CN203362668U - Balance valve of dynamic load differential pressure protection and flow pressure air chamber compensation - Google Patents
Balance valve of dynamic load differential pressure protection and flow pressure air chamber compensation Download PDFInfo
- Publication number
- CN203362668U CN203362668U CN 201320055566 CN201320055566U CN203362668U CN 203362668 U CN203362668 U CN 203362668U CN 201320055566 CN201320055566 CN 201320055566 CN 201320055566 U CN201320055566 U CN 201320055566U CN 203362668 U CN203362668 U CN 203362668U
- Authority
- CN
- China
- Prior art keywords
- valve
- pressure
- spring
- dynamic load
- air chamber
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Images
Abstract
Disclosed is a balance valve of dynamic load differential pressure protection and flow pressure air chamber compensation. The balance valve is composed of combination and communication of the balance valve, a two-level protection overflow valve and a pressure flow compensator. The balance valve is characterized in that: a one-way valve core (6) is installed in a hole of a main valve core (5) in a sleeved mode; a right end spring cavity controlling the main valve core (5) is composed of a hydraulic control one-way valve whether is communicated with an A cavity or a B cavity; several uniformly distributed axial small grooves are arranged in a large cylinder at the right end of the main valve core (5); and an accommodating cavity is communicated with the A cavity and is arranged between a main spring seat (10) and a valve body (3). The two-level overflow valve is characterized in that: a throttling opening of the two-level overflow valve is formed by the combination that a fixing throttling opening and a variable throttling opening are in series connection. The pressure flow compensator is arranged on the left cavity of an overflow valve core (14). The control principle of opening the differential pressure protection is that opening of the overflow valve core (14) is controlled by the difference value of surge pressure of the B cavity and lifting pressure of an oil cylinder. The balance valve of dynamic load differential pressure protection and flow pressure air chamber compensation is beneficial to the fact that an arm frame is returned after the surge pressure triggered by a dynamic load is released and the vibration and the swaying which are possible to emerge of the arm frame can be avoided.
Description
One, technical field:
The present invention relates to the equilibrium valve of a kind of dynamic load differential pressure security and the compensation of flow pressure air chamber.This equilibrium valve especially is adapted to the concrete mixer of highi degree of accuracy, high pressure and the requirement of high sealing life and reliability, also is adapted to other all kinds of heavy machinery equipments.
Two, background technique:
Development along with the heavy machinery equipment; performance to equilibrium valve proposes some new requirements; as concrete mixer in order to protect the structural safety of its jib under Under Dynamic Load, the difference requirements that the import equilibrium valve accessory that its adopts just has 15% left and right to cracking pressure and the closing pressure of its secondary relief valve.And these are that current domestic equilibrium valve is not available, caused so the long-term dependence on import accessory of this series products, hindered the development of China's main frame equipment.In addition, the starting differential pressure of its secondary relief valve generally is set as 1.15 times of rated working pressure.This design in use brings two problems: the one, and the cracking pressure that rated working pressure is 1.15 times deducts very low return pressure, the pressure reduction of restriction is too large, the very little opening of restriction all can cause the quick decompression of fluid in the oil cylinder support chamber, causes jib whereabouts out of control.The 2nd, along with the light-weighted process of main frame, the rated working pressure of hydraulic system improves thereupon, and the raising of cracking pressure just needs larger spring rate and pre compressed magnitude to carry out the balancing overflow spool.The response inertia of large rigid spring is larger, the overshoot caused also can strengthen, the relief valve that this is huge for restriction pressure reduction, the surge pressure that originates from the dynamic load of jib, can change with the elasticity undulate of jib structure, totally unfavorable to its dynamic stability, may cause the runout up and down of jib, the intensity of infringement jib.In order to alleviate this drawback, the import accessory just have to have been set up an one-way throttle valve at oil cylinder to the oil circuit of equilibrium valve, and the liquid produced with extremely strong fixed restriction hinders to prevent jib possible downslide out of control in this process.Although alleviating under certain conditions, this way stablizes the downslide out of control of the poor jib caused because of relief valve, but in the normal arm operating mode of receiving, bring the huge pressure loss and energy consumption to system, caused the system heating, damaged the sealability of working medium and hydraulic system.
