CN103482502A - Crane and boom variable amplitude control system thereof - Google Patents

Crane and boom variable amplitude control system thereof Download PDF

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Publication number
CN103482502A
CN103482502A CN201310460953.1A CN201310460953A CN103482502A CN 103482502 A CN103482502 A CN 103482502A CN 201310460953 A CN201310460953 A CN 201310460953A CN 103482502 A CN103482502 A CN 103482502A
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China
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control
hydraulic fluid
fluid port
valve
communicated
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CN201310460953.1A
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Chinese (zh)
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CN103482502B (en
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史先信
胡小冬
李增彬
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徐州重型机械有限公司
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Abstract

The invention discloses a boom variable amplitude control system of a crane. The system comprises a main reversing valve, a variable amplitude cylinder and an overflow valve group, wherein a first oil port and a second oil port of the main reversing valve are communicated with a rod cavity and a rodless cavity of the variable amplitude cylinder respectively; and the overflow valve group is free of overflowing when a load is smaller than a preset value and has overflowing when the load is larger than the preset value, and the overflow valve group is connected to an oil supply way during variable amplitude drop. According to the boom variable amplitude control system, advantages of power variable amplitude control and gravity variable amplitude control in the prior art are integrated, through control of the overflow valve group, the oil pressure of the oil supply way can be increased under the condition of the a light load to realize efficient drop, and the oil pressure of the oil supply way can be unloaded under the condition of the a heavy load to realize stable drop. The invention further provides the crane comprising the boom variable amplitude control system. The crane has same technical effects.

Description

A kind of hoisting crane and suspension arm variable-amplitude control system thereof
Technical field
The present invention relates to technical field of engineering machinery, relate in particular to a kind of hoisting crane and suspension arm variable-amplitude control system thereof.
Background technology
The crane radical function comprises the actions such as revolution, rising, flexible, luffing, and the luffing of hoisting crane refers to the arm hinge axle rotation after platform that rotates under the induced effect of oil cylinder, and doing luffing rises and the luffing drop action, thereby realizes the variation of boom angle.
The flexible of amplitude oil cylinder realized by HYDRAULIC CONTROL SYSTEM, the luffing control system mainly comprises main reversing valve, balance cock and amplitude oil cylinder, main reversing valve is for controlling oil-feed and the oil return of oil cylinder, balance cock is for controlling the luffing falling speed and keep load when static, and amplitude oil cylinder utilizes its flexible arm that drives rise or fall.
In prior art, the dynamic whereabouts of suspension arm variable-amplitude control system luffing control system and gravity fall luffing control system:
The first, as shown in Figure 1, the hydraulic schematic diagram that this figure is power of the prior art whereabouts luffing control system.
During as the luffing drop action, main reversing valve 1 ' spool be moved to the left under the control of external control oil sources and switch to right position, main reversing valve 1 ' oil-feed port P be connected to amplitude oil cylinder 2 ' rod chamber, oil return inlet T be connected to balance cock 3 ', the rod chamber internal pressure constantly raises under the effect of pump.Balance cock 3 ' control mouthful directly is connected to rod chamber by pipeline, when the rod chamber force value is elevated to can promote balance cock 3 ' commutation the time, oil cylinder is done drop action, until rod chamber pressure, balance cock 3 ' openings of sizes, rodless cavity oil return flow three when balance, are realized stablely falling.
This mode can the self adaptation external loading, according to the variation automatic adjustable balance valve 3 ' openings of sizes of load, makes the luffing falling speed stable within limits.But this mode is responsive to the load variations reaction, for balance cock 3 ' component reliability, response characteristic and and system between matching performance have relatively high expectations, any little deviation all likely causes luffing whereabouts controller performance unstable, causes luffing to fall to shaking.
The second, as shown in Figure 2, the hydraulic schematic diagram that this figure is gravity fall luffing control system of the prior art.
When the luffing drop action, main reversing valve 1 ' spool be moved to the left under the control of external control oil sources and switch to right position, main reversing valve 1 ' oil-feed port P shut, amplitude oil cylinder 2 ' rodless cavity, rod chamber all be connected to oil return inlet T; The external control pilot control is connected directly to balance cock 3 ' control mouthful, and the pressure of external control pilot control is by the decision of handle openings size, and external control pilot control pressure size determines balance cock 3 ' openings of sizes, has determined the size of luffing falling speed.When balance cock 3 ' after opening, arm is done the luffing drop action under the Action of Gravity Field of self gravitation and weight.
This mode, owing to adopting stable outside oil sources to control balance cock 3 ' openings of sizes, can avoid external loading to change the variation of the valve core opening size caused by actv., guarantees the dropping process ride comfort.But only with to control oil supply pressure relevant, when controlling oil supply pressure one regularly, the pressure of luffing falling speed in the derricking cylinder rodless cavity determines due to balance cock 3 ' openings of sizes, so boom angle, weight weight size have a significant impact the luffing falling speed.The pressure simultaneously produced due to arm self when unloaded luffing falls is less, and derricking speed is slower, not strong for high efficiency handling operating mode applicability.
In view of this, urgently for above-mentioned technical matters, power distribution means of the prior art is done to further optimal design, both guaranteed reliability when luffing falls, can improve derricking speed and work efficiency again.
Summary of the invention
Purpose of the present invention is for a kind of hoisting crane and suspension arm variable-amplitude control system thereof are provided, and stability and reliability when this system can either guarantee the luffing whereabouts, can improve again the speed that luffing falls, and increases work efficiency.
For solving the problems of the technologies described above, the invention provides a kind of suspension arm variable-amplitude control system of hoisting crane, comprise main reversing valve and amplitude oil cylinder; The first hydraulic fluid port of described main reversing valve, the second hydraulic fluid port are communicated with rod chamber, the rodless cavity of described amplitude oil cylinder respectively; Also comprise when load is less than preset value that overflow, load do not occur, and the by pass valve group of overflow, supplying on oil circuit when described by pass valve group is connected in the luffing whereabouts occur while being greater than described preset value.
Preferably, described by pass valve group comprises by pass valve and switch valve, confession oil circuit when the first control port of described by pass valve is fallen with described luffing is communicated with, the second control port is communicated with the first hydraulic fluid port of described switch valve, and the second hydraulic fluid port of described switch valve is communicated with the external control oil sources; The first hydraulic fluid port and second hydraulic fluid port of described switch valve disconnect when load is less than described preset value, when load is greater than described preset value, are communicated with.
Adopt this structure, in the luffing dropping process, main reversing valve switched to right position so that the oil-feed port of main reversing valve through the first hydraulic fluid port the rod chamber fuel feeding to amplitude oil cylinder, the rodless cavity of amplitude oil cylinder is communicated with oil return inlet T through the second hydraulic fluid port.
When the load of amplitude oil cylinder is less than preset value, under light duty, the first hydraulic fluid port and the disconnection of the second hydraulic fluid port due to switch valve, therefore, the second hydraulic fluid port of by pass valve is shut, and now overflow is not opened, do not occurred to by pass valve, the rod chamber of amplitude oil cylinder produces certain pressure under the effect of pump, this pressure increases gradually, be applied to rodless cavity after, can accelerate the speed that luffing falls, therefore can realize luffing fast-descending when underloading.
