CN201593533U - Engineering machinery flow collecting valve - Google Patents
Engineering machinery flow collecting valve Download PDFInfo
- Publication number
- CN201593533U CN201593533U CN2009202847642U CN200920284764U CN201593533U CN 201593533 U CN201593533 U CN 201593533U CN 2009202847642 U CN2009202847642 U CN 2009202847642U CN 200920284764 U CN200920284764 U CN 200920284764U CN 201593533 U CN201593533 U CN 201593533U
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- over valve
- solenoid directional
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Abstract
The utility model discloses an engineering machinery flow collecting valve comprising a shuttle valve installed in the valve body, a solenoid directional valve, three hydraulic change-over valves, three check valves, a throttle valve and a relief valve, wherein a pressure oil port P is connected with the third hydraulic change-over valve through the check valve; the end A5 of the third hydraulic change-over valve is divided into two paths which are respectively connected with the end P3 and end P4 of the first hydraulic change-over valve and the second hydraulic change-over valve; the end A3 of the first hydraulic change-over valve is connected with the end C1 and the second end of the shuttle valve and then communicated with the port B; the end A4 of the second hydraulic change-over valve is connected with the end D1 and the first end of the shuttle valve and then communicated with the port A; the third end of the shutter valve is connected with the ends EI, E2 of the third hydraulic change-over valve and the end T2 of the solenoid directional valve; the pressure oil port P is also connected with the end P2 of the solenoid directional valve; and the ends C2, ends D2 and ends B5 of all the hydraulic change-over valves are connected with the end A2 of the solenoid directional valve and then communicated with the oil return port T. The flow collecting valve has simple structure, lower manufacturing cost, safety and reliability.
Description
Technical field
The utility model relates to a kind of interflow valve in the hydraulic system, particularly in the construction machinery hydraulic system two-way pressure oil is merged into one tunnel interflow valve before selector valve, belongs to hydraulic transmission technology field.
Background technique
Engineering machinery often will be accelerated the operating rate of facility in the course of the work, at this moment needs the output flow of two oil hydraulic pumps in the hydraulic system is exported by interflow valve and Cheng Yilu.Interflow valve in the existing construction machinery hydraulic system adopts following dual mode usually: 1. adopt the selector valve that has the interflow mouth to provide hydraulic oil to realize the interflow in selector valve two oil hydraulic pumps.2. adopt cartridge valve and the selector valve composite control formed by solenoid valve outside selector valve, to realize the interflow.But, be with the selector valve difficulty of processing of interflow mouth higher, cost an arm and a leg, in order to realize collaborating function, existing engineering machinery mainly selects selector valve to collaborate outward, promptly adopts cartridge valve and the selector valve composite control be made up of solenoid valve, realizes the interflow outside selector valve.Collaborate outward though this control mode can realize the valve in the hydraulic system, the control mode more complicated need be controlled two-way hydraulic oil during the interflow, and one road hydraulic oil is by electromagnetic valve, and another road hydraulic oil is controlled by selector valve.The A of selector valve output, B chamber must make interflow solenoid valve outage earlier when switching, the fluid of electromagnetic valve oil circuit is got back to fuel tank earlier; After switch in A, B chamber that selector valve is exported, could allow solenoid valve switch on once more, make the fluid and the oil circuit after the switching of the oil circuit of electromagnetic valve realize collaborating.As not cutting off the output high pressure oil of interflow pump earlier, two chambeies that actuator then can occur all are high pressure oils, the hydraulic system of spoiled work machinery during operation.
China's utility model patent (CN1136397C) discloses a kind of priority-type flow rate enlarging and merging valve, the left and right oil cylinder that turns to that is used for engineering machinery, this valve comprises valve body, amplifying valve, pressure-gradient control valve, cone valve, rib valve, when the guide oil that amplifies spool two ends all is cut off, cuts off this by priority spool and left and rightly turn to being connected of cylinder ports and pressure oil import; When guide oil promotes from amplifying spool right left, by amplifying valve, pressure-gradient control valve pressure oil import and right steering cylinder ports are connected gradually, when guide oil, is connected pressure oil import and left steering cylinder ports by the amplifying valve pressure-gradient control valve during to right-hand promotion gradually from the left that amplifies spool.This valve belongs in selector valve the structural type that realizes the interflow, exists complex structure inevitably, costs an arm and a leg and defective that difficulty of processing is higher.
The model utility content
The purpose of this utility model provides a kind of easy to use, interflow valve that cost is lower and safe and reliable.When hydraulic system need increase hydraulic fluid flow rate,, just can realize the interflow as long as it is electric that solenoid directional control valve is got; When A, the B chamber of selector valve output need directly to switch, need not cut off earlier and connect the solenoid directional control valve realization again after switchings such as solenoid directional control valve finished and collaborate, two chambeies that final controlling element can not occur all are the situations that high pressure oil causes the spoiled work machinery hydraulic system.
