CN203513118U - Hydraulic confluence control system of truck crane - Google Patents
Hydraulic confluence control system of truck crane Download PDFInfo
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- CN203513118U CN203513118U CN201320381342.3U CN201320381342U CN203513118U CN 203513118 U CN203513118 U CN 203513118U CN 201320381342 U CN201320381342 U CN 201320381342U CN 203513118 U CN203513118 U CN 203513118U
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Abstract
The utility model relates to a hydraulic confluence control system of a truck crane. The hydraulic confluence control system comprises a confluence control network and a pilot control manifold block. The confluence control network comprises a shuttle valve S1, a shuttle valve S2, a shuttle valve S3, a shuttle valve S4, a confluence valve H1 and a control valve K1 which are connected with each element in a hydraulic-control upper truck reversing valve of a crane, oil inlets P1 and P2, an oil return port T and a pilot control block by an oil path. The pilot control manifold block comprises a shuttle valve S5, a shuttle valve S6, a shuttle valve S7 and control valves K2, K3 and K4 which are communicated with the hydraulic-control upper truck reversing valve by the oil path. The hydraulic confluence control system disclosed by the utility model is more matched to the truck crane hydraulic system control design, and well satisfies performance requirements of a consumer on the truck crane; moreover, whole machine performance, whole machine safety performance, temperature increase balance and whole machine power utilization rate of the whole machine hydraulic system are improved greatly.
Description
Technical field
The utility model relates to a kind of pair of fix-displacement pump hydraulic oil Confluent control system of Hydraulic guide control hoisting crane.
Background technology
On fully hydraulic truck crane, vehicle hydraulic system is pressed work and can be divided into platform revolution, telescopic boom (hoisting arm expansion), luffing, master winch and five subsystems of secondary elevator, because respectively move the different of features and Hydraulic Elements configuration, in conjunction with overall performance, require and safety performance requirement consideration, rated pressure, flow that hydraulic efficiency pressure system has needed while just having determined above-mentioned each subsystem work at the beginning of design differ huge.Because controllable capacity pump cost is higher, therefore in industry generally on medium and small tonnage car hosit, adopt a plurality of fix-displacement pump to be respectively above-mentioned several subsystem fuel feeding, when specific action needs pressure oil flow larger, by the several fix-displacement pump interflow in a plurality of fix-displacement pump, to reach the object that increases specific action speed.
At present, fully hydraulic truck crane hydraulic converging control system generally adopts working connection interflow control program, and major way has two kinds, i.e. the unidirectional interflow of elevator and the interflow mode of entirely moving are described below:
The unidirectional converging system of elevator
As shown in Figure 2, principle of work is: this system is that two quantitative gear pumps are supplied with truck crane master winch, secondary elevator, telescopic boom, luffing action.Pump one output high pressure oil is P1, and pump two pressure oil output are P2.
When master winch spool or the action of secondary elevator spool, converging valve, in upper work, collaborates P1, P2 pressure oil, flow system flow Q=Q pump one+Q pump two, and elevator responsiveness is determined by pump one and pump two pressure oil output flow summations.
When luffing spool or telescoping spool action, pressure oil makes converging valve in the next work by shuttle valve, disconnects interflow state, now, hoisting system flow Q volume=Q pump one, master/secondary elevator responsiveness is determined by pump one delivery rate; Flexible, changing-breadth system flow Q stretches/becomes=Q pump two.Flexible, luffing responsiveness is determined by pump two delivery rates.
When master/secondary elevator spool and flexible/luffing spool move simultaneously, when car hosit is done composite move, converging valve in upper work, disconnects interflow state under flexible/luffing load pressure effect.Main/secondary elevator action and flexible/luffing action are respectively pump one and pump two fuel feeding, prevent undercurrent amount saturation conditions and cannot carry out composite move.
This system exists major defect to be: can only have the unidirectional interflow of elevator state, be that system can only be collaborated to elevator action, and telescopic boom, luffing action cannot collaborate, when telescopic boom, luffing action need fast speed, this system cannot realize, and can only solve by other schemes.
Full action converging system
As shown in Figure 3, this system is supplied with by two quantitative gear pump pressure oil output P1 and P2 the pressure oil of getting on the bus and is driven master winch, secondary elevator, telescopic boom, luffing to move.Interflow principle is:
When master winch spool or the action of secondary elevator spool, pressure oil, by shuttle valve, makes converging valve one in the next work, now, P2 pressure oil, through converging valve two, is supplied with major and minor elevator action with P1 pressure oil interflow, reaches the object that increases major and minor elevator responsiveness.