When the load of amplitude oil cylinder is greater than preset value, be that amplitude oil cylinder is under severe duty, the first hydraulic fluid port and the connection of the second hydraulic fluid port due to switch valve, therefore there are certain difference of pressure in the first control port and second control port of by pass valve, along with the pressure of the rod chamber of amplitude oil cylinder increases gradually, when the pressure difference value of the first control port of by pass valve and the second control port is greater than the response pressure that this by pass valve sets, by pass valve generation overflow, the rod chamber of amplitude oil cylinder is without pressure, and now arm starts only to rely on himself gravity and weight weight steadily to descend.
As can be seen here, the suspension arm variable-amplitude control system of said structure has been integrated the advantage that prior art medium power luffing is controlled and the gravity luffing is controlled, and by the control to the by pass valve group, has realized efficient whereabouts when underloading, has realized stable decline during heavy duty.
Preferably, described switch valve is the 2/2-way change-over valve, and when the first control position, its first hydraulic fluid port is communicated with the second hydraulic fluid port; When the second control position, its first hydraulic fluid port and the second hydraulic fluid port disconnect.
Preferably, described by pass valve group is electric proportional pressure control valve.
Preferably, described main reversing valve is three position four-way directional control valve, and when primary importance, its oil-feed port is communicated with the first hydraulic fluid port, and its return opening is communicated with the second hydraulic fluid port; When the second place, its oil-feed port and the first hydraulic fluid port, the second hydraulic fluid port all disconnect; When the 3rd position, its oil-feed port is communicated with the second hydraulic fluid port, and its return opening is communicated with the first hydraulic fluid port.
Preferably, on the oil return line that the luffing of described control system falls, be connected with balance cock, the control port of described balance cock is communicated with the external control oil sources.
The present invention also provides a kind of hoisting crane, comprises arm and the suspension arm variable-amplitude control system be connected with described arm; Described suspension arm variable-amplitude control system adopts structure as above.
Because above-mentioned luffing control system has technique effect as above, therefore, comprise that the hoisting crane of above-mentioned suspension arm variable-amplitude control system also should have identical technique effect, do not repeat them here.
The accompanying drawing explanation
The hydraulic schematic diagram that Fig. 1 is power of the prior art whereabouts luffing control system;
The hydraulic schematic diagram that Fig. 2 is gravity fall luffing control system of the prior art;
The structural representation of a kind of specific embodiment that Fig. 3 is luffing control system provided by the present invention.
Wherein, the Reference numeral in Fig. 1 and Fig. 2 and the corresponding relation between component names are:
Main reversing valve 1 '; Amplitude oil cylinder 2 '; Balance cock 3 ';
Reference numeral and the corresponding relation between component names in Fig. 3 are:
Main reversing valve 1; Amplitude oil cylinder 2; Balance cock 3; By pass valve group 4; By pass valve 41; Switch valve 42.
The specific embodiment
Core of the present invention is for a kind of hoisting crane and suspension arm variable-amplitude control system thereof are provided, and the connection by pass valve group on oil circuit that supplies by falling at luffing, realize not overflow of underloading, heavily loaded overflow, thus the effect of quickening falling speed, the stable whereabouts of heavy duty while reaching underloading.
In order to make those skilled in the art understand better technical scheme of the present invention, below in conjunction with the drawings and specific embodiments, the present invention is described in further detail.
Please refer to Fig. 3, the structural representation of a kind of specific embodiment that Fig. 3 is luffing control system provided by the present invention.
In a kind of specific embodiment, as shown in Figure 3, the invention provides a kind of suspension arm variable-amplitude control system of hoisting crane, comprise main reversing valve 1 and amplitude oil cylinder 2.The first hydraulic fluid port A of main reversing valve 1, the second hydraulic fluid port B are communicated with rod chamber, the rodless cavity of amplitude oil cylinder 2 respectively.This suspension arm variable-amplitude control system also comprises when load is less than preset value that overflow, load do not occur, and the by pass valve group 4 of overflow, supplying on oil circuit when by pass valve group 4 is connected in the luffing whereabouts occur while being greater than preset value.
In concrete scheme, above-mentioned by pass valve group 4 can comprise by pass valve 41 and switch valve 42, confession oil circuit when the first control port of by pass valve 41 is fallen with luffing is communicated with, the second control port is communicated with the first hydraulic fluid port of switch valve 42, and the second hydraulic fluid port of switch valve 42 is communicated with the external control oil sources; The first hydraulic fluid port and second hydraulic fluid port of switch valve 42 disconnect when load is less than preset value, when load is greater than preset value, are communicated with.
Adopt this structure, in the luffing dropping process, as shown in Figure 3, main reversing valve 1 is switched to right position, so that the oil-feed port P of main reversing valve 1 through the first hydraulic fluid port A the rod chamber fuel feeding to amplitude oil cylinder 2, the rodless cavity of amplitude oil cylinder 2 is communicated with oil return inlet T through the second hydraulic fluid port B.
When the load of amplitude oil cylinder 2 is less than preset value, under light duty, the first hydraulic fluid port and the disconnection of the second hydraulic fluid port due to switch valve 42, therefore, the second hydraulic fluid port of by pass valve 41 is shut, and now overflow is not opened, do not occurred to by pass valve 41, the rod chamber of amplitude oil cylinder 2 produces certain pressure under the effect of pump, this pressure increases gradually, be applied to rodless cavity after, can accelerate the speed that luffing falls, therefore can realize luffing fast-descending when underloading.
When the load of amplitude oil cylinder 2 is greater than preset value, be that amplitude oil cylinder 2 is under severe duty, the first hydraulic fluid port and the connection of the second hydraulic fluid port due to switch valve 42, therefore there are certain difference of pressure in the first control port and second control port of by pass valve 41, along with the pressure of the rod chamber of amplitude oil cylinder 2 increases gradually, when the pressure difference value of the first control port of by pass valve 41 and the second control port is greater than the response pressure that this by pass valve 41 sets, overflow occurs in by pass valve 41, the rod chamber of amplitude oil cylinder 2 is without pressure, now arm starts only to rely on himself gravity and weight weight steadily to descend.
As can be seen here, the suspension arm variable-amplitude control system of said structure has been integrated the advantage that prior art medium power luffing is controlled and the gravity luffing is controlled, and by the control to by pass valve group 4, has realized efficient whereabouts when underloading, has realized stable decline during heavy duty.
In scheme, above-mentioned switch valve 42 can be the 2/2-way change-over valve more specifically, and when the first control position, its first hydraulic fluid port is communicated with the second hydraulic fluid port; When the second control position, its first hydraulic fluid port and the second hydraulic fluid port disconnect.
Like this, can realize simply, easily connection or the disconnection of two hydraulic fluid ports of switch valve 42 by the switching of control position, and then realize the control to the overflow action of by pass valve 41.Certainly, above-mentioned switch valve 42, not only for the 2/2-way change-over valve, can also adopt the change-over valve of other structures.
Above-mentioned 2/2-way change-over valve can adopt electromagnetic valve, by electromagnet electric or dead electricity realizes the switching of two control positioies, certainly, this 2/2-way change-over valve also can adopt pilot operated valve device.
Can expect, above-mentioned by pass valve group 4 is not limited in the combination of switch valve 42 and by pass valve 41, and in the another kind of specific embodiment, above-mentioned by pass valve group 4 can also be electric proportional pressure control valve.
Adopt this structure, can accurately control by electric current the openings of sizes of electric proportional pressure control valve 41.The opening that keeps electric proportional pressure control valve 41 when amplitude oil cylinder 2 underloading is zero, so that the pressure of rod chamber increases gradually, realizes that quick luffing falls; When amplitude oil cylinder 2 heavy duty, the opening of electric proportional pressure control valve 41 is adjusted into to maximum, so that the pressure of rod chamber is zero, realizes that arm steadily descends under himself gravity and the effect of weight weight.What is more important, electricity proportional pressure control valve 41 can carry out electrodeless adjusting to its openings of sizes, and then the pressure of the rod chamber of amplitude oil cylinder 2 is carried out to electrodeless adjusting, and therefore can more accurately control the speed that arm descends, guarantee the reliability and stability that arm descends.
In the another kind of specific embodiment, as shown in Figure 3, above-mentioned main reversing valve 1 can be three position four-way directional control valve, and when primary importance, its oil-feed port is communicated with the first hydraulic fluid port, and its return opening is communicated with the second hydraulic fluid port; When the second place, its oil-feed port and the first hydraulic fluid port, the second hydraulic fluid port all disconnect; When the 3rd position, its oil-feed port is communicated with the second hydraulic fluid port, and its return opening is communicated with the first hydraulic fluid port.
Adopt this structure, when control cock, during in the second place, the luffing control system is in off working state.When control cock during in primary importance, the fluid that oil sources provides is filled with the rod chamber of oil cylinder 2 through oil-feed port P, the first oil outlet A and hydraulic tubing, drive the piston rod of oil cylinder 2 to move to rodless cavity, the rodless cavity inner fluid flows back to fuel tank through hydraulic tubing, the second oil outlet B and oil return inlet T, realizes that the luffing of arm falls.When control cock during in the 3rd position, the fluid that oil sources provides is filled with the rodless cavity of oil cylinder 2 through oil-feed port P, the second oil outlet B and hydraulic tubing, drive the piston rod of oil cylinder 2 to move to rod chamber, the rod chamber inner fluid flows back to fuel tank through hydraulic tubing, the first oil outlet A and oil return inlet T, realizes that the luffing of arm rises.
As can be seen here, adopt above-mentioned three position four-way directional control valve as main reversing valve 1, can realize the motion of two oil cylinder 2 different directions, and then realize fixedly rising or the whereabouts of auxiliary.Certainly, above-mentioned control cock, not only for above-mentioned three position four-way directional control valve, can also be other structures.
In the another kind of specific embodiment, be connected with balance cock 3 on the oil return line that the luffing of above-mentioned control system falls, the control port of this balance cock 3 is communicated with the external control oil sources.
Adopt this structure, in the luffing dropping process, control the external control oil sources so that balance cock 3 is opened, the hydraulic oil of the rodless cavity of amplitude oil cylinder 2 can be realized stable the backflow by balance cock 3.Can control the luffing falling speed and can when static, keep load by the openings of sizes of controlling balance cock 3.
The present invention also provides a kind of hoisting crane, comprises arm and the suspension arm variable-amplitude control system be connected with described arm; Described suspension arm variable-amplitude control system adopts structure as above.
Because above-mentioned suspension arm variable-amplitude control system has technique effect as above, therefore, comprise that the hoisting crane of this suspension arm variable-amplitude control system also should have identical technique effect, do not repeat them here.
Above a kind of hoisting crane provided by the present invention and suspension arm variable-amplitude control system thereof are described in detail.Applied specific case herein principle of the present invention and embodiment are set forth, the explanation of above embodiment is just for helping to understand method of the present invention and core concept thereof.It should be pointed out that for those skilled in the art, under the premise without departing from the principles of the invention, can also carry out some improvement and modification to the present invention, these improvement and modification also fall in the protection domain of the claims in the present invention.

Claims (7)

1. the suspension arm variable-amplitude control system of a hoisting crane, comprise main reversing valve (1) and amplitude oil cylinder (2); The first hydraulic fluid port of described main reversing valve (1), the second hydraulic fluid port are communicated with rod chamber, the rodless cavity of described amplitude oil cylinder (2) respectively; It is characterized in that, also comprise when load is less than preset value that overflow, load do not occur, and the by pass valve group (4) of overflow, supplying on oil circuit when described by pass valve group (4) is connected in the luffing whereabouts occur while being greater than described preset value.
2. the suspension arm variable-amplitude control system of hoisting crane according to claim 1, it is characterized in that, described by pass valve group (4) comprises by pass valve (41) and switch valve (42), confession oil circuit when the first control port of described by pass valve (41) is fallen with described luffing is communicated with, the second control port is communicated with the first hydraulic fluid port of described switch valve (42), and the second hydraulic fluid port of described switch valve (42) is communicated with the external control oil sources; The first hydraulic fluid port and second hydraulic fluid port of described switch valve (42) disconnect when load is less than described preset value, when load is greater than described preset value, are communicated with.
3. the suspension arm variable-amplitude control system of hoisting crane according to claim 2, is characterized in that, described switch valve (42) is the 2/2-way change-over valve, and when the first control position, its first hydraulic fluid port is communicated with the second hydraulic fluid port; When the second control position, its first hydraulic fluid port and the second hydraulic fluid port disconnect.
4. the suspension arm variable-amplitude control system of hoisting crane according to claim 1, is characterized in that, described by pass valve group (4) is electric proportional pressure control valve.
5. according to the suspension arm variable-amplitude control system of the described hoisting crane of claim 1-4 any one, it is characterized in that, described main reversing valve (1) is three position four-way directional control valve,
When primary importance, its oil-feed port is communicated with the first hydraulic fluid port, and its return opening is communicated with the second hydraulic fluid port;
When the second place, its oil-feed port and the first hydraulic fluid port, the second hydraulic fluid port all disconnect;
When the 3rd position, its oil-feed port is communicated with the second hydraulic fluid port, and its return opening is communicated with the first hydraulic fluid port.
6. according to the suspender luffing control system of the described hoisting crane of claim 1-4 any one, it is characterized in that, be connected with balance cock (3) on the oil return line that the luffing of described control system falls, the control port of described balance cock (3) is communicated with the external control oil sources.
7. a hoisting crane, comprise arm and the suspension arm variable-amplitude control system be connected with described arm; It is characterized in that, described suspension arm variable-amplitude control system adopts as the described structure of claim 1-6 any one.
CN201310460953.1A 2013-09-30 2013-09-30 A kind of lifting machine and boom variable amplitude control system thereof Active CN103482502B (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104591000A (en) * 2015-02-11 2015-05-06 河海大学常州校区 Accurate lifting rig for travelling crane
CN105201937A (en) * 2014-12-31 2015-12-30 徐州重型机械有限公司 Hydraulic system, crane and auxiliary drive method of hydraulic system
CN106395660A (en) * 2016-10-19 2017-02-15 中联重科股份有限公司 Hydraulic control system of hoisting mechanism and crane

