CN103010069A - Electric-hydraulic control system for lifting bucket trolley - Google Patents
Electric-hydraulic control system for lifting bucket trolley Download PDFInfo
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- CN103010069A CN103010069A CN2011102828910A CN201110282891A CN103010069A CN 103010069 A CN103010069 A CN 103010069A CN 2011102828910 A CN2011102828910 A CN 2011102828910A CN 201110282891 A CN201110282891 A CN 201110282891A CN 103010069 A CN103010069 A CN 103010069A
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Abstract
The invention relates to an electric-hydraulic control system for a lifting bucket trolley, comprising an oil tank, a constant-displacement pump, a three-way pressure compensator, a safety valve, a pressure reducing valve, four three-way electromagnetic proportional pressure reducing valves, two hydraulic reversing valves, four three-way proportional pressure reducing valves, two balance valves, seven shuttle valves, two movable-arm lifting cylinders, two supporting-leg cylinders, two hook cylinders and a hydraulic one-way valve, wherein an inlet of the constant-displacement pump is connected with an oil outlet of the oil tank, and an outlet of the constant-displacement pump is respectively connected with an oil inlet of the three-way pressure compensator, an oil inlet of the pressure reducing valve, an oil inlet of the first three-way electromagnetic proportional pressure reducing valve, an oil inlet of the second three-way electromagnetic proportional pressure reducing valve, an oil inlet of the third three-way electromagnetic proportional pressure reducing valve, an oil inlet of the fourth three-way electromagnetic proportional pressure reducing valve, an oil inlet of the first hydraulic reversing valve and an oil inlet of the second hydraulic reversing valve. The electric-hydraulic control system has the advantages that the installation is convenient, the connecting pipelines are reduced, the oil leakage is reduced, no mechanical wearing is caused, the interference resistance is strong, the operation is simple and no maintenance is needed.
Description
Technical field
The present invention relates to a kind of electrohydraulic control system, be used for specifically the electrohydraulic control system of bucket crane.
Background technology
Bucket crane is the special-use vehicle of the material transportations such as the waste material that is specifically designed to all kinds of iron and steel material qualities in the iron and steel enterprise, sheet material crop, and bucket crane is made of upper dress equipment and chassis two parts.Bucket crane and feed hopper are used transported material, by self fluid pressure drive device feed hopper are hung on the car body platform from ground, perhaps feed hopper is hung onto on the ground from the car body platform, and the self-unloading function of material.
There is the moved arm lifting oil cylinder bucket crane both sides, the action of moved arm lifting oil cylinder makes the swing arm entablatrance make circular movement, four chain-driving feed hoppers by its end are made the circular movement motion of translation, carry out the lifting of feed hopper and transfer, in the time will transferring feed hopper, hook is thrown off under the oil cylinder effect automatically.In the time will tumbling feed hopper, hook and do not put, feed hopper is done the circumference flip-flop movement centered by namely can linking up with, and finishes the material self-unloading.
Existing bucket crane all adopts hydraulic-driven, and the power of hydraulic efficiency pressure system is all from engine in situ, and power is passed to Hydraulic Pump through change speed gear box and power takeoff.The high pressure oil of Hydraulic Pump output drives each oil cylinder through behind the various fluid control valves, promotes load and realizes exercises.
In order to control the kinematic velocity of each oil cylinder, common hydraulic efficiency pressure system mostly adopts the mode of entrance throttle governing circuit, this mode requires the by pass valve of system must be always in running order, cause pump to be operated in the high pressure conditions that by pass valve is set always, and unnecessary flow must under high pressure overflow back fuel tank by by pass valve, cause the unnecessary energy of hydraulic efficiency pressure system all to be converted into heat energy, system's cal val is very large, and the temperature of hydraulic oil rises very fast.And analysis of hydraulic oil overheat can make hydraulic efficiency pressure system produce leakage of oil, slow, the problems such as aggravation, rubber seal accelerated weathering of wearing and tearing of power element speed.
Simultaneously common bucket crane generally adopts the action of mechanical flexible axle control change-over valve, and this mode installs, uses all not too convenient, and the installing space that takies is larger, and operational torque is also larger, uses simultaneously that wearing and tearing can appear in flexible axle after a period of time, the phenomenon of clamping stagnation.Give bucket crane use and maintenance is made troubles.
Summary of the invention
The present invention is intended to overcome the defective of prior art, and a kind of electrohydraulic control system for bucket crane is provided, and is easy for installation, reduces connecting line, reduces leakage of oil, and machinery-free weares and teares, antijamming capability is strong, simple to operate, non-maintaining.
