CN202294449U - Electrohydraulic control system used for movable arm of bucket crane - Google Patents
Electrohydraulic control system used for movable arm of bucket crane Download PDFInfo
- Publication number
- CN202294449U CN202294449U CN2011203568047U CN201120356804U CN202294449U CN 202294449 U CN202294449 U CN 202294449U CN 2011203568047 U CN2011203568047 U CN 2011203568047U CN 201120356804 U CN201120356804 U CN 201120356804U CN 202294449 U CN202294449 U CN 202294449U
- Authority
- CN
- China
- Prior art keywords
- valve
- oil
- oil inlet
- reducing valve
- threeway
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Images
Abstract
The utility model relates to an electrohydraulic control system used for a movable arm of a bucket crane. The electrohydraulic control system comprises an oil tank, a dosing pump, a three-way pressure compensator, a safety valve, a reducing valve, a hydraulic-control reversing valve, two three-way electromagnetic proportion reducing valves, two three-way proportion reducing valves, two equilibrium valves, three shuttle valves and two movable arm lifting oil cylinders; the inlet of the dosing pump is connected with the oil outlet of the oil tank; the outlet of the dosing pump is respectively connected with the oil inlets of the three-way pressure compensator, the reducing valve, the two three-way electromagnetic proportion reducing valves and the hydraulic-control reversing valve; the two three-way electromagnetic proportion reducing valves are respectively connected with the two three-way proportion reducing valve and the hydraulic-control reversing valve through the shuttle valves respectively; and the hydraulic-control reversing valve is connected with the movable arm lifting oil cylinders through the equilibrium valves. The electrohydraulic control system has the advantages of convenience in installation, no mechanical wear, strong anti-interference ability, simplicity in operation, and no maintenance.
Description
Technical field
The utility model relates to a kind of electrohydraulic control system, is used for the electrohydraulic control system of suspension bucket car swing arm specifically.
Background technology
The suspension bucket car is the special-use vehicle of 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 the suspension bucket car is made up of last dress equipment and chassis two parts.Suspension bucket car and feed hopper are used transported material, through 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 material from unloading functions.
There is the moved arm lifting oil cylinder suspension bucket car both sides, and the action of moved arm lifting oil cylinder makes the swing arm entablatrance make circular movement, drive feed hoppers through its four terminal chains and make the circular movement motion of translation, carry out the lifting of feed hopper and transfer.
Existing suspension bucket car 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, and this mode requires the by pass valve of system must be in running order always, causes 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 through 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 big, and the temperature of hydraulic oil rises very fast.And hydraulic fluid temperature is too high, 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 suspension bucket car 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 bigger, and operational torque is also bigger, uses simultaneously that wearing and tearing can appear in flexible axle after a period of time, the phenomenon of clamping stagnation.Give the suspension bucket car use and maintenance is made troubles.
Summary of the invention
The utility model is intended to overcome the defective of prior art, and a kind of electrohydraulic control system that is used for suspension bucket car swing arm is provided, and is easy for installation, and nothing machinery weares and teares, antijamming capability is strong, simple to operate, non-maintaining.
