CN203685739U - Servo valve based on speed difference dynamic pressure feedback hydraulic control guide level - Google Patents
Servo valve based on speed difference dynamic pressure feedback hydraulic control guide level Download PDFInfo
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- CN203685739U CN203685739U CN201420010655.2U CN201420010655U CN203685739U CN 203685739 U CN203685739 U CN 203685739U CN 201420010655 U CN201420010655 U CN 201420010655U CN 203685739 U CN203685739 U CN 203685739U
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- 238000013016 damping Methods 0.000 claims abstract description 34
- 230000008713 feedback mechanism Effects 0.000 claims abstract description 16
- 239000000945 filler Substances 0.000 claims description 10
- 239000002828 fuel tank Substances 0.000 claims description 7
- 238000000034 method Methods 0.000 description 18
- 238000006073 displacement reaction Methods 0.000 description 8
- 238000003032 molecular docking Methods 0.000 description 5
- 238000004088 simulation Methods 0.000 description 4
- 230000001276 controlling effect Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 230000007246 mechanism Effects 0.000 description 3
- 230000001105 regulatory effect Effects 0.000 description 3
- 238000004080 punching Methods 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000001970 hydrokinetic effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000013507 mapping Methods 0.000 description 1
- 238000004886 process control Methods 0.000 description 1
- 230000035939 shock Effects 0.000 description 1
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Abstract
The utility model discloses a servo valve based on a speed difference dynamic pressure feedback hydraulic control guide level. The servo valve comprises a dynamic pressure feedback mechanism, a hydraulic control guide valve, a pressure adjusting valve and a main valve element. The dynamic pressure feedback mechanism comprises a plunger cylinder, first damping and second damping. The body of the plunger cylinder is provided with a feedback pressure port. One end of the first damping is communicated with an oil inlet of guide oil, and the other end of the first damping is communicated with the body of the plunger cylinder. One end of the second damping is communicated with an oil tank, and the other end of the second damping is communicated with the body of the plunger cylinder. The body of the plunger cylinder is communicated with a first control cavity of the hydraulic control guide valve through the feedback pressure port. The inlet of the pressure adjusting valve is communicated with the oil inlet of the guide oil, and the outlet of the pressure adjusting valve is communicated with a second control cavity of the hydraulic control guide valve. A port A of the hydraulic control guide valve is communicated with a lower control cavity of the main valve element, a port B of the hydraulic control guide valve is communicated with an upper control cavity of the main valve element, a port P of the hydraulic control guide valve is communicated with the oil inlet of the guide oil, and a port T of the hydraulic control guide valve is communicated with the oil tank.
Description
Technical field
The utility model relates to a kind of servovalve, relate in particular to a kind of applicable to fields such as punching press, hydraulic actuator docking in order to realize the servovalve of actuator's preacceleration control procedure.
Background technique
In stamping line, often adopt hydraulic cushion pad (abbreviation hydraulic die cushion) to reduce the collision impact of stamping process, as shown in Figure 1, the way that hydraulic die cushion is commonly used is to adopt the form of many group servovalve control oil hydraulic cylinders to form a servo-fluid pressure pad.In a press cycle, the variable such as pressure, displacement that servo-fluid pressure pad need to be controlled oil hydraulic cylinder 17 by electrohydraulic control 16 is accurately realized the desired pressure of stamping process, displacement.Impact for the impact pressure that reduces drawing moment, servo-fluid pressure pad need to have preacceleration function to eliminate the impact that the drawing stage sets up moment.Like this, in whole work cycle, automatical control system need to be controlled electrohydraulic control 16 and realize the displacement of oil hydraulic cylinder 17, speed, three state variables of pressure, especially in the preacceleration stage, automatical control system need to be switched to speed control from displacement control, then switches the pressure-pad-force control in drawing stage, the repeatedly switching control problem of existence variable, performance requirement to controller and electrohydraulic control 16 is higher, and the good effect of more difficult acquisition.In addition, adopt the form of electrohydraulic control control oil hydraulic cylinder to need the feedback of speed sensor as controlled variable in the preacceleration stage, multiple links adopt automatical control system, poor reliability.