In order to solve the problems of the technologies described above, the present invention is achieved in that
A kind of electrohydraulic control system for bucket crane is characterized in that: it comprises fuel tank, fix-displacement pump, three-way pressure compensating device, safety valve, reducing valve, four threeway solenoid-operated proportional reducing valves, two pilot operated directional control valves, four threeway proportional pressure-reducing valves, two balance cocks, seven shuttle valves, two moved arm lifting oil cylinders, two support oil cylinders, two hook oil cylinders and a hydraulic control one-way valve;
The entrance of fix-displacement pump connects the fuel tank oil outlet, quantitatively oil inlet, the oil inlet of reducing valve, the oil inlet of the first threeway solenoid-operated proportional reducing valve, the oil inlet of the second threeway solenoid-operated proportional reducing valve, the oil inlet of the 3rd threeway solenoid-operated proportional reducing valve, the oil inlet of the 4th threeway solenoid-operated proportional reducing valve, the oil inlet of the first pilot operated directional control valve and the oil inlet of the second pilot operated directional control valve of delivery side of pump difference connecting tee pressure compensator;
The oil outlet of the first threeway solenoid-operated proportional reducing valve connects the first oil inlet of the first shuttle valve, the oil outlet of the second threeway solenoid-operated proportional reducing valve connects the first oil inlet of the second shuttle valve, the oil outlet of the 3rd threeway solenoid-operated proportional reducing valve connects the first oil inlet of the 3rd shuttle valve, the oil outlet of the 4th threeway solenoid-operated proportional reducing valve connects the first oil inlet of the 4th shuttle valve, the return opening of the first threeway solenoid-operated proportional reducing valve, the return opening of the second threeway solenoid-operated proportional reducing valve, the return opening of the return opening of the 3rd threeway solenoid-operated proportional reducing valve and the 4th threeway solenoid-operated proportional reducing valve is parallel-connected to the first return opening of fuel tank;
The second oil inlet of the first shuttle valve connects the oil outlet of the first threeway proportional pressure-reducing valve, and the oil outlet of the first shuttle valve connects the left side commutation control mouth of the first pilot operated directional control valve;
The second oil inlet of the second shuttle valve connects the oil outlet of the second threeway proportional pressure-reducing valve, and the oil outlet of the second shuttle valve connects the right side commutation control mouth of the first pilot operated directional control valve;
The second oil inlet of the 3rd shuttle valve connects the oil outlet of the 3rd threeway proportional pressure-reducing valve, and the oil outlet of the 3rd shuttle valve connects the left side commutation control mouth of the second pilot operated directional control valve;
The second oil inlet of the 4th shuttle valve connects the oil outlet of the 4th threeway proportional pressure-reducing valve, and the oil outlet of the 4th shuttle valve connects the right side commutation control mouth of the second pilot operated directional control valve;
The oil inlet of the oil inlet of the oil inlet of the oil inlet of the first threeway proportional pressure-reducing valve, the second threeway proportional pressure-reducing valve, the 3rd threeway proportional pressure-reducing valve and the 4th threeway proportional pressure-reducing valve is parallel-connected to the oil outlet of reducing valve, and the return opening of the return opening of the return opening of the first threeway proportional pressure-reducing valve, the second threeway proportional pressure-reducing valve, the return opening of the 3rd threeway proportional pressure-reducing valve and the 4th threeway proportional pressure-reducing valve is parallel-connected to the first return opening of fuel tank;
The outer drain tap of reducing valve is connected to the first return opening of fuel tank;
The first load communication port of the first pilot operated directional control valve connects respectively the second oil inlet of the 5th shuttle valve and the oil inlet of the first balance cock, the second load communication port of the first pilot operated directional control valve connects respectively the first oil inlet of the 5th shuttle valve and the oil inlet of the second balance cock, and the return opening of the first pilot operated directional control valve connects the second return opening of fuel tank;
The first load communication port of the second pilot operated directional control valve connects respectively the second oil inlet, the first hook oil cylinder and second hook oil cylinder, the first support oil cylinder and second support oil cylinder of the 6th shuttle valve, the second load communication port of the second pilot operated directional control valve connects respectively the first oil inlet, the first hook oil cylinder and second hook oil cylinder, the first support oil cylinder and second support oil cylinder of the 6th shuttle valve, and the return opening of the second pilot operated directional control valve connects the second return opening of fuel tank;
The oil outlet of the 5th shuttle valve connects the second oil inlet of the 7th shuttle valve, and the oil outlet of the 6th shuttle valve connects the first oil inlet of the 7th shuttle valve, the feedback signal mouth of the oil outlet difference connecting tee pressure compensator of the 7th shuttle valve and the oil inlet of safety valve;
Be connected in parallel the second return opening of fuel tank of the return opening of three-way pressure compensating device and the oil outlet of safety valve;
The oil outlet of the first balance cock be connected the oil outlet of balance cock and connect respectively the first moved arm lifting oil cylinder and the second moved arm lifting oil cylinder, the outside control mouth of the first balance cock connects the oil inlet of the second balance cock, and the outside control mouth of the second balance cock connects the oil inlet of the first balance cock.
Described electrohydraulic control system for bucket crane is characterized in that: the first load communication port of the second pilot operated directional control valve and the second load communication port arrive the first hook oil cylinder and the second hook oil cylinder by hydraulic control one-way valve respectively.
The invention has the beneficial effects as follows: adopt the electric-hydraulic proportion mode, reduce the cal val of hydraulic efficiency pressure system, reduce the power dissipation of driving engine, adopt the inserted valve integrated oil path block, installation dimension is little, realizes the directly connection from the integrated package to the oil cylinder, reduces connecting line, reduces leakage of oil, the present invention is easy for installation, machinery-free wearing and tearing, strong, the reduction oil consumption, energy-conservation, simple to operate, non-maintaining of antijamming capability.
Description of drawings
The present invention is described in further detail below in conjunction with drawings and embodiments:
Fig. 1 is structural representation of the present invention.