In order to solve the problems of the technologies described above, the utility model is achieved in that
A kind of electrohydraulic control system that is used for suspension bucket car swing arm is characterized in that: it comprises fuel tank, fix-displacement pump, three-way pressure compensating device, safety valve, reducing valve, pilot operated directional control valve, two threeway solenoid-operated proportional reducing valves, two threeway proportional pressure-reducing valves, two balance cocks, three shuttle valves and two moved arm lifting oil cylinders;
The inlet of fix-displacement pump connects the fuel tank oil outlet, and quantitatively delivery side of pump connects the oil inlet of three-way pressure compensating device, 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 and the oil inlet of pilot operated directional control valve respectively;
The oil outlet of the first threeway solenoid-operated proportional reducing valve connects first oil inlet of first shuttle valve; The oil outlet of the second threeway solenoid-operated proportional reducing valve connects first oil inlet of second shuttle valve, and the return opening of the return opening of the first threeway solenoid-operated proportional reducing valve and the second threeway solenoid-operated proportional reducing valve is parallel-connected to first return opening of fuel tank;
Second oil inlet of first shuttle valve connects the oil outlet of the first threeway proportional pressure-reducing valve, and the oil outlet of first shuttle valve connects the left side switching-over control mouth of pilot operated directional control valve;
Second oil inlet of second shuttle valve connects the oil outlet of the second threeway proportional pressure-reducing valve, and the oil outlet of second shuttle valve connects the right side switching-over control mouth of pilot operated directional control valve;
The oil inlet of the oil inlet of the first threeway proportional pressure-reducing valve and the second 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 first threeway proportional pressure-reducing valve and the second threeway proportional pressure-reducing valve is parallel-connected to first return opening of fuel tank;
The outer drain tap of reducing valve is connected to first return opening of fuel tank;
The first load communication port of pilot operated directional control valve connects second oil inlet of the 3rd shuttle valve and the oil inlet of first balance cock respectively; The second load communication port of pilot operated directional control valve connects first oil inlet of the 3rd shuttle valve and the oil inlet of second balance cock respectively, and the return opening of pilot operated directional control valve connects second return opening of fuel tank;
The oil outlet of the 3rd shuttle valve connects the feedback signal mouth of three-way pressure compensating device and the oil inlet of safety valve respectively;
Be connected in parallel 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 oil outlet of first balance cock and second balance cock is connected the first moved arm lifting oil cylinder and the second moved arm lifting oil cylinder respectively; The outside control mouth of first balance cock connects the oil inlet of second balance cock, and the outside control mouth of second balance cock connects the oil inlet of first balance cock.
The beneficial effect of the utility model is: employing electric-hydraulic proportion mode, and the cal val of reduction hydraulic efficiency pressure system, the power dissipation of minimizing driving engine, easy for installation, nothing machinery weares and teares, antijamming capability is strong, simple to operate, non-maintaining.
Description of drawings
Below in conjunction with accompanying drawing and embodiment the utility model is done further to specify:
Fig. 1 is the structural representation of the utility model.
The specific embodiment
As shown in Figure 1: a kind of electrohydraulic control system that is used for suspension bucket car swing arm, it comprises fuel tank 15, fix-displacement pump 1, three-way pressure compensating device 2, safety valve 3, reducing valve 4, pilot operated directional control valve 6, two threeway solenoid-operated proportional reducing valve 5A, 5B, two threeway proportional pressure-reducing valve 8A, 8B, two balance cock 9A, 9B, three shuttle valve 10A, 10D, 10E and two moved arm lifting oil cylinder 11A, 11B;
The inlet of fix-displacement pump 1 connects fuel tank 15 oil outlets 3, and the outlet of fix-displacement pump 1 connects the oil inlet 21 of three-way pressure compensating device 2, 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 and the oil inlet 63 of pilot operated directional control valve 6 respectively;