When luffing spool or the action of telescopic boom spool, pressure oil, by shuttle valve, makes converging valve one in the next work, now, P1 pressure oil, through converging valve two, is supplied with telescopic boom, luffing action with P1 pressure oil interflow, reaches the object that increases telescopic boom, luffing responsiveness.
This system major defect has 2 points, is described below:
1, loss in efficiency increases, luffing fall and contracting arm action in, supply luffing falls and contracting arm operating pressure oil is still the pressure oil P1+P2 behind interflow, but luffing falls and the action of contracting arm needs limit movement speed to improve complete machine safety performance, now, system pressure difference increases, and balance cock performance requriements is increased, cause hydraulic efficiency pressure system excess flow loss to increase, high unfavorable factor is crossed in temperature rise simultaneously.
2, main control valve processing difficulties, easily produces fault, and converging valve all needs to be integrated in main control valve, adds that in main control valve, shuttle valve control network is numerous and diverse unbearably, increases main control valve difficulty of processing, and easily causes shuttle valve to control the faults such as network blockage.
Utility model content
The technical problems to be solved in the utility model is to provide a kind of interflow control program for fully hydraulic truck crane hydraulic efficiency pressure system, it both can solve flexible, the slow problem of luffing responsiveness that in the current industry of main control valve, the unidirectional converging system of elevator causes, also efficiently solve two-way converging system energy consumption problem, and when composite move reasonable distribution system pressure oil flow and effectively increase complete machine power utilization, improve safety performance, thereby effectively reduce fault ratio of hydraulic pressure system.
The utility model solves the technical scheme that its technical matters adopts:
Car hosit hydraulic converging control system, comprise the first oil inlet P 1 and the second oil inlet P 2 that are communicated with use with pump, the first described oil inlet is communicated with vehicle reversing valve on master/secondary elevator respectively by oil circuit, and get on the bus change-over valve to master/secondary elevator fuel feeding by master/secondary elevator, the second described oil inlet is communicated with flexible/luffing change-over valve of getting on the bus respectively by oil circuit, and get on the bus change-over valve to flexible/amplitude oil cylinder fuel feeding by flexible/luffing, described master/secondary elevator change-over valve and flexible/luffing change-over valve of getting on the bus of getting on the bus is connected with oil return inlet T by oil circuit respectively, 2 of the first described oil inlet P 1 and the second oil inlet P are controlled network-in-dialing by an interflow, it is characterized in that: shuttle valve S1 by oil circuit respectively with the master winch change-over valve oil inlet of getting on the bus, the secondary elevator change-over valve oil inlet of getting on the bus, shuttle valve S2, shuttle valve S3 is connected, described shuttle valve S2 is connected with the three-way flow measuring device PC1 between oil return inlet T with shuttle valve S1, control cock K1 and the first oil inlet P 1 respectively by oil circuit, described shuttle valve S3 is connected with get on the bus change-over valve oil inlet, shuttle valve S1, shuttle valve S4 of luffing respectively by oil circuit, described shuttle valve S4 is connected with the three-way flow measuring device PC2 between oil return inlet T with get on the bus change-over valve oil inlet and the second oil inlet P 2 of shuttle valve S3, telescopic boom respectively by oil circuit, described control cock K1 is connected with the three-way flow measuring device PC2 between oil return inlet T with shuttle valve S2, oil return inlet T, the second oil inlet P 2 respectively by oil circuit, and described control cock K1 is connected with external pilot control integrated package guide oil outlet by oil circuit with converging valve H1.
On the basis of above-mentioned main technical schemes, can increase following further perfect technical scheme:
Described pilot control integrated package comprises shuttle valve S5, shuttle valve S6, shuttle valve S7 and control cock K2, control cock K3, control cock K4; Converging valve H1, control cock K1, control cock K2, control cock K3 that described shuttle valve S5 controls in network with interflow by oil circuit are connected; Described shuttle valve S6 is connected with control cock K2, luffing change-over valve guide hydraulic fluid port a1, the telescopic boom change-over valve guide hydraulic fluid port b2 that gets on the bus that gets on the bus respectively by oil circuit; Described shuttle valve S7 is connected with control cock K4, master winch braking hydraulic fluid port z1, secondary elevator braking hydraulic fluid port z2 respectively by oil circuit; Described control cock K2 is connected with shuttle valve S5, shuttle valve S6, control cock K3, control cock K4 and fuel tank respectively by oil circuit, and described control cock K3 is connected with get on the bus change-over valve guide hydraulic fluid port b1 and fuel tank of shuttle valve S5, control cock K2, telescopic boom respectively by oil circuit; Described control cock K4 is connected with shuttle valve S7, control cock K2, guide's oil inlet P and fuel tank by oil circuit.