For this reason, solve the shock problem that traditional control mode produces in preacceleration control procedure, and the integrity problem of electrohydraulic servo-controlling system, it is necessary that development can realize the machinery Hydraulic Servo valve of preacceleration process control automatically.
Model utility content
The purpose of this utility model is to provide a kind of servovalve based on speed difference dynamic pressure feedback fluid-control pilot stage, and it can realize the preacceleration under the operating modes such as hydraulic die cushion automatically without the conversion through automatical control system.
For achieving the above object, technical solution adopted in the utility model is:
The utility model comprises dynamic pressure feedback mechanism based on speed difference dynamic pressure feedback fluid-control guide servovalve, hydraulic control pilot valve, pressure regulator valve and main valve plug, described dynamic pressure feedback mechanism comprises plunger case, the first damping and the second damping, the cylinder body of described plunger case is provided with feedback pressure mouth, one end of the first damping is communicated with the filler opening of guide oil, the other end of the first damping is communicated with the cylinder body of plunger case, one end of the second damping is communicated with fuel tank, the other end of the second damping is communicated with the cylinder body of plunger case, the cylinder body of described plunger case is communicated with the first control chamber of hydraulic control pilot valve by feedback pressure mouth, the entrance of pressure regulator valve and the filler opening of guide oil
be communicated with, the outlet of pressure regulator valve is communicated with the second control chamber of hydraulic control pilot valve, and the A mouth of hydraulic control pilot valve is communicated with the control cavity of resorption of main valve plug, and the B mouth of hydraulic control pilot valve is communicated with the control epicoele of main valve plug, the P mouth of hydraulic control pilot valve and with the filler opening of guide oil
be communicated with, the T mouth of hydraulic control pilot valve is communicated with described fuel tank.
In dynamic pressure feedback of the present utility model mechanism, the pressure of the rodless cavity of (when stable state) plunger case when regulating between plunger rod that the first damping and the second damping can adjustable column plug cylinder and cylinder body without speed difference, and make the speed difference between the spool travel of hydraulic control pilot valve and the plunger rod of piston cylinder and cylinder body linear.
Further, the utility model is provided with the first spring and the second spring between the spool of described hydraulic control pilot valve and valve body, and the first spring and the second spring are placed in the both sides of spool of described hydraulic control pilot valve so that this spool centering.
Further, pressure regulator valve described in the utility model is reduction valve, and the outlet pressure of this reduction valve is constant, adjustable, is used for setting pilot valve the second control chamber pressure.
Further, the speed difference between the spool travel of hydraulic control pilot valve described in the utility model and the plunger rod of piston cylinder and cylinder body is linear.
Further, hydraulic control pilot valve described in the utility model is Proportional valve or servovalve.
Further, main valve plug described in the utility model is Twoway valves or three-way valve.
Compared with background technique, the utlity model has useful effect and be:
1) the utility model changes into pressure by the speed difference signal of main valve plug control object by mechanical structure auto linear by the feedback pressure mouth arranging on the first damping in dynamic pressure feedback mechanism, the second damping and plunger case, as the driving instruction of hydraulic control pilot valve.The utility model does not have complicated automatical control system and sensor device, simple in structure, cheap, has most importantly solved state switching and integrity problem that automatical control system exists in preacceleration process.
2) speed difference dynamic pressure feedback control function of the present utility model is applied in and can docks performer with less relative velocity combination, reduce the impact that docking final controlling element produces in preacceleration process, be applied in the field such as punching press, hydraulic actuator docking and can improve well the quality of production and the efficiency of product.
