CN104879336A - Valve back compensation type load-sensitive multitandem valve with bidirectional confluence function - Google Patents
Valve back compensation type load-sensitive multitandem valve with bidirectional confluence function Download PDFInfo
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- CN104879336A CN104879336A CN201510176056.7A CN201510176056A CN104879336A CN 104879336 A CN104879336 A CN 104879336A CN 201510176056 A CN201510176056 A CN 201510176056A CN 104879336 A CN104879336 A CN 104879336A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/021—Valves for interconnecting the fluid chambers of an actuator
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/40—Flow control
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Abstract
The invention discloses a valve back compensation type load-sensitive multitandem valve with a bidirectional confluence function. The valve back compensation type load-sensitive multitandem valve comprises a confluence tandem and two oil inlet operation tandems arranged at two ends of the confluence tandem. The confluence tandem is provided with a confluence valve with the bidirectional confluence function and comprises an electromagnetic valve, a hydraulic control valve, a shuttle valve II and an electro-hydraulic joint control confluence switching valve, an oil inlet tandem and two operation tandems are integrated in each oil inlet operation tandem and each operation tandem comprises a reversing speed-regulation valve and a pressure compensation valve arranged at an outlet of the reversing speed-regulation valve. The confluence tandem is detachably connected with the oil inlet operation tandems on two sides. The output end of the electro-hydraulic joint control confluence switching valve in the confluence tandem is communicated with the operation tandems. The confluence tandem allows oil to flow bidirectionally from p1 to p2 or vice versa, flow speed range of the tandems is broadened, and the executing mechanisms can act more quickly. By the pressure compensation technology, the problem that high-load executing mechanisms have little flow or even no flow when the executing mechanisms act at the same is solved, and action stability is improved.
Description
Technical field
The present invention relates to a kind of multi-way valve, specifically a kind of valve post-compensation type load sensing multi-way valve be applied to the two-way interflow of band that the master file on truck crane, secondary volume, luffing, four kinds of actuators such as to stretch control, belongs to multi-way valve technical field.
Background technique
On current medium and small tonnage truck crane at home and abroad, the main control valve of extensive use generally has two oil inlet P 1 and P2, these two oil inlet P 1 are connected different oil pumps respectively with P2, and the fluid in oil inlet P 1 and P2 can as required simultaneously to any one actuator's fuel feeding.In this main control valve, fluid can only be collaborated to P2 by P1, cannot realize the interflow of P2 to P1 direction, and cause the movement velocity of actuator slow, operating efficiency is low.
On existing medium and small tonnage automobile crane owner control valve, it is generally the pressure compensation mode adopting valve precompensation, when the multiple actuators action simultaneously of different operating load, fluid can the low actuator of preferential supply load pressure, causes actuator's coordination reduction.
In order to improve the harmony of composite move, the engineering machinery such as excavator are widely used the load sensing multi-way valve based on valve post-compensation principle, but at home medium and small tonnage truck crane have not yet been applied.Wherein, load-sensitive refers to that system can provide corresponding flow to reduce energy dissipation according to workload demands; And assignment of traffic refers to that, when the action simultaneously of multiple actuator, if flow system flow can not meet the requirement of operating load, the reduction flow making actuator proportional, with the harmony of safety action.