The oil outlet 1 of the first threeway solenoid-operated proportional reducing valve 5A connects first oil inlet 3 of the first shuttle valve 10D; The return opening 3 of first oil inlet, 3, the first threeway solenoid-operated proportional reducing valve 5A of the oil outlet 1 connection second shuttle valve 10E of the second threeway solenoid-operated proportional reducing valve 5B and the return opening 3 of the second threeway solenoid-operated proportional reducing valve 5B are parallel-connected to first return opening 1 of fuel tank 15;
The oil outlet 2 of oil outlet 2, the first shuttle valve 10D of second oil inlet, 1 connection, the first threeway proportional pressure-reducing valve 8A of the first shuttle valve 10D connects the left side switching-over control mouth 65 of pilot operated directional control valves 6;
The oil outlet 2 of oil outlet 2, the second shuttle valve 10E of second oil inlet, 1 connection, the second threeway proportional pressure-reducing valve 8B of the second shuttle valve 10E connects the right side switching-over control mouth 66 of pilot operated directional control valves 6;
The return opening 1 of return opening 1 and the second threeway proportional pressure-reducing valve 8B that the oil inlet 3 of the oil inlet 3 of the first threeway proportional pressure-reducing valve 8A and the second threeway proportional pressure-reducing valve 8B is parallel-connected to oil outlet 41, the first threeway proportional pressure-reducing valve 8A of reducing valve 4 is parallel-connected to first return opening 1 that T2, T3 arrive fuel tank 15;
The outer drain tap 43 of reducing valve 4 is connected to first return opening 1 of fuel tank 15;
The first load communication port 61 of pilot operated directional control valve 6 connects second oil inlet 1 of the 3rd shuttle valve 10A and the oil inlet 2 of the first balance cock 9A respectively; The second load communication port 62 of pilot operated directional control valve 6 connects first oil inlet 3 of the 3rd shuttle valve 10A and the oil inlet 2 of the second balance cock 9B respectively, and the return opening 64 of pilot operated directional control valve 6 connects second return opening 2 of fuel tank 15;
The oil outlet 2 of the 3rd shuttle valve 10A connects the feedback signal mouth 23 of three-way pressure compensating device 2 and the oil inlet 31 of safety valve 3 respectively;
Be connected in parallel 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 is connected the first moved arm lifting oil cylinder 11A and the second moved arm lifting oil cylinder 11B respectively with the oil outlet 1 of the second balance cock 9B; The outside control mouth 3 of oil inlet 2, the second balance cock 9B of the outside control mouth 3 connections second balance cock 9B of the first balance cock 9A connects the oil inlet 2 of the first balance cock 9A.
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 pilot operated directional control valve 6, 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 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.
When four, 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 first oil inlet 3, the oil outlet 2 of the first shuttle valve 10D; The final left side switching-over control mouth 65 that arrives 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 causes the pressure oil of working connection P1 to arrive the oil inlet 2 of the first balance cock 9A and second oil inlet 1 of the 3rd shuttle valve 10A through the first load communication port 61 of pilot operated directional control valve 6.
Most of pressure oil promotes piston rod and stretches out through the big chamber that oil inlet 2, oil outlet 1, the A1 of the first balance cock 9A arrive the first moved arm lifting oil cylinder 11A and the second moved arm lifting oil cylinder 11B; Some pressure oil arrives the feedback signal mouth 23 of three-way pressure compensating device 2 through second oil inlet 1, the oil outlet 2 of the 3rd shuttle valve 10A, 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 pilot operated directional control valve 6 and the pressure reduction between the first load communication port 61 also do at this moment; Be certain value; Make through the flow of pilot operated directional control valve 6 only relevant in its valve core opening size; System provides its flow that needs to the big chamber of the first moved arm lifting oil cylinder 11A and the second moved arm lifting oil cylinder 11B, and the flow that fix-displacement pump 1 is unnecessary is overflowed back 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 more little, and then oil pressure relief is low more.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, and cal val is significantly 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 first oil inlet 3, the oil outlet 2 of the second shuttle valve 10E; The final right side switching-over control mouth 66 that arrives pilot operated directional control valve 6, this pilot pressure oil promotes the spool of pilot operated directional control valve 6, makes 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 first oil inlet 3 of the 3rd shuttle valve 10A through the second load communication port 62 of pilot operated directional control valve 6.
