CN101451548B - Hydraulic transmission system implementing rapid starting/stopping and stable steering for large inertia load - Google Patents

Hydraulic transmission system implementing rapid starting/stopping and stable steering for large inertia load Download PDF

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Publication number
CN101451548B
CN101451548B CN2007101924859A CN200710192485A CN101451548B CN 101451548 B CN101451548 B CN 101451548B CN 2007101924859 A CN2007101924859 A CN 2007101924859A CN 200710192485 A CN200710192485 A CN 200710192485A CN 101451548 B CN101451548 B CN 101451548B
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China
Prior art keywords
oiler
oil outlet
valve
relief valve
liquid ratio
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Expired - Fee Related
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CN2007101924859A
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Chinese (zh)
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CN101451548A (en
Inventor
邓华
夏毅敏
李群明
何竞飞
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Central South University
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Central South University
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Abstract

The present invention discloses a smooth and steady inverting hydraulic gear system that can realize big mass load quick startup and brake and dispel pitch play, which includes a oil tank, a variable capacity pump, a filter, a sequence valve, a one way valve, a three-position four-way electrohydraulic reversal valve, electrohydraulic proportionality over-flow valve, a hydraulic slave motor, a decelerator and pairs of wheel gear big and small. A hydraulic system in the invention is composed by two pars of a accelerate loop and a decelerate loop, wherein the accelerate loop and the decelerate loop supply oil in inverse direction on accelerate startup and decelerate brake stages, and adjust pressure value on each loop through four electrohydraulic proportionality over-flow valves to get enough pressure to drive the motor on the accelerate loop, and pressure on decelerate brake loop only need to be adjusted to make small gear wheel driven by motor on its loop stay close to the big gear wheel. From that gear influence from pitch play to transmission when gears engage can be dispelled and smooth and steady inverting can be done through the invention.

Description

A kind of large inertia load rapid starting/stopping and Hydraulic Power Transmission System that steadily commutates of realizing
Affiliated technical field:
The invention belongs to the hydraulics field, relate to a kind of heavy manipulator for forging clamp rotating hydraulic system.
Background technique:
The rapid starting/stopping of large inertia load acceleration and deceleration process and steady commutation problem are of long duration, especially in field of metallurgical machine, because some harsh job requirement of metallurgical machinery requires the system of large inertia load can finish acceleration startup and retarding braking apace.Sometimes an operation cycle itself is exactly very of short duration, as the heavy manipulator for forging of the corollary equipment of large pressing machine, owing to forge the requirement that adds the Forging Technology in man-hour, manipulator requires per minute to finish tens times and quickens the work of startup, retarding braking, and each operation cycle will turn over the angle of regulation, load for this big inertia, require per minute to finish tens such work rotation driving hydraulic system has been proposed very high requirement, system must be able to finish the function of quick startup and steady commutation.Be delivered to small gear from the moment of oil hydraulic motor output through retarder, and then drive gearwheel (large inertia load) rotation.In the gear train assembly since when Errors in Gear Processing, alignment error and gear engagement the wearing and tearing of flank profil cause the existence of gear clearance, for the big inertia system of frequent clockwise and anticlockwise, when will certainly causing the gear clockwise and anticlockwise, the existence of gear clearance produces very big impact.Next is for the system that requires frequent clockwise and anticlockwise and require rapid starting/stopping, and the element responds time that plays the role of changing in the fast-response requirement system of system must lack.In order to overcome backlash between the gear purpose of rapid starting/stopping is impacted and reached in the startup of the influence of system's transmission stability, mild hydraulic system itself, design a kind of large inertia load rapid starting/stopping and Hydraulic Power Transmission System that steadily commutates of realizing.
Summary of the invention:
Quick startup and retarding braking and the requirement that commutates stably for the load that overcomes big inertia, the invention provides a kind ofly, regulate the purpose of finishing commutation by the pressure of electricity liquid ratio relief valve by speed-up loop and retarding braking Hydraulic Power Transmission System dimerous.
