CN103742473B - Split type pilot load control valve - Google Patents
Split type pilot load control valve Download PDFInfo
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- CN103742473B CN103742473B CN201310749304.3A CN201310749304A CN103742473B CN 103742473 B CN103742473 B CN 103742473B CN 201310749304 A CN201310749304 A CN 201310749304A CN 103742473 B CN103742473 B CN 103742473B
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Abstract
The invention discloses a kind of split type pilot load control valve.Comprise pilot valve left end cap, control piston, control piston damping, guide valve blocks, control spring, pilot valve, guide's valve pocket, overcompensation damping, pilot valve spring seat, pilot valve Returnning spring, pilot valve right end cap, main valve plug, main valve housing, main valve Returnning spring, main spool spring seat, main valve end cap, main valve body.This load control valve inside defines control chamber, draining chamber, oil back chamber, pilot valve inner chamber, load cavity, control sensitive cavity.Owing to adopting leading type structure, this valve acts on control piston-pilot valve assembly by pilot pressure, and indirect control bound core motion, for the hydraulic system that there is Exceed load, this load control valve accurately can control load lowering velocity.Overcompensation function, will enable this valve in the application that crane variable-amplitude hydraulic system even load pressure increases along with transferring, and effectively suppression induced pressure increases the speed brought and increases problem.
Description
Technical field
The present invention relates to hydraulic control component, especially relate to a kind of split type pilot load control valve.
Background technique
In the hydraulic system applications such as such as engineering machinery, crane gear and winch, often can occur the situation that load force direction is consistent with load movement direction, this kind of load is called as Exceed load (negative load).Bear the hydraulic system of Exceed load, need special control valve to control the flow of the hydraulic oil from load flow oil return source, thus the speed that control load is transferred, this kind of control valve is commonly referred to as load control valve or equilibrium valve.Because induced pressure is higher, loading condition is complicated, and the metering characteristics of load control valve directly determine speed control characteristic and the speed stability of hydraulic system.
But transfer along with load at crane variable-amplitude hydraulic system even load pressure and in the application increased, normal load control valve often also exists along with load is transferred, induced pressure increases and then lowering velocity increases the problem of even stall.In such applications, load control valve becomes the bottleneck of hydraulic system performance, is badly in need of the load control valve that design can resist the lowering velocity increase caused because induced pressure raises.
In view of this, application new principle, new method, the speed increase novel load control valve that development is applicable to being highly resistant to of the hydraulic system that there is Exceed load and causes because induced pressure raises has important practical meaning in engineering.
Summary of the invention
In order to realize existing in background technique Exceed load hydraulic system in the control of load lowering velocity, especially the problem existing for conventional load control valve of the lowering velocity increase caused because induced pressure raises is overcome, the object of the present invention is to provide a kind of split type pilot load control valve, owing to adopting leading type structure, this valve acts on control piston-pilot valve assembly by pilot pressure, indirect control bound core motion, for the hydraulic system that there is Exceed load, this load control valve accurately can control load lowering velocity.Overcompensation function, will enable this valve in the application that crane variable-amplitude hydraulic system even load pressure increases along with transferring, and effectively suppression induced pressure increases the speed brought and increases problem.