Most of pressure oil promotes the piston rod withdrawal through the loculus that oil inlet 2, oil outlet 1, the B1 of the second balance cock 9B arrive the first moved arm lifting oil cylinder 11A and the second moved arm lifting oil cylinder 11B; Some pressure oil arrives the feedback signal mouth 23 of three-way pressure compensating device 2 through first oil inlet 3, the oil outlet 2 of the 3rd shuttle valve 10A, 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 pilot operated directional control valve 6 and the pressure reduction between the second load communication port 62 also do at this moment; Be certain value; Make through the flow of pilot operated directional control valve 6 only relevant in its valve core opening size; System provides its flow that needs to the loculus of the first moved arm lifting oil cylinder 11A and the second moved arm lifting oil cylinder 11B, and the flow that fix-displacement pump 1 is unnecessary is overflowed back 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 more little, and then oil pressure relief is low more.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, and cal val is significantly 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 outside operator's compartment, adopting remote operation, 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 second oil inlet 1, the oil outlet 2 of the first shuttle valve 10D; The final left side switching-over control mouth 65 that arrives 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.
Seven, 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 second oil inlet 1, the oil outlet 2 of the second shuttle valve 10E; The final right side switching-over control mouth 66 that arrives pilot operated directional control valve 6, this pilot pressure oil promotes the spool of pilot operated directional control valve 6, makes it to left movement; Spool is opened, and the follow-up work principle is with the same described in above-mentioned five.
Eight, 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; Pilot operated directional control valve 6; The first threeway proportional pressure-reducing valve 8A, the second threeway proportional pressure-reducing valve 8B; The first balance cock 9A, the second balance cock 9B, the 3rd shuttle valve 10A, the first shuttle valve 10D, the second shuttle valve 10E all adopt inserted valve, are integrated on the oil path block.
Nine, electrical signal generator is installed in the operator's compartment, through cable with the electromagnet Y1 of electric signal transmission to the first threeway solenoid-operated proportional reducing valve 5A, the electromagnet Y2 of the second threeway solenoid-operated proportional reducing valve 5B.
The utility model employing electric-hydraulic proportion mode, the cal val of reduction hydraulic efficiency pressure system, the power dissipation of minimizing driving engine, easy for installation, nothing machinery weares and teares, antijamming capability is strong, simple to operate, non-maintaining.
Claims (1)
1. electrohydraulic control system that is used for suspension bucket car swing arm, it is characterized in that: it comprises fuel tank, fix-displacement pump, three-way pressure compensating device, safety valve, reducing valve, pilot operated directional control valve, two threeway solenoid-operated proportional reducing valves, two threeway proportional pressure-reducing valves, two balance cocks, three shuttle valves and two moved arm lifting oil cylinders;
The inlet of fix-displacement pump connects the fuel tank oil outlet, and quantitatively delivery side of pump connects the oil inlet of three-way pressure compensating device, 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 and the oil inlet of pilot operated directional control valve respectively;
The oil outlet of the first threeway solenoid-operated proportional reducing valve connects first oil inlet of first shuttle valve; The oil outlet of the second threeway solenoid-operated proportional reducing valve connects first oil inlet of second shuttle valve, and the return opening of the return opening of the first threeway solenoid-operated proportional reducing valve and the second threeway solenoid-operated proportional reducing valve is parallel-connected to first return opening of fuel tank;
Second oil inlet of first shuttle valve connects the oil outlet of the first threeway proportional pressure-reducing valve, and the oil outlet of first shuttle valve connects the left side switching-over control mouth of pilot operated directional control valve;
Second oil inlet of second shuttle valve connects the oil outlet of the second threeway proportional pressure-reducing valve, and the oil outlet of second shuttle valve connects the right side switching-over control mouth of pilot operated directional control valve;
The oil inlet of the oil inlet of the first threeway proportional pressure-reducing valve and the second 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 first threeway proportional pressure-reducing valve and the second threeway proportional pressure-reducing valve is parallel-connected to first return opening of fuel tank;