Three, summary of the invention:
Purpose of the present invention be exactly to develop a kind of reliable performance, structure is relatively simple, adopt and control the secondary relief valve by oil cylinder abutment pressure and the pressure reduction of the surge pressure produced open, by the pressurising air chamber, received surge pressure and liquid and it is carried out to flow and pressure compensated pump truck equilibrium valve at the oil pressure of oil cylinder during lower than abutment pressure under Under Dynamic Load.
Solution of the present invention is: the equilibrium valve of a kind of dynamic load differential pressure security and the compensation of flow pressure air chamber, and equilibrium valve mainly is comprised of orifice plug 1, valve body 3, control piston 4, main valve plug 5, nonreturn valve core 6, little spring 7, submissile spring abutment 8, main spring 9, main spring seat 10 etc.; The second class protection relief valve mainly is comprised of valve body 3, damping plug 11, overflow spool 14, relief valve spring 15, relief valve spring seat 16, cage 24, nut cap 17, locking nut 18, air chamber base 19, air bag cushion 21, steel ball 27 and little spring 26 etc.; Wherein by nut cap 17, air chamber base 19, air bag cushion 21, steel ball 27 and little spring 26 etc., form a flow pressure compensator, be filled with the inert gas equated with the oil cylinder abutment pressure before installing and using; Be provided with an one-way valve formed by spring seat 25, little spring 26 and steel ball 27 and valve body 3 etc. between them; Also have a little relief valve be comprised of valve body 3, spring 28, steel ball 22 and spring seat 29, its oil pressure relief is higher than the oil cylinder abutment pressure; Four combine connection has formed the present invention; Equilibrium valve is characterised in that: nonreturn valve core 6 is sleeved in the hole of main valve plug 5, the endoporus right angle of its male cone (strobilus masculinus) and main valve plug 5 has formed a sealing pair, and is communicated with A chamber or the Pilot operated check valve in connection B chamber with little spring 7, submissile spring abutment 8 composition control main valve plug 5 right-hand member spring chambers; Have several uniform axial sulculuses on main valve plug 5 right-hand member large cylinders, be communicated with the cavity volume between B chamber and main spring seat 10 and valve body 3, the endoporus of the cylindrical of main spring seat 10 left end boss and main valve plug 5 right-hand members is for movingly.The second class protection relief valve is characterised in that: restriction is combined by the restriction of two series windings, they are arranged on respectively the fixed restriction aperture in overflow spool 14 center portions and are arranged on the several radially throttling pore of overflow spool 14 left ends near its sealing cone, they divide several section settings along axis, and with the throttling pore in center portion, be communicated with respectively, they are moved to the left and progressively open with overflow spool 14, are settable orifices; The B chamber is communicated with the fixed orifice of its central position by the radial hole that is arranged on overflow spool 14 intermediate portions; The fixed orifice of overflow spool 14 central positions also has been communicated with the cavity volume of its right-hand member by damping plug 11; Also be provided with a repairing one-way valve formed by cage 24 and little spring 26 and steel ball 27 at the left end of overflow spool 14.The pressure reduction of second class protection relief valve is controlled the opening and closing principle: the left chamber of overflow spool 14 is identical with the A chamber by one-way valve, in just being full of the pressure oil equated with lift-off pressures and being closed and being kept in the lifting process of oil cylinder, the difference that deducts lift-off pressures when the B cavity pressure impact value caused by dynamic load is multiplied by the spring force that power that the sectional area of overflow spool 14 produces is greater than relief valve spring 15, overflow spool 14 is pushed to and moves to left, the pressure oil in B chamber flows to the left chamber of overflow spool 14 from flow through the radially throttling pore of left end of the axial restraint throttling pore in overflow spool 14 center portions, and promoted the pressurized air that 21 compressions of air bag barrier film have been filled with simultaneously and be moved to the left, B the chamber pressure surge caused by dynamic load and the liquid be discharged from have been received, in this process, the power that overflow spool 14 is opened is that difference that the surge pressure in B chamber deducts lift-off pressures is multiplied by the power that the sectional area of overflow spool 14 produces, impact force is larger, the opening of overflow spool 14 is just larger, the liquid resistance of its settable orifice is just less, and the surge pressure in B chamber just discharges manyly.Along with the release of B chamber surge pressure, original equilibrium of forces is broken, and under the effect of the pressure that overflow spool 14 stores at relief valve spring 15 and the air chamber that separated by air bag barrier film 21, moves right; In this of overflow spool 14 moves closing process, during the B cavity pressure stores lower than the air chamber that separated by air bag