CN103148036A - Hydraulic valve - Google Patents
Hydraulic valve Download PDFInfo
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- CN103148036A CN103148036A CN2013100877292A CN201310087729A CN103148036A CN 103148036 A CN103148036 A CN 103148036A CN 2013100877292 A CN2013100877292 A CN 2013100877292A CN 201310087729 A CN201310087729 A CN 201310087729A CN 103148036 A CN103148036 A CN 103148036A
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Abstract
The invention discloses a hydraulic valve, which consists of a differential pressure control unloading valve (21) and two or more flow direction control valves (22), wherein the differential pressure control unloading valve (21) consists of a control valve body (1), a hydraulic control one-way valve core (2), a differential pressure control valve core (3), a differential pressure control spring (4), an overflow valve (5) and a speed regulating valve (6); each flow direction control valve (22) consists of a valve body (7), a control valve rod (8), a valve rod control spring (9), a pressure compensating valve core (10), a hydraulic control one-way valve control oil circuit (11) and a load retaining one-way valve (13); and the flow of hydraulic oil supplied to each current working device by using the hydraulic pump is proportional to the through-flow area of the valve port opening of a corresponding flow direction control valve (22), and is irrelevant to the load magnitude.
Description
Technical field
The present invention relates to a kind of hydrovalve, concrete is a kind of hydrovalve that supplies flow and valve rod opening flow area relation in direct ratio.
Background technique
At present, known main-control valve of excavating machine mainly contains: the minus flow control valve, positive flow control valve, LS control valve, the LUDV control valve that 1, are applied to variable system, when minus flow control valve, positive flow control valve are worked simultaneously when a plurality of actuators, relevant to load to flow that each actuator supplies, handling poor, above various main control valve can only be applied to variable delivery hydraulic system, if be used for fixed dilivery hydraulic system, due to directly off-load oil return of meta, will bring the problems such as the hydraulic system energy consumption is too high, heating value is excessive.2, be applied to the switching mode multiple directional control valve of fixed dilivery hydraulic system, when single or multiple actuators work simultaneously, relevant to load to flow that each actuator supplies, hydraulic shock is large, and is handling poor, mostly do not carry out joint operation in situation, at the bottom of working efficiency.
Summary of the invention
Relevant to load to flow that actuator supplies with the fixed dilivery hydraulic system main control valve in order to overcome existing excavator, handling poor, hydraulic shock is large, joint operation is difficult, the problem such as at the bottom of working efficiency, the invention provides. a kind of hydrovalve, be comprised of pressure reduction control unloading valve, two or more flow direction control valves, described pressure reduction is controlled unloading valve and is comprised of control valve body, fluid-control one-way spool, pressure difference control valve core, pressure reduction control spring, relief valve, series flow control valve; Described flow direction control valve keeps one-way valve to form by valve body, control valve rod, valve rod control spring, pressure compensation spool, Pilot operated check valve oil circuit control, load, oil hydraulic pump to current each equipment the hydraulic fluid flow rate of confession and the flow area relation in direct ratio of corresponding discharge position control valve valve port opening, and irrelevant with load.
Further, described flow direction control valve also comprises the secondary relief valve, determines whether as required configuration.
Further, when hydraulic system was not worked, each described flow direction control valve all was in the neutral position, and the hydraulic oil that described oil hydraulic pump provides is through the oil return of Pilot operated check valve oil circuit.
Further, when one or more described flow direction control valve commutation work, described Pilot operated check valve oil circuit control is closed.
Further, when single flow direction control valve work, the forward and backward pressure reduction of the flow direction control valve valve port opening of work at present is controlled described pressure reduction control unloading valve and whether is opened off-load, unnecessary hydraulic oil is controlled the unloading valve off-load through pressure reduction, makes the forward and backward pressure reduction of flow direction control valve valve port opening of work at present keep constant.