The specific embodiment
As shown in Figure 1: a kind of electrohydraulic control system for bucket crane, it comprises fuel tank 15, fix-displacement pump 1, three-way pressure compensating device 2, safety valve 3, reducing valve 4, four threeway solenoid-operated proportional reducing valve 5A, 5B, 5C, 5D, two pilot operated directional control valves 6,7, four threeway proportional pressure-reducing valve 8A, 8B, 8C, 8D, two balance cock 9A, 9B, seven shuttle valve 10A, 10B, 10C, 10D, 10E, 10F, 10G, two moved arm lifting oil cylinder 11A, 11B, two support oil cylinder 12A, 12B, two hook oil cylinder 13A, 13B and hydraulic control one-way valves 14;
The entrance of fix-displacement pump 1 connects fuel tank 15 oil outlets 3, and the outlet of fix-displacement pump 1 is oil inlet 21, the oil inlet 42 of reducing valve 4, the oil inlet 2 of the first threeway solenoid-operated proportional reducing valve 5A, the oil inlet 2 of the second threeway solenoid-operated proportional reducing valve 5B, the oil inlet 2 of the 3rd threeway solenoid-operated proportional reducing valve 5C, the oil inlet 2 of the 4th threeway solenoid-operated proportional reducing valve 5D, the oil inlet 63 of the first pilot operated directional control valve 6 and the oil inlet 73 of the second pilot operated directional control valve 7 of connecting tee pressure compensator 2 respectively;
The oil outlet 1 of the first threeway solenoid-operated proportional reducing valve 5A connects the first oil inlet 3 of the first shuttle valve 10D, the oil outlet 1 of the second threeway solenoid-operated proportional reducing valve 5B connects the first oil inlet 3 of the second shuttle valve 10E, the oil outlet 1 of the 3rd threeway solenoid-operated proportional reducing valve 5C connects the first oil inlet 3 of the 3rd shuttle valve 10F, the oil outlet 1 of the 4th threeway solenoid-operated proportional reducing valve 5D connects the return opening 3 of the first oil inlet 3, the first threeway solenoid-operated proportional reducing valve 5A of the 4th shuttle valve 10G, the return opening 3 of the second threeway solenoid-operated proportional reducing valve 5B, the return opening 3 of the return opening 3 of the 3rd threeway solenoid-operated proportional reducing valve 5C and the 4th threeway solenoid-operated proportional reducing valve 5D is parallel-connected to the first return opening 1 of fuel tank 15;
The oil outlet 2 of oil outlet 2, the first shuttle valve 10D of the second oil inlet 1 connection the first threeway proportional pressure-reducing valve 8A of the first shuttle valve 10D connects the left side commutation control mouth 65 of the first pilot operated directional control valve 6;
The oil outlet 2 of oil outlet 2, the second shuttle valve 10E of the second oil inlet 1 connection the second threeway proportional pressure-reducing valve 8B of the second shuttle valve 10E connects the right side commutation control mouth 66 of the first pilot operated directional control valve 6;
The oil outlet 2 of oil outlet 2, the three shuttle valve 10F of the second oil inlet 1 connection the 3rd threeway proportional pressure-reducing valve 8C of the 3rd shuttle valve 10F connects the left side commutation control mouth 75 of the second pilot operated directional control valve 7;
The oil outlet 2 of oil outlet 2, the four shuttle valve 10G of the second oil inlet 1 connection the 4th threeway proportional pressure-reducing valve 8D of the 4th shuttle valve 10G connects the right side commutation control mouth 76 of the second pilot operated directional control valve 7;
The return opening 2 that the oil inlet 3 of the oil inlet 3 of the oil inlet 3 of the oil inlet 3 of the first threeway proportional pressure-reducing valve 8A, the second threeway proportional pressure-reducing valve 8B, the 3rd threeway proportional pressure-reducing valve 8C and the 4th threeway proportional pressure-reducing valve 8D is parallel-connected to the return opening 1 of return opening 2, the 3rd threeway proportional pressure-reducing valve 8C of return opening 1, the second threeway proportional pressure-reducing valve 8B of oil outlet 41, the first threeway proportional pressure-reducing valve 8A of reducing valve 4 and the 4th threeway proportional pressure-reducing valve 8D is parallel-connected to the first return opening 1 of fuel tank 15;
The outer drain tap 43 of reducing valve 4 is connected to the first return opening 1 of fuel tank 15;
The first load communication port 61 of the first pilot operated directional control valve 6 connects respectively the second oil inlet 1 of the 5th shuttle valve 10A and the oil inlet 2 of the first balance cock 9A, the return opening 64 that the second load communication port 62 of the first pilot operated directional control valve 6 connects respectively oil inlet 2, the first pilot operated directional control valves 6 of the first oil inlet 3 of the 5th shuttle valve 10A and the second balance cock 9B connects the second return opening 2 of fuel tanks 15;
The first load communication port 71 of the second pilot operated directional control valve 7 connects respectively the second oil inlet 1, the first hook oil cylinder 13A and the second hook oil cylinder 13B, the first support oil cylinder 12A and the second support oil cylinder 12B of the 6th shuttle valve 10C, the second load communication port 72 of the second pilot operated directional control valve 7 connects respectively the first oil inlet 3, the first hook oil cylinder 13A and the second hook oil cylinder 13B, the first support oil cylinder 12A and the second support oil cylinder 12B of the 6th shuttle valve 10C, and the return opening 74 of the second pilot operated directional control valve 7 connects the second return opening 2 of fuel tank 15;
The oil outlet 2 of the 5th shuttle valve 10A connects the second oil inlet 1 of the 7th shuttle valve 10B, the feedback signal mouth 23 of the oil outlet 2 difference connecting tee pressure compensators 2 of the first oil inlet 3, the seven shuttle valve 10B of oil outlet 2 connections the 7th shuttle valve 10B of the 6th shuttle valve 10C and the oil inlet 31 of safety valve 3;
Be connected in parallel the second return opening 2 of fuel tank 15 of the return opening 22 of three-way pressure compensating device 2 and the oil outlet 32 of safety valve 3;
The oil outlet 1 of the first balance cock 9A be connected the oil outlet 1 of balance cock 9B and connect respectively the first moved arm lifting oil cylinder 11A and the second moved arm lifting oil cylinder 11B, the outside control mouth 3 of oil inlet 2, the second balance cock 9B of outside control mouth 3 connections the second balance cock 9B of the first balance cock 9A connects the oil inlet 2 of the first balance cock 9A.