barrier film 21 if occur pressure, the liquid that the oil cylinder cavity of resorption is that discharge in this release of pressure process, receive after gas compression that separated by air bag barrier film 21, can push steel ball 27 open through cage 24 and flow back to the oil cylinder cavity of resorption.So just can guarantee that jib still can get back to original position after discharging the surge pressure caused by dynamic load, and suppress the runout that jib may occur.The working principle of equilibrium valve is: the sealing operating mode: the high pressure oil in B chamber is by the aperture of the end of keeping right on main valve plug 5, with the spring chamber of main valve plug 5 right-hand members, be communicated with, nonreturn valve core 6 is all locked with its sealing seat with main valve plug 5 under the effect of high pressure oil and spring separately, closed the flow channel of the high pressure oil in B chamber to the A chamber, and sealing power strengthens with the increased pressure in B chamber.Hydraulic oil flows to B chamber operating mode from the A chamber, nonreturn valve core 6 is under the effect of little spring 7, in closed condition, the right chamber of main valve plug 5 is in being communicated with the B chamber, the hydraulic oil promotion main valve plug 5 in A chamber compresses main spring 9 together with nonreturn valve core 6 and moves right, the throttle orifice that main valve plug 5 left end small columns put is opened, and hydraulic oil this restriction of flowing through flows to the B chamber from the A chamber.Hydraulic oil flows to A chamber operating mode from the B chamber: pressure oil is supplied with in the C chamber, throttle orifice on orifice plug 1 promotes piston 4 and moves to right, first promote nonreturn valve core 6 and close on main valve plug 5 aperture of keeping right and holding, the right-hand member spring chamber of main valve plug 5 is communicated with the A chamber, then promoting main valve plug 5 moves right together with nonreturn valve core 6, the throttle orifice that main valve plug 5 left end small columns put is progressively opened, hydraulic oil flows to the A chamber from the B chamber, in this process, the aperture of main valve plug 5 restrictions is controlled by the hydraulic oil in C chamber, the B cavity pressure that main valve plug 5 restriction throttlings are set up and hydraulic jack induced pressure coupling, ensure the controlled decline of load.
Of the present inventionly from the B chamber to all sealing pairs in A chamber, all adopted the mechanical wires sealing, the reliability of its sealing and sealing pair life-span are all strong than the sealing of the Sealing of prior art.The difference that the opening and closing pressure difference of secondary relief valve of the present invention deducts lift-off pressures by B cavity pressure impact value is controlled, control more rationally with controlled, throttle orifice on damping plug 11 can effectively suppress the response overshoot of overflow spool 14, and set up a damping buffering when overflow spool 14 is closed, be conducive to improve its stability.Several radially throttling pore of close its sealing cone of overflow spool 14 left ends of the second class protection relief valve of the present invention axially structural type of throttling groove are arranged on the cylindrical of overflow spool 14.Damping plug 11 of the present invention also can replace with one-way damper valve.Damping plug 11 of the present invention also can cover to replace with damping.
The return spring of the overflow spool 14 of second class protection relief valve of the present invention can be with two.
Four, accompanying drawing explanation:
Accompanying drawing 1 is structural drawing of the present invention.
Five, embodiment:
The embodiment of equilibrium valve of the present invention is: the sealing operating mode: the high pressure oil in B chamber is by the aperture of the end of keeping right on main valve plug 5, with the spring chamber of main valve plug 5 right-hand members, be communicated with, nonreturn valve core 6 is all locked with its sealing seat with main valve plug 5 under the effect of high pressure oil and spring separately, has closed the flow channel of the high pressure oil in B chamber to the A chamber.Hydraulic oil flows to B chamber operating mode from the A chamber, nonreturn valve core 6 is under the effect of little spring 7, in closed condition, the right chamber of main valve plug 5 is in being communicated with the B chamber, the hydraulic oil promotion main valve plug 5 in A chamber compresses main spring 9 together with nonreturn valve core 6 and moves right, the throttle orifice that main valve plug 5 left end small columns put is opened, and hydraulic oil this restriction of flowing through flows to the B chamber from the A chamber.Hydraulic oil flows to A chamber operating mode from the B chamber: pressure oil is supplied with in the C chamber, throttle orifice on orifice plug 1 promotes piston 4 and moves to right, first promote nonreturn valve core 6 and close on main valve plug 5 aperture of keeping right and holding, the right-hand member spring chamber of main valve plug 5 is communicated with the A chamber, then promoting main valve plug 5 moves right together with nonreturn valve core 6, the throttle orifice that main valve plug 5 left end small columns put is progressively opened, and hydraulic oil flows to the A chamber from the B chamber.