Further, when two and the work of two the above flow direction control valves, oil hydraulic pump through each flow direction control valve of work at present simultaneously to the respective execution mechanisms fuel feeding, meanwhile get the forward and backward pressure reduction control of the flow direction control valve valve port opening pressure reduction control unloading valve that working pressure is the highest instantly and whether open off-load, unnecessary hydraulic oil is controlled the unloading valve off-load through pressure reduction.
Further, at this moment, the control oil of LS oil circuit control is from the highest flow direction control valve valve port open rearward end of work at present pressure, relevant pressure recuperation valve on each lower flow direction control valve of working pressure cuts out towards the oil circuit control of LS, thereby the LS oil circuit control compensates the forward and backward pressure of flow direction control valve valve port opening of work at present, makes the forward and backward pressure reduction of each flow direction control valve valve port opening of work at present keep the same.
When this hydrovalve is in the neutral position from the hydraulic oil of oil hydraulic pump through the Pilot operated check valve oil return, can solve well that hydrovalve is relevant to load to flow that each actuator supplies, hydraulic shock is large, handling poor, mostly do not carry out joint operation, inefficiency in situation, the problem such as energy consumption is high, heating value is large.
This valve is irrelevant to each working hole fuel supply flow rate and load, determined by corresponding valve rod opening flow area, the flow that supplies and valve rod opening flow area relation in direct ratio; This valve can be controlled a plurality of actuators simultaneously, and is irrelevant to flow that each actuator supplies and load, and with corresponding valve rod opening flow area relation in direct ratio, possess the anti-saturation ability.Working flow that this valve supplies and load have nothing to do, also can control simultaneously the joint work of a plurality of actuators, handling good, high working efficiency.
Description of drawings
Fig. 1 is the hydraulic schematic diagram of hydrovalve of the present invention;
Fig. 2 is that the pressure reduction of hydrovalve of the present invention is controlled the unloading valve structural drawing;
Fig. 3 is the flow direction control valve structural drawing of hydrovalve of the present invention.
Embodiment
The present invention is further described below in conjunction with accompanying drawing.
As Figure 1-3, hydrovalve of the present invention mainly is comprised of pressure reduction control unloading valve 21, two or more flow direction control valves 22.Described pressure reduction is controlled unloading valve 21 and mainly is comprised of control valve body 1, fluid-control one-way spool 2, pressure difference control valve core 3, pressure reduction control spring 4, relief valve 5, series flow control valve 6 etc.; Flow direction control valve 22 mainly is comprised of valve body 7, control valve rod 8, valve rod control spring 9, pressure compensation spool 10, Pilot operated check valve oil circuit control 11, secondary relief valve 12, load maintenance one-way valve 13 etc., and secondary relief valve 12 determines whether configuration as required.
as shown in Figure 1, hydrovalve working principle of the present invention is: 1, when hydraulic system is not worked, each flow direction control valve 22 all is in neutral position Pilot operated check valve oil circuit control 11 and communicates with oil return, and the hydraulic oil that oil hydraulic pump provides is through Pilot operated check valve 2 oil returns, 2, when hydraulic system is in running order, one or more flow direction control valve 22 commutation work, Pilot operated check valve oil circuit control 11 is closed, Pilot operated check valve 2 is closed, arrive the oil circuit sealing of oil return from the hydraulic oil of oil hydraulic pump, oil hydraulic pump through flow direction control valve 22 to the equipment fuel feeding: 1) when single flow direction control valve 22 work, oil hydraulic pump is through the flow direction control valve 22 of work at present equipment and the LS oil circuit control fuel feeding to work at present, before the flow direction control valve 22 valve port openings of work at present, rear pressure reduction is controlled pressure reduction control unloading valve 21 and whether is opened off-load, unnecessary hydraulic oil is controlled unloading valve 21 off-loads through pressure reduction, before making the flow direction control valve valve port opening of work at present, it is constant that rear pressure reduction keeps, thereby oil hydraulic pump to the work at present device the hydraulic fluid flow rate of confession and the flow area relation in direct ratio of flow direction control valve valve port opening, and it is irrelevant in load, 2) when two and two above flow direction control valves work, oil hydraulic pump through each flow direction control valve 22 of work at present simultaneously to the respective execution mechanisms fuel feeding, before this gets the flow direction control valve valve port opening that working pressure is the highest instantly simultaneously, rear pressure reduction is controlled pressure reduction control unloading valve and whether is opened off-load, unnecessary hydraulic oil is controlled unloading valve 21 off-loads through pressure reduction, this moment the LS oil circuit control control oil from working pressure is the highest instantly flow direction control valve 22 valve port open rearward end, relevant pressure recuperation valve on each lower flow direction control valve 22 of working pressure cuts out towards the oil circuit control of LS, thereby before the flow direction control valve 22 valve port openings of LS oil circuit control to work at present, rear pressure compensates, before making each flow direction control valve valve port opening of work at present, it is the same that rear pressure reduction keeps, thereby oil hydraulic pump to current each equipment the hydraulic fluid flow rate of confession and the flow area relation in direct ratio of corresponding discharge position control valve valve port opening, flow area by corresponding discharge position control valve 22 valve port openings carries out pro rate, and it is irrelevant with load.