The utility model is achieved by the following technical programs:
A kind of engineering machinery interflow valve, comprise the shuttle valve that is installed in the valve body, solenoid directional control valve, first hydraulicchange-over valve, second hydraulicchange-over valve, the 3rd hydraulicchange-over valve, first one-way valve, second one-way valve, the 3rd one-way valve, throttle valve and relief valve, pressure hydraulic fluid port P communicates with oil return inlet T by relief valve, pressure hydraulic fluid port P also links to each other with the P5 end of the 3rd hydraulicchange-over valve by the 3rd one-way valve, the A5 end of the 3rd hydraulicchange-over valve is divided into two-way, link to each other with the P3 end of first hydraulicchange-over valve by first one-way valve respectively, link to each other with the P4 end of second hydraulicchange-over valve by second one-way valve; Logical B chamber delivery outlet after the A3 end of first hydraulicchange-over valve links to each other with C1 control end, shuttle valve second end, logical A chamber delivery outlet after the A4 end of second hydraulicchange-over valve links to each other with D1 control end, shuttle valve first end, shuttle valve the 3rd end links to each other with the E2 control end of the 3rd hydraulicchange-over valve and the T2 end of solenoid directional control valve by throttle valve, and links to each other with the E1 control end; Pressure hydraulic fluid port P also links to each other with the P2 end of solenoid directional control valve, and the C2 control end of first hydraulicchange-over valve is held the logical oil return inlet T in the back that links to each other with the B5 end of the D2 control end of second hydraulicchange-over valve, the 3rd hydraulicchange-over valve, the A2 of solenoid directional control valve.
The purpose of this utility model can also further realize by following technical measures.
Aforesaid engineering machinery interflow valve, wherein said solenoid directional control valve and the 3rd hydraulicchange-over valve are two-position three-way valve, first hydraulicchange-over valve and second hydraulicchange-over valve are two Twoway valvess.
The utility model is simple in structure, manufacture cost is lower, when the operating rate of needs quickening engineering machinery facility is about to the output flow merging of two oil hydraulic pumps, only solenoid directional control valve is got, just can realize the output flow interflow of two oil hydraulic pumps, adopt hydraulic system of the present utility model safe and reliable.Two chambeies that actuator can not occur all are the situations that high pressure oil causes the spoiled work machinery hydraulic system.
Advantage of the present utility model and characteristics will illustrate by the non-limitative illustration of following preferred embodiment and explain that these embodiments only provide as an example with reference to accompanying drawing.
Description of drawings
Fig. 1 is a systematic schematic diagram of the present utility model.
Embodiment
The utility model is described in further detail below in conjunction with drawings and Examples.
As shown in Figure 1, the utility model comprises shuttle valve 1, solenoid directional control valve 2, first hydraulicchange-over valve 3, second hydraulicchange-over valve 4, the 3rd hydraulicchange-over valve 5, first one-way valve 6, second one-way valve 7, the 3rd one-way valve 8, throttle valve 9 and the relief valve 10 that is installed in the valve body 101, pressure hydraulic fluid port P communicates with oil return inlet T by relief valve 10, relief valve 10 is used to set operating oil pressure of the present utility model as the safety valve of system.Pressure hydraulic fluid port P also links to each other with the P5 end of the 3rd hydraulicchange-over valve 5 by the 3rd one-way valve 8, the A5 end of the 3rd hydraulicchange-over valve 5 is divided into two-way, link to each other with the P3 end of first hydraulicchange-over valve 3 by first one-way valve 6 respectively, link to each other with the P4 end of second hydraulicchange-over valve 4 by second one-way valve 7.Logical B chamber delivery outlet after the A3 end of first hydraulicchange-over valve 3 links to each other with C1 control end, shuttle valve second end 12, the A4 end of second hydraulicchange-over valve 4 links to each other and logical A chamber delivery outlet with D1 control end, shuttle valve first end 11, shuttle valve the 3rd end 13 links to each other with the E2 control end of the 3rd hydraulicchange-over valve 5 and the T2 end of solenoid directional control valve 2 by throttle valve 9, and links to each other with the E1 control end.Pressure hydraulic fluid port P also links to each other with the P2 end of solenoid directional control valve, and the C2 control end of first hydraulicchange-over valve 3 is held the logical oil return inlet T in the back that links to each other with the D2 control end of second hydraulicchange-over valve 4, the B5 end of the 3rd hydraulicchange-over valve, the A2 of solenoid directional control valve 2.Wherein, solenoid directional control valve 2 and the 3rd hydraulicchange-over valve 5 are two-position three-way valve, and first hydraulicchange-over valve 3 and second hydraulicchange-over valve 4 are two Twoway valvess.