The utility model is to realize like this, when giving guide's hydraulic fluid port a3/a4/b3/b4 fuel feeding, when the change-over valve master winch of getting on the bus connection or the interlock of secondary elevator are done, control cock K4 left position work, but control cock K2 in right position and control cock K3 in left position, disconnect oil duct mode of operation, external integrated package is inoperative.Now, converging valve H1, in upper work, collaborates P1, P2 pressure oil, improves master winch, secondary elevator responsiveness.
When giving guide's hydraulic fluid port b2 or a1 fuel feeding, luffing action done by the change-over valve luffing of getting on the bus connection or the change-over valve telescopic boom of getting on the bus joins while doing stretch, control cock K2 left position work, but control cock K3 in left position and control cock K4 all in right position, disconnect oil duct mode of operation, external integrated package is inoperative.Now, converging valve H1, in upper work, collaborates P1, P2 pressure oil, has improved luffing or stretch speed.
When giving guide's hydraulic fluid port b1 fuel feeding, when the change-over valve telescopic boom of getting on the bus connection is done the action of contracting arm, control cock K3 right position work, integrated package guide hydraulic fluid port P oil-feed, make converging valve H1 in the next mode of operation, disconnect P1/P2 pressure oil interflow state, restriction luffing falls and contracting arm responsiveness.
When move that elevator+luffing rises or during stretch simultaneously, do that elevator and luffing rise or during semi-girder composite move, in integrated package, control cock K2, K3 are in left position mode of operation, the oil-feed of pilot control integrated package guide P mouth, make converging valve H1 in the next mode of operation, disconnect P1/P2 pressure oil interflow state, system pressure oil flow during reasonable distribution composite move.
Below in conjunction with drawings and Examples, the utility model is further illustrated.
Accompanying drawing explanation
Fig. 1 is car hosit hydraulic converging control system figure of the present utility model.
Fig. 2 is unidirectional converging system hydraulic schematic diagram.
Fig. 3 is two-way converging system hydraulic schematic diagram.
In accompanying drawing: 1. three-way flow measuring device PC1, the 2. master winch change-over valve of getting on the bus, the 3. secondary elevator change-over valve of getting on the bus, 4. the luffing change-over valve of getting on the bus, 5. flexible get on the bus change-over valve, 6. three-way flow measuring device PC2,7. shuttle valve S4,8. shuttle valve S3,9. converging valve H1,10. shuttle valve S1,11. shuttle valve S2,12.q63 pump, 13. shuttle valve S6,14. shuttle valve S7,15. control cock K4,16. control cock K2,17. shuttle valve S5,18. control cock K3,19.q50 pump, 20. control cock K1,21. converging valve one, 22. shuttle valves one, 23. shuttle valves two, 24. converging valve two, 25. converging valve three, 26. shuttle valves three.