as shown in Figure 2, pressure reduction is controlled unloading valve 21 and mainly is comprised of control valve body 1, fluid-control one-way spool 2, pressure difference control valve core 3, pressure reduction control spring 4, relief valve 5, series flow control valve 6 etc., when the oil circuit control of fluid-control one-way spool 2 communicates with oil return circuit through each flow direction control valve 22, the 2 oil circuit control oil returns of fluid-control one-way spool, fluid-control one-way spool 2 is opened under the pressure-acting from the hydraulic oil of oil hydraulic pump, from the hydraulic oil oil return of squeeze pump, when one or more flow direction control valve 22 work, fluid-control one-way spool oil circuit control is closed, this moment, the hydraulic fluid pressure of fluid-control one-way spool oil circuit control equated with hydraulic fluid pressure from oil hydraulic pump, fluid-control one-way spool 2 is closed, oil hydraulic pump through flow direction control valve 22 to the equipment fuel feeding, unnecessary hydraulic oil is controlled 3 off-loads of off-load spool through pressure reduction, before pressure reduction control off-load spool 3 is used for guaranteeing flow direction control valve valve port opening with pressure reduction control spring 4, it is constant that rear pressure reduction keeps, unnecessary hydraulic oil off-load, and when working pressure reaches setting pressure, relief valve 5 is opened, the overflow of LS oil circuit, pressure reduction is controlled off-load spool 3 overcomes pressure reduction control spring 4 under the hydraulic fluid pressure effect from oil hydraulic pump spring force unlatching, hydraulic oil from oil hydraulic pump is controlled 3 overflows of off-load spool through pressure reduction, guarantee the hydraulic system trouble free service, series flow control valve 6 is used for guaranteeing that the pilot pressure of LS oil circuit control in time disappears and less flow loss.