The technical solution used in the present invention is:
Main valve housing of the present invention is installed in the cylindrical hole of main valve body, main valve plug small end passes main valve housing and is positioned at oil back chamber, the large end of main valve plug and main valve housing endoporus are for being slidably matched, main spool spring seat is held greatly and is placed in the large end step hole of main valve housing, and compress the large end of main valve housing, main spool spring seat small end is pressed on the rear portion of main valve housing by main valve end cap, one end of main valve Returnning spring is placed in bottom the hole of main valve plug, and the other end of main valve Returnning spring is placed in bottom the hole of main spool spring seat;
Guide's valve pocket is installed in the cylindrical hole of guide valve blocks one end, jointly oil back chamber is formed with pilot valve body opening bottom main valve housing with bottom main valve body opening and guide's valve pocket, pilot valve small end passes guide's valve pocket and is positioned at oil back chamber, the large end of pilot valve is placed in guide's valve pocket to be formed and is slidably matched, the large end of the large side pressure of pilot valve spring seat tight guide valve pocket, the small end of pilot valve spring seat is pressed in guide valve blocks cylindrical hole by pilot valve right end cap, one end of pilot valve Returnning spring is set on the large end stand shoulder of pilot valve, the other end of pilot valve Returnning spring is placed in bottom the hole of pilot valve spring seat, overcompensation damping is installed in the hole of the pilot valve of the large end in pilot valve Returnning spring side, main valve plug large bottom portion, main valve housing large bottom portion, main valve body opening, main valve end cap, pilot valve large bottom portion, guide's valve pocket large bottom portion, pilot valve body opening and pilot valve right end cap surround control sensitive cavity jointly, be bolted between guide valve blocks and main valve body,
Formed with guide valve blocks and be slidably matched in the cylindrical hole that control piston is placed in the guide valve blocks the other end, the small end of control piston withstands on the small end of the pilot valve through guide's valve pocket; One end of control spring withstands on bottom the cylindrical hole of guide valve blocks, and the other end of control spring withstands on control piston shoulder, and control piston damping is installed in control piston hole; Pilot valve left end cap is arranged on guide valve blocks by bolt, and pushes down the large end of control piston; Control piston, guide valve blocks and pilot valve left end cap coordinate formation control chamber jointly, and the center hole of pilot valve left end cap is control port X, and control port X is communicated with control chamber;
In the middle part of main valve body cylindrical hole, outside the large end of main valve plug, in the middle part of main valve housing, guide valve blocks cylindrical hole, outside the large end of pilot valve, guide's valve pocket coordinates formation load cavity jointly; Main valve body is provided with return opening A and is communicated with oil back chamber, and main valve body is provided with load hydraulic fluid port B and is communicated with load cavity; Oil back chamber is communicated with load cavity by valve port in the middle part of main valve plug; Control sensitive cavity to be communicated with load cavity by the large end rectangle groove of main valve plug, control sensitive cavity is communicated with load cavity by the valve port of the large end of pilot valve, controls sensitive cavity by overcompensation damping internal holes and pilot valve inner space; Pilot valve cylindrical hole, overcompensation damping and guide's valve pocket coordinate formation pilot valve inner chamber, and pilot valve inner chamber is communicated with oil back chamber by pilot valve small end valve port; Guide valve blocks coordinates with control piston and forms draining chamber, and the radial drain tap L of guide valve blocks is communicated with draining chamber; Be control chamber on the left of aperture in control piston damping, right side is draining chamber.
Described pilot valve and main valve plug axis being parallel, and pilot valve is identical with the little extreme direction of main valve plug.
Described pilot valve is coaxial with control piston, and pilot valve is relative with control piston small end.
Described pilot valve is provided with overcompensation damping, makes load control valve have overcompensation function.
The beneficial effect that the present invention has is:
For existing in the hydraulic system of Exceed load, this load control valve accurately can control the flow by load control valve, and then carries out the control of efficiently and accurately to the speed that load is transferred; Owing to adopting leading type structure, this valve acts on control piston-pilot valve assembly by pilot pressure, and indirect control bound core motion, for the hydraulic system that there is Exceed load, this load control valve accurately can control load lowering velocity.Because the overcompensation damping structure of pilot valve, this valve has overcompensation function, enables this valve in the application that crane variable-amplitude hydraulic system even load pressure increases along with transferring, and effectively suppression induced pressure increases the speed brought and increases problem.The matching design of pilot valve and guide's valve pocket, when pilot valve is closed, load cavity is directly linked up with control sensitive cavity, thus control sensitive cavity pressure is raised rapidly, thus promotes main valve plug quick closedown, makes load control valve have quick closedown function.
Accompanying drawing explanation
Fig. 1 is structural principle schematic diagram of the present invention.
Fig. 2 is the sectional drawing in A-A cross section in Fig. 1.
The phase diagram of Fig. 3 when to be that load rising load control valve is unidirectional open.
Fig. 4 is the phase diagram of load decline load control valve guide when opening.
Fig. 5 is the partial enlarged view at C place in Fig. 1.
Fig. 6 is the partial enlarged view at D place in Fig. 1.