At present, the Patents file of existing a lot of this respect, as: (patent No. is a kind of double pump confluence type multi-way ratio control valve with load sensitivity information circuit of Chinese patent: 200410093222.9) disclosed in the 21 days June in 2006, it comprises the input interface P1 of pump I and pump II, P2, tank drainback interface T and be connected in parallel extending means proportional operating valve with described input interface, jib lubbing mechanism proportional operating valve, Fu Juan mechanism proportional operating valve, master file mechanism proportional operating valve, also be provided with the diverter valve and safety valve that are connected with pump discharge, extending means proportional operating valve, jib lubbing mechanism proportional operating valve, Fu Juan mechanism proportional operating valve, load-sensitive information circuits is provided with between master file mechanism proportional operating valve, single double pump fuel feeding automatic transfer valve and one-way valve is provided with between pump I and pump II loop, automatic selection list oil pump feed or double pump fuel feeding.Control flexible, luffing, master file, the commutation speed control valves series of Fu Juan mechanism connects a decompression compensation valve, make actuator's movement velocity not be subject to the impact of operating load change.It is a kind of multi-way valve with load-sensitive function that can realize Dual-pump flow-converging function, but in actual use, there are the following problems:
1, in Dual-pump flow-converging function, fluid by input interface P1 to the unidirectional interflow of input interface P2, can only cannot realize input interface P1 to input interface P2, input interface P2 to the two-way interflow of input interface P1;
2, multi-way valve is carrying out composite move, namely during the action simultaneously of multiple actuator, preferentially meets actuator's action that operating load is lower, makes actuator's exercise not harmony.
3, the Placement of hydraulic fluid port is only limitted to be threaded, and limits using scope.
Summary of the invention
For above-mentioned prior art Problems existing, the invention provides a kind of valve post-compensation type load sensing multi-way valve with two-way interflow, several actuator can be realized and under different load, there is good assignment of traffic.
To achieve these goals, a kind of valve post-compensation type load sensing multi-way valve with two-way interflow that the present invention adopts, comprise interflow connection and be positioned at two the oil-feed work connection collaborating connection two ends, described interflow connection is the converging valve with two-way interflow function, comprise solenoid valve, hydraulic control valve, shuttle valve II and electric liquid joint control interflow switching valve, the input end of described solenoid valve communicates with interflow external control pressure introduction port, and output terminal communicates with the input end of shuttle valve II; The pilot control end of described hydraulic control valve leads to shuttle valve I, oil circuit T-phase respectively, and input end leads to shuttle valve III, oil circuit T-phase respectively, and output terminal communicates with the input end of shuttle valve II; The pilot control end of described electric liquid joint control interflow switching valve leads to the output terminal of shuttle valve II, oil circuit T-phase respectively, and input end communicates with the input interface of pump I discharge capacity, the input interface of pump II discharge capacity respectively; Described hydraulic control valve, electric liquid joint control interflow switching valve and shuttle valve II are used for realizing selector valve internal control two-way interflow function; Described oil-feed work connection is integrated with an oil-feed connection and two work connection, and described work connection comprises commutation series flow control valve and is arranged on the pressure-compensated valve in commutation series flow control valve outlet port; Described interflow connection joins with the oil-feed work on both sides and removably connects; The output terminal of described electric liquid joint control interflow switching valve joins with each work and communicates.
Preferably, described solenoid valve is two position, three-way electromagnetic change valve, and described hydraulic control valve is two-position three way pilot operated directional control valve, and described electric liquid joint control interflow switching valve is two-position two-way hydraulic control selector valve.
Preferably, pilot control oil pocket and the hydraulic fluid port of two working oil path in described oil-feed work connection are integrated on same end cap, described end cap comprises end cover body, two solenoid valves be arranged on end cover body control guide's oil circuit of two working oil path respectively, stop screw is arranged in the pilot control oil pocket of end cap, and choke plug is arranged on solenoid valve oil outlet in the pipeline of pilot control oil pocket.Wherein, described choke plug can be damping.
Preferably, the work connection place in described oil-feed work connection is provided with overload oil compensating valve.
Preferably, the diverging three way valve of relief valve, pressure shut-off valve and pump input interface is provided with in described oil-feed work connection.
Further, also comprise constant flow rate valve I and constant flow rate valve II, described constant flow rate valve I and constant flow rate valve II is arranged on the LS loop of multi-way valve valve group inside.
Compared with prior art, tool of the present invention has the following advantages:
1. the main overall hydraulic parameter of this valve is: rated pressure 350bar, single pump displacement 200L/min, Dual-pump flow-converging 400L/min, Hydraulic guide control, pilot pressure 6-19bar;
2. there are external control and internal control two kinds of patterns in interflow.Converging valve is energy of often starting shooting, and original state is interflow.DPT3 is external control solenoid valve, and priority is the highest, during solenoid valves, forces converging valve to disconnect.The internal control priority of converging valve is lower, is in internal control pattern when DPT3 power-off.Internal control pattern is controlled by the information on load loop of multi-way valve inside completely, and relative to prior art, the internal control pattern in the present invention allows fluid by p1 to p2 with by p2 to p1 two-way flow, and make each flow speed regulating section larger, actuator's action is rapider.