The technical solution adopted for the present invention to solve the technical problems comprises: fuel tank, gearwheel, two variable displacement pumps, two filters, two relief valves, two electro-hydraulic reversing valves, two motors, two retarders, two small gears, four electricity liquid ratio relief valves, six one-way valves.Because speed-up loop and retarding braking return circuit can exchange in the system, rotate clockwise with fluid motor-driven gearwheel in the system with reference to figure 1 and describe.The oiler A1 of the filter 2 in the speed-up loop leads to fuel tank, the oiler A2 of the logical variable displacement pump 3 of the oil outlet B1 of filter 2, the oil outlet B2 of variable displacement pump 3 respectively with the oiler P1 of relief valve 4, the oiler A3 of one-way valve 5 communicates, the oil outlet T1 of relief valve 4 leads to fuel tank, the oiler P2 of the oil outlet B3 energising liquid selector valve 6 of one-way valve 5, the oil outlet A4 of electro-hydraulic reversing valve 6 respectively with the oil outlet B5 of one-way valve 7, the oiler P3 of electricity liquid ratio relief valve 9, the oiler A7 of oil hydraulic motor 11 communicates, the oiler A5 of one-way valve 7 communicates with fuel tank, the oil outlet T3 of electricity liquid ratio relief valve 9 leads to fuel tank, the oil outlet B7 of oil hydraulic motor 11 respectively with the oiler P4 of electricity liquid ratio relief valve 10, the oil outlet B6 of one-way valve 8, the oil outlet B4 of electro-hydraulic reversing valve 6 communicates, the oil outlet T4 of electricity liquid ratio relief valve 10 leads to fuel tank, the oiler A6 of one-way valve 8 leads to fuel tank, the oil return inlet T 2 logical fuel tanks of electro-hydraulic reversing valve 6; The oiler A8 of the filter 15 in the retarding braking loop leads to fuel tank, the oiler A9 of the logical variable displacement pump 16 of the oil outlet B8 of filter 15, the oil outlet B9 of variable displacement pump 16 respectively with the oiler P5 of relief valve 17, the oiler A10 of one-way valve 18 communicates, the oil outlet T5 of relief valve 17 leads to fuel tank, the oiler P6 of the oil outlet B10 energising liquid selector valve 19 of one-way valve 20, the oil outlet A11 of electro-hydraulic reversing valve 19 respectively with the oil outlet B12 of one-way valve 20, the oiler P7 of electricity liquid ratio relief valve 22, the oiler A14 of oil hydraulic motor 24 communicates, the oiler A12 of one-way valve 20 communicates with fuel tank, the oil outlet T7 of electricity liquid ratio relief valve 22 leads to fuel tank, the oil outlet B14 of oil hydraulic motor 24 respectively with the oiler P8 of electricity liquid ratio relief valve 23, the oil outlet B13 of one-way valve 21, the oil outlet B11 of electro-hydraulic reversing valve 19 communicates, the oil outlet T8 of electricity liquid ratio relief valve 23 leads to fuel tank, the oiler A13 of one-way valve 21 leads to fuel tank, the oil return inlet T 6 logical fuel tanks of electro-hydraulic reversing valve 19.
The present invention compares with technical background, and the useful effect that has is:
1) adopted oil hydraulic motor to import and export the pressure feedback of oily side and the pressure control technology of electricity liquid ratio relief valve, realized the real-time regulated of various load different pressures, the operating range of system is wide
2) adopt by the scheme of quickening the combination of startup and retarding braking loop, quickening and the decelerating phase, each loop is the while fuel feeding all, motor driven small gear separately on acceleration and the deceleration loop oppositely is meshed with gearwheel, eliminated because there is the impact that system is produced in the gap between the gear when retarding braking, reached the purpose of steady commutation.
3) because the commutation of system is the electricity liquid ratio relief valve that quickens on startup and the retarding braking loop by regulating, and the adjusting that the force value of electricity liquid ratio relief valve can be real-time, thereby can reach pinpoint function.And the native system commutation is to finish by regulating the force value of quickening the electricity liquid ratio relief valve on startup and the retarding braking loop, under the identical situation of system pressure the response time of electricity liquid ratio relief valve faster than the response time of electro-hydraulic reversing valve, thereby reached the effect of fast braking.
Heighten to value the electricity liquid ratio relief valve that quickens on startup and the retarding braking loop when 4) being about to brake simultaneously together in system, make system after under the motor braking, can form high residual pressure, and high residual pressure starts the time that the required high pressure in loop forms when having shortened system start-up on the one hand, reached the purpose of quick startup, quicken to start on the other hand and the retarding braking loop on high residual pressure reduced to quicken to start and the pressure reduction in retarding braking loop the hydraulic shock during mild startup.
Native system is not only applicable to the system of two fluid motor-driven, is applicable to the system of a plurality of fluid motor-driven simultaneously yet.
Description of drawings
The present invention is further illustrated with the concrete mode of implementing below in conjunction with accompanying drawing.
Accompanying drawing 1 is a structural principle schematic representation of the present invention.Fig. 2 a is the pressure setting curve of system's electricity liquid ratio relief valve 9 when rotating clockwise.Fig. 2 b is the pressure setting curve of system's electricity liquid ratio relief valve 23 when rotating clockwise.Fig. 2 c is the pressure setting curve of system's electricity liquid ratio relief valve 10,22 when rotating clockwise.The pressure setting curve of electricity liquid ratio relief valve 9 when Fig. 3 a is system's counterclockwise rotation.The pressure setting curve of electricity liquid ratio relief valve 23 when Fig. 3 b is system's counterclockwise rotation.The pressure setting curve of electricity liquid ratio relief valve 10,22 when Fig. 3 c is system's counterclockwise rotation.Y coordinate is represented pressure in Fig. 2 a, Fig. 2 b, Fig. 2 c, Fig. 3 a, Fig. 3 b, Fig. 3 c, the abscissa express time.
Embodiment:
As shown in the figure, present invention includes a fuel tank 1,14, two variable displacement pumps of gearwheel 3,16, filter 2,15, relief valve 4,17, electro-hydraulic reversing valve 6,19, motor 11,24, retarder 12,25, small gear 13,26,9,10,22,23, six one-way valves 5,7,8,18,20,21 of four electricity liquid ratio relief valves.Because speed-up loop and retarding braking return circuit can exchange in the system, rotate clockwise with fluid motor-driven gearwheel in the system with reference to figure 1 and describe.The oiler of the filter 2 in the speed-up loop leads to fuel tank, the oiler A2 of the logical variable displacement pump 3 of the oil outlet B1 of first filter 2, the oil outlet B2 of first variable displacement pump 3 respectively with the oiler P1 of first relief valve 4, the oiler A3 of first one-way valve 5 communicates, the oil outlet T1 of first relief valve 4 leads to fuel tank, the oiler P2 of logical first electro-hydraulic reversing valve 6 of the oil outlet B3 of first one-way valve 5, the oil outlet A4 of first electro-hydraulic reversing valve 6 respectively with the oil outlet B5 of second one-way valve 7, the oiler P3 of first electricity liquid ratio relief valve 9, the oiler A7 of first oil hydraulic motor 11 communicates, the oiler A5 of second one-way valve 7 communicates with fuel tank, the oil outlet T3 of first electricity liquid ratio relief valve 9 leads to fuel tank, the oil outlet B7 of first oil hydraulic motor 11 respectively with the oiler P4 of second electricity liquid ratio relief valve 10, the oil outlet B6 of the 3rd one-way valve 8, the oil outlet B4 of first electro-hydraulic reversing valve 6 communicates, the oil outlet T4 of second electricity liquid ratio relief valve 10 leads to fuel tank, the oiler A6 of the 3rd one-way valve 8 leads to fuel tank, the oil return inlet T 2 logical fuel tanks of first electro-hydraulic reversing valve 6; The oiler A8 of second filter 15 leads to fuel tank, the oiler A9 of logical second variable displacement pump 16 of the oil outlet B8 of second filter 15, the oil outlet B9 of second variable displacement pump 16 respectively with the oiler P5 of second relief valve 17, the oiler A10 of the 4th one-way valve 18 communicates, the oil outlet T5 of second relief valve 17 leads to fuel tank, the oiler P6 of logical second electro-hydraulic reversing valve 19 of the oil outlet B10 of the 