Brief description of the drawings
Fig. 1 is the hydraulic principle sketch of numerical control hydraulic pad;
Fig. 2 is the structural representation of the servovalve of speed difference dynamic pressure feedback fluid-control pilot stage;
Fig. 3 applies schematic diagram for the typical case of the servovalve of speed difference dynamic pressure feedback fluid-control pilot stage;
Fig. 4 is the mapping relations figure between feedback pressure and speed difference in preacceleration process;
Fig. 5 is the change in displacement figure of slide block and blank-holding workbench in preacceleration process;
Fig. 6 is the velocity profile of slide block and blank-holding workbench in preacceleration process;
In figure, 1. plunger case, 2. the first damping, 3. the second damping, 4. pressure feedback mouth, 5. the first spring, 6. the second spring, 7 hydraulic pilot valves, 8. pressure regulator valve, 9. main valve plug, 10. flanging cylinder, 11. drivers, 12. slide blocks, 13. worktable, 14. first control chambers, 15. second control chambers, 16. servovalves, 17. oil hydraulic cylinders.
Embodiment
As shown in Figure 2, the utility model is made up of dynamic pressure feedback mechanism, hydraulic control pilot valve 7, pressure regulator valve 8 and main valve plug 9.Wherein, dynamic pressure feedback mechanism comprises plunger case 1, the first damping 2 and the second damping 3, and the cylinder body of plunger case 1 is provided with feedback pressure mouth 4, the first one end of damping 2 and the filler opening of guide oil
be communicated with, the other end of the first damping 2 is communicated with the cylinder body of plunger case 1, one end of the second damping 3 is communicated with fuel tank, and the other end of the second damping 3 is communicated with the cylinder body of plunger case 1, and the cylinder body of plunger case 1 is communicated with the first control chamber of hydraulic control pilot valve 7 by feedback pressure mouth 4.Dynamic pressure feedback device is by regulating the first damping 2 and the second damping 3, can be adjusted between the plunger rod of plunger case 1 and cylinder body without speed difference time (when stable state), the pressure of the rodless cavity of plunger case 1, and then by the feedback pressure mouth 4 on the cylinder body of plunger case 1, the pressure feedback of the rodless cavity of plunger case 1 is arrived to the first control chamber 14 of hydraulic control pilot valve 7.The entrance of pressure regulator valve 8 and the filler opening of guide oil
be communicated with, the outlet of pressure regulator valve 8 is communicated with the second control chamber 15 of hydraulic control pilot valve 7.The A mouth of hydraulic control pilot valve 7 is communicated with the control cavity of resorption of main valve plug 9, and the B mouth of hydraulic control pilot valve 7 is communicated with the control epicoele of main valve plug 9, the P mouth of hydraulic control pilot valve 7 and the filler opening of guide oil
be communicated with, the T mouth of hydraulic control pilot valve 7 is communicated with fuel tank.By the outlet pressure value of setting pressure modulating valve 8, make it mate the control that realizes the spool travel (being pilot valve core openings of sizes) to hydraulic control pilot valve 7 with the pressure of the first control chamber 14 of hydraulic control pilot valve 7, the size of the valve core opening of hydraulic control pilot valve 7 has determined the size of the pressure of main valve plug 9 upper and lower control chambers.
Known according to hydrokinetics, the feedback pressure value of the feedback pressure mouth 4 of plunger case 1
with the plunger rod of plunger case 1 and the speed difference of cylinder body
between function relation be:
In above formula, a, b, c, d are constant coefficients.
In matlab, carry out simulation analysis, obtain
with
relation as shown in Figure 4, as can be seen from Figure 4, the force value of the feedback pressure mouth 4 of plunger case 1
with the plunger rod of plunger case 1 and the speed difference of cylinder body
for linear approximate relationship.It can be said that bright, dynamic pressure feedback of the present utility model mechanism can realize the speed difference signal auto linear between the plunger rod of plunger case 1 and cylinder body is turned to pressure signal, to use for sophisticated sensors and controller realizing this process with respect to automatical control system, the utility model is simple in structure, and reliability is high.