3. the present invention improves in Pressure Compensation Technology.Be provided with pressure compensator at the entrance of all selector valves in prior art, achieve the stability of the action simultaneously of multiple actuator and flow.Pressure compensator is arranged on the outlet of selector valve by the present invention, when the flow that pump provides can not meet the traffic demand of multiple actuator action simultaneously (that is: flow is saturated), the flow of each actuating mechanism controls oil circuit of proportional reduction, thus the movement velocity of multiple actuator is reduced simultaneously, thus the harmony of safety action.Meanwhile, when in the present invention, the improvement of Pressure Compensation Technology also overcomes the simultaneously action of many actuators, high capacity actuator flow reduces even without the problem of flow, the stability of raising action.
4., in order to the stability of proof load feedback signal (LS pressure signal) and the accuracy of signal feed back and ageing, the inner LS loop of valve group is provided with the constant flow rate valve of 0.7-1L/min.
5. the LS pressure shut-off valve of this valve group, main safety valve, secondary relief, shuttle valve are all designed to screw thread inserting type structure, and convenient for maintaining is changed and debugging.Wherein LS pressure shut-off valve, main safety valve, overload oil compensating valve pressure adjustable, expands the Applicable scope of valve group.
6. valve group adopts the fabricated structure of valve block+interflow connection, and both sides are oil-feed work connection, and middle is interflow connection.The oil-feed work connection on both sides is same foundry goods, and each valve body is integrated with 1 oil-feed connection and 2 work connection, makes valve body structure compacter, reduces junction plane and reduce leakage of oil risk, realize lightweight.Middle interflow connection is detachable, and can design different interflow connection as required and realize required function.Other connection can also be superposed between interflow connection and oil-feed work connection and expand performance loop quantity, achieve modularization.
7. actuator port adopts flange and worm structure.Be suitable for different mounting types, more general.
8. one-sided two adjacent working oil path share one and control end cap, and end cap adopts casting structure, reduce size and installing space, reduce processing cost.
Accompanying drawing explanation
Fig. 1 is the hydraulic schematic diagram of the valve post-compensation type load sensing multi-way valve at the two-way interflow of band of the present invention;
Fig. 2 is the surface structure schematic diagram of the valve post-compensation type load sensing multi-way valve at the two-way interflow of band of the present invention;
Fig. 3 is the structural representation of end cap;
Fig. 4 be in Fig. 3 A-A to sectional view;
Fig. 5 be in Fig. 3 B-B to sectional view;
Fig. 6 is the structural representation of end cap other direction.
In figure: 1, O type circle I, 2, choke plug, 3, end cover body, 4, electromagnetic valve I, 5, stop screw, 6, O type circle II, 7, ball rises stifled, and 8, electromagnetic valve II, 9, interflow connection, 10, oil-feed work joins, P1, the input interface of pump I discharge capacity, P2, the input interface of pump II discharge capacity, R1, relief valve I, R2, relief valve II, RL1, pressure shut-off valve I, RL2, pressure shut-off valve II, S1, constant flow rate valve I, S2, constant flow rate valve II, RA1, overload oil compensating valve I, RA2, overload oil compensating valve II, RB1, overload oil compensating valve III, RB2, overload oil compensating valve IV, RB3, overload oil compensating valve V, RB4, for overload oil compensating valve VI, PS, electricity liquid joint control interflow switching valve, SV1, shuttle valve I, SV2, shuttle valve II, SV3, shuttle valve III, T1, tank drainback interface I, T2, tank drainback interface II, S1, constant flow rate valve I, S2, constant flow rate valve II, LPD, hydraulic pressure internal control interflow pilot-actuated valve, DTP3, solenoid valve, P3, interflow external control pressure introduction port, LS1, load-sensitive pressure output I, LS2, load-sensitive pressure output II, RS1, the diverging three way valve of pump I input interface, RS2, the diverging three way valve of pump II input interface.