The first load communication port 71 of the second pilot operated directional control valve 7 and the second load communication port 72 arrive the first hook oil cylinder 13A and the second hook oil cylinder 13B by hydraulic control one-way valve 14 respectively.
Embodiment:
One, fix-displacement pump 1 is as propulsion source, and power is all from engine in situ, and power is passed to Hydraulic Pump through change speed gear box and power takeoff.
Two, the pressure oil of the outlet P1 of fix-displacement pump 1 directly arrives the oil inlet 21 of three-way pressure compensating device 2, the oil inlet 63 of the first pilot operated directional control valve 6, the oil inlet 73 of the second pilot operated directional control valve 7, the oil inlet 2 of the first threeway solenoid-operated proportional reducing valve 5A, the oil inlet 2 of the second threeway solenoid-operated proportional reducing valve 5B, the oil inlet 2 of the 3rd threeway solenoid-operated proportional reducing valve 5C, the oil inlet 2 of the 4th threeway solenoid-operated proportional reducing valve 5D, the oil inlet 42 of reducing valve 4.
Three, after fix-displacement pump 1 starts, when system did not have electric signal, three-way pressure compensating device 2 was with setting pressure (general 0.9MPa) overflow of pressure spring, and whole flows of pump overflow back fuel tank.The pressure of the oil outlet P1 of fix-displacement pump 1 is.
Four, when the electromagnet Y1 of the first threeway solenoid-operated proportional reducing valve 5A obtains signal generator sends in the operator's compartment electric signal, then the oil outlet 1 of the first threeway solenoid-operated proportional reducing valve 5A has the pilot pressure oil that is in proportion with electric signal to flow out, pilot pressure oil is through the first oil inlet 3 of the first shuttle valve 10D, oil outlet 2, the final left side commutation control mouth 65 that arrives the first pilot operated directional control valve 6, this pilot pressure oil promotes the spool of the first pilot operated directional control valve 6, it is moved right, spool is opened, and causes the pressure oil of working connection P1 to arrive the oil inlet 2 of the first balance cock 9A and the second oil inlet 1 of the 5th shuttle valve 10A through the first load communication port 61 of the first pilot operated directional control valve 6.
Most of pressure oil arrives the large chamber of the first moved arm lifting oil cylinder 11A and the second moved arm lifting oil cylinder 11B through oil inlet 2, oil outlet 1, the A1 of the first balance cock 9A, and the pushing piston bar stretches out; Some pressure oil is through the second oil inlet 1, the oil outlet 2 of the 5th shuttle valve 10A, arrive the oil outlet 2 of the first oil inlet 3, the 7th shuttle valve 10B of the 7th shuttle valve 10B to the feedback signal mouth 23 of three-way pressure compensating device 2, this hydraulic oil is the load pressure feedback signal.
Three-way pressure compensating device 2 is under the effect of the load feedback signal of feedback signal mouth 23, and the pressure of oil inlet 21 only also can rise to the setting pressure (general 0.9MPa) than the high pressure spring of load feedback signal.The pressure that is P1 is only high than load pressure.The oil inlet 63 of the first pilot operated directional control valve 6 and the pressure reduction between the first load communication port 61 also are at this moment, be certain value, so that only relevant in its valve core opening size by the flow of the first pilot operated directional control valve 6, system provides the flow of its needs to the large chamber of the first moved arm lifting oil cylinder 11A and the second moved arm lifting oil cylinder 11B, the flow that fix-displacement pump 1 is unnecessary, overflowed back the second return opening 2 of fuel tank 15 through return opening 22, the T1 of three-way pressure compensating device 2 with only high than load pressure pressure by three-way pressure compensating device 2, load pressure is less, and then oil pressure relief is lower.And unlike common throttling speed control circuit, no matter load pressure is high or low, fix-displacement pump 1 is set high pressure with constant by pass valve all the time and is overflowed back fuel tank 15, and cal val is greatly reduced.
The effect of safety valve 3 its safety valves, when the load feedback pressure signal surpassed its setting value, safety valve 3 work were limited to the pressure of load system in its range of set value.