During engineering machinery work, the pressure oil of first oil hydraulic pump output drives the work of engineering machinery final controlling element by hydraulic system.The pressure oil of second oil hydraulic pump output is held direct oil return inlet T, second oil hydraulic pump off-load by the P2-A2 end of solenoid directional control valve 2, the P5-B5 of the 3rd hydraulicchange-over valve 5.The final controlling element ante-chamber oil pressure that connects as hydraulic fluid port A is during greater than the final controlling element back cavity oil pressure that is connected with hydraulic fluid port B, shuttle valve first end 11 is opened, the D1 control end that leads to second hydraulicchange-over valve 4 from the pressure oil of hydraulic fluid port A, promoting second hydraulicchange-over valve 4 switches, at this moment, though the E1 control end of the 3rd hydraulicchange-over valve 5 has the pressure oil from hydraulic fluid port A, the E2 control end is sealed by solenoid directional control valve 2, and the 3rd hydraulicchange-over valve 5 keeps closed condition.When the operating rate of engineering machinery final controlling element is accelerated at two oil hydraulic pump interflow of needs, making solenoid directional control valve 2 get TURP changes, the E2 control end of the 3rd hydraulicchange-over valve 5 is by the directly logical oil return inlet T of T2-A2 end of solenoid directional control valve 2, the oil pressure at E2 control end place is zero, at this moment, the pressure oil that arrives the E1 control end from shuttle valve the 3rd end 13 promotes 5 commutations of the 3rd hydraulicchange-over valve, the pressure oil of second oil hydraulic pump output successively passes through pressure hydraulic fluid port P, the 3rd one-way valve 8, the P5A5 end of the 3rd hydraulicchange-over valve 5, second one-way valve 7, the P4-A4 end of second hydraulicchange-over valve is after hydraulic fluid port A exports, and the pressure oil of exporting with first oil hydraulic pump collaborates.Throttle valve 7 plays confining pressure oil, regulates the oil pressure effect of the E2 control end that leads to the 3rd hydraulicchange-over valve 5.
When the selector valve outside the valve of interflow switches to hydraulic fluid port B oil-feed, the final controlling element back cavity oil pressure that is connected with hydraulic fluid port B is greater than the final controlling element ante-chamber oil pressure that is connected with hydraulic fluid port A, shuttle valve second end 12 oil circuits that connect hydraulic fluid port B are connected, shuttle valve first end 11 is closed, and the pressure oil of hydraulic fluid port B promotes 3 commutations of first hydraulicchange-over valve by the C1 control end of first hydraulicchange-over valve 3.When solenoid directional control valve 2 TURP when changing, after hydraulic fluid port B exports, the pressure oil of exporting with first oil hydraulic pump collaborates the pressure oil of second oil hydraulic pump output through the P3-A3 of the P5-A5 of pressure hydraulic fluid port P, the 3rd one-way valve 8, the 3rd hydraulicchange-over valve 5 end, first one-way valve 6, first hydraulicchange-over valve 3 end.
In sum, during the work of engineering machinery final controlling element, no matter hydraulic fluid port A advances pressure oil still is that hydraulic fluid port B advances pressure oil, as long as make solenoid directional control valve of the present utility model 2 electric commutation, the pressure oil that the pressure oil that just can make second oil hydraulic pump output is exported by the utility model and first oil hydraulic pump collaborates outside the selector valve of system.
In addition to the implementation, the utility model can also have other mode of executions, and all employings are equal to the technological scheme of replacement or equivalent transformation formation, all drop in the protection domain of the utility model requirement.
Claims (2)
1. an engineering machinery is collaborated valve, comprise the shuttle valve (1), solenoid directional control valve (2), first hydraulicchange-over valve (3), second hydraulicchange-over valve (4), the 3rd hydraulicchange-over valve (5), first one-way valve (6), second one-way valve (7), the 3rd one-way valve (8), throttle valve (9) and the relief valve (10) that are installed in the valve body (101), pressure hydraulic fluid port P communicates with oil return inlet T by relief valve (10); It is characterized in that: pressure hydraulic fluid port P also links to each other with the P5 end of the 3rd hydraulicchange-over valve (5) by the 3rd one-way valve (8), the A5 end of the 3rd hydraulicchange-over valve (5) is divided into two-way, link to each other with the P3 end of first hydraulicchange-over valve (3) by first one-way valve (6) respectively, link to each other with the P4 end of second hydraulicchange-over valve (4) by second one-way valve (7); Logical B chamber delivery outlet after the A3 end of first hydraulicchange-over valve (3) links to each other with C1 control end, shuttle valve second end (12), logical A chamber delivery outlet after the A4 end of second hydraulicchange-over valve (4) links to each other with D1 control end, shuttle valve first end (11), shuttle valve the 3rd end (13) links to each other with the E2 control end of the 3rd hydraulicchange-over valve (5) and the T2 end of solenoid directional control valve (2) by throttle valve (9), and links to each other with the E1 control end; Pressure hydraulic fluid port P also links to each other with the P2 end of solenoid directional control valve (2), and the C2 control end of first hydraulicchange-over valve (3) is held the logical oil return inlet T in the back that links to each other with the D2 control end of second hydraulicchange-over valve (4), the B5 end of the 3rd hydraulicchange-over valve (5), the A2 of solenoid directional control valve (2).