Fig. 3 shows the servovalve applications of the utility model speed difference dynamic pressure feedback fluid-control pilot stage in a kind of structural representation of final controlling element docking mechanism.Wherein the A mouth of main valve plug 9 is communicated with the rodless cavity of flanging cylinder 10, and the T mouth of main valve plug 9 is communicated with fuel tank, the P mouth of main valve plug 9 and rod chamber and the filler opening of flanging cylinder 10
be communicated with, flanging cylinder 10 support table 13, drive motor 11 moves up and down by actuator drives slide block 12, and the plunger case 1 of dynamic pressure feedback device is arranged on the side of worktable 13, the speed of the speed reflection worktable 13 of the cylinder body of plunger case 1.Drive motor 11 drives slide block 12 to move downward, when (speed of the speed reflection slide block 12 of plunger rod) after the plunger rod of plunger case 1 that touches dynamic pressure feedback mechanism in slide block 12 dropping process, dynamic pressure feedback mechanism is by the first damping 2, the hydraulic pressure A type half-bridge that the second damping 3 forms can become pressure signal with the speed difference signal linearization of worktable 13 by slide block 12, feedback pressure mouth 4 on plunger case 1 is guided to this pressure signal the first control chamber 14 of pilot valve 7, control the upper of the spool travel size of hydraulic control pilot valve 7 and main valve plug 9 by the pressure signal feeding back, the pressure of lower control chamber.Regulate delivery pressure and the flow of the A mouth of main valve plug 9 by the upper and lower control chamber pressure of being controlled by hydraulic control pilot valve 7, thereby regulating flanging cylinder 10(is worktable 13) speed, the progressively speeds match of realization and slide block, finally reaches both with less relative velocity contact, reduces to impact.
Further in matlab, to slide block 12 and blank-holding workbench 13, displacement and the velocity relationship in preacceleration process carries out simulation analysis, and simulation result as shown in Figure 5,6.Shown from Fig. 5, the displacement diagram of slide block 12 and blank-holding workbench 13 is tending towards gradually tangent under the effect of feedback mechanism, and two slope of a curves (being both speed) are tending towards equal gradually.As shown in Figure 6, the speed of blank-holding workbench 13 levels off to gradually the speed of slide block 12 under the adjusting of feedback mechanism, and finally both speed reach equal.
(be that the time is t) known, valve piece 13 and blank-holding workbench 14 equate (being Fig. 6 medium velocity intersections of complex curve) in both speed of contact position (being displacement intersections of complex curve in Fig. 5) to the abscissa of intersections of complex curve in comparison diagram 5 and Fig. 6.
Based on matlab simulation result, illustrate that the utility model is applied in the preacceleration process of final controlling element docking control, the rodless cavity pressure of the plunger case 1 of dynamic pressure feedback mechanism
speed difference with slide block 12 and worktable 13
be proportionate.The spool parameter of hydraulic control pilot valve 7 is rationally set, make spool aperture with
proportional routine relation.In the time that slide block 12 contacts with the plunger rod of the plunger case 1 of dynamic pressure feedback mechanism, dynamic pressure feedback mechanism turns to pressure signal according to slide block 12 and the speed difference signal auto linear of blank-holding workbench 13, thereby control hydraulic control pilot valve 7 and drive main valve plug 9, realize the preacceleration process of whole system shown in Fig. 3.In this process, can allow slide block 12 be combined with less relative velocity with blank-holding workbench 13, thereby reduce the impact of preacceleration process.