4th one-way valve 18, the oil outlet A11 of second electro-hydraulic reversing valve 19 respectively with the oil outlet B12 of the 5th one-way valve 20, the oiler P7 of the 3rd electricity liquid ratio relief valve 22, the oiler A14 of second oil hydraulic motor 24 communicates, the oiler A12 of the 5th one-way valve 20 communicates with fuel tank, the oil outlet T7 of the 3rd electricity liquid ratio relief valve 22 leads to fuel tank, the oil outlet B14 of second oil hydraulic motor 24 respectively with the oiler P8 of the 4th electricity liquid ratio relief valve 23, the oil outlet B13 of the 6th one-way valve 21, the oil outlet B11 of second electro-hydraulic reversing valve 19 communicates, the oil outlet T8 of the 4th electricity liquid ratio relief valve 23 leads to fuel tank, the oiler A13 of the 6th one-way valve 21 leads to fuel tank, the oil return inlet T 6 logical fuel tanks of second electro-hydraulic reversing valve 19.Electricity liquid ratio relief valve 9 control signals (see that Fig. 2 a) imports by the pressure signal of setting, electricity liquid ratio relief valve 23 control signals are by an other setting pressure signal (seeing Fig. 2 b) input, and electricity liquid ratio relief valve 10,22 control signals are again by an other setting pressure signal (seeing Fig. 2 c) input.When the counterclockwise rotation is pressed by system, quicken to start loop and the exchange of retarding braking return circuit, this moment, electricity liquid ratio relief valve 9 control signals (saw that Fig. 3 a) imports by the pressure signal of setting, electricity liquid ratio relief valve 23 control signals are by an other setting pressure signal (seeing Fig. 3 b) input, and electricity liquid ratio relief valve 10,22 control signals are again by an other setting pressure signal (seeing Fig. 3 c) input.
Working procedure of the present invention is as follows:
With reference to figure 1, when the system drive gearwheel moved clockwise, system was at boost phase, and first oil hydraulic circuit (loop, left side) starts the loop as quickening, and second oil hydraulic circuit (loop, right side) is as the retarding braking loop.Electro-hydraulic reversing valve 6 when system begins to start in first oil hydraulic circuit is connected position, a left side, and the electro-hydraulic reversing valve 19 in second oil hydraulic circuit is connected right position.The force value of the electricity liquid ratio relief valve 9 in first oil hydraulic circuit is transferred to the needed maximum pressure value of system drive large inertia load, the force value of the electricity liquid ratio relief valve in second oil hydraulic circuit is set up and can be made small gear 35 be close to gearwheel 18 to get final product, quicken to start the oiler A2 of logical first variable displacement pump 3 of oil outlet B1 of the pressure oil process filter 2 on the loop, the oil outlet B2 of first variable displacement pump 3 respectively with the oiler P1 of first relief valve 4, the oiler A3 of first one-way valve 5 communicates, the oil outlet T1 of first relief valve 4 leads to fuel tank, the oiler P2 of logical first electro-hydraulic reversing valve 6 of the oil outlet B3 of first one-way valve 5, the oil outlet A4 of first electro-hydraulic reversing valve 6 respectively with the oil outlet B5 of second one-way valve 7, the oiler P3 of first electricity liquid ratio relief valve 9, the oiler A7 of first oil hydraulic motor 11 communicates, the oiler A5 of second one-way valve 7 communicates with fuel tank, the oil outlet T3 of first electricity liquid ratio relief valve 9 leads to fuel tank, the oil outlet B7 of first oil hydraulic motor 11 respectively with the oiler P4 of second electricity liquid ratio relief valve 10, the oil outlet B6 of the 3rd one-way valve 8, the oil outlet B4 of first electro-hydraulic reversing valve 6 communicates, the oil outlet T4 of second electricity liquid ratio relief valve 10 leads to fuel tank, the oiler A6 of the 3rd one-way valve 8 leads to fuel tank, the oil return inlet T 2 logical fuel tanks of first electro-hydraulic reversing valve 6; The oiler A8 of second filter 15 leads to fuel tank, the oiler A9 of logical second variable displacement pump 16 of the oil outlet B8 of second filter 15, the oil outlet B9 of second variable displacement pump 16 respectively with the oiler P5 of second relief valve 17, the oiler A10 of the 4th one-way valve 18 communicates, the oil outlet T5 of second relief valve 17 leads to fuel tank, the oiler P6 of logical second electro-hydraulic reversing valve 19 of the oil outlet B10 of the 4th one-way valve 18, the oil outlet A11 of second electro-hydraulic reversing valve 19 respectively with the oil outlet B12 of the 5th one-way valve 20, the oiler P7 of the 3rd electricity liquid ratio relief valve 22, the oiler A14 of second oil hydraulic motor 24 communicates, the oiler A12 of the 5th one-way valve 20 communicates with fuel tank, the oil outlet T7 of the 3rd electricity liquid ratio relief valve 22 leads to fuel tank, the oil outlet B14 of second oil hydraulic motor 24 respectively with the oiler P8 of the 4th electricity liquid ratio relief valve 23, the oil outlet B13 of the 6th one-way valve 21, the oil outlet B11 of second electro-hydraulic reversing valve 19 communicates, the oil outlet T8 of the 4th electricity liquid ratio relief valve 23 leads to fuel tank, the oiler A13 of the 6th one-way valve 21 leads to fuel tank, the oil return inlet T 6 logical fuel tanks of second electro-hydraulic reversing valve 19.Reach hydraulic system after the moment that needs retarding braking and will finish the action of retarding braking, this moment is former, and to be used as quickening starting the fuel feeding direction of oil hydraulic circuit of retarding braking still the same, selector valve 6 and 19 does not commutate yet, just the force value as the electricity liquid ratio relief valve 9 on first oil hydraulic circuit that quickens startup usefulness will reduce, as long as electricity liquid ratio relief valve 9 can guarantee motor and can be close to above the gearwheel by driving pinion, and the force value side of the electricity liquid ratio relief valve 23 on the retarding braking loop needs to rise, and making to have enough big force value to make load can reach braking in scheduled time in the deceleration system.The moment under motor is about to brake, electricity liquid ratio relief valve 23 force value on acceleration primer fluid hydraulic circuit electricity liquid ratio relief valve 9 and the retarding braking loop are while heightening with value all, can prevent on the one hand since on two the pressure difference on the oil hydraulic circuit cause motor generation backward rotation, can make the certain remaining oil pressure of formation in two oil hydraulic circuits on the other hand again, thereby start the time that the required high pressure in loop forms when having shortened system start-up, reached the purpose of quick startup, moreover quicken to start and the retarding braking loop on high residual pressure reduced to quicken the pressure reduction in startup and retarding braking loop, hydraulic shock during mild the startup, when system will carry out the rotation of inverse clock aspect, only the exchange function in acceleration startup in the original system and retarding braking loop need be got final product.

Claims (1)

1. realize large inertia load rapid starting/stopping and the Hydraulic Power Transmission System that steadily commutates for one kind, it is characterized in that system forms by quickening startup loop and retarding braking loop two-part; This Hydraulic Power Transmission System comprises: a fuel tank (1), gearwheel (14), two variable displacement pumps (3,16), filter (2,15), relief valve (4,17), electro-hydraulic reversing valve (6,19), motor (11,24), retarder (12,25), small gear (13,26), four electricity liquid ratio relief valves (9,10,22,23), six one-way valves (5,7,8,18,20,21); The oiler A1 of first filter (2) leads to fuel tank, the oiler A2 of logical first variable displacement pump (3) of the oil outlet B1 of first filter (2), the oil outlet B2 of first variable displacement pump (3) respectively with the oiler P1 of first relief valve (4), the oiler A3 of first one-way valve (5) communicates, the oil outlet T1 of first relief valve (4) leads to fuel tank, the oiler P2 of logical first electro-hydraulic reversing valve (6) of the oil outlet B3 of first one-way valve (5), the oil outlet A4 of first electro-hydraulic reversing valve (6) respectively with the oil outlet B5 of second