Embodiment
Below in conjunction with accompanying drawing, the invention will be further described.
As depicted in figs. 1 and 2, a kind of valve post-compensation type load sensing multi-way valve with two-way interflow, comprise interflow connection and be positioned at two the oil-feed work connection collaborating connection two ends, described interflow connection is the converging valve with two-way interflow function, comprise solenoid valve DTP3, hydraulic control valve LPD, shuttle valve IISV2 and electric liquid joint control interflow switching valve PS, the input end of described solenoid valve DTP3 communicates with interflow external control pressure introduction port P3, and output terminal communicates with the input end of shuttle valve IISV2; The pilot control end of described hydraulic control valve LPD leads to shuttle valve ISV1, oil circuit T-phase respectively, and input end leads to shuttle valve IIISV3, oil circuit T-phase respectively, and output terminal communicates with the input end of shuttle valve IISV2; The pilot control end of described electric liquid joint control interflow switching valve PS leads to the output terminal of shuttle valve IISV2, oil circuit T-phase respectively, and input end communicates with the input interface P1 of pump I discharge capacity, the input interface P2 of pump II discharge capacity respectively; Described hydraulic control valve LPD, electric liquid joint control interflow switching valve PS and shuttle valve IISV2 is used for realizing selector valve internal control two-way interflow function; Described oil-feed work connection is integrated with an oil-feed connection and two work connection, and described work connection comprises commutation series flow control valve and is arranged on the pressure-compensated valve in commutation series flow control valve outlet port; Described interflow connection joins with the oil-feed work on both sides and removably connects; The output terminal of described electric liquid joint control interflow switching valve PS joins with each work and communicates.
Preferably, described solenoid valve DTP3 is two position, three-way electromagnetic change valve, and described hydraulic control valve LPD is two-position three way pilot operated directional control valve, and described electric liquid joint control interflow switching valve PS is two-position two-way hydraulic control selector valve.
Preferably, pilot control oil pocket and the hydraulic fluid port of two working oil path in described oil-feed work connection are integrated on same end cap, described end cap comprises end cover body, two solenoid valves be arranged on end cover body control guide's oil circuit of two working oil path respectively, stop screw 5 is arranged in the pilot control oil pocket of end cap, and choke plug 2 is arranged on solenoid valve oil outlet in the pipeline of pilot control oil pocket.
Preferably, described choke plug 2 is damping.
Preferably, the work connection place in described oil-feed work connection is provided with overload oil compensating valve.
Preferably, the diverging three way valve of relief valve, pressure shut-off valve and pump input interface is provided with in described oil-feed work connection.