The specific embodiment
As shown in Figure 1, car hosit hydraulic converging control system, comprise the first oil inlet P 1 and the second oil inlet P 2 that are communicated with use with at least two connection pumps, the first described oil inlet is connected with master winch change-over valve/secondary elevator change-over valve of getting on the bus of getting on the bus respectively by oil circuit, and get on the bus change-over valve to master/secondary elevator fuel feeding by master/secondary elevator, the second described oil inlet is connected with the flexible change-over valve/luffing of the getting on the bus change-over valve of getting on the bus respectively by oil circuit, and by flexible/luffing to the change-over valve of getting on the bus flexible/amplitude oil cylinder fuel feeding, described master/secondary elevator change-over valve and flexible/luffing change-over valve of getting on the bus of getting on the bus is connected with oil return inlet T by oil circuit respectively, 2 of the first described oil inlet P 1 and the second oil inlet P are controlled network-in-dialing by an interflow, shuttle valve S1 by oil circuit respectively with the master winch change-over valve oil inlet of getting on the bus, secondary elevator commutation 3 oil inlets of getting on the bus, shuttle valve S2, shuttle valve S3 is connected, described shuttle valve S2 is connected with the three-way flow measuring device PC1 between oil return inlet T with shuttle valve S1, control cock K1 and the first oil inlet P 1 respectively by oil circuit, described shuttle valve S3 is connected with get on the bus change-over valve oil inlet, shuttle valve S1, shuttle valve S4 of luffing respectively by oil circuit, described shuttle valve S4 is connected with the three-way flow measuring device PC2 between oil return inlet T with get on the bus change-over valve oil inlet, the second oil inlet P 2 of shuttle valve S3, telescopic boom respectively by oil circuit, described control cock K1 is the three-way flow measuring device PC2 respectively and between shuttle valve S2, oil return inlet T, the second oil inlet P 2 and oil return inlet T by oil circuit, described control cock K1 is connected with external pilot control integrated package guide oil outlet by oil circuit with converging valve H1, and described pilot control integrated package comprises shuttle valve S5, shuttle valve S6, shuttle valve S7 and control cock K2, control cock K3, control cock K4, , described control cock K2, control cock K3, control cock K4 adopt pilot operated directional control valve, and described shuttle valve S5 is connected with control cock K1, control cock K2, control cock K3 with converging valve H1 respectively by oil circuit, described shuttle valve S6 by oil circuit respectively with control cock K2, control luffing and play action guide oil mouth b2, control stretch guide hydraulic fluid port a1 and be connected, described shuttle valve S7 is connected with control cock K4, master winch drg guide hydraulic fluid port z1, secondary hoist brake guide hydraulic fluid port z2 respectively by oil circuit, described control cock K2 is connected with shuttle valve S5, shuttle valve S6, control cock K3, control cock K4 and fuel tank respectively by oil circuit, and described control cock K3 is connected with shuttle valve S5, control cock K2, control contracting arm action guide hydraulic fluid port b1, fuel tank respectively by oil circuit, described control cock K4 is connected with shuttle valve S7, control cock K2, guide's oil inlet P, fuel tank by oil circuit.
Hydraulic principle of the present utility model, as shown in Figure 1, supposes to adopt two fix-displacement pump fuel feeding, and wherein q63 pump is fix-displacement pump rated discharge 63 ml/r, and q50 pump is fix-displacement pump rated discharge 50 ml/r, and supposes that engine governed speed is 2000 r/min.
1, when single movement master winch or secondary elevator, be that master winch is got on the bus change-over valve or secondary elevator while getting on the bus change-over valve action, pilot operated directional control valve K2 left position work, but pilot operated directional control valve K3 disconnects oil duct mode of operation in right position and pilot operated directional control valve K4 in left, external integrated package oil circuit disconnects, inoperative.Now, converging valve H1, in upper work, collaborates P1, P2 pressure oil.Now master winch/secondary hoisting system pressure oil flow Q volume is:
Q volume=(q63 pump+q50 pump) * n=(63+50) * 2000=226 (L/min)
2, when the luffing change-over valve of getting on the bus is done luffing action or semi-girder and got on the bus change-over valve while doing stretch, pilot operated directional control valve K2 left position work, but pilot operated directional control valve K3 in left position and pilot operated directional control valve K4 all in right position, disconnect oil circuit mode of operation, external integrated package is inoperative.Now, converging valve H1, in upper work, collaborates P1, P2 pressure oil, has improved luffing or stretch speed.Now a semi-girder/variable amplitude hydraulic system pressure oil flow Q stretches/rises and is:
Q stretches, rises=(q63 pump+q50 pump) * n=(63+50) * 2000=226 (L/min)
3, when the telescopic boom change-over valve of getting on the bus is done contracting arm when action, pilot operated directional control valve K3 right position work, integrated package guide hydraulic fluid port P oil-feed, makes converging valve H1 in the next mode of operation, disconnects P1/P2 pressure oil interflow state, restriction contracting arm responsiveness.Now supply with the contracting arm/changing-breadth system pressure oil that falls and supplied with by q 50 pumps, pressure oil flow Q contract/fall for:
Q contracts/falls=q50 pump * n=50*2000=100 (L/min)
4, when move that elevator+luffing rises or during stretch simultaneously, do that elevator and luffing rise or during semi-girder composite move, in integrated package, pilot operated directional control valve K2, pilot operated directional control valve K4 are in left position mode of operation, the oil-feed of integrated package guide P mouth, make converging valve H1 in the next mode of operation, disconnect P1/P2 pressure oil interflow state, system pressure oil flow during reasonable distribution composite move.Now, now hoisting system flow Q volume is:
Q volume=q63 pump * n=63*2000=126 (L/min)
Flexible/changing-breadth system flow Q stretches/becomes:
Q stretches/becomes=q50 pump * n=50*2000=100 (L/min)
And the unidirectional converging system hydraulic principle of existing configuration elevator, as shown in Figure 2,
1, when car hosit one action elevator, when single movement master winch spool or secondary elevator spool.Because flexible, luffing join spool without system pressure, in shuttle valve network, without pressure oil, exist, now unidirectional converging valve one is in upper work.Hoisting system flow is Dual-pump flow-converging, and now hoisting system flow Q volume is:
Q volume=(q63 pump+q50 pump) * n=(63+50) * 2000=226 (L/min)
2, when car hosit is done separately luffing, expanding-contracting action, due to luffing, telescopic system, build-up pressure is oily, and high pressure oil disconnects unidirectional converging valve one by shuttle valve network makes it in the next work.Flexible/changing-breadth system flow is the independent fuel feeding of q50 pump, now flexible, luffing connection pressure oil flow Q stretches, becomes:
Q stretches, becomes=q50 pump * n=50*2000=100 (L/min)
3, when car hosit is done elevator, flexible/luffing composite move simultaneously, while moving master/secondary elevator spool and stretch/luffing spool simultaneously, due to luffing, telescopic system, build-up pressure is oily, and high pressure oil disconnects unidirectional converging valve one by shuttle valve one makes it in the next work.Hoisting system is by q63 oil pump feed, and flexible/changing-breadth system is by q50 oil pump feed, and now hoisting system flow Q volume is:
Q volume=q63 pump * n=63*2000=126 (L/min)
Flexible/changing-breadth system flow Q stretches/becomes:
Q stretches/becomes=q50 pump * n=50*2000=100 (L/min)
Configure two-way converging system hydraulic principle, as shown in Figure 3,
1, when car hosit one action elevator, when single movement master winch spool or secondary elevator spool.Because flexible, luffing join spool without system pressure, shuttle valve two is interior to be existed without pressure oil, and now unidirectional converging valve two is in upper work; Hoisting system is build-up pressure, and high pressure oil disconnects converging valve three in the next work by shuttle valve three.Hoisting system hydraulic fluid flow rate is Dual-pump flow-converging, and now hoisting system flow Q volume is:
Q volume=(q63 pump+q50 pump) * n=(63+50) * 2000=226 (L/min)
2, when car hosit, do separately luffing, expanding-contracting action, while moving luffing spool or telescoping spool, due to luffing, telescopic system, build-up pressure is oily, and high pressure oil disconnects unidirectional converging valve two by shuttle valve two makes it in the next work; But now hoisting system build-up pressure not, causes converging valve three in upper work.Flexible/changing-breadth system hydraulic fluid flow rate is Dual-pump flow-converging, now flexible, luffing connection pressure oil flow Q stretches, becomes:
Q stretches, becomes=(q63 pump+q50 pump) * n=(63+50) * 2000=226 (L/min)
3, when car hosit, do elevator, flexible/luffing composite move, hoisting system and luffing/telescopic system be build-up pressure oil simultaneously, and high pressure oil is by shuttle valve two and shuttle valve three disconnects converging valve two and converging valve three makes it all in the next work.Hoisting system is by q63 oil pump feed, and flexible/changing-breadth system is by q50 oil pump feed, and now hoisting system flow Q volume is:
Q volume=q63 pump * n=63*2000=126 (L/min)
Flexible/changing-breadth system flow Q stretches/becomes:
Q stretches/becomes=q50 pump * n=50*2000=100 (L/min)
By above-mentioned, can draw:
While doing separately elevator action, three kinds of interflow schemes all can reach client to the requirement of elevator subsystem responsiveness, increase elevator subsystem flow.
While doing separately semi-girder/play luffing action, hydraulic converging control system and the converging system two schemes that entirely moves all can reach client to semi-girder/rise luffing responsiveness requirement.
While doing separately the action of the contracting arm/luffing that falls, only have full action converging system by P1, P2 interflow, extremely bad on overall performance impact, not only cause Hydraulic System Fever serious, cause complete machine power dissipation, even jeopardize complete machine safety.
Compound while doing the action of elevator+telescopic boom/luffing, three kinds of schemes all can disconnect system P1, P2 interflow state, avoid the saturated fault of minus flow that flow system flow causes not when composite move.