In figure: 1, pilot valve left end cap, 2, control piston, 3, control piston damping, 4, guide valve blocks, 5, control spring, 6, pilot valve, 7, guide's valve pocket, 8, overcompensation damping, 9, pilot valve spring seat, 10, pilot valve Returnning spring, 11, pilot valve right end cap, 12, main valve plug, 13, main valve housing, 14, main valve Returnning spring, 15, main spool spring seat, 16, main valve end cap, 17, main valve body, 18, control chamber, 19, draining chamber, 20, oil back chamber, 21, pilot valve inner chamber, 22, load cavity, 23, control sensitive cavity.
Embodiment
Below in conjunction with drawings and Examples, the invention will be further described.
As shown in Figure 1, the present invention includes pilot valve left end cap 1, control piston 2, control piston damping 3, guide valve blocks 4, control spring 5, pilot valve 6, guide's valve pocket 7, overcompensation damping 8, pilot valve spring seat 9, pilot valve Returnning spring 10, pilot valve right end cap 11, main valve plug 12, main valve housing 13, main valve Returnning spring 14, main spool spring seat 15, main valve end cap 16 and main valve body 17.
As Fig. 1, shown in Fig. 2, main valve housing 13 is installed in the cylindrical hole of main valve body 17, main valve plug 12 small end passes main valve housing 13 and is positioned at oil back chamber 20, main valve plug 12 is held with main valve housing 13 endoporus as being slidably matched greatly, main spool spring seat 15 greatly end is placed in main valve housing 13 end step hole greatly, and compress the large end of main valve housing 13, main spool spring seat 15 small end is pressed on the rear portion of main valve housing 13 by main valve end cap 16, one end of main valve Returnning spring 14 is placed in bottom the hole of main valve plug 12, the other end of main valve Returnning spring 14 is placed in bottom the hole of main spool spring seat 15, guide's valve pocket 7 is installed in guide valve blocks 4 cylindrical hole, oil back chamber 20 is jointly formed with guide valve blocks 4 hole bottom main valve housing 13 with bottom main valve body 17 hole and guide's valve pocket 7, pilot valve 6 small end passes guide's valve pocket 7 and is positioned at oil back chamber 20, pilot valve 6 is held greatly to be placed in guide's valve pocket 7 to be formed and is slidably matched, overcompensation damping 8 is installed in the hole of the pilot valve 6 of the large end in pilot valve Returnning spring 10 side, the large end of the large side pressure tight guide valve pocket 7 of pilot valve spring seat 9, the small end of pilot valve spring seat 9 is pressed in guide valve blocks 4 cylindrical hole by pilot valve right end cap 11, one end of pilot valve Returnning spring 10 is set on the large end stand shoulder of pilot valve 6, the other end of pilot valve Returnning spring 10 is placed in bottom the hole of pilot valve spring seat 9, the large bottom portion of main valve plug 12, the large bottom portion of main valve housing 13, main valve body 17 hole, main valve end cap 16, the large bottom portion of pilot valve 6, the large bottom portion of guide's valve pocket 7, guide valve blocks 4 hole, pilot valve right end cap 11 jointly surround and control sensitive cavity 23, be bolted between guide valve blocks 4 and main valve body 17.Control piston damping 3 is installed in control piston 2 hole, and formed with guide valve blocks 4 and be slidably matched in the cylindrical hole that control piston 2 is placed in guide valve blocks 4, the small end of control piston 2 withstands on the small end of the pilot valve 6 through guide's valve pocket 7; One end of control spring 5 withstands on bottom the cylindrical hole of guide valve blocks 4, and the other end of control spring 5 withstands on control piston 2 shoulder, and pilot valve left end cap 1 is arranged on guide valve blocks 4 by bolt, and pushes down the large end of control piston 2; Control piston 2, guide valve blocks 4 and pilot valve left end cap 1 coordinate formation control chamber 18 jointly, and the center of pilot valve left end cap 1 is provided with control port X, and control port X is communicated with control chamber 18.