As shown in Figure 3, flow direction control valve 22 mainly is comprised of valve body 7, control valve rod 8, valve rod control spring 9, pressure compensation spool 10, Pilot operated check valve oil circuit control 11, secondary relief valve 12, load maintenance one-way valve 13 etc., and secondary relief valve 12 determines whether configuration as required.Control the Main Function of valve rod 8 and valve rod control spring 9: 1, control from the hydraulic oil of the oil hydraulic pump fuel feeding direction to actuator; The flow area of the valve port opening that 2, control is relevant to fuel supply flow rate for the execution speed of controlling actuator, guarantees controllability, mechanism's traveling comfort of the execution speed of actuator; 3, control oil circuit control directly oil return when each flow direction control valve all is in the neutral position that Pilot operated check valve oil circuit control 11 guarantees Pilot operated check valves, make Pilot operated check valve be in the enable possition, from the hydraulic oil of oil hydraulic pump through the Pilot operated check valve oil return; When guaranteeing that one or more flow direction control valves are in running order, the oil circuit control of Pilot operated check valve is in closed condition, seal with oil return circuit, the oil circuit control pressure of Pilot operated check valve equates with the hydraulic fluid pressure from oil hydraulic pump, Pilot operated check valve is closed under the pilot pressure effect, this moment oil hydraulic pump through flow direction control valve to the equipment fuel feeding.when pressure compensation spool 10 is worked simultaneously for two or more flow direction control valves, before getting the highest flow direction control valve valve port opening of work at present pressure, rear pressure reduction is controlled pressure reduction control unloading valve 21 and whether is opened off-load, unnecessary hydraulic oil is controlled unloading valve 21 off-loads through pressure reduction, the control oil of LS oil circuit control is from the highest flow direction control valve valve port open rearward end of work at present pressure at this moment, relevant pressure recuperation valve on each lower flow direction control valve of working pressure cuts out towards the oil circuit control of LS, thereby before the flow direction control valve valve port opening of LS oil circuit control to work at present, rear pressure compensates, before making each flow direction control valve valve port opening of work at present, it is the same that rear pressure reduction keeps, thereby oil hydraulic pump to current each equipment the hydraulic fluid flow rate of confession and the flow area relation in direct ratio of corresponding discharge position control valve valve port opening, flow area by corresponding discharge position control valve valve port opening carries out the pro rate flow, and it is irrelevant with load, secondary relief valve 21 determines whether configuration according to the need of work of each flow direction control valve, is mainly used in the effects such as buffering and anti-locking system overload, load keeps one-way valve 13 to prevent that hydraulic oil from refluxing, the first-class phenomenon of equipment appearance point.
Claims (7)
1. hydrovalve, be comprised of pressure reduction control unloading valve (21), two or more flow direction control valves (22), it is characterized in that: described pressure reduction is controlled unloading valve (21) and is comprised of control valve body (1), fluid-control one-way spool (2), pressure difference control valve core (3), pressure reduction control spring (4), relief valve (5), series flow control valve (6); Described flow direction control valve (22) keeps one-way valve (13) to form by valve body (7), control valve rod (8), valve rod control spring (9), pressure compensation spool (10), Pilot operated check valve oil circuit control (11), load, oil hydraulic pump to current each equipment the hydraulic fluid flow rate of confession and the flow area relation in direct ratio of corresponding discharge position control valve (22) valve port opening, and irrelevant with load.
2. hydrovalve as claimed in claim 1, it is characterized in that: described flow direction control valve (22) also comprises secondary relief valve (12), determines whether as required configuration.
3. hydrovalve as claimed in claim 1, it is characterized in that: when hydraulic system was not worked, each described flow direction control valve (22) all was in the neutral position, and the hydraulic oil that described oil hydraulic pump provides is through Pilot operated check valve oil circuit (11) oil return.
4. hydrovalve as claimed in claim 1 is characterized in that: when one or more described flow direction control valves (22) commutation work, described Pilot operated check valve oil circuit control (11) is closed.
5. hydrovalve as claimed in claim 5, it is characterized in that: when single flow direction control valve (22) is worked, the forward and backward pressure reduction of the flow direction control valve of work at present (22) valve port opening is controlled described pressure reduction control unloading valve (21) and whether is opened off-load, unnecessary hydraulic oil is controlled unloading valve (21) off-load through pressure reduction, makes the forward and backward pressure reduction of flow direction control valve (22) valve port opening of work at present keep constant.
6. hydrovalve as claimed in claim 1, it is characterized in that: when the work of two and two the above flow direction control valves (22), oil hydraulic pump through each flow direction control valve (22) of work at present simultaneously to the respective execution mechanisms fuel feeding, meanwhile get the forward and backward pressure reduction control pressure reduction control unloading valve of flow direction control valve valve port opening (21) that working pressure is the highest instantly and whether open off-load, unnecessary hydraulic oil is controlled unloading valve (21) off-load through pressure reduction.