Five, when the electromagnet Y2 of the second threeway solenoid-operated proportional reducing valve 5B obtains signal generator sends in the operator's compartment electric signal, then the oil outlet 1 of the second threeway solenoid-operated proportional reducing valve 5B has the pilot pressure oil that is in proportion with electric signal to flow out, pilot pressure oil is through the first oil inlet 3 of the second shuttle valve 10E, oil outlet 2, the final right side commutation control mouth 66 that arrives the first pilot operated directional control valve 6, this pilot pressure oil promotes the spool of the first pilot operated directional control valve 6, make it to left movement, spool is opened, and causes the pressure oil of working connection P1 to arrive the oil inlet 2 of the second balance cock 9B and the first oil inlet 3 of the 5th shuttle valve 10A through the second load communication port 62 of the first pilot operated directional control valve 6.
Most of pressure oil arrives the loculus of the first moved arm lifting oil cylinder 11A and the second moved arm lifting oil cylinder 11B through oil inlet 2, oil outlet 1, the B1 of the second balance cock 9B, and the pushing piston bar is retracted; Some pressure oil is through the first oil inlet 3, the oil outlet 2 of the 5th shuttle valve 10A, arrive the second oil inlet 1 of the 7th shuttle valve 10B, the oil outlet 2 of the 7th shuttle valve 10B is to the feedback signal mouth 23 of three-way pressure compensating device 2, and this hydraulic oil is the load pressure feedback signal.
Three-way pressure compensating device 2 is under the effect of the load feedback signal of feedback signal mouth 23, and the pressure of oil inlet 21 only also can rise to the setting pressure (general 0.9MPa) than the high pressure spring of load feedback signal.The pressure that is P1 is only high than load pressure.The oil inlet 63 of the first pilot operated directional control valve 6 and the pressure reduction between the second load communication port 62 also are at this moment, be certain value, so that only relevant in its valve core opening size by the flow of the first pilot operated directional control valve 6, system provides the flow of its needs to the loculus of the first moved arm lifting oil cylinder 11A and the second moved arm lifting oil cylinder 11B, the flow that fix-displacement pump 1 is unnecessary, overflowed back the second return opening 2 of fuel tank 15 through return opening 22, the T1 of three-way pressure compensating device 2 with only high than load pressure pressure by three-way pressure compensating device 2, load pressure is less, and then oil pressure relief is lower.And unlike common throttling speed control circuit, no matter load pressure is high or low, fix-displacement pump 1 is set high pressure with constant by pass valve all the time and is overflowed back fuel tank 15, and cal val is greatly reduced.
The effect of safety valve 3 its safety valves, when the load feedback pressure signal surpassed its setting value, safety valve 3 work were limited to the pressure of load system in its range of set value.
Six, when the electromagnet Y3 of the 3rd threeway solenoid-operated proportional reducing valve 5C obtains signal generator sends in the operator's compartment electric signal, then the oil outlet 1 of the 3rd threeway solenoid-operated proportional reducing valve 5C has the pilot pressure oil that is in proportion with electric signal to flow out, pilot pressure oil is through the first oil inlet 3 of the 3rd shuttle valve 10F, oil outlet 2, the final left side commutation control mouth 75 that arrives the second pilot operated directional control valve 7, this pilot pressure oil promotes the spool of the second pilot operated directional control valve 7, it is moved right, spool is opened, cause the pressure oil of working connection P1 through the second oil inlet 1 of the first load communication port 71 arrival the 6th shuttle valve 10C of the second pilot operated directional control valve 7, and the first support oil cylinder 12A, the large chamber of the second support oil cylinder 12B and the first hook oil cylinder 13A, the large chamber of the second hook oil cylinder 13B.
Most of pressure oil arrives the large chamber of the first support oil cylinder 12A, the second support oil cylinder 12B and the large chamber of the first hook oil cylinder 13A, the second hook oil cylinder 13B through A2, and the pushing piston bar stretches out; Some pressure oil is through the second oil inlet 1, the oil outlet 2 of the 6th shuttle valve 10C, arrive the oil outlet 2 of the first oil inlet 3, the 7th shuttle valve 10B of the 7th shuttle valve 10B to the feedback signal mouth 23 of three-way pressure compensating device 2, this hydraulic oil is the load pressure feedback signal.
Three-way pressure compensating device 2 is under the effect of the load feedback signal of feedback signal mouth 23, and the pressure of oil inlet 21 only also can rise to the setting pressure (general 0.9MPa) than the high pressure spring of load feedback signal.The pressure that is P1 is only high than load pressure.The oil inlet 73 of the second pilot operated directional control valve 7 and the pressure reduction between the first load communication port 71 also are at this moment, be certain value, so that only relevant in its valve core opening size by the flow of the second pilot operated directional control valve 7, system is to the first support oil cylinder 12A, the large chamber of the second support oil cylinder 12B and the first hook oil cylinder 13A, the flow that the large chamber of the second hook oil cylinder 13B provides it to need, the flow that fix-displacement pump 1 is unnecessary, by three-way pressure compensating device 2 with only than the return opening 22 of the high pressure of load pressure through three-way pressure compensating device 2, T1 overflows back the second return opening 2 of fuel tank 15, load pressure is less, and then oil pressure relief is lower.And unlike common throttling speed control circuit, no matter load pressure is high or low, fix-displacement pump 1 is set high pressure with constant by pass valve all the time and is overflowed back fuel tank 15, and cal val is greatly reduced.
