CN104477798A - Main arm variable amplitude control system of crane and crane - Google Patents
Main arm variable amplitude control system of crane and crane Download PDFInfo
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- CN104477798A CN104477798A CN201410756088.XA CN201410756088A CN104477798A CN 104477798 A CN104477798 A CN 104477798A CN 201410756088 A CN201410756088 A CN 201410756088A CN 104477798 A CN104477798 A CN 104477798A
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- 239000003921 oil Substances 0.000 claims abstract description 246
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 33
- 230000005484 gravity Effects 0.000 claims abstract description 29
- 239000012530 fluid Substances 0.000 claims description 9
- 239000002828 fuel tank Substances 0.000 claims description 9
- 230000001502 supplementing effect Effects 0.000 abstract 3
- 230000007246 mechanism Effects 0.000 description 18
- 238000000034 method Methods 0.000 description 8
- 230000008569 process Effects 0.000 description 8
- 230000009471 action Effects 0.000 description 5
- 230000000694 effects Effects 0.000 description 5
- 239000010729 system oil Substances 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 229910000831 Steel Inorganic materials 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
- 239000010959 steel Substances 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 238000013016 damping Methods 0.000 description 2
- 230000005611 electricity Effects 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000001360 synchronised effect Effects 0.000 description 2
- 230000001133 acceleration Effects 0.000 description 1
- 230000008901 benefit Effects 0.000 description 1
- 230000033228 biological regulation Effects 0.000 description 1
- 230000000052 comparative effect Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C13/00—Other constructional features or details
- B66C13/18—Control systems or devices
- B66C13/20—Control systems or devices for non-electric drives
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C23/00—Cranes comprising essentially a beam, boom, or triangular structure acting as a cantilever and mounted for translatory of swinging movements in vertical or horizontal planes or a combination of such movements, e.g. jib-cranes, derricks, tower cranes
- B66C23/62—Constructional features or details
- B66C23/82—Luffing gear
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Automation & Control Theory (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The invention discloses a main arm variable amplitude control system of a crane and the crane, which are used for improving the operation stability and safety of the crane. The main arm variable amplitude control system of the crane comprises a reversing valve, a variable amplitude oil cylinder, a rod cavity balance valve, a stop valve and an oil supplementing device, wherein: the reversing valve is provided with a first working position and a second working position which respectively control the amplitude variation oil cylinder to fall back and rise, and comprises a first working oil port, a second working oil port, an oil inlet and an oil return port; the rod cavity balance valve is arranged on an oil path of a rod cavity oil port of the amplitude variation oil cylinder and is used for closing when the amplitude variation oil cylinder falls back and opening when the amplitude variation oil cylinder rises; the stop valve is arranged on an oil way between a first working oil port of the reversing valve and the balance valve with the rod cavity and is used for conducting when the power of the main arm is lowered and stopping when the gravity of the main arm is lowered; the oil supplementing device is arranged on an oil path between an oil return port of the reversing valve and the balance valve with the rod cavity and used for supplementing hydraulic oil to the rod cavity of the amplitude-variable oil cylinder when the main arm is lowered by gravity.
Description
Technical field
The present invention relates to technical field of engineering machinery, particularly relate to a kind of principal arm luffing control system of hoisting crane and a kind of hoisting crane.
Background technology
As shown in Figure 1a, the structure of existing super-tonnage crane generally includes: swing arm 100, hoisting rope 110, surpassed steel rope 120, principal arm 130 and amplitude oil cylinder 140, and wherein, one end and the vehicle frame 150 of principal arm 130 are hinged, the other end and swing arm 100 hinged; Amplitude oil cylinder 140 for drive the luffing of principal arm 130 hoist and luffing transfer; Hoisting rope 110 is set around on the arm head pulley of swing arm 100, for the weight that hoists; Surpassed steel rope 120 for improve hang carry operation time the force-bearing situation of principal arm 130 and balance quality.As shown in Figure 1 b, to return the vehicle to the garage and knock off state at car load, amplitude oil cylinder 140 falls after rise packs up, and principal arm 130 is delegated on the supporting mechanism 160 of vehicle frame.
At present, the luffing of main arm of crane is transferred and is mainly contained power and transfer and transfer two kinds of modes with gravity.