As depicted in figs. 1 and 2, C1, C2, C3, C4 are respectively the commutation speed governing of four performance loop, and SC1, SC2, SC3, SC4 are respectively the outlet port reduction valve of C1, C2, C3, C4 commutation series flow control valve, i.e. pressure-compensated valve; A1, A2, A3, A4, B1, B2, B3, B4 are the interface to four actuators; A1, a2, a3, a4, b1, b2, b3, b4 are external pilot pressure inlet opening; L1, L2, L3, L4 are drain tap, and the specific implementation at interflow is as follows:
1) when each oil circuit does not have action, the Maximum operating pressure that shuttle valve ISV1 feeds back first and second oil circuit is 0, and hydraulic pressure internal control interflow pilot-actuated valve LPD is in left position.During solenoid valve DTP3 power-off, external control pressure introduction port P3 and shuttle valve IISV2 is obstructed at interflow, and it is 0 that shuttle valve IISV2 feeds back maximum pressure, and now electric liquid joint control interflow switching valve PS is in two-way interflow state under spring force; When solenoid valve DTP3 is energized, interflow external control pressure introduction port P3 is communicated with shuttle valve IISV2, shuttle valve IISV2 feedback interflow external control pressure introduction port P3 pressure is to electric liquid joint control interflow switching valve PS control end, and now electric liquid joint control interflow switching valve PS overcomes spring force closedown, does not collaborate;
2) when the first or second working oil path action, third and fourth working oil path are failure to actuate, shuttle valve ISV1 feeds back the hydraulic control end of Maximum operating pressure to hydraulic pressure internal control interflow pilot-actuated valve LPD of first and second oil circuit, hydraulic pressure internal control interflow pilot-actuated valve LPD is in right position, and it is 0 to shuttle valve IISV2 that shuttle valve IIISV3 feeds back third and fourth oil circuit pressure.During solenoid valve DTP3 power-off, electric liquid joint control interflow switching valve PS is in two-way interflow state under spring force; When solenoid valve DTP3 is energized, interflow external control pressure introduction port P3 is communicated with shuttle valve IISV2, the pressure of shuttle valve IISV2 feedback interflow external control pressure introduction port P3 is to electric liquid joint control interflow switching valve PS control end, and now electric liquid joint control interflow switching valve PS overcomes spring force closedown, does not collaborate;
3) when the first or second working oil path action, the 3rd or the 4th working oil path also action, shuttle valve ISV1 feeds back the Maximum operating pressure of first and second oil circuit to hydraulic pressure internal control interflow pilot-actuated valve LPD hydraulic control end, hydraulic pressure internal control interflow pilot-actuated valve LPD is in right position, and shuttle valve IIISV3 feeds back third and fourth oil circuit maximum pressure to shuttle valve IISV2.During solenoid valve DTP3 power-off, shuttle valve IISV2 feeds back third and fourth working oil path maximum pressure to electric liquid joint control interflow switching valve PS control end, and now electric liquid joint control interflow switching valve PS overcomes spring force closedown, does not collaborate; When solenoid valve DTP3 is energized, interflow external control pressure introduction port P3 is communicated with shuttle valve IIISV3, shuttle valve IIISV3 feeds back the maximum pressure of interflow external control pressure introduction port P3 and third and fourth working oil path to electric liquid joint control interflow switching valve PS control end, now electric liquid joint control interflow switching valve PS overcomes spring force closedown, does not collaborate.
Therefore, electric liquid external control pattern has limit priority, and hydraulic pressure internal control pattern can to automatically switch interflow mode according to operating load.
As shown in Figure 2, this valve group adopts valve block to add the fabricated structure of interflow connection, and both sides are oil-feed work connection, and middle is interflow connection.The oil-feed work connection on both sides is same foundry goods, and each valve body is integrated with an oil-feed connection and two work connection, makes valve body structure compacter, reduces junction plane and reduce leakage of oil risk, realize lightweight.Middle interflow connection is detachable, and can design different interflow connection as required and realize required function.Other connection can also be superposed between interflow connection and oil-feed work connection and expand performance loop quantity, achieve modularization.In addition, also can design the boss of adpting flange when the casting of oil-feed work connection, the hydraulic fluid port linkage structure of screw thread and flange can be applicable to simultaneously.
One-sided two adjacent working oil path share one and control end cap, and end cap adopts casting structure.As shown in Figures 3 to 6, end cap forms primarily of end cover body 3, stop screw 5, two solenoid valves and choke plug 2.The pilot control oil pocket of two working oil path and hydraulic fluid port are integrated on same end cap, and two solenoid valves control guide's oil circuit of two working oil path clearly.Stop screw 5 is arranged in the pilot control oil pocket of end cap, and choke plug 2 is arranged on solenoid valve oil outlet in the pipeline of pilot control oil pocket.
In addition, in order to the stability of proof load feedback signal (LS pressure signal) and the accuracy of signal feed back and ageing, the constant flow rate valve of 0.7-1L/min can be set in the inner LS loop of valve group, as the constant flow rate valve IS1 in Fig. 1 and constant flow rate valve IIS2.Pressure shut-off valve in the present invention, main safety valve, secondary relief, shuttle valve can all be designed to screw thread inserting type structure, installation and removal of being more convenient for.Wherein, the pressure of the pressure shut-off valve in LS loop, main safety valve, overload oil compensating valve is all adjustable.
