passes to as Fig. 4 and spool left end cavity 51 and spool right-hand member cavity 53 shown in Figure 12 with water, make pressure ratio spool left end cavity 51 big of spool right-hand member cavity 53, spool 11 will be moved to the left like this, left end on the valve pocket 9 first rectangular window 52 is just opened a part so, right-hand member second rectangular window 46 on the valve pocket 9 is also opened a part, the size that these two rectangular windows are opened part is the same, the water source is behind input port P process cylinder type cavity volume 31 as shown in Figure 8 like this, most of valve body rectangular window 30 through the valve body two ends, flow to left end first cavity volume 12 that valve body as shown in Figure 45 and valve pocket 9 form, flow to the valve pocket left end cavity volume 49 of spool 11 and valve pocket 9 formation again through left end first rectangular window 52 of part unlatching as shown in figure 12, the left end circular channel 48 that has from valve pocket 9 flows to left control port A then, flows to extraneous load left end again; Then through right control port B process right-hand member second cavity volume 15, the right-hand member circular channel 45 that has from valve pocket 9 enters valve pocket right-hand member cavity volume 44 to the water of extraneous load right-hand member, flows to output port T by right-hand member second rectangular window 46 of opening a part then simultaneously.The water of another fraction is through as shown in Figure 8 gross porosity 29, flow to filter 23, flow to the left and right respectively again, the water that flows to left end flows to a filter retaining recess 25 through filter screen termination damping hole 24, flow to valve body 5 and filter screen termination 20 and filter retaining 19 a solid of rotation cavity volume 26 that form again, current flow to valve body 5 from filter retaining 19 and concentric gap 27 between the valve body 5 and keep off a cavity volume 28 with filter retaining 19 filter that form then, stream separated into two parts then: a part is through flows through elongated bore 22, flow to left end nozzle shown in Figure 5 21 and valve body 5 formed left end nozzle exocoels 36, flow into left end nozzle ante-chamber 38 through nozzle circular channel 37 then, flow to left end nozzle 39 at last until baffle plate 33; Another part through as shown in figure 10 valve body fixedly damping hole 42 flow into left end second cavity volume 13 that valve bodies 5 shown in Figure 4 and valve pocket 9 form, then by the left end on the valve pocket 9 fixedly damping hole 50 flow to spool left end cavity 51.Flow to the passage that the water that flows to right-hand member after the filter 23 more also experiences same symmetry and flow to right-hand member nozzle 40 and spool right-hand member cavity 53.
When the controlled deflection to the right of armature 34, as a same reason, just the pressure of left end nozzle ante-chamber 38 is greater than the pressure of right-hand member nozzle ante-chamber 41, cause the pressure of spool left end cavity 51 pressure greater than spool right-hand member cavity 53, spool 11 just moves right like this, then correspondingly right-hand member first rectangular window 43 on the valve pocket 9 and left end second rectangular window 47 are opened same size, the water of extraneous load left end flows to valve pocket left end cavity volume 49 through left control port A through the left end circular channel 48 on the valve pocket 9, flow to output port T through left end second rectangular window 47 of opening a part, and the water of input port P passes through right-hand member first rectangular window 43 on the valve pocket 9 successively from right-hand member first cavity volume 14, valve pocket right-hand member cavity volume 44, right-hand member circular channel 45, right-hand member second cavity volume 15 shown in Figure 4, flow to right control port B, flow to extraneous load right-hand member at last.When signal code changed, corresponding variation also took place in the displacement of spool 11 and output flow.Signal code is bigger, and spool 11 displacements are also bigger, thereby output flow is also bigger.
Claims (2)
1. hydraulic pressure servo valve, form by permanent magnetic torque motor, preposition enlarged portion and guiding valve power section, the armature component of permanent magnetic torque motor is made up of feedback rod, baffle plate, armature, bourdon tube, the bourdon tube upper end is built in the armature mesopore, the baffle plate upper end is fixed in the bourdon tube mesopore, the feedback rod upper end is fixed in the baffle plate mesopore, and the coil that is wrapped on the armature is connected with extraneous power supply by power cord connector; Preposition enlarged portion comprises the filter that is fixed in the valve body, filter screen termination, left end nozzle and the right-hand member nozzle at filter two ends; The guiding valve power section comprises valve body, valve pocket, spool, and spool is built in valve pocket, and valve pocket is fixed in the valve body, and valve body has front cover and rear end cover, and spool interrelates by described feedback rod and armature component; It is characterized in that:
(1), filter retaining head is housed at the two ends, filter screen termination of filter, form concentric gap between filter retaining head and the valve body; Have fixedly damping hole of valve body on the valve body between valve pocket and the filter retaining head;
(2), have the gap between spool and the valve pocket, existing aqueous medium constitutes the fixer resistance of preposition enlarged portion and the hydrostatic support of spool in this gap.