The outer drain tap of reducing valve is connected to first return opening of fuel tank;
The first load communication port of pilot operated directional control valve connects second oil inlet of the 3rd shuttle valve and the oil inlet of first balance cock respectively; The second load communication port of pilot operated directional control valve connects first oil inlet of the 3rd shuttle valve and the oil inlet of second balance cock respectively, and the return opening of pilot operated directional control valve connects second return opening of fuel tank;
The oil outlet of the 3rd shuttle valve connects the feedback signal mouth of three-way pressure compensating device and the oil inlet of safety valve respectively;
Be connected in parallel 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 oil outlet of first balance cock and second balance cock is connected the first moved arm lifting oil cylinder and the second moved arm lifting oil cylinder respectively; The outside control mouth of first balance cock connects the oil inlet of second balance cock, and the outside control mouth of second balance cock connects the oil inlet of first balance cock.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011203568047U CN202294449U (en) | 2011-09-22 | 2011-09-22 | Electrohydraulic control system used for movable arm of bucket crane |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011203568047U CN202294449U (en) | 2011-09-22 | 2011-09-22 | Electrohydraulic control system used for movable arm of bucket crane |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202294449U true CN202294449U (en) | 2012-07-04 |
Family
ID=46363405
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011203568047U Expired - Fee Related CN202294449U (en) | 2011-09-22 | 2011-09-22 | Electrohydraulic control system used for movable arm of bucket crane |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202294449U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103671364A (en) * | 2012-09-12 | 2014-03-26 | 上海宝冶集团有限公司 | Steering electrohydraulic control system for remote control loading machine |
-
2011
- 2011-09-22 CN CN2011203568047U patent/CN202294449U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103671364A (en) * | 2012-09-12 | 2014-03-26 | 上海宝冶集团有限公司 | Steering electrohydraulic control system for remote control loading machine |
| CN103671364B (en) * | 2012-09-12 | 2015-12-23 | 上海宝冶集团有限公司 | Electrohydraulic control system is turned to for remote control loader |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN202827716U (en) | Steering electro-hydraulic control system for remote-control loader | |
| CN103671364B (en) | Electrohydraulic control system is turned to for remote control loader | |
| CN102588359A (en) | Hydraulic system, excavator and control method of hydraulic system | |
| CN103047208A (en) | Load-sensitive electro-hydraulic proportional multi-way valve | |
| CN103010069B (en) | For the electrohydraulic control system of bucket crane | |
| CN104047912B (en) | The digital pump controlled hydraulic differential cylinder in self-powered source | |
| CN202643158U (en) | Constant tension hoisting operation wave compensation device | |
| CN104554432A (en) | Novel engineering machine steer-by-wire system | |
| CN105422521A (en) | Hydraulic linear drive system based on control of servo pumps, and control method | |
| CN208634118U (en) | The distributed direct of the double accumulators of the double constant displacement pumps of motor driven drives excavator hydraulic system | |
| CN104632794A (en) | Electro-hydraulic servo system of direct drive type hydraulic hoist | |
| CN103161190A (en) | Hybrid power full hydraulic loading machine hydraulic system based on pressure common rail system | |
| CN203114764U (en) | Load-sensitive electro-hydraulic proportional multi-way valve | |
| CN201560422U (en) | Electro-hydraulic proportional control piston-type single-hoisting-point hydraulic hoist | |
| CN105178383B (en) | Load electromechanical drive independent steering system | |
| CN102926359A (en) | Manual and electric dual-purpose integrated hydraulic hoist | |
| CN202827257U (en) | Hydraulic lifting control system for mine self-discharging vehicle and mine self-discharging vehicle | |
| CN101004190A (en) | Open type integral hydraulic motor system | |
| CN202294449U (en) | Electrohydraulic control system used for movable arm of bucket crane | |
| CN104421237A (en) | Hydraulic system for dumper lifting mechanism | |
| CN202544013U (en) | Excavator hydraulic system and excavator | |
| CN202291180U (en) | Water pressure quick forging machine set | |
| CN202108032U (en) | Emergency operating device and gate system of winch hoist | |
| CN202294727U (en) | Electric hydraulic control system for landing legs and hooks of bucket truck | |
| CN208634147U (en) | A kind of driving motor directly drives the hydraulic energy-saving system of pump control cylinder with differential effect |
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: 20120704 Termination date: 20200922 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |