CN103089730A - Balance valve for pump truck and response differential pressure control method of secondary overflow valve of balance valve for pump truck - Google Patents
Balance valve for pump truck and response differential pressure control method of secondary overflow valve of balance valve for pump truck Download PDFInfo
- Publication number
- CN103089730A CN103089730A CN 201310020108 CN201310020108A CN103089730A CN 103089730 A CN103089730 A CN 103089730A CN 201310020108 CN201310020108 CN 201310020108 CN 201310020108 A CN201310020108 A CN 201310020108A CN 103089730 A CN103089730 A CN 103089730A
- Authority
- CN
- China
- Prior art keywords
- chamber
- valve
- spring
- plug
- main
- 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.)
- Pending
Links
- 238000000034 method Methods 0.000 title claims abstract description 19
- 230000004044 response Effects 0.000 title claims abstract description 10
- 238000013016 damping Methods 0.000 claims abstract description 30
- 239000010720 hydraulic oil Substances 0.000 claims description 19
- 238000007789 sealing Methods 0.000 claims description 19
- 239000003921 oil Substances 0.000 claims description 16
- 230000000694 effects Effects 0.000 claims description 12
- 230000008569 process Effects 0.000 claims description 10
- 239000012530 fluid Substances 0.000 claims description 9
- 230000007423 decrease Effects 0.000 claims description 4
- 230000006835 compression Effects 0.000 claims description 3
- 238000007906 compression Methods 0.000 claims description 3
- 239000007788 liquid Substances 0.000 claims description 3
- 239000000203 mixture Substances 0.000 claims description 3
- 239000011148 porous material Substances 0.000 claims description 3
- 230000001737 promoting effect Effects 0.000 claims description 3
- 230000035939 shock Effects 0.000 claims description 3
- 230000008878 coupling Effects 0.000 claims description 2
- 238000010168 coupling process Methods 0.000 claims description 2
- 238000005859 coupling reaction Methods 0.000 claims description 2
- 238000004804 winding Methods 0.000 claims description 2
- 238000005336 cracking Methods 0.000 description 2
- 230000008676 import Effects 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000007774 longterm Effects 0.000 description 1
Landscapes
- Safety Valves (AREA)
Abstract
The invention discloses a balance valve for a pump truck and a response differential pressure control method of a secondary overflow valve of the balance valve for the pump truck. The balance valve for the pump truck is structurally and mainly composed of an orifice plug 1, a valve body 3, a control piston 4, a main valve core 5, a one-way valve core 6, a small spring 7, a small spring seat 8, a main spring 9, a main spring seat 10, a damping plug 11, an overflow valve core 14, an overflow valve spring 15, an overflow valve spring seat 16, a locking nut 17, an adjusting screw rod 18, an adjusting seat 19 and other components. The opening and closing pressure difference control principle of the secondary overflow valve is that as long as the overflow valve core 14 is flushed open and oil flows, the force balanced with the spring force of the overflow valve spring 15 turns into the force which is obtained by adding the force I generated by multiplying pressure of a cavity A by the area of a small overflow hole in the valve body 3, and the force II generated by multiplying a pressure value obtained from a small damping hole in the damping plug 11 by the area obtained by deducting a circular area of the area of the small overflow hole in the valve body 3 from the sectional area of a guiding support column of the overflow valve core 14; and the pressure drop generated by the small damping hole forms the differential pressure of the overflow valve core 14 at the closing time and the opening time.
Description
One, technical field:
The present invention relates to a kind of pump truck and respond differential pressure control method with equilibrium valve and secondary relief valve thereof.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:
China's to be the supporting equilibrium valve of heavy mechanized equipment product pass by so far from the series product of first autonomous Design to the design of system type many decades along with the development of main frame, improves constantly its every usability requirement.Original equilibrium valve product can not adapt to, and the main deficiency that they reveal is: the runner conveyance capacity is poor, and the pressure loss is large; Pilot pressure is high, and system's temperature rise is fast; Sealing reliability is poor, and the life-span is short; Lack the flow sectional control function.In order to satisfy the usage requirement of main frame, each enterprise adopts import equilibrium valve product supporting in some on mainframe, but the contradiction with China's main computer boxes hydraulic system turbidity test in use occurred.A large amount of throttling pore that adopt Φ 0.3 ~ Φ 0.4 in the oil circuit control of these imported products and Counterfeit Item thereof.Such throttling pore is stopped up in actual use often generation, causes host computer control malfunctioning.In addition, the development of heavy machinery equipment proposes some new performance requirements to the performance requirement of equilibrium valve, the difference requirements that just cracking pressure and the closing pressure of its secondary relief valve is had 15% left and right with equilibrium valve as concrete pump truck arm.And these are that present domestic equilibrium valve is not available, have caused so the long-term dependence on import accessory of this series products, have hindered the development of China's main frame equipment.
Three, summary of the invention:
Purpose of the present invention be exactly to develop a kind of reliable performance, structure is relatively simple, pump truck equilibrium valve with Novel two-stage relief valve opening and closing pressure gap controlling method.
Solution of the present invention is: a kind of pump truck responds differential pressure control method with equilibrium valve and secondary relief valve thereof, 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, overflow spool 14, relief valve spring 15, relief valve spring seat 16, locking nut 17, adjusting screw rod 18 and adjustment seat 19 etc.; Both make up to be communicated with and have consisted of 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 the Pilot operated check valve that the A chamber still is communicated with the B chamber with little spring 7, submissile spring abutment 8 composition control main valve plug 5 right-hand member spring chambers; Have three uniform axial sulculuses on main valve plug 5 right-hand member large cylinders, be communicated with the cavity volume between A 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, is provided with Sealing at their matching part; 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. form the hydraulic-control throttling valve; The composition hydraulic oil such as valve body 3, main valve plug 5, nonreturn valve core 6, little spring 7, submissile spring abutment 8, main spring 9, main spring seat 10 flow to the one-way valve in A chamber from the B chamber.The secondary relief valve is characterised in that: restriction is combined by the restriction of two series windings; The opening and closing pressure gap control principle of second class protection relief valve is: when the A cavity pressure that caused by dynamic load impacts power that the area of aperture on duty and valve body 3 produces greater than the spring force of overflow spring 15, overflow spool 14 is pushed to and moves to left, the damping hole that the pressure oil in A chamber aperture from the valve body 3 is flowed through through damping plug 11 flows to the B chamber, has discharged the compression shock that is caused by dynamic load; In this process, the power that overflow spool 14 is opened by the surge pressure in A chamber is the power that sectional area produced that the surge pressure in A chamber multiply by aperture on valve body 3, as long as overflow spool 14 is rushed to open and have fluid to flow, multiply by with regard to the pressure that has become by the A chamber power that on valve body 3, the aperture sectional area produces with the power of the spring force balance of relief valve spring 15, add that force value that the damping hole on damping plug 11 is set up multiply by the power that produces on the ring area of the sectional area deduction valve body 3 little hole areas of overflow of overflow spool 14 guide support cylinders; The opening of overflow spool 14 is issued to new balance in their effect, and the result that fluid flows out is exactly the release of A chamber surge pressure; Along with the release of A chamber surge pressure, original equilibrium of forces is broken, and overflow spool 14 moves to closing direction under the effect of the spring force of relief valve spring 15; In this of overflow spool 14 moves closing process, still have fluid to flow to the B chamber from the A chamber, the flow through needed force value of damping hole on damping plug 11 of this liquid multiply by power that the ring area of the sectional area deduction valve body 3 little hole areas of overflow of overflow spool 14 guide support cylinders produces and has just consisted of when closing response pressure difference when opening response; Its cracking pressure is set up according to the requirement of main frame by relief valve spring 15, relief valve spring seat 16, locking nut 17, adjusting screw rod 18 and adjustment seat 19; Determine and close poor diameter and the length by the damping hole on damping plug 11 of response pressure; Working principle of the present invention is: the sealing operating mode: the high pressure oil in A chamber is by the aperture of the end of keeping right on main valve plug 5, be communicated with the spring chamber of main valve plug 5 right-hand members, nonreturn valve core 6 is all locked with its sealing seat under the effect of high pressure oil and spring separately with main valve plug 5, closed the high pressure oil in A chamber to the flow channel in B chamber, and sealing power strengthens with the increased pressure in A chamber.Hydraulic oil flows to A chamber operating mode from the B chamber, nonreturn valve core 6 is under the effect of little spring 7, be in closed condition, the right chamber of main valve plug 5 is in the A chamber and is communicated with, the hydraulic oil in B chamber promotes main valve plug 5 and compresses main spring 9 together with nonreturn valve core 6 and move right, and the restriction that main valve plug 5 left end small columns put is opened, and hydraulic oil this restriction of flowing through flows to the A chamber from the B chamber, in this process, main valve plug 5 right chamber is communicated with the A chamber.hydraulic oil flows to B chamber operating mode from the A chamber: C supplies with pressure oil in the chamber, move to right via the throttle orifice pushing piston 4 on orifice plug 1, first promote nonreturn valve core 6 and close the aperture of keeping right on main valve plug 5 and holding, the right-hand member spring chamber of main valve plug 5 is in and B chamber connected state, then promoting main valve plug 5 moves right together with nonreturn valve core 6, the restriction that main valve plug 5 left end small columns put is progressively opened, hydraulic oil flows to the B chamber from the A chamber, in this process, the aperture of main valve plug 5 restrictions is controlled by the hydraulic oil in C chamber, the A cavity pressure that main valve plug 5 restriction throttlings are set up and hydraulic jack induced pressure coupling, controlled decline is stablized in the guarantee load.