Claims (5)
1. one kind based on speed difference dynamic pressure feedback fluid-control guide servovalve, it is characterized in that: comprise dynamic pressure feedback mechanism, hydraulic control pilot valve (7), pressure regulator valve (8) and main valve plug (9), described dynamic pressure feedback mechanism comprises plunger case (1), the first damping (2) and the second damping (3), the cylinder body of described plunger case is provided with feedback pressure mouth (4), one end of the first damping (2) is communicated with the filler opening of guide oil, the other end of the first damping (3) is communicated with the cylinder body of plunger case (1), one end of the second damping (3) is communicated with fuel tank, the other end of the second damping (3) is communicated with the cylinder body of plunger case (1), the cylinder body of described plunger case (1) is communicated with the first control chamber of hydraulic control pilot valve (7) by feedback pressure mouth (4), the entrance of pressure regulator valve (8) is communicated with the described filler opening of guide oil, the outlet of pressure regulator valve (8) is communicated with the second control chamber of hydraulic control pilot valve (7), the A mouth of hydraulic control pilot valve (7) is communicated with the control cavity of resorption of main valve plug (9), the B mouth of hydraulic control pilot valve (7) is communicated with the control epicoele of main valve plug (9), the P mouth of hydraulic control pilot valve (7) is communicated with the described filler opening of guide oil, the T mouth of hydraulic control pilot valve (7) is communicated with described fuel tank.
2. according to claim 1 based on speed difference dynamic pressure feedback fluid-control guide servovalve, it is characterized in that: between the spool of described hydraulic control pilot valve (7) and valve body, be provided with the first spring (5) and the second spring (6), the first spring (5) and the second spring (6) are placed in the both sides of spool of described hydraulic control pilot valve (7) so that this spool centering.
3. according to claim 1 and 2 based on speed difference dynamic pressure feedback fluid-control guide servovalve, it is characterized in that: described pressure regulator valve (8) is reduction valve, and the outlet pressure of this reduction valve is constant, adjustable.
4. according to claim 1 and 2 based on speed difference dynamic pressure feedback fluid-control guide servovalve, it is characterized in that: described hydraulic control pilot valve (7) is Proportional valve or servovalve.
5. according to claim 1 and 2 based on speed difference dynamic pressure feedback fluid-control guide servovalve, it is characterized in that: described main valve plug (9) is Twoway valves or three-way valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420010655.2U CN203685739U (en) | 2014-01-08 | 2014-01-08 | Servo valve based on speed difference dynamic pressure feedback hydraulic control guide level |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201420010655.2U CN203685739U (en) | 2014-01-08 | 2014-01-08 | Servo valve based on speed difference dynamic pressure feedback hydraulic control guide level |
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| Publication Number | Publication Date |
|---|---|
| CN203685739U true CN203685739U (en) | 2014-07-02 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201420010655.2U Expired - Lifetime CN203685739U (en) | 2014-01-08 | 2014-01-08 | Servo valve based on speed difference dynamic pressure feedback hydraulic control guide level |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103775411A (en) * | 2014-01-08 | 2014-05-07 | 浙江大学 | Hydraulically-controlled pilot level servo valve based on speed difference dynamic pressure feedback |
| CN104132016A (en) * | 2014-07-25 | 2014-11-05 | 常德中联重科液压有限公司 | Three-way flow valve, load-sensitive multi-way valve, hydraulic system and engineering machinery |
-
2014
- 2014-01-08 CN CN201420010655.2U patent/CN203685739U/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103775411A (en) * | 2014-01-08 | 2014-05-07 | 浙江大学 | Hydraulically-controlled pilot level servo valve based on speed difference dynamic pressure feedback |
| CN103775411B (en) * | 2014-01-08 | 2015-09-23 | 浙江大学 | A kind of servovalve based on speed difference dynamic pressure feedback fluid-control pilot stage |
| CN104132016A (en) * | 2014-07-25 | 2014-11-05 | 常德中联重科液压有限公司 | Three-way flow valve, load-sensitive multi-way valve, hydraulic system and engineering machinery |
| CN104132016B (en) * | 2014-07-25 | 2016-03-09 | 常德中联重科液压有限公司 | Three-way flow valve, load-sensitive multi-way valve, hydraulic system and engineering machinery |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20140702 Effective date of abandoning: 20150923 |
|
| RGAV | Abandon patent right to avoid regrant |