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Publication number Priority date Publication date Assignee Title
JPS54126354A (en) * 1978-03-24 1979-10-01 Aisin Seiki Co Ltd Crane boom rise-fall controller
JPS5631507A (en) * 1979-08-24 1981-03-30 Kayaba Ind Co Ltd Preventive circuit for buckling in hydraulic cylinder
CN202164063U (en) * 2011-06-28 2012-03-14 长沙中联重工科技发展股份有限公司 Automobile crane and suspension arm falling hydraulic system
CN102874697A (en) * 2012-10-18 2013-01-16 中联重科股份有限公司 Hydraulic system for controlling amplitude variation of arm support and crane
CN102887435A (en) * 2012-10-19 2013-01-23 中联重科股份有限公司 Hydraulic system for controlling amplitude variation of crane boom, control method and crane
CN103482476A (en) * 2013-09-29 2014-01-01 徐州重型机械有限公司 Control device for increasing variable-amplitude falling speed of crane
CN203602272U (en) * 2013-09-30 2014-05-21 徐州重型机械有限公司 Crane and crane jib luffing control system thereof

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54126354A (en) * 1978-03-24 1979-10-01 Aisin Seiki Co Ltd Crane boom rise-fall controller
JPS5631507A (en) * 1979-08-24 1981-03-30 Kayaba Ind Co Ltd Preventive circuit for buckling in hydraulic cylinder
CN202164063U (en) * 2011-06-28 2012-03-14 长沙中联重工科技发展股份有限公司 Automobile crane and suspension arm falling hydraulic system
CN102874697A (en) * 2012-10-18 2013-01-16 中联重科股份有限公司 Hydraulic system for controlling amplitude variation of arm support and crane
CN102887435A (en) * 2012-10-19 2013-01-23 中联重科股份有限公司 Hydraulic system for controlling amplitude variation of crane boom, control method and crane
CN103482476A (en) * 2013-09-29 2014-01-01 徐州重型机械有限公司 Control device for increasing variable-amplitude falling speed of crane
CN203602272U (en) * 2013-09-30 2014-05-21 徐州重型机械有限公司 Crane and crane jib luffing control system thereof

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105201937A (en) * 2014-12-31 2015-12-30 徐州重型机械有限公司 Hydraulic system, crane and auxiliary drive method of hydraulic system
CN104591000A (en) * 2015-02-11 2015-05-06 河海大学常州校区 Accurate lifting rig for travelling crane
CN106395660A (en) * 2016-10-19 2017-02-15 中联重科股份有限公司 Hydraulic control system of hoisting mechanism and crane
CN106395660B (en) * 2016-10-19 2019-04-02 中联重科股份有限公司 The hydraulic control system and crane of hoisting mechanism

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