From said structure, tool of the present invention has the following advantages:
1. the main overall hydraulic parameter of this valve is: rated pressure 350bar, single pump displacement 200L/min, Dual-pump flow-converging 400L/min, Hydraulic guide control, pilot pressure 6-19bar;
2. there are external control and internal control two kinds of patterns in interflow.Converging valve is energy of often starting shooting, and original state is interflow.DPT3 is external control solenoid valve, and priority is the highest, during solenoid valves, forces converging valve to disconnect.The internal control priority of converging valve is lower, is in internal control pattern when DPT3 power-off.Internal control pattern is controlled by the information on load loop of multi-way valve inside completely, and relative to prior art, the internal control pattern in the present invention allows fluid by p1 to p2 with by p2 to p1 two-way flow, and make each flow speed regulating section larger, actuator's action is rapider.
3. the present invention improves in Pressure Compensation Technology.Be provided with pressure compensator at the entrance of all selector valves in prior art, achieve the stability of the action simultaneously of multiple actuator and flow.Pressure compensator is arranged on the outlet of selector valve by the present invention, when the flow that pump provides can not meet the traffic demand of multiple actuator action simultaneously (that is: flow is saturated), the flow of each actuating mechanism controls oil circuit of proportional reduction, thus the movement velocity of multiple actuator is reduced simultaneously, thus the harmony of safety action.Meanwhile, when in the present invention, the improvement of Pressure Compensation Technology also overcomes the simultaneously action of many actuators, high capacity actuator flow reduces even without the problem of flow, the stability of raising action.
4., in order to the stability of proof load feedback signal (LS pressure signal) and the accuracy of signal feed back and ageing, the inner LS loop of valve group is provided with the constant flow rate valve of 0.7-1L/min.
5. the LS pressure shut-off valve of this valve group, main safety valve, secondary relief, shuttle valve are all designed to screw thread inserting type structure, and convenient for maintaining is changed and debugging.Wherein LS pressure shut-off valve, main safety valve, overload oil compensating valve pressure adjustable, expands the Applicable scope of valve group.
6. valve group adopts the fabricated structure of valve block+interflow connection, and both sides are oil-feed work connection, and middle is interflow connection.The oil-feed work connection on both sides is same foundry goods, and each valve body is integrated with 1 oil-feed connection and 2 work connection, makes valve body structure compacter, reduces junction plane and reduce leakage of oil risk, realize lightweight.Middle interflow connection is detachable, and can design different interflow connection as required and realize required function.Other connection can also be superposed between interflow connection and oil-feed work connection and expand performance loop quantity, achieve modularization.
7. actuator port adopts flange and worm structure.Be suitable for different mounting types, more general.
8. one-sided two adjacent working oil path share one and control end cap, and end cap adopts casting structure, reduce size and installing space, reduce processing cost.
Claims (7)
1. the valve post-compensation type load sensing multi-way valve at the two-way interflow of band, it is characterized in that, comprise interflow connection and be positioned at two the oil-feed work connection collaborating connection two ends, described interflow connection is the converging valve with two-way interflow function, comprise solenoid valve (DTP3), hydraulic control valve (LPD), shuttle valve II (SV2) and electric liquid joint control interflow switching valve (PS), the input end of described solenoid valve (DTP3) communicates with interflow external control pressure introduction port (P3), and output terminal communicates with the input end of shuttle valve II (SV2); The pilot control end of described hydraulic control valve (LPD) leads to shuttle valve I (SV1), oil circuit T-phase respectively, input end leads to shuttle valve III (SV3), oil circuit T-phase respectively, and output terminal communicates with the input end of shuttle valve II (SV2); The pilot control end of described electric liquid joint control interflow switching valve (PS) leads to the output terminal of shuttle valve II (SV2), oil circuit T-phase respectively, and input end communicates with the input interface (P1) of pump I discharge capacity, the input interface (P2) of pump II discharge capacity respectively; Described hydraulic control valve (LPD), electric liquid joint control interflow switching valve (PS) and shuttle valve II (SV2) are for realizing selector valve internal control two-way interflow function; Described oil-feed work connection is integrated with an oil-feed connection and two work connection, and described work connection comprises commutation series flow control valve and is arranged on the pressure-compensated valve in commutation series flow control valve outlet port; Described interflow connection joins with the oil-feed work on both sides and removably connects; The output terminal of described electric liquid joint control interflow switching valve (PS) joins with each work and communicates.