All sealing pairs of the present invention have all adopted the mechanical wires sealing, and the reliability of its sealing and sealing pair life-span are all strong than the Sealing sealing of existing importing technology.The opening and closing pressure difference of secondary relief valve of the present invention is fully by the orifices controls on damping plug 11, more reasonable and controlled than control of the prior art, the throttle orifice on damping plug 11 can effectively suppress the too large drawback of the A cavity pressure range of decrease that the response overshoot of overflow spool 14 under step input action causes.Throttle orifice on the damping plug 11 of the secondary relief valve of the present invention axially structural type of throttling groove is arranged on the cylindrical of overflow spool 14.
Four, description of drawings:
Accompanying drawing 1 is structural drawing of the present invention.
Five, embodiment:
The specific embodiment of the present invention is: when hydraulic oil flows to the A chamber from the B chamber, nonreturn valve core 6 is under the effect of little spring 7, be in closed condition, the right chamber of main valve plug 5 is communicated with the A chamber, hydraulic oil promotion main valve plug 5 compresses main spring 9 together with nonreturn valve core 6 and moves right, the restriction that main valve plug 5 left end small columns put is opened, and hydraulic oil flows to the A chamber from the B chamber.when hydraulic oil flows to the B chamber from the A chamber, pressure oil is supplied with in the C chamber, flow through and moved to right by the throttle orifice pushing piston 4 on orifice plug 1, first promote nonreturn valve core 6 and close the aperture of keeping right on main valve plug 5 and holding, the right-hand member spring chamber of main valve plug 5 is in and B chamber connected state, then promoting main valve plug 5 moves right together with nonreturn valve core 6, the restriction that main valve plug 5 left end small columns put is progressively opened, hydraulic oil flows to the B chamber from the A chamber, in this process, the aperture of main valve plug 5 restrictions is controlled by the hydraulic oil in C chamber, A cavity pressure and the hydraulic jack induced pressure set up by the restriction throttling of main valve plug 5 mate, controlled decline is stablized in the guarantee load.When this valve cuts out, the high pressure oil in A chamber is by the aperture of the end of keeping right on main valve plug 5, afterbody via nonreturn valve core 6 is communicated with the spring chamber of main valve plug 5 right-hand members, nonreturn valve core 6 is all locked with its sealing seat under the effect of high pressure oil and spring separately with main valve plug 5, closed the high pressure oil in A chamber to the flow channel in B chamber, and sealing power strengthens with the increased pressure in A chamber.
When the spring force of the power that the impact of A cavity pressure is on duty and areas valve body 3 overflow apertures produce that has dynamic load to cause greater than overflow spring 15, overflow spool 14 is pushed to and moves to left, the little damping hole that the pressure oil in A chamber is flowed through through damping plug 11 from this flow-off flows to the B chamber, has discharged the compression shock that is caused by dynamic load.In this process, the power that overflow spool 14 is opened by the surge pressure in A chamber is the power that sectional area produced that the surge pressure in A chamber multiply by aperture on valve body 3, as long as overflow spool 14 is rushed to open and have fluid to flow, multiply by with regard to the pressure that has become by the A chamber power that on valve body 3, the aperture sectional area produces with the power of the spring force balance of relief valve spring 15, add that force value that the damping hole on damping plug 11 is set up multiply by the power that produces on the ring area of the sectional area deduction valve body 3 little hole areas of overflow of overflow spool 14 guide support cylinders; The opening of overflow spool 14 is issued to new balance in their effect, and the result that fluid flows out is exactly the release of A chamber surge pressure; Along with the release of A chamber surge pressure, original equilibrium of forces is broken, and overflow spool 14 moves to closing direction under the effect of the spring force of relief valve spring 15; In this of overflow spool 14 moves closing process, still have fluid to flow to the B chamber from the A chamber, the flow through needed force value of damping hole on damping plug 11 of this liquid multiply by power that the ring area of the sectional area deduction valve body 3 little hole areas of overflow of overflow spool 14 guide support cylinders produces and has just consisted of when closing response pressure difference when opening response.