The working procedure of second class protection relief valve is: the left chamber of overflow spool 14 is identical with the A chamber by one-way valve, in just being full of the pressure oil equated with lift-off pressures and being closed and being kept in the lifting process of oil cylinder; The difference that deducts lift-off pressures when the B cavity pressure impact value caused by dynamic load is multiplied by the spring force that power that the sectional area of overflow spool 14 produces is greater than relief valve spring 15, overflow spool 14 is pushed to and moves to left, the pressure oil in B chamber flows to the left chamber of overflow spool 14 from flow through the radially throttling pore of left end of the axial restraint throttling pore in overflow spool 14 center portions, and promoted the pressurized air that 21 compressions of air bag barrier film have been filled with simultaneously and be moved to the left, received the pressure surge that the B chamber caused by dynamic load and the liquid be discharged from; Along with the release of B chamber surge pressure, original equilibrium of forces is broken, and under the effect of the pressure that overflow spool 14 stores at relief valve spring 15 and the air chamber that separated by air bag barrier film 21, moves right; In this of overflow spool 14 moves closing process, during the B cavity pressure stores lower than the air chamber that separated by air bag barrier film 21 if occur pressure, the liquid that the oil cylinder cavity of resorption is that discharge in this release of pressure process, receive during gas compression that separated by air bag barrier film 21, can push steel ball 27 open through cage 24 and flow back to the oil cylinder cavity of resorption.So just can guarantee that jib still can get back to original position after discharging the surge pressure caused by dynamic load, and suppress the runout that jib may occur.
Claims (5)
1. the equilibrium valve of a dynamic load differential pressure security and the compensation of flow pressure air chamber, equilibrium valve mainly is comprised of orifice plug (1), valve body (3), control piston (4), main valve plug (5), nonreturn valve core (6), little spring (7), submissile spring abutment (8), main spring (9), main spring seat (10); The second class protection relief valve mainly is comprised of valve body (3), damping plug (11), overflow spool (14), relief valve spring (15), relief valve spring seat (16), cage (24), nut cap (17), locking nut (18), air chamber base (19), air bag cushion (21), steel ball (27) and little spring (26); Wherein by nut cap (17), air chamber base (19), air bag cushion (21), steel ball (27) and little spring (26) etc., form a flow pressure compensator, be filled with the inert gas equated with the oil cylinder abutment pressure before installing and using; Be provided with an one-way valve formed by spring seat (25), little spring (26) and steel ball (27) and valve body (3) etc. between them; Also have a little relief valve be comprised of valve body (3), spring (28), steel ball (22) and spring seat (29), its oil pressure relief is higher than the oil cylinder abutment pressure; Four combine connection has formed the present invention; Equilibrium valve is characterised in that: nonreturn valve core (6) is sleeved in the hole of main valve plug (5), and the endoporus right angle of its male cone (strobilus masculinus) and main valve plug (5) has formed a sealing pair, and forms Pilot operated check valve with little spring (7), submissile spring abutment (8); Have several uniform axial sulculuses on main valve plug (5) right-hand member large cylinder, be communicated with the cavity volume between B chamber and main spring seat (10) and valve body (3); The second class protection relief valve is characterised in that: restriction is combined by the restriction of two series windings; The B chamber is communicated with the fixed orifice of its central position by the radial hole that is arranged on overflow spool (14) intermediate portion; The fixed orifice of overflow spool (14) central position also has been communicated with the cavity volume of its right-hand member by damping plug (11); Also be provided with a repairing one-way valve formed by cage (24) and little spring (26) and steel ball (27) at the left end of overflow spool (14).
2. the equilibrium valve that a kind of dynamic load differential pressure security according to claim 1 and flow pressure air chamber compensate, it is characterized in that: the damping plug of second class protection relief valve (11) replaces with one-way throttle valve.
3. the equilibrium valve that a kind of dynamic load differential pressure security according to claim 1 and flow pressure air chamber compensate is characterized in that: the restriction of overflow spool (14) is arranged on overflow spool (14) by the cylindrical of sealing cone end with the structural type of axial throttling groove.
4. the equilibrium valve that a kind of dynamic load differential pressure security according to claim 1 and flow pressure air chamber compensate, it is characterized in that: damping plug (11) covers to replace with damping.