2. a kind of valve post-compensation type load sensing multi-way valve with two-way interflow according to claim 1, it is characterized in that, described solenoid valve (DTP3) is two position, three-way electromagnetic change valve, described hydraulic control valve (LPD) is two-position three way pilot operated directional control valve, and described electric liquid joint control interflow switching valve (PS) is two-position two-way hydraulic control selector valve.
3. a kind of valve post-compensation type load sensing multi-way valve with two-way interflow according to claim 1, it is characterized in that, pilot control oil pocket and the hydraulic fluid port of two working oil path in described oil-feed work connection are integrated on same end cap, described end cap comprises end cover body, two solenoid valves be arranged on end cover body control guide's oil circuit of two working oil path respectively, stop screw (5) is arranged in the pilot control oil pocket of end cap, and choke plug (2) is arranged on solenoid valve oil outlet in the pipeline of pilot control oil pocket.
4. a kind of valve post-compensation type load sensing multi-way valve with two-way interflow according to claim 3, it is characterized in that, described choke plug (2) is damping.
5. a kind of valve post-compensation type load sensing multi-way valve with two-way interflow according to claim 1, is characterized in that, the work connection place in described oil-feed work connection is provided with overload oil compensating valve.
6. a kind of valve post-compensation type load sensing multi-way valve with two-way interflow according to claim 1, is characterized in that, is provided with the diverging three way valve of relief valve, pressure shut-off valve and pump input interface in described oil-feed work connection.
7. a kind of valve post-compensation type load sensing multi-way valve with two-way interflow according to claim 1, it is characterized in that, also comprise constant flow rate valve I (S1) and constant flow rate valve II (S2), described constant flow rate valve I (S1) and constant flow rate valve II (S2) are arranged on the LS loop of multi-way valve valve group inside.
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| CN201510176056.7A CN104879336B (en) | 2015-04-14 | 2015-04-14 | Valve back compensation type load-sensitive multitandem valve with bidirectional confluence function |
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| CN201510176056.7A CN104879336B (en) | 2015-04-14 | 2015-04-14 | Valve back compensation type load-sensitive multitandem valve with bidirectional confluence function |
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| CN106884820A (en) * | 2015-12-16 | 2017-06-23 | 中国科学院沈阳自动化研究所 | A kind of storage winch hydraulic system |
| CN108087367A (en) * | 2018-01-25 | 2018-05-29 | 陈艳艳 | A kind of flow divider valve for load-sensitive pumping system |
| CN108506259A (en) * | 2018-04-09 | 2018-09-07 | 徐州燕大传动与控制技术有限公司 | A kind of load sensing formula multi-way valve of the inlet and outlet independent control of valve post-compensation |
| CN109723693A (en) * | 2019-01-15 | 2019-05-07 | 江苏徐工工程机械研究院有限公司 | A kind of load sensing multi-way valve and hydraulic system |
| CN110714957A (en) * | 2019-08-26 | 2020-01-21 | 宁波江北宇洲液压设备厂 | High-integration pilot multi-way valve bank and crane |