The effect of safety valve 3 its safety valves, when the load feedback pressure signal surpassed its setting value, safety valve 3 work were limited to the pressure of load system in its range of set value.
Seven, when the electromagnet Y4 of the 4th threeway solenoid-operated proportional reducing valve 5D obtains signal generator sends in the operator's compartment electric signal, then the oil outlet 1 of the 4th threeway solenoid-operated proportional reducing valve 5D has the pilot pressure oil that is in proportion with electric signal to flow out, pilot pressure oil is through the first oil inlet 3 of the 4th shuttle valve 10G, oil outlet 2, the final right side commutation control mouth 76 that arrives the second pilot operated directional control valve 7, this pilot pressure oil promotes the spool of the second pilot operated directional control valve 7, make it to left movement, spool is opened, cause the pressure oil of working connection P1 through the first oil inlet 3 of the second load communication port 72 arrival the 6th shuttle valve 10C of the second pilot operated directional control valve 7, and the first support oil cylinder 12A, the loculus of the second support oil cylinder 12B and the first hook oil cylinder 13A, the loculus of the second hook oil cylinder 13B.
Most of pressure oil arrives the loculus of the first support oil cylinder 12A, the second support oil cylinder 12B and the loculus of the first hook oil cylinder 13A, the second hook oil cylinder 13B through B2, and the pushing piston bar is retracted; Some pressure oil is through the first oil inlet 3, the oil outlet 2 of the 6th shuttle valve 10C, arrive the oil outlet 2 of the first oil inlet 3, the 7th shuttle valve 10B of the 7th shuttle valve 10B to the feedback signal mouth 23 of three-way pressure compensating device 2, this hydraulic oil is the load pressure feedback signal.
Three-way pressure compensating device 2 is under the effect of the load feedback signal of feedback signal mouth 23, and the pressure of oil inlet 21 only also can rise to the setting pressure (general 0.9MPa) than the high pressure spring of load feedback signal.The pressure that is P1 is only high than load pressure.The oil inlet 73 of the second pilot operated directional control valve 7 and the pressure reduction between the second load communication port 72 also are at this moment, be certain value, so that only relevant in its valve core opening size by the flow of the second pilot operated directional control valve 7, system is to the first support oil cylinder 12A, the loculus of the second support oil cylinder 12B and the first hook oil cylinder 13A, the flow that the loculus of the second hook oil cylinder 13B provides it to need, the flow that fix-displacement pump 1 is unnecessary, by three-way pressure compensating device 2 with only than the return opening 22 of the high pressure of load pressure through three-way pressure compensating device 2, T1 overflows back the second return opening 2 of fuel tank 15, load pressure is less, and then oil pressure relief is lower.And unlike common throttling speed control circuit, no matter load pressure is high or low, fix-displacement pump 1 is set high pressure with constant by pass valve all the time and is overflowed back fuel tank 15, and cal val is greatly reduced.
The effect of safety valve 3 its safety valves, when the load feedback pressure signal surpassed its setting value, safety valve 3 work were limited to the pressure of load system in its range of set value.
Eight, when adopting remote operation outside operator's compartment, after fix-displacement pump 1 delivery pressure oil P1 arrived the oil inlet 42 of reducing valve 4, low pressure oil arrived the oil inlet 3 of the first threeway proportional pressure-reducing valve 8A through P2 from oil outlet 41.When operating the handle of the first threeway proportional pressure-reducing valve 8A, then the oil outlet 2 of the first threeway proportional pressure-reducing valve 8A has and the outflow of the proportional pilot pressure oil of the spool stroke of the first threeway proportional pressure-reducing valve 8A.Pilot pressure oil is through the second oil inlet 1, the oil outlet 2 of the first shuttle valve 10D, the final left side commutation control mouth 65 that arrives the first pilot operated directional control valve 6, this pilot pressure oil promotes the spool of pilot operated directional control valve 6, and it is moved right, spool is opened, and the follow-up work principle is with the same described in above-mentioned four.
Nine, when operating the handle of the second threeway proportional pressure-reducing valve 8B, then the oil outlet 2 of the second threeway proportional pressure-reducing valve 8B has and the outflow of the proportional pilot pressure oil of the spool stroke of the second threeway proportional pressure-reducing valve 8B.Pilot pressure oil is through the second oil inlet 1, the oil outlet 2 of the second shuttle valve 10E, the final right side commutation control mouth 66 that arrives the first pilot operated directional control valve 6, this pilot pressure oil promotes the spool of the first pilot operated directional control valve 6, make it to left movement, spool is opened, and the follow-up work principle is with the same described in above-mentioned five.
Ten, when operating the handle of the 3rd threeway proportional pressure-reducing valve 8C, then the oil outlet 2 of the 3rd threeway proportional pressure-reducing valve 8C has and the outflow of the proportional pilot pressure oil of the spool stroke of the 3rd threeway proportional pressure-reducing valve 8C.Pilot pressure oil is through the second oil inlet 1, the oil outlet 2 of the 3rd shuttle valve 10F, the final left side commutation control mouth 75 that arrives the second pilot operated directional control valve 7, this pilot pressure oil promotes the spool of the second pilot operated directional control valve 7, it is moved right, spool is opened, and the follow-up work principle is with the same described in above-mentioned six.