5. the equilibrium valve of a kind of dynamic load differential pressure security according to claim 1 and the compensation of flow pressure air chamber, is characterized in that: two return springs for overflow spool (14).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320055566 CN203362668U (en) | 2013-01-31 | 2013-01-31 | Balance valve of dynamic load differential pressure protection and flow pressure air chamber compensation |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201320055566 CN203362668U (en) | 2013-01-31 | 2013-01-31 | Balance valve of dynamic load differential pressure protection and flow pressure air chamber compensation |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203362668U true CN203362668U (en) | 2013-12-25 |
Family
ID=49810442
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201320055566 Expired - Fee Related CN203362668U (en) | 2013-01-31 | 2013-01-31 | Balance valve of dynamic load differential pressure protection and flow pressure air chamber compensation |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203362668U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105370641A (en) * | 2015-12-07 | 2016-03-02 | 浙江美科斯叉车有限公司 | Differential pressure protecting system for pitching oil cylinders of container reach stacker |
| CN106481866A (en) * | 2016-11-16 | 2017-03-08 | 广州市精鼎电器科技有限公司 | The multifunctional servo control device being convenient to clean |
| CN108974333A (en) * | 2018-08-17 | 2018-12-11 | 中航飞机起落架有限责任公司 | A kind of full liquid shock absorber and compensation device |
-
2013
- 2013-01-31 CN CN 201320055566 patent/CN203362668U/en not_active Expired - Fee Related
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105370641A (en) * | 2015-12-07 | 2016-03-02 | 浙江美科斯叉车有限公司 | Differential pressure protecting system for pitching oil cylinders of container reach stacker |
| CN105370641B (en) * | 2015-12-07 | 2017-03-08 | 浙江美科斯叉车有限公司 | Pitching oil cylinder differential pressure security system for container front crane |
| CN106481866A (en) * | 2016-11-16 | 2017-03-08 | 广州市精鼎电器科技有限公司 | The multifunctional servo control device being convenient to clean |
| CN108974333A (en) * | 2018-08-17 | 2018-12-11 | 中航飞机起落架有限责任公司 | A kind of full liquid shock absorber and compensation device |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN103089737A (en) | Balance valve of dynamic load differential pressure protection and flow pressure air chamber compensation | |
| CN100441885C (en) | Hydraulic balance valve capable of automatically adapting load change | |
| TWI554416B (en) | Height adjustment device | |
| WO2011040808A3 (en) | Adjustable shock absorber | |
| CN203362668U (en) | Balance valve of dynamic load differential pressure protection and flow pressure air chamber compensation | |
| KR101675660B1 (en) | Actuator | |
| CN103089736A (en) | Balance valve and differential pressure protection controlling method of two-level protection overflow valve thereof | |
| EP3581489B1 (en) | Dual-stage, separated gas/fluid shock strut servicing | |
| CN204226320U (en) | Equilibrium valve and truck crane | |
| CN103089735A (en) | Dynamic load differential pressure protection balance valve controlled by three-level overflow valve | |
| CN203272298U (en) | Dynamic load differential pressure protective balance valve controlled by three-level overflow valve | |
| US3036669A (en) | Hydraulic shock absorber with compression cut-off | |
| CN108437734B (en) | Hydro-pneumatic suspension system and engineering machinery with same | |
| CN108825577B (en) | Balance valve with variable hydraulic control ratio | |
| CN104444893A (en) | Winch control system | |
| CN104310221A (en) | Double cylinder synchronous and independent control method, system and crane | |
| CN204281092U (en) | A kind of two-tank method and separately control system and hoisting crane | |
| CN203373114U (en) | Tube explosion resistant oil hydraulic circuit of vertical lifting mechanism | |
| CN103089730A (en) | Balance valve for pump truck and response differential pressure control method of secondary overflow valve of balance valve for pump truck | |
| CN103115029A (en) | Balance valve for pump truck and secondary overflow valve response differential pressure control method thereof | |
| CN203655745U (en) | Hydro-pneumatic suspension hydraulic system and engineering vehicle | |
| CN203488477U (en) | Second-level synchronous hydraulic cylinder | |
| CN201874925U (en) | Adjustable buffer structure of hydraulic cylinder | |
| CN202108801U (en) | Built-in speed limiting valve for fork truck | |
| CN203081887U (en) | Secondary overflow valve of balance valve for pump truck |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20131225 Termination date: 20180131 |