Claims (2)
1. a pump truck responds differential pressure control method with equilibrium valve and secondary relief valve thereof, 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), locking nut (17), adjusting screw rod (18) and adjustment seat (19) etc., both make up to be communicated with and have consisted of 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 the A chamber with little spring (7), submissile spring abutment (8) composition control main valve plug (5) right-hand member spring chamber and still is communicated with B chamber Pilot operated check valve, have three uniform axial sulculuses on main valve plug (5) right-hand member large cylinder, be communicated with the cavity volume between A 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 member is for movingly, is provided with Sealing at their matching part, the secondary relief valve is characterised in that: restriction is combined by the restriction of two series windings, and its two-step throttle mouth is arranged on damping plug (11) with the form of throttling pore, the opening and closing pressure gap control principle of second class protection relief valve is: when the A cavity pressure that caused by dynamic load impacts power that area on duty and the upper aperture of valve body (3) produces greater than the spring force of overflow spring (15), overflow spool (14) is pushed to and moves to left, the damping hole that the pressure oil in A chamber is flowed through through damping plug (11) from the upper aperture of valve body (3) flows to the B chamber, has discharged the compression shock that is caused by dynamic load, in this process, the power that overflow spool (14) is opened by the surge pressure in A chamber is the power that sectional area produced that the surge pressure in A chamber multiply by the upper aperture of valve body (3), as long as overflow spool (14) is rushed to open and have fluid to flow, multiply by with regard to the pressure that has become by the A chamber power that the upper aperture sectional area of valve body (3) produces with the power of the spring force balance of relief valve spring (15), add that the needed force value of damping hole on damping plug (11) multiply by the power that produces on the ring area of the little hole area of sectional area deduction valve body (3) overflow of overflow spool (14) guide support cylinder, the opening of overflow spool (14) is issued to new balance in their effect, and fluid flows out, and its result is exactly the release of A chamber surge pressure, along with the release of A chamber surge pressure, original equilibrium of forces is broken, and overflow spool (14) moves to closing direction under the effect of the spring force of relief valve spring (15), in this of overflow spool (14) moves closing process, still have fluid to flow to the B chamber from the A chamber, the flow through needed force value of damping hole on damping plug (11) of this liquid multiply by power that the ring area of the little hole area of sectional area deduction valve body (3) overflow of overflow spool (14) guide support cylinder produces and has just consisted of when closing response pressure difference when opening response, working principle of the present invention is: the sealing operating mode: the aperture of the high pressure oil in A chamber by keeping right on main valve plug (5) and holding, be communicated with the spring chamber of main valve plug (5) right-hand member, nonreturn valve core (6) is all locked with its sealing seat under the effect of high pressure oil and spring separately with main valve plug (5), has closed the high pressure oil in A chamber to the flow channel in B chamber, hydraulic oil flows to A chamber operating mode from the B chamber, nonreturn valve core (6) is under the effect of little spring (7), be in closed condition, the right chamber of main valve plug (5) is communicated with the A chamber, the hydraulic oil promotion main valve plug (5) in B chamber compresses main spring (9) together with nonreturn valve core (6) and moves right, the restriction that main valve plug (5) left end small column puts is opened, and hydraulic oil this restriction of flowing through flows to the A chamber from the B chamber, hydraulic oil flows to B chamber operating mode from the A chamber: C supplies with pressure oil in the chamber, move to right via the throttle orifice pushing piston (4) on orifice plug (1), first promote nonreturn valve core (6) and close the aperture of keeping right on main valve plug (5) and holding, the right-hand member spring chamber of main valve plug (5) is in and B chamber connected state, then promoting main valve plug (5) moves right together with nonreturn valve core (6), the restriction that main valve plug (5) left end small column puts is progressively opened, hydraulic oil flows to the B chamber from the A chamber, in this process, the aperture of main valve plug (5) restriction is controlled by the hydraulic oil in C chamber, the A cavity pressure that main valve plug (5) restriction throttling is set up and hydraulic jack induced pressure coupling, controlled decline is stablized in the guarantee load.