As shown in Figure 1, Figure 2, Figure 3 shows, main valve body 17 is provided with return opening A and is communicated with oil back chamber 20, and main valve body 17 is provided with load hydraulic fluid port B and is communicated with load cavity 22; In the middle part of main valve body 17 cylindrical hole, main valve plug 12 is held greatly in the middle part of outside, main valve housing 13, guide valve blocks 4 cylindrical hole, pilot valve 6 holds greatly outside, guide's valve pocket 7 coordinates formation load cavity 22 jointly, and oil back chamber 20 is communicated with load cavity 22 by valve port in the middle part of main valve plug 12; Controlling sensitive cavity 23 holds greatly rectangle groove to be communicated with load cavity 22 by main valve plug 12, and control sensitive cavity 23 is communicated with load cavity 22 by the valve port of the large end of pilot valve 6, controls sensitive cavity 23 and is communicated with pilot valve inner chamber 21 by overcompensation damping 8 internal holes; Pilot valve 6 cylindrical hole, overcompensation damping 8 and guide's valve pocket 7 coordinate formation pilot valve inner chamber 21, and pilot valve inner chamber 21 is communicated with oil back chamber 20 by pilot valve 6 small end valve port; Guide valve blocks 4 coordinates with control piston 2 and forms draining chamber 19, and the radial drain tap L of guide valve blocks 4 is communicated with draining chamber 19.
Described pilot valve 6 and main valve plug 12 axis being parallel, and pilot valve 6 is identical with the little extreme direction of main valve plug 12.
Described pilot valve 6 is coaxial with control piston 2, and pilot valve 6 is relative with control piston 2 small end.
Described pilot valve 6 is provided with overcompensation damping 8, makes load control valve have overcompensation function.Along with induced pressure increases, reduced by the hydraulic fluid flow rate of load control valve, the effect of the safety of proof load and hydraulic system.
The matching design of pilot valve 6 and guide's valve pocket 7, when pilot valve 6 is closed, load cavity 22 is directly linked up with control sensitive cavity 23, thus control sensitive cavity 23 pressure is raised rapidly, thus promote main valve plug 12 quick closedown, make load control valve have quick closedown function.
As shown in Figure 1, the split type pilot load control valve of the present invention mainly comprises main valve plug assembly, pilot valve assembly, control piston assembly and valve component.Main valve plug assembly comprises main valve plug 12, main valve housing 13 and main valve Returnning spring 14, main valve plug is placed in main valve housing, and can move vertically in main valve housing, main valve Returnning spring 14 one end withstands on the bottom of main valve plug endoporus, wherein the oil back chamber 20 of main valve plug left end communicates with load control valve return opening A, load cavity 22 communicates with load control valve load hydraulic fluid port B, and main valve plug right-hand member cavity volume is for controlling sensitive cavity 23; Pilot valve assembly is made up of pilot valve 6, guide's valve pocket 7, overcompensation damping 8 and pilot valve Returnning spring 10, pilot valve is placed in guide's valve pocket, and can move vertically in first guide valve bushing, overcompensation damping 8 is installed on pilot valve afterbody by screw thread, pilot valve Returnning spring one end is enclosed within pilot valve afterbody ladder place, and withstand its convex shoulder, wherein overcompensation damping left end cavity volume is pilot valve inner chamber 21, and overcompensation damping right-hand member cavity volume is for controlling sensitive cavity 23; Control piston assembly is made up of control piston 2 and control spring 5, control piston is placed in guide valve blocks cylindrical hole and can moves vertically wherein, control spring one end is withstood bottom guide valve blocks cylindrical hole, the other end to be enclosed within control piston and to withstand control piston, wherein the control chamber 18 of control piston left end communicates with load control valve control port X, and the draining chamber 19 of control piston right-hand member communicates with load control valve drain tap L; Valve component is made up of main valve body 17, guide valve blocks 4, main valve end cap 16, pilot valve left end cap 1 and pilot valve right end cap 11, main valve end cap and main valve body are threaded connection, main valve body is connected by 6 interior hexagonal cylindrical hook bolts with guide valve blocks, pilot valve left end cap is connected by 4 interior hexagonal cylindrical hook bolts with guide valve blocks, and pilot valve right end cap and guide valve blocks are threaded connection.
What Fig. 2 showed load control valve load hydraulic fluid port B and load cavity 22 is communicated with situation.