2. hydraulic pressure servo valve as claimed in claim 1 is characterized in that: the zero-bit distance between described preposition enlarged portion left end nozzle, right-hand member nozzle and the baffle plate is 0.15～0.2mm; The material of described spool is a pottery, and the material of valve pocket is engineering plastics.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2006101248870A CN100441887C (en) | 2006-10-30 | 2006-10-30 | Hydraulic pressure servo valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB2006101248870A CN100441887C (en) | 2006-10-30 | 2006-10-30 | Hydraulic pressure servo valve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1959130A CN1959130A (en) | 2007-05-09 |
| CN100441887C true CN100441887C (en) | 2008-12-10 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2006101248870A Expired - Fee Related CN100441887C (en) | 2006-10-30 | 2006-10-30 | Hydraulic pressure servo valve |
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Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102146690B (en) * | 2011-01-28 | 2012-09-05 | 徐州工程学院 | Control method for excavation force of hydraulic control vibration excavator and special servo valve |
| CN105570219A (en) * | 2014-10-11 | 2016-05-11 | 北京精密机电控制设备研究所 | Split type filter throttling device for servo valve |
| CN105041753A (en) * | 2015-08-21 | 2015-11-11 | 华中科技大学 | Water pressure servo valve |
| CN105909587A (en) * | 2016-07-06 | 2016-08-31 | 上海衡拓液压控制技术有限公司 | Force feedback structure for electro-hydraulic servo valve |
| CN106247003B (en) * | 2016-07-26 | 2018-06-26 | 安徽理工大学 | A kind of spool and valve pocket friction subcomponent and preparation method thereof |
| CN107061398B (en) * | 2016-12-20 | 2018-05-22 | 华中科技大学 | A kind of high-pressure high-flow electric-gas servo proportion |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH109437A (en) * | 1996-06-25 | 1998-01-13 | Ebara Corp | Hydraulic servo valve |
| JPH1026251A (en) * | 1996-07-11 | 1998-01-27 | Ebara Corp | Fluid pressure solenoid proportion control valve |
| JP2000283112A (en) * | 1999-03-31 | 2000-10-13 | Kawasaki Steel Corp | Hydraulic servo valve |
| CN1434218A (en) * | 2003-02-25 | 2003-08-06 | 吉林大学 | Novel nozzle baffle-plate type servo valve |
| US6648014B1 (en) * | 1999-09-01 | 2003-11-18 | Ebara Corporation | Fluid control valve and plate with filter |
| CN200975376Y (en) * | 2006-11-24 | 2007-11-14 | 华中科技大学 | Water pressure servo valve |
-
2006
- 2006-10-30 CN CNB2006101248870A patent/CN100441887C/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH109437A (en) * | 1996-06-25 | 1998-01-13 | Ebara Corp | Hydraulic servo valve |
| JPH1026251A (en) * | 1996-07-11 | 1998-01-27 | Ebara Corp | Fluid pressure solenoid proportion control valve |
| JP2000283112A (en) * | 1999-03-31 | 2000-10-13 | Kawasaki Steel Corp | Hydraulic servo valve |
| US6648014B1 (en) * | 1999-09-01 | 2003-11-18 | Ebara Corporation | Fluid control valve and plate with filter |
| CN1434218A (en) * | 2003-02-25 | 2003-08-06 | 吉林大学 | Novel nozzle baffle-plate type servo valve |
| CN200975376Y (en) * | 2006-11-24 | 2007-11-14 | 华中科技大学 | Water pressure servo valve |
Non-Patent Citations (2)
| Title |
|---|
| 水压与油压对称伺服阀控制单出杆液压缸特性的比较分析. 吴正江，聂松林，陈春，朱玉泉.液压与气动, 2005年 03期. 2005 |
| 水压与油压对称伺服阀控制单出杆液压缸特性的比较分析. 吴正江，聂松林，陈春，朱玉泉.液压与气动, 2005年 03期. 2005 * |
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| CN1959130A (en) | 2007-05-09 |
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