one-way valve (7), the oiler P3 of first electricity liquid ratio relief valve (9), the oiler A7 of first oil hydraulic motor (11) communicates, the oiler A5 of second one-way valve (7) communicates with fuel tank, the oil outlet T3 of first electricity liquid ratio relief valve (9) leads to fuel tank, the oil outlet B7 of first oil hydraulic motor (11) respectively with the oiler P4 of second electricity liquid ratio relief valve (10), the oil outlet B6 of the 3rd one-way valve (8), the oil outlet B4 of first electro-hydraulic reversing valve (6) communicates, the oil outlet T4 of second electricity liquid ratio relief valve (10) leads to fuel tank, the oiler A6 of the 3rd one-way valve (8) leads to fuel tank, the oil return inlet T 2 logical fuel tanks of first electro-hydraulic reversing valve (6); The oiler A8 of second filter (15) leads to fuel tank, the oiler A9 of logical second variable displacement pump (16) of the oil outlet B8 of second filter (15), the oil outlet B9 of second variable displacement pump (16) respectively with the oiler P5 of second relief valve (17), the oiler A10 of the 4th one-way valve (18) communicates, the oil outlet T5 of second relief valve (17) leads to fuel tank, the oiler P6 of logical second electro-hydraulic reversing valve (19) of the oil outlet B10 of the 4th one-way valve (18), the oil outlet A11 of second electro-hydraulic reversing valve (19) respectively with the oil outlet B12 of the 5th one-way valve (20), the oiler P7 of the 3rd electricity liquid ratio relief valve (22), the oiler A14 of second oil hydraulic motor (24) communicates, the oiler A12 of the 5th one-way valve (20) communicates with fuel tank, the oil outlet T7 of the 3rd electricity liquid ratio relief valve (22) leads to fuel tank, the oil outlet B14 of second oil hydraulic motor (24) respectively with the oiler P8 of the 4th electricity liquid ratio relief valve (23), the oil outlet B13 of the 6th one-way valve (21), the oil outlet B11 of second electro-hydraulic reversing valve (19) communicates, the oil outlet T8 of the 4th electricity liquid ratio relief valve (23) leads to fuel tank, the oiler A13 of the 6th one-way valve (21) leads to fuel tank, the oil return inlet T 6 logical fuel tanks of second electro-hydraulic reversing valve (19), first electricity liquid ratio relief valve (9) control signal is by the first pressure signal input of setting, the 4th electricity liquid ratio relief valve (23) control signal is by the input of the second setting pressure signal, the second and the 3rd electricity liquid ratio relief valve (10,22) control signal is again by the input of the 3rd setting pressure signal.
CN2007101924859A 2007-12-04 2007-12-04 Hydraulic transmission system implementing rapid starting/stopping and stable steering for large inertia load Expired - Fee Related CN101451548B (en)

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CN102121846A (en) * 2010-11-30 2011-07-13 中南大学 Method and device for testing vibration effect of multi-combination hydraulic long pipeline system
WO2014063490A1 (en) * 2012-10-26 2014-05-01 中联重科股份有限公司 Hydraulic system for controlling boom to rotate and control method therefor and concrete pumping equipment

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CN102352832A (en) * 2011-11-03 2012-02-15 徐工集团工程机械股份有限公司 Control method and control device of soft start and soft stop of air compressor
CN102705283A (en) * 2012-05-29 2012-10-03 中南大学 Hydraulic synchronous system for realizing load balance based on proportional relief valve
CN102773397B (en) * 2012-07-18 2014-07-02 中国重型机械研究院有限公司 Walking closed system of forging manipulator
CN105485076B (en) * 2014-11-07 2017-04-05 芜湖新兴铸管有限责任公司 A kind of Centrifugal smearing machine Hydraulic Power Transmission System
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CN102121846A (en) * 2010-11-30 2011-07-13 中南大学 Method and device for testing vibration effect of multi-combination hydraulic long pipeline system
CN102121846B (en) * 2010-11-30 2012-10-31 中南大学 Method and device for testing vibration effect of multi-combination hydraulic long pipeline system
WO2014063490A1 (en) * 2012-10-26 2014-05-01 中联重科股份有限公司 Hydraulic system for controlling boom to rotate and control method therefor and concrete pumping equipment

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