| CN110848190A (en) * | 2019-09-25 | 2020-02-28 | 张家口凯航液压科技有限公司 | Integrated load sensitive flow divider valve |
| CN113107921A (en) * | 2021-04-19 | 2021-07-13 | 三一汽车起重机械有限公司 | Multi-way valve group system of working machine, control method and working machine |
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| CN113464514A (en) * | 2021-07-30 | 2021-10-01 | 湖南三一中型起重机械有限公司 | Integrated electric control multi-way valve and crane |
| CN113669323A (en) * | 2021-10-22 | 2021-11-19 | 宁波市博尔法液压有限公司 | Load-sensitive multi-way valve |
| CN113931894A (en) * | 2021-09-28 | 2022-01-14 | 中联重科股份有限公司 | Load-sensitive multi-way valve with independently controlled load port and hydraulic system |
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| CN106884820A (en) * | 2015-12-16 | 2017-06-23 | 中国科学院沈阳自动化研究所 | A kind of storage winch hydraulic system |
| CN106884820B (en) * | 2015-12-16 | 2018-04-06 | 中国科学院沈阳自动化研究所 | A kind of storage winch hydraulic system |
| CN105508338B (en) * | 2016-01-26 | 2018-01-23 | 圣邦集团有限公司 | One kind is applied to Dual-pump flow-converging crane banked direction control valves |
| CN105508338A (en) * | 2016-01-26 | 2016-04-20 | 圣邦集团有限公司 | Multiway valve applicable to double-pump confluence crane |
| CN106523455A (en) * | 2016-10-31 | 2017-03-22 | 西南大学 | Tractor load-sensitive hydraulic system with double-pump confluence function |
| CN108087367A (en) * | 2018-01-25 | 2018-05-29 | 陈艳艳 | A kind of flow divider valve for load-sensitive pumping system |
| CN108087367B (en) * | 2018-01-25 | 2019-07-26 | 凯文斯流体控制(江苏)有限公司 | A kind of flow divider valve for load-sensitive pumping system |
| CN108506259B (en) * | 2018-04-09 | 2022-02-11 | 徐州燕大传动与控制技术有限公司 | Load sensing type multi-way valve with independently controlled inlet and outlet for valve post compensation |
| CN108506259A (en) * | 2018-04-09 | 2018-09-07 | 徐州燕大传动与控制技术有限公司 | A kind of load sensing formula multi-way valve of the inlet and outlet independent control of valve post-compensation |
| CN109723693A (en) * | 2019-01-15 | 2019-05-07 | 江苏徐工工程机械研究院有限公司 | A kind of load sensing multi-way valve and hydraulic system |
| CN109723693B (en) * | 2019-01-15 | 2023-10-03 | 江苏徐工工程机械研究院有限公司 | Load-sensitive multi-way valve and hydraulic system |
| CN110714957A (en) * | 2019-08-26 | 2020-01-21 | 宁波江北宇洲液压设备厂 | High-integration pilot multi-way valve bank and crane |
| CN110848190A (en) * | 2019-09-25 | 2020-02-28 | 张家口凯航液压科技有限公司 | Integrated load sensitive flow divider valve |
| CN113107921A (en) * | 2021-04-19 | 2021-07-13 | 三一汽车起重机械有限公司 | Multi-way valve group system of working machine, control method and working machine |
| CN113217500A (en) * | 2021-06-10 | 2021-08-06 | 徐州徐工液压件有限公司 | Time sharing multi-way valve |
| CN113217500B (en) * | 2021-06-10 | 2023-12-12 | 徐州徐工液压件有限公司 | Time sharing multi-way valve |
| CN113464514A (en) * | 2021-07-30 | 2021-10-01 | 湖南三一中型起重机械有限公司 | Integrated electric control multi-way valve and crane |
| CN113931894A (en) * | 2021-09-28 | 2022-01-14 | 中联重科股份有限公司 | Load-sensitive multi-way valve with independently controlled load port and hydraulic system |
| CN113669323A (en) * | 2021-10-22 | 2021-11-19 | 宁波市博尔法液压有限公司 | Load-sensitive multi-way valve |
| CN113669323B (en) * | 2021-10-22 | 2022-02-18 | 宁波市博尔法液压有限公司 | Load-sensitive multi-way valve |
| CN114109947A (en) * | 2021-10-25 | 2022-03-01 | 保定优佰协力电子科技有限公司 | Mining confluence valve |
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