11, when operating the handle of the 4th threeway proportional pressure-reducing valve 8D, then the oil outlet 2 of the 4th threeway proportional pressure-reducing valve 8D has and the outflow of the proportional pilot pressure oil of the spool stroke of the 4th threeway proportional pressure-reducing valve 8D.Pilot pressure oil is through the second oil inlet 1, the oil outlet 2 of the 4th shuttle valve 10G, the final right side commutation control mouth 76 that arrives the second pilot operated directional control valve 7, this pilot pressure oil promotes the spool of the second pilot operated directional control valve 7, make it to left movement, spool is opened, and the follow-up work principle is with the same described in above-mentioned seven.
12, three-way pressure compensating device 2, safety valve 3, reducing valve 4, the first threeway solenoid-operated proportional reducing valve 5A, the second threeway solenoid-operated proportional reducing valve 5B, the 3rd threeway solenoid-operated proportional reducing valve 5C, the 4th threeway solenoid-operated proportional reducing valve 5D, the first pilot operated directional control valve 6, the second pilot operated directional control valve 7, the first threeway proportional pressure-reducing valve 8A, the second threeway proportional pressure-reducing valve 8B, the 3rd threeway proportional pressure-reducing valve 8C, the 4th threeway proportional pressure-reducing valve 8D, the first balance cock 9A, the second balance cock 9B, the first shuttle valve 10D, the second shuttle valve 10E, the 3rd shuttle valve 10F, the 4th shuttle valve 10G, the 5th shuttle valve 10A, the 6th shuttle valve 10C, the 7th shuttle valve 10B all adopts inserted valve, is integrated on the oil path block.
13, electrical signal generator is installed in the operator's compartment, by cable with the electromagnet Y3 of electromagnet Y2, the 3rd threeway solenoid-operated proportional reducing valve 5C of electromagnet Y1, the second threeway solenoid-operated proportional reducing valve 5B of electric signal transmission to the first threeway solenoid-operated proportional reducing valve 5A, the electromagnet Y4 of the 4th threeway solenoid-operated proportional reducing valve 5D.
The present invention adopts the electric-hydraulic proportion mode, reduce the cal val of hydraulic efficiency pressure system, reduce the power dissipation of driving engine, adopt the inserted valve integrated oil path block, installation dimension is little, realizes the directly connection from the integrated package to the oil cylinder, reduces connecting line, reduces leakage of oil, the present invention is easy for installation, machinery-free wearing and tearing, strong, the reduction oil consumption, energy-conservation, simple to operate, non-maintaining of antijamming capability.
Claims (2)
1. electrohydraulic control system that is used for bucket crane, it is characterized in that: it comprises fuel tank, fix-displacement pump, three-way pressure compensating device, safety valve, reducing valve, four threeway solenoid-operated proportional reducing valves, two pilot operated directional control valves, four threeway proportional pressure-reducing valves, two balance cocks, seven shuttle valves, two moved arm lifting oil cylinders, two support oil cylinders, two hook oil cylinders and a hydraulic control one-way valve;
The entrance of fix-displacement pump connects the fuel tank oil outlet, quantitatively oil inlet, the oil inlet of reducing valve, the oil inlet of the first threeway solenoid-operated proportional reducing valve, the oil inlet of the second threeway solenoid-operated proportional reducing valve, the oil inlet of the 3rd threeway solenoid-operated proportional reducing valve, the oil inlet of the 4th threeway solenoid-operated proportional reducing valve, the oil inlet of the first pilot operated directional control valve and the oil inlet of the second pilot operated directional control valve of delivery side of pump difference connecting tee pressure compensator;
The oil outlet of the first threeway solenoid-operated proportional reducing valve connects the first oil inlet of the first shuttle valve, the oil outlet of the second threeway solenoid-operated proportional reducing valve connects the first oil inlet of the second shuttle valve, the oil outlet of the 3rd threeway solenoid-operated proportional reducing valve connects the first oil inlet of the 3rd shuttle valve, the oil outlet of the 4th threeway solenoid-operated proportional reducing valve connects the first oil inlet of the 4th shuttle valve, the return opening of the first threeway solenoid-operated proportional reducing valve, the return opening of the second threeway solenoid-operated proportional reducing valve, the return opening of the return opening of the 3rd threeway solenoid-operated proportional reducing valve and the 4th threeway solenoid-operated proportional reducing valve is parallel-connected to the first return opening of fuel tank;
The second oil inlet of the first shuttle valve connects the oil outlet of the first threeway proportional pressure-reducing valve, and the oil outlet of the first shuttle valve connects the left side commutation control mouth of the first pilot operated directional control valve;
The second oil inlet of the second shuttle valve connects the oil outlet of the second threeway proportional pressure-reducing valve, and the oil outlet of the second shuttle valve connects the right side commutation control mouth of the first pilot operated directional control valve;
The second oil inlet of the 3rd shuttle valve connects the oil outlet of the 3rd threeway proportional pressure-reducing valve, and the oil outlet of the 3rd shuttle valve connects the left side commutation control mouth of the second pilot operated directional control valve;