7. hydrovalve as claimed in claim 6, it is characterized in that: at this moment, the control oil of LS oil circuit control is from the highest flow direction control valve (22) the valve port open rearward end of work at present pressure, relevant pressure recuperation valve on lower each flow direction control valve (22) of working pressure cuts out towards the oil circuit control of LS, thereby the LS oil circuit control compensates the forward and backward pressure of flow direction control valve valve port opening of work at present, makes the forward and backward pressure reduction of each flow direction control valve (22) valve port opening of work at present keep the same.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310087729.2A CN103148036B (en) | 2013-03-19 | 2013-03-19 | Hydrovalve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310087729.2A CN103148036B (en) | 2013-03-19 | 2013-03-19 | Hydrovalve |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103148036A true CN103148036A (en) | 2013-06-12 |
| CN103148036B CN103148036B (en) | 2015-09-09 |
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ID=48546293
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310087729.2A Expired - Fee Related CN103148036B (en) | 2013-03-19 | 2013-03-19 | Hydrovalve |
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| Country | Link |
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| CN (1) | CN103148036B (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103452935A (en) * | 2013-08-27 | 2013-12-18 | 北京机械设备研究所 | Hydraulic valve for closed system with pump output pressure not interfered by load |
| CN104500477A (en) * | 2014-12-18 | 2015-04-08 | 宁波市镇海展跃液压件制造有限公司 | Pressure release type hydraulic control one-way logical valve |
| CN104912857A (en) * | 2014-03-11 | 2015-09-16 | 江苏科迈液压控制***有限公司 | Multi-way valve |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20030115865A1 (en) * | 2001-12-21 | 2003-06-26 | Volvo Construction Equipment Holding Sweden Ab | Hydraulic variable control apparatus for heavy construction equipment |
| CN2844532Y (en) * | 2005-07-19 | 2006-12-06 | 四川长江液压件有限责任公司 | Multi-path switching valve of hydraulic crane |
| CN101858368A (en) * | 2010-05-13 | 2010-10-13 | 山东泰丰液压设备有限公司 | Multiple directional control valve system for return oil throttle control with load sensitive pressure compensation |
| CN101936316A (en) * | 2010-09-30 | 2011-01-05 | 临海市海克力机械有限公司 | Positive flow control engineering machinery multi-path reversing valve |
-
2013
- 2013-03-19 CN CN201310087729.2A patent/CN103148036B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20030115865A1 (en) * | 2001-12-21 | 2003-06-26 | Volvo Construction Equipment Holding Sweden Ab | Hydraulic variable control apparatus for heavy construction equipment |
| CN2844532Y (en) * | 2005-07-19 | 2006-12-06 | 四川长江液压件有限责任公司 | Multi-path switching valve of hydraulic crane |
| CN101858368A (en) * | 2010-05-13 | 2010-10-13 | 山东泰丰液压设备有限公司 | Multiple directional control valve system for return oil throttle control with load sensitive pressure compensation |
| CN101936316A (en) * | 2010-09-30 | 2011-01-05 | 临海市海克力机械有限公司 | Positive flow control engineering machinery multi-path reversing valve |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103452935A (en) * | 2013-08-27 | 2013-12-18 | 北京机械设备研究所 | Hydraulic valve for closed system with pump output pressure not interfered by load |
| CN103452935B (en) * | 2013-08-27 | 2015-11-18 | 北京机械设备研究所 | A kind of pump delivery pressure is not by the closed system hydrovalve of load disturbance |
| CN104912857A (en) * | 2014-03-11 | 2015-09-16 | 江苏科迈液压控制***有限公司 | Multi-way valve |
| CN104500477A (en) * | 2014-12-18 | 2015-04-08 | 宁波市镇海展跃液压件制造有限公司 | Pressure release type hydraulic control one-way logical valve |
| CN104500477B (en) * | 2014-12-18 | 2016-08-24 | 宁波市镇海展跃液压件制造有限公司 | Pressure-releasing type fluid-control one-way logical valve |
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| Publication number | Publication date |
|---|---|
| CN103148036B (en) | 2015-09-09 |
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Granted publication date: 20150909 |
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