As illustrated in figure 1 c, luffing control system that mode transfers principal arm mainly comprises to adopt power to transfer: amplitude oil cylinder 140, rodless cavity balance cock 202, guide proportion reducing valve 203, rod chamber balance cock 204 and change-over valve 205.When power transfers principal arm, rod chamber balance cock 204 is closed, the high-pressure oil passage of hydraulic efficiency pressure system and the rod chamber conducting of amplitude oil cylinder 140, the Action of Gravity Field of piston rod by principal arm of amplitude oil cylinder 140 and the pressure effect compression rodless cavity of hydraulic oil, amplitude oil cylinder 140 is fallen after rise pack up, principal arm is transferred on supporting mechanism.But, when the principal arm that again hoists, unlatching rod chamber balance cock 204, the rod chamber of amplitude oil cylinder 140 can by rod chamber balance cock 204 and change-over valve 205 and fuel tank transient switching, the rod chamber moment pressure release of amplitude oil cylinder 140 can produce larger impact to hydraulic efficiency pressure system, thus cause principal arm to rebound, badly influence stationarity and the safety of lifting operation.In addition, if principal arm transfers to level attitude, and operating personal does not stop power lowering operation in time, and the supporting mechanism of vehicle frame is probably by principal arm crimp.
As shown in Figure 1 d, the luffing control system adopting mode of transferring of conducting oneself with dignity to transfer principal arm mainly comprises: amplitude oil cylinder 140, rodless cavity balance cock 202, guide proportion reducing valve 203 and change-over valve 205.When gravity transfers principal arm, the rod chamber of amplitude oil cylinder 140 and fuel tank conducting, the piston rod of amplitude oil cylinder 140 is not by the pressure effect of hydraulic oil, and principal arm is transferred on supporting mechanism under gravity, and amplitude oil cylinder 140 falls after rise and packs up simultaneously.For super-tonnage crane, Chao Qi mechanism can apply one to principal arm makes it to the application force of layback, and transfer mode according to deadweight and transfer principal arm, the piston rod of amplitude oil cylinder 140 is probably pulled out cylinder body suddenly, thus causes comparatively serious safety misadventure.
Therefore, how improving stationarity and the safety of crane hanging component operation, is technical matters urgently to be resolved hurrily at present.
Prior art Reference numeral:
100-swing arm; 110-hoisting rope; 120-has surpassed steel rope; 130-principal arm; 140-amplitude oil cylinder;
150-vehicle frame; 160-supporting mechanism; 202-rodless cavity balance cock; 203-guide proportion reducing valve;
204-rod chamber balance cock; 205-change-over valve.
Embodiment of the present invention Reference numeral:
1,4-amplitude oil cylinder; 2,3-rod chamber balance cock; 5,15-rodless cavity balance cock;
6-main transformer width balance cock; The main balance cock of 6a-; 6b-guide proportion reducing valve; 7-shuttle valve;
8-proportional reversing valve; 8 '-switch change-over valve; 9-pressure-compensated valve; 10-controllable capacity pump;
10 '-proportional variable pump; 11-slippage pump; 12-repairing back pressure valve; 13-repairing check valve;
14-shutoff valve; 14a-pressure-compensated valve element; 14b-inserted valve element; 14c-solenoid directional control valve element;
14d-shuttle valve member.
Summary of the invention
Embodiments provide a kind of principal arm luffing control system of hoisting crane and a kind of hoisting crane, to improve smooth operation and the safety of hoisting crane.
The principal arm luffing control system of the hoisting crane that the embodiment of the present invention provides, comprises change-over valve, amplitude oil cylinder, rod chamber balance cock, shutoff valve and recharging oil device, wherein:
Described change-over valve, has the first control position controlling amplitude oil cylinder and fall after rise, and the second control position that control amplitude oil cylinder hoists, and described change-over valve comprises the first actuator port, the second actuator port, oil inlet and return opening; At described first control position, oil inlet to the first actuator port conducting of change-over valve, the second actuator port of change-over valve is to return opening conducting; At described second control position, oil inlet to the second actuator port conducting of change-over valve, the first actuator port of change-over valve is to return opening conducting;
Described rod chamber balance cock, is arranged on the rod chamber hydraulic fluid port oil circuit of amplitude oil cylinder, for closing when amplitude oil cylinder falls after rise and opening when amplitude oil cylinder hoists;
Described shutoff valve, is arranged on the oil circuit between the first actuator port of change-over valve and rod chamber balance cock, ends for the conducting when principal arm power is transferred and when principal arm gravity is transferred;
Described recharging oil device, is arranged on the oil circuit between the return opening of change-over valve and rod chamber balance cock, and for when principal arm gravity is transferred, the rod chamber to amplitude oil cylinder fills into hydraulic oil.
Preferably, described recharging oil device comprises slippage pump and repairing back pressure valve, wherein:
The oil inlet of described slippage pump and fuel tank conducting, the oil circuit between the return opening of the oil outlet access change-over valve of described slippage pump and rod chamber balance cock;
The oil inlet of described repairing back pressure valve and fuel tank conducting, the oil circuit between the return opening of the oil outlet access change-over valve of described repairing back pressure valve and rod chamber balance cock.
More excellent, the repairing check valve of the oil circuit one-way conduction between described recharging oil device also comprises the return opening of change-over valve to rod chamber balance cock.
Preferably, principal arm luffing control system also comprises: rodless cavity balance cock, is arranged on the rodless cavity hydraulic fluid port oil circuit of amplitude oil cylinder, for opening when amplitude oil cylinder falls after rise and closing when amplitude oil cylinder hoists.
More excellent, principal arm luffing control system also comprises main transformer width balance cock, is arranged on the oil circuit between the second actuator port of change-over valve and rodless cavity balance cock, comprises main balance cock and guide proportion reducing valve, wherein:
Two actuator ports of described main balance cock respectively with the second actuator port of change-over valve, and rodless cavity balance cock is away from the actuator port conducting of amplitude oil cylinder rodless cavity, for opening when amplitude oil cylinder falls after rise and closing when amplitude oil cylinder hoists;
The oil outlet of described guide proportion reducing valve respectively with the control port of rodless cavity balance cock and the control port conducting of main balance cock, for controlling the open and-shut mode of rodless cavity balance cock and main balance cock, and control hydraulic oil flow velocity when main balance cock is opened.
Optionally, when described change-over valve is proportional reversing valve, described principal arm luffing control system also comprises controllable capacity pump, pressure-compensated valve and shuttle valve, wherein:
Described pressure-compensated valve is arranged on the oil circuit between controllable capacity pump and the oil inlet of proportional reversing valve;
Two oil inlets of described shuttle valve respectively with the first actuator port of proportional reversing valve and the control port conducting of rodless cavity balance cock, the oil outlet of described shuttle valve and pressure-compensated valve and controllable capacity pump conducting respectively.
Optionally, when described change-over valve is switch change-over valve, described principal arm luffing control system also comprises the proportional variable pump with the oil inlet conducting of switch change-over valve.
Preferably, principal arm luffing control system also comprises the control setup be connected with shutoff valve electric signal, for controlling shutoff valve conducting receiving when principal arm power transfers instruction, and controls shutoff valve cut-off receiving when principal arm gravity transfers instruction.
More excellent, described control setup, also for when receiving principal arm and transferring instruction, controls shutoff valve first conducting in the first stroke that principal arm is transferred, then ends in the second stroke that principal arm is transferred.
When super-tonnage crane adopt gravity transfer mode transfer principal arm time, recharging oil device can continue in the rod chamber of amplitude oil cylinder, to fill into hydraulic oil to prevent from inhaling sky, and, because rod chamber balance cock is closed, hydraulic oil in the rod chamber of amplitude oil cylinder is locked, therefore, the piston rod avoiding amplitude oil cylinder is pulled out by Chao Qi mechanism.When principal arm hoist, rod chamber balance cock open time, because the rod chamber pressure of amplitude oil cylinder equals oil compensation pressure, therefore, hydraulic oil in the rod chamber of amplitude oil cylinder can not abrupt release, this considerably reduce principal arm to hoist suffered impact, thus improve smooth operation and the safety of hoisting crane.Adopt the technical scheme of the embodiment of the present invention, first can transfer mode with power and transfer principal arm fast, and then transfer mode with gravity and transfer principal arm and support to principal arm supported body; Also all can transfer mode with gravity to transfer principal arm and support to principal arm supported body.
In addition, when principal arm gravity is transferred, because the hydraulic oil filled in the rod chamber of amplitude oil cylinder is low-pressure hydraulic oil, oil pressure when pressure is transferred well below power, therefore, can greatly reduce the extruding of principal arm to supporting mechanism, reduces the distortion of supporting mechanism.
The hoisting crane that the embodiment of the present invention provides, comprises the principal arm luffing control system described in aforementioned any embodiment, and the smooth operation of this hoisting crane is better, and safety is higher, and supporting mechanism is not easily extruded distortion.
Accompanying drawing explanation
Fig. 1 a is the structural representation of super-tonnage crane;
Fig. 1 b is that hoisting crane returns the vehicle to the garage and knock off view;
Fig. 1 c adopts power to transfer the luffing control system schematic diagram that mode transfers principal arm;
Fig. 1 d adopts gravity to transfer the luffing control system schematic diagram that mode transfers principal arm;
The principal arm luffing control system schematic diagram of the hoisting crane that Fig. 2 provides for one embodiment of the invention;
The principal arm luffing control system schematic diagram of the hoisting crane that Fig. 3 provides for another embodiment of the present invention.
Reference numeral:
Detailed description of the invention
In order to improve smooth operation and the safety of hoisting crane, embodiments provide a kind of principal arm luffing control system of hoisting crane and a kind of hoisting crane.In the technical scheme of the embodiment of the present invention, principal arm luffing control system, comprise change-over valve, amplitude oil cylinder, rod chamber balance cock, shutoff valve and recharging oil device, when super-tonnage crane adopt gravity transfer mode transfer principal arm time, it is empty to prevent from inhaling that recharging oil device can continue to fill into hydraulic oil in the rod chamber of amplitude oil cylinder, and, because rod chamber balance cock is closed, hydraulic oil in the rod chamber of amplitude oil cylinder is locked, and therefore, the piston rod avoiding amplitude oil cylinder is pulled out by Chao Qi mechanism.When principal arm hoist, rod chamber balance cock open time, because the rod chamber pressure of amplitude oil cylinder equals oil compensation pressure, therefore, hydraulic oil in the rod chamber of amplitude oil cylinder can not abrupt release, this considerably reduce principal arm to hoist suffered impact, thus improve smooth operation and the safety of hoisting crane.The present invention is described with reference to the accompanying drawings below with specific embodiment.
As shown in Figure 2, the principal arm luffing control system of the hoisting crane that one embodiment of the invention provides, comprise change-over valve (this embodiment change-over valve is specially proportional reversing valve 8), amplitude oil cylinder 1,4, rod chamber balance cock 2,3, shutoff valve 14 and recharging oil device (this embodiment recharging oil device specifically comprises slippage pump 11, repairing back pressure valve 12 and repairing check valve 13), wherein:
Change-over valve, there is the first control position (when namely the electromagnet Y2 of change-over valve obtains electric) controlling amplitude oil cylinder 1,4 and fall after rise, and the second control position (when namely the electromagnet Y1 of change-over valve obtains electric) that control amplitude oil cylinder 1,4 hoists, change-over valve comprises the first actuator port B, the second actuator port A, oil inlet P and oil return inlet T; At the first control position, oil inlet P to the first working oil B mouth conducting of change-over valve, the second actuator port A of change-over valve is to oil return inlet T conducting; At the second control position, oil inlet P to the second actuator port A conducting of change-over valve, the first actuator port B of change-over valve is to oil return inlet T conducting;
Rod chamber balance cock 2,3, is arranged on the rod chamber hydraulic fluid port oil circuit of amplitude oil cylinder 1,4 respectively, for closing when amplitude oil cylinder 1,4 falls after rise and opening when amplitude oil cylinder 1,4 hoists;
Shutoff valve 14, is arranged on the oil circuit between first actuator port (i.e. B mouth) of change-over valve and rod chamber balance cock 2,3, ends for the conducting when principal arm power is transferred and when principal arm gravity is transferred;
Recharging oil device, be arranged on the oil circuit between the return opening (i.e. T mouth) of change-over valve and rod chamber balance cock 2,3, for when principal arm gravity is transferred, the rod chamber to amplitude oil cylinder 1,4 fills into hydraulic oil.
In the above-described embodiments, the particular type of hoisting crane is not limit, such as, can be medium and small tonnage hoisting crane, also can be the hoister in large tonnage with Chao Qi mechanism.In hoister in large tonnage, the quantity of amplitude oil cylinder is generally two, is symmetrically distributed in the both sides of jib.It is consistent that the hoisting of hoist falling action and the principal arm of amplitude oil cylinder transfers action.
The particular type of change-over valve is not limit, concrete adoption rate change-over valve 8 embodiment illustrated in fig. 2.In other embodiments of the invention (as shown in Figure 3), change-over valve also can adopt switch change-over valve 8 ', such as switch electromagnetic valve or pilot operated directional control valve etc.Change-over valve generally includes 4 hydraulic fluid ports, is respectively oil inlet P, oil return inlet T, the first actuator port B and the second actuator port A.
As shown in Figure 2, rod chamber balance cock 2,3 is separately positioned on the rod chamber hydraulic fluid port oil circuit of amplitude oil cylinder 1,4, in its closed condition, lockedly cannot to flow out in the rod chamber that hydraulic oil can only flow into amplitude oil cylinder 1,4 by one-way valve element; In its opening, the hydraulic oil in the rod chamber of amplitude oil cylinder 1,4 can only pass through the unidirectional outflow of damping element.The opening and closing of rod chamber balance cock 2,3 can be controlled by the pressure of the second actuator port A of change-over valve, and when amplitude oil cylinder 1,4 hoists, the second actuator port A of change-over valve flows out high pressure oil, and now rod chamber balance cock 2,3 is opened; Otherwise when amplitude oil cylinder 1,4 falls after rise, the second actuator port A of change-over valve flows into low pressure oil, and now rod chamber balance cock 2,3 is closed.
Shutoff valve can realize conducting and the cut-off of CD oil circuit, and its specific constructive form is not limit.As shown in Figure 2, in this embodiment, shutoff valve 14 comprises pressure-compensated valve element 14a, inserted valve element 14b, solenoid directional control valve element 14c and shuttle valve member 14d.When solenoid directional control valve element 14c electromagnet Y3 not electric time, the spring cavity of inserted valve element 14b and fuel tank conducting, inserted valve element 14b opens under oil pressure effect, the oil inlet C of shutoff valve 14 and oil outlet D conducting.When the electromagnet Y3 of solenoid directional control valve element 14c obtains electric, inserted valve element 14b closes, not conducting between the oil inlet C of shutoff valve 14 and oil outlet D.
The specific constructive form of recharging oil device is not limit.Shown in Fig. 2, in this embodiment, recharging oil device comprises slippage pump 11, repairing back pressure valve 12 and repairing check valve 13.Wherein: the oil inlet of slippage pump 11 and fuel tank conducting, the oil outlet of slippage pump 11 accesses the oil circuit between the oil return inlet T of change-over valve and rod chamber balance cock 2,3; The oil inlet of repairing back pressure valve 12 and fuel tank conducting, the oil circuit between the oil return inlet T of the oil outlet access change-over valve of repairing back pressure valve 12 and rod chamber balance cock 2,3; Repairing check valve 13 directly accesses in the oil circuit between the oil return inlet T of change-over valve and rod chamber balance cock 2,3, by the oil circuit one-way conduction between the oil return inlet T of change-over valve to rod chamber balance cock 2,3.
Particularly, slippage pump 11 can be gear type pump, for providing hydraulic oil to systems stay.Repairing back pressure valve 12 can limit slippage pump 11 provides pressure from hydraulic oil to system, its setup pressure value is usually lower, can ensure that the hydraulic oil that slippage pump 11 provides and system oil return are enough to enter the rod chamber of amplitude oil cylinder 1,4, prevent vacuum and be as the criterion.Repairing check valve 13 can guarantee the rod chamber of the hydraulic oil that slippage pump 11 provides and the unidirectional inflow amplitude oil cylinder 1,4 of system oil return, and there will not be counter-flow.
In embodiment illustrated in fig. 2, for the rod chamber and rodless cavity that make amplitude oil cylinder 1,4 reach equilibrium of pressure, principal arm luffing control system also comprises: rodless cavity balance cock 15,5, be arranged on the rodless cavity hydraulic fluid port oil circuit of amplitude oil cylinder 1,4 respectively, for opening when amplitude oil cylinder 1,4 falls after rise and closing when amplitude oil cylinder 1,4 hoists.The opening and closing principle of rodless cavity balance cock 5,15 and rod chamber balance cock 2,3 similar, it is no longer repeated here.
More excellent, principal arm luffing control system also comprises main transformer width balance cock 6, be arranged on the oil circuit between the second actuator port A of change-over valve and rodless cavity balance cock 15,5, comprise main balance cock 6a and guide proportion reducing valve 6b, wherein: two actuator ports of main balance cock 6a respectively with the second actuator port A of change-over valve, and rodless cavity balance cock 15,5 is away from the actuator port conducting of the rodless cavity of amplitude oil cylinder 1,4,, for opening when amplitude oil cylinder 1,4 falls after rise and closing when amplitude oil cylinder 1,4 hoists; The oil outlet of guide proportion reducing valve 6b respectively with the control port of rodless cavity balance cock 15,5 and the control port conducting of main balance cock 6a, for controlling the open and-shut mode of rodless cavity balance cock 15,5 and main balance cock 6a, and control hydraulic oil flow velocity when main balance cock 6a opens.
The structure of main balance cock 6a and rod chamber balance cock 2,3 and rodless cavity balance cock 15,5 similar, but its damping element is mutative damp element.Main transformer width balance cock 6 can when amplitude oil cylinder 1,4 falls after rise, the rate of outflow of hydraulic oil in the rodless cavity of control amplitude oil cylinder 1,4.The fall velocity of amplitude oil cylinder 1,4 is by the size of current Linear Control of electromagnet Y4 passing into guide proportion reducing valve 6b.When the electric current passing into electromagnet Y4 is larger