2. a kind of pump truck according to claim 1 responds differential pressure control method with equilibrium valve and secondary relief valve thereof, and it is characterized in that: the throttle orifice on the damping plug of secondary relief valve (11) the axially structural type of throttling groove is arranged on the cylindrical of overflow spool (14).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201310020108 CN103089730A (en) | 2013-01-21 | 2013-01-21 | Balance valve for pump truck and response differential pressure control method of secondary overflow valve of balance valve for pump truck |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201310020108 CN103089730A (en) | 2013-01-21 | 2013-01-21 | Balance valve for pump truck and response differential pressure control method of secondary overflow valve of balance valve for pump truck |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103089730A true CN103089730A (en) | 2013-05-08 |
Family
ID=48202711
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201310020108 Pending CN103089730A (en) | 2013-01-21 | 2013-01-21 | Balance valve for pump truck and response differential pressure control method of secondary overflow valve of balance valve for pump truck |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103089730A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104500475A (en) * | 2014-12-11 | 2015-04-08 | 湘潭大学 | Mechanical balance valve with foldable cantilever crane |
| CN110285104A (en) * | 2019-06-04 | 2019-09-27 | 常德中联重科液压有限公司 | Constant difference overflow valve and engineering machinery |
| CN112392788A (en) * | 2019-08-15 | 2021-02-23 | 罗伯特·博世有限公司 | Overflow valve |
-
2013
- 2013-01-21 CN CN 201310020108 patent/CN103089730A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104500475A (en) * | 2014-12-11 | 2015-04-08 | 湘潭大学 | Mechanical balance valve with foldable cantilever crane |
| CN110285104A (en) * | 2019-06-04 | 2019-09-27 | 常德中联重科液压有限公司 | Constant difference overflow valve and engineering machinery |
| CN110285104B (en) * | 2019-06-04 | 2020-12-01 | 常德中联重科液压有限公司 | Fixed-difference overflow valve and engineering machinery |
| CN112392788A (en) * | 2019-08-15 | 2021-02-23 | 罗伯特·博世有限公司 | Overflow valve |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN204186666U (en) | A kind of plug-in type load holding valve and hydraulic load retentive control system | |
| CN103089737A (en) | Balance valve of dynamic load differential pressure protection and flow pressure air chamber compensation | |
| CN103573735B (en) | Guide's heavy traffic load control valve of application displacement-force feedback principle | |
| CN103089730A (en) | Balance valve for pump truck and response differential pressure control method of secondary overflow valve of balance valve for pump truck | |
| CN203627369U (en) | Pressure compensation valve | |
| CN203784001U (en) | Overflow valve | |
| CN204226320U (en) | Equilibrium valve and truck crane | |
| CN103115029A (en) | Balance valve for pump truck and secondary overflow valve response differential pressure control method thereof | |
| CN201461573U (en) | Proportional flow valve | |
| CN103089736A (en) | Balance valve and differential pressure protection controlling method of two-level protection overflow valve thereof | |
| CN203176467U (en) | Direct-acting type overflow valve | |
| CN103867511B (en) | Flow control valve | |
| CN103321987A (en) | Hydraulic motor buffer control mechanism | |
| CN203081887U (en) | Secondary overflow valve of balance valve for pump truck | |
| CN203362668U (en) | Balance valve of dynamic load differential pressure protection and flow pressure air chamber compensation | |
| CN105422538B (en) | The multi-passage current sharing valve of pressure adaptive | |
| CN103089735A (en) | Dynamic load differential pressure protection balance valve controlled by three-level overflow valve | |
| CN105201942A (en) | Balance valve and automobile crane | |
| CN104162967A (en) | Quick hydraulic control device of hydraulic injection molding machine | |
| CN204729389U (en) | A kind of oil hydraulic cylinder with pressure-reducing cushioning | |
| CN104196802B (en) | Variable displacement control valve | |
| CN203272298U (en) | Dynamic load differential pressure protective balance valve controlled by three-level overflow valve | |
| CN103644338A (en) | Pressure regulating valve and balance valve assembly with same | |
| CN102878334A (en) | Flow-stabilizing controller | |
| CN103032562B (en) | The gearshift stable combination valve of power-shift transmission and shifting and pressure regulating system |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20130508 |