When Fig. 3 is load rising, load control valve is as state during one-way valve opens, now hydraulic oil enters load control valve from A mouth, promotion main valve plug 12 compresses main valve Returnning spring 14 and moves to main valve end cap 16 direction, valve port is opened, and hydraulic oil enters load cavity 22 through valve port, and then flows out from B mouth, when load control valve is as one-way valve opens, pilot valve 6, that control piston 2 is in original position is motionless.
When Figure 4 shows that load declines, state when load control valve guide opens, first, pilot control pressure oil enters control chamber 18 from control port X, promote control piston 2 compression control spring 5 to move to pilot valve 6 direction, under the promotion of control piston 2, pilot valve 6 moves to pilot valve right end cap 11 direction, poppet port between pilot valve 6 and guide's valve pocket 7 is opened, link up pilot valve inner chamber 21 and oil back chamber 20, pilot valve inner chamber 21 pressure reduces, be connected by overcompensation damping 8 with pilot valve inner chamber 21 owing to controlling sensitive cavity 23, reduce so control sensitive cavity 23 pressure, main valve plug 12 stress balance is broken, main valve plug 12 moves to main valve end cap 16 direction, primary valve is opened, the pressure oil of B mouth is by load cavity 22, primary valve enters oil back chamber 20, and then flow out from load control valve A mouth.
Fig. 5 is the partial enlarged view at C place in Fig. 1, show load cavity 22 with control sensitive cavity 23 be communicated with situation, when pilot valve 6 moves right, load cavity 22 is blocked with control being communicated with of sensitive cavity 23, when pilot valve 6 sets back, load cavity 22 is communicated with again with control sensitive cavity 23, pressure oil now in load cavity enters and controls sensitive cavity 23, the pressure controlling sensitive cavity 23 raises, thus promotion main valve plug 12 moves to the direction away from main valve end cap 16, and then load control valve is closed.
Fig. 6 is the partial enlarged view at D place in Fig. 1, show the details of the large end valve mouth of main valve plug, when guide opens, control pressure the opening and reducing because of pilot valve 6 of sensitive cavity 23, main valve plug stress balance is broken, main valve plug moves to the direction of main valve end cap 16, now the large end valve of main valve plug make a slip of the tongue flow area increase, the pressure oil of load cavity 22 enters through this valve port and controls sensitive cavity 23, control sensitive cavity pressure to raise, main valve plug reaches stress balance again, and then is stabilized in certain enable possition.
Claims (4)
1. a split type pilot load control valve, is characterized in that: comprise pilot valve left end cap (1), control piston (2), control piston damping (3), guide valve blocks (4), control spring (5), pilot valve (6), guide's valve pocket (7), overcompensation damping (8), pilot valve spring seat (9), pilot valve Returnning spring (10), pilot valve right end cap (11), main valve plug (12), main valve housing (13), main valve Returnning spring (14), main spool spring seat (15), main valve end cap (16) and main valve body (17);
Main valve housing (13) is installed in the cylindrical hole of main valve body (17), main valve plug (12) small end passes main valve housing (13) and is positioned at oil back chamber (20), main valve plug (12) is held with main valve housing (13) endoporus as being slidably matched greatly, main spool spring seat (15) greatly end is placed in main valve housing (13) end step hole greatly, and compress the large end of main valve housing (13), main spool spring seat (15) small end is pressed on the rear portion of main valve housing (13) by main valve end cap (16), one end of main valve Returnning spring (14) is placed in bottom the hole of main valve plug (12), the other end of main valve Returnning spring (14) is placed in bottom the hole of main spool spring seat (15),
Guide's valve pocket (7) is installed in the cylindrical hole of guide valve blocks (4) one end, main valve housing (13) bottom forms oil back chamber (20) with main valve body (17) hole and guide's valve pocket (7) bottom jointly with guide valve blocks (4) hole, pilot valve (6) small end passes guide's valve pocket (7) and is positioned at oil back chamber (20), pilot valve (6) is held greatly to be placed in guide's valve pocket (7) to be formed and is slidably matched, the large end of large side pressure tight guide valve pocket (7) of pilot valve spring seat (9), the small end of pilot valve spring seat (9) is pressed in guide valve blocks (4) cylindrical hole by pilot valve right end cap (11), one end of pilot valve Returnning spring (10) is set on the large end stand shoulder of pilot valve (6), the other end of pilot valve Returnning spring (10) is placed in bottom the hole of pilot valve spring seat (9), overcompensation damping (8) is installed in the hole of the pilot valve (6) of the large end in pilot valve Returnning spring (10) side, the large bottom portion of main valve plug (12), the large bottom portion of main valve housing (13), main valve body (17) hole, main valve end cap (16), the large bottom portion of pilot valve (6), the large bottom portion of guide's valve pocket (7), guide valve blocks (4) hole and pilot valve right end cap (11) jointly surround and control sensitive cavity (23), be bolted between guide valve blocks (4) and main valve body (17),