The second oil inlet of the 4th shuttle valve connects the oil outlet of the 4th threeway proportional pressure-reducing valve, and the oil outlet of the 4th shuttle valve connects the right side commutation control mouth of the second pilot operated directional control valve;
The oil inlet of the oil inlet of the oil inlet of the oil inlet of the first threeway proportional pressure-reducing valve, the second threeway proportional pressure-reducing valve, the 3rd threeway proportional pressure-reducing valve and the 4th threeway proportional pressure-reducing valve is parallel-connected to the oil outlet of reducing valve, and the return opening of the return opening of the return opening of the first threeway proportional pressure-reducing valve, the second threeway proportional pressure-reducing valve, the return opening of the 3rd threeway proportional pressure-reducing valve and the 4th threeway proportional pressure-reducing valve is parallel-connected to the first return opening of fuel tank;
The outer drain tap of reducing valve is connected to the first return opening of fuel tank;
The first load communication port of the first pilot operated directional control valve connects respectively the second oil inlet of the 5th shuttle valve and the oil inlet of the first balance cock, the second load communication port of the first pilot operated directional control valve connects respectively the first oil inlet of the 5th shuttle valve and the oil inlet of the second balance cock, and the return opening of the first pilot operated directional control valve connects the second return opening of fuel tank;
The first load communication port of the second pilot operated directional control valve connects respectively the second oil inlet, the first hook oil cylinder and second hook oil cylinder, the first support oil cylinder and second support oil cylinder of the 6th shuttle valve, the second load communication port of the second pilot operated directional control valve connects respectively the first oil inlet, the first hook oil cylinder and second hook oil cylinder, the first support oil cylinder and second support oil cylinder of the 6th shuttle valve, and the return opening of the second pilot operated directional control valve connects the second return opening of fuel tank;
The oil outlet of the 5th shuttle valve connects the second oil inlet of the 7th shuttle valve, and the oil outlet of the 6th shuttle valve connects the first oil inlet of the 7th shuttle valve, the feedback signal mouth of the oil outlet difference connecting tee pressure compensator of the 7th shuttle valve and the oil inlet of safety valve;
Be connected in parallel the second return opening of fuel tank of the return opening of three-way pressure compensating device and the oil outlet of safety valve;
The oil outlet of the first balance cock be connected the oil outlet of balance cock and connect respectively the first moved arm lifting oil cylinder and the second moved arm lifting oil cylinder, the outside control mouth of the first balance cock connects the oil inlet of the second balance cock, and the outside control mouth of the second balance cock connects the oil inlet of the first balance cock.
2. the electrohydraulic control system for bucket crane according to claim 1 is characterized in that: the first load communication port of the second pilot operated directional control valve and the second load communication port arrive the first hook oil cylinder and the second hook oil cylinder by hydraulic control one-way valve respectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201110282891.0A CN103010069B (en) | 2011-09-22 | 2011-09-22 | For the electrohydraulic control system of bucket crane |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201110282891.0A CN103010069B (en) | 2011-09-22 | 2011-09-22 | For the electrohydraulic control system of bucket crane |
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| CN103010069A true CN103010069A (en) | 2013-04-03 |
| CN103010069B CN103010069B (en) | 2015-09-30 |
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Cited By (5)
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| CN105201951A (en) * | 2015-10-16 | 2015-12-30 | 浙江大学 | High-efficiency high-precision controllable-flow TBM (tunnel boring machine) support hydraulic system |
| WO2017080230A1 (en) * | 2015-11-13 | 2017-05-18 | 上海华测导航技术股份有限公司 | Hydraulic control valve assembly of automatic steering system for agricultural machinery |
| CN107178532A (en) * | 2017-05-19 | 2017-09-19 | 青神格林维尔流体动力控制技术有限公司 | A kind of compressor assembly plug-in integrated package |
| CN107762995A (en) * | 2017-09-13 | 2018-03-06 | 江苏恒立液压科技有限公司 | Novel electric proportional overflow device |
| CN114060332A (en) * | 2021-12-02 | 2022-02-18 | 中煤科工集团重庆研究院有限公司 | Anti-deviation crawler walking hydraulic system |
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| KR101965094B1 (en) * | 2015-11-13 | 2019-04-02 | 샹하이 화처 네비게이션 테크놀로지 엘티디. | Hydraulic control valve assembly of automatic steering system for agricultural machinery |
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| CN107178532A (en) * | 2017-05-19 | 2017-09-19 | 青神格林维尔流体动力控制技术有限公司 | A kind of compressor assembly plug-in integrated package |
| CN107762995A (en) * | 2017-09-13 | 2018-03-06 | 江苏恒立液压科技有限公司 | Novel electric proportional overflow device |
| CN107762995B (en) * | 2017-09-13 | 2023-12-22 | 江苏恒立液压科技有限公司 | Novel electric proportion overflow device |
| CN114060332A (en) * | 2021-12-02 | 2022-02-18 | 中煤科工集团重庆研究院有限公司 | Anti-deviation crawler walking hydraulic system |
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Effective date of registration: 20210419 Address after: 200941, No. 8, building 168, four Yuan Road, Shanghai, Baoshan District Patentee after: SHANGHAI BAOYE METALLURGY ENGINEERING Co.,Ltd. Address before: 200941 No. 2457, Fuyuan Road, Shanghai, Baoshan District Patentee before: SHANGHAI BAOYE GROUP Corp.,Ltd. |
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