Hydraulic converging control system is matched with system for hydraulic system of truck crane design more, employing is Dual-pump flow-converging when elevator moves, Dual-pump flow-converging when semi-girder and a luffing move, and the scheme that disconnection is collaborated when the action of contracting arm, composite move, more meet client to car hosit performance requriements, and all improving a lot aspect the temperature rise balance of overall performance, complete machine safety performance, complete machine hydraulic efficiency pressure system, complete machine power utilization.
Claims (2)
1. car hosit hydraulic converging control system, comprise the first oil inlet P 1 and the second oil inlet P 2 that are communicated with use with pump, the first described oil inlet is communicated with master/secondary elevator change-over valve of getting on the bus respectively by oil circuit, and get on the bus change-over valve to master/secondary elevator fuel feeding by master/secondary elevator, the second described oil inlet is communicated with flexible/luffing change-over valve of getting on the bus respectively by oil circuit, and get on the bus change-over valve to flexible/amplitude oil cylinder fuel feeding by flexible/luffing, described master/secondary elevator change-over valve and flexible/luffing change-over valve of getting on the bus of getting on the bus is connected with oil return inlet T by oil circuit respectively, 2 of the first described oil inlet P 1 and the second oil inlet P are controlled network-in-dialing by an interflow, it is characterized in that: shuttle valve S1 by oil circuit respectively with the master winch change-over valve oil inlet of getting on the bus, the secondary elevator change-over valve oil inlet of getting on the bus, shuttle valve S2, shuttle valve S3 is connected, described shuttle valve S2 is connected with the three-way flow measuring device PC1 between oil return inlet T with shuttle valve S1, control cock K1 and the first oil inlet P 1 respectively by oil circuit, described shuttle valve S3 is connected with get on the bus change-over valve oil inlet, shuttle valve S1, shuttle valve S4 of luffing respectively by oil circuit, described shuttle valve S4 is connected with the three-way flow measuring device PC2 between oil return inlet T with get on the bus change-over valve oil inlet and the second oil inlet P 2 of shuttle valve S3, telescopic boom respectively by oil circuit, described control cock K1 is connected with the three-way flow measuring device PC2 between oil return inlet T with shuttle valve S2, oil return inlet T, the second oil inlet P 2 respectively by oil circuit, and described control cock K1 is connected with external pilot control integrated package guide oil outlet by oil circuit with converging valve H1.
2. car hosit hydraulic converging control system according to claim 1, is characterized in that; Described pilot control integrated package comprises shuttle valve S5, shuttle valve S6, shuttle valve S7 and control cock K2, control cock K3, control cock K4; Converging valve H1, control cock K1, control cock K2, control cock K3 that described shuttle valve S5 controls in network with interflow by oil circuit are connected; Described shuttle valve S6 is connected with control cock K2, luffing change-over valve guide hydraulic fluid port a1, the telescopic boom change-over valve guide hydraulic fluid port b2 that gets on the bus that gets on the bus respectively by oil circuit; Described shuttle valve S7 is connected with control cock K4, master winch braking hydraulic fluid port z1, secondary elevator braking hydraulic fluid port z2 respectively by oil circuit; Described control cock K2 is connected with shuttle valve S5, shuttle valve S6, control cock K3, control cock K4 and fuel tank respectively by oil circuit, and described control cock K3 is connected with get on the bus change-over valve guide hydraulic fluid port b1 and fuel tank of shuttle valve S5, control cock K2, telescopic boom respectively by oil circuit; Described control cock K4 is connected with shuttle valve S7, control cock K2, guide's oil inlet P and fuel tank by oil circuit.
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| CN201320381342.3U CN203513118U (en) | 2013-06-30 | 2013-06-30 | Hydraulic confluence control system of truck crane |
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| CN201320381342.3U CN203513118U (en) | 2013-06-30 | 2013-06-30 | Hydraulic confluence control system of truck crane |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103303801A (en) * | 2013-06-30 | 2013-09-18 | 安徽柳工起重机有限公司 | Hydraulic confluence control system for truck crane |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103303801A (en) * | 2013-06-30 | 2013-09-18 | 安徽柳工起重机有限公司 | Hydraulic confluence control system for truck crane |
| CN103303801B (en) * | 2013-06-30 | 2015-03-11 | 安徽柳工起重机有限公司 | Hydraulic confluence control system for truck crane |
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Granted publication date: 20140402 Effective date of abandoning: 20150311 |
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