2. engineering machinery as claimed in claim 1 interflow valve is characterized in that described solenoid directional control valve (2) and the 3rd hydraulicchange-over valve (5) are two-position three-way valve, and first hydraulicchange-over valve (3) and second hydraulicchange-over valve (4) are two Twoway valvess.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009202847642U CN201593533U (en) | 2009-12-07 | 2009-12-07 | Engineering machinery flow collecting valve |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2009202847642U CN201593533U (en) | 2009-12-07 | 2009-12-07 | Engineering machinery flow collecting valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201593533U true CN201593533U (en) | 2010-09-29 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2009202847642U Expired - Fee Related CN201593533U (en) | 2009-12-07 | 2009-12-07 | Engineering machinery flow collecting valve |
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| CN (1) | CN201593533U (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102094861A (en) * | 2010-12-02 | 2011-06-15 | 徐州重型机械有限公司 | Multi-pump concurrent flow hydraulic system for crane and concurrent valve bank |
| CN102345749A (en) * | 2011-08-29 | 2012-02-08 | 徐州重型机械有限公司 | Flow collecting valve and crane hydraulic control system with the same |
| CN102734501A (en) * | 2012-07-05 | 2012-10-17 | 徐州重型机械有限公司 | Converging multipath valve and crane hydraulic system |
| CN104863914A (en) * | 2015-04-13 | 2015-08-26 | 徐州徐工液压件有限公司 | Electrohydraulic joint control flow collecting valve |
| CN104633221B (en) * | 2013-11-12 | 2017-07-21 | 宁夏巨能机器人系统有限公司 | A kind of plant equipment multidigit various way solenoid valve |
| CN107044460A (en) * | 2017-03-17 | 2017-08-15 | 郑州宇通重工有限公司 | A kind of engineering machinery turns to interflow current stabilization valve group |
| CN111720376A (en) * | 2020-06-29 | 2020-09-29 | 徐工集团工程机械股份有限公司科技分公司 | A diverter valve and its hydraulic system, construction machinery |
-
2009
- 2009-12-07 CN CN2009202847642U patent/CN201593533U/en not_active Expired - Fee Related
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102094861A (en) * | 2010-12-02 | 2011-06-15 | 徐州重型机械有限公司 | Multi-pump concurrent flow hydraulic system for crane and concurrent valve bank |
| CN102094861B (en) * | 2010-12-02 | 2013-04-10 | 徐州重型机械有限公司 | Multi-pump concurrent flow hydraulic system for crane and concurrent valve bank |
| CN102345749A (en) * | 2011-08-29 | 2012-02-08 | 徐州重型机械有限公司 | Flow collecting valve and crane hydraulic control system with the same |
| CN102734501A (en) * | 2012-07-05 | 2012-10-17 | 徐州重型机械有限公司 | Converging multipath valve and crane hydraulic system |
| CN104633221B (en) * | 2013-11-12 | 2017-07-21 | 宁夏巨能机器人系统有限公司 | A kind of plant equipment multidigit various way solenoid valve |
| CN104863914A (en) * | 2015-04-13 | 2015-08-26 | 徐州徐工液压件有限公司 | Electrohydraulic joint control flow collecting valve |
| CN107044460A (en) * | 2017-03-17 | 2017-08-15 | 郑州宇通重工有限公司 | A kind of engineering machinery turns to interflow current stabilization valve group |
| CN107044460B (en) * | 2017-03-17 | 2018-07-24 | 郑州宇通重工有限公司 | A kind of engineering machinery steering interflow current stabilization valve group |
| CN111720376A (en) * | 2020-06-29 | 2020-09-29 | 徐工集团工程机械股份有限公司科技分公司 | A diverter valve and its hydraulic system, construction machinery |
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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 |
Granted publication date: 20100929 Termination date: 20151207 |
|
| EXPY | Termination of patent right or utility model |