Formed with guide valve blocks (4) and be slidably matched in the cylindrical hole that control piston (2) is placed in guide valve blocks (4) the other end, the small end of control piston (2) withstands on the small end of the pilot valve (6) through guide's valve pocket (7); One end of control spring (5) withstands on bottom the cylindrical hole of guide valve blocks (4), and the other end of control spring (5) withstands on control piston (2) shoulder, and control piston damping (3) is installed in control piston (2) hole; Pilot valve left end cap (1) is arranged on guide valve blocks (4) by bolt, and pushes down the large end of control piston (2); Control piston (2), guide valve blocks (4) and pilot valve left end cap (1) coordinate formation control chamber (18) jointly, and the center hole of pilot valve left end cap (1) is control port X, and control port X is communicated with control chamber (18);
In the middle part of main valve body (17) cylindrical hole, main valve plug (12) is held greatly in the middle part of outside, main valve housing (13), guide valve blocks (4) cylindrical hole, pilot valve (6) holds greatly outside, guide's valve pocket (7) coordinates formation load cavity (22) jointly; Main valve body (17) is provided with return opening A and is communicated with oil back chamber (20), and main valve body (17) is provided with load hydraulic fluid port B and is communicated with load cavity (22); Oil back chamber (20) is communicated with load cavity (22) by main valve plug (12) middle part valve port; Controlling sensitive cavity (23) holds greatly rectangle groove to be communicated with load cavity (22) by main valve plug (12), control sensitive cavity (23) to be communicated with load cavity (22) by the large valve port held of pilot valve (6), control sensitive cavity (23) and be communicated with pilot valve inner chamber (21) by overcompensation damping (8) internal holes; Pilot valve (6) cylindrical hole, overcompensation damping (8) and guide's valve pocket (7) coordinate formation pilot valve inner chamber (21), and pilot valve inner chamber (21) is communicated with oil back chamber (20) by pilot valve (6) small end valve port; Guide valve blocks (4) coordinates with control piston (2) and forms draining chamber (19), and the radial drain tap L of guide valve blocks (4) is communicated with draining chamber (19); Be control chamber (18) on the left of aperture in control piston damping (3), right side is draining chamber (19).
2. the split type pilot load control valve of one according to claim 1, is characterized in that: described pilot valve (6) and main valve plug (12) axis being parallel, and pilot valve (6) small end is identical with main valve plug (12) little extreme direction.
3. the split type pilot load control valve of one according to claim 1, is characterized in that: described pilot valve (6) is coaxial with control piston (2), and pilot valve (6) small end is relative with control piston (2) small end.
4. the split type pilot load control valve of one according to claim 1, is characterized in that: described pilot valve (6) is provided with overcompensation damping (8), makes load control valve have overcompensation function.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310749304.3A CN103742473B (en) | 2013-12-31 | 2013-12-31 | Split type pilot load control valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310749304.3A CN103742473B (en) | 2013-12-31 | 2013-12-31 | Split type pilot load control valve |
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| Publication Number | Publication Date |
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| CN103742473A CN103742473A (en) | 2014-04-23 |
| CN103742473B true CN103742473B (en) | 2015-12-09 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201310749304.3A Active CN103742473B (en) | 2013-12-31 | 2013-12-31 | Split type pilot load control valve |
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| CN (1) | CN103742473B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105971956A (en) * | 2016-05-31 | 2016-09-28 | 宁波文泽机电技术开发有限公司 | Pilot control valve |
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| CN106050775B (en) * | 2016-06-11 | 2017-12-08 | 宁波文泽机电技术开发有限公司 | Structure improved pilot-actuated valve |
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| CN103742473A (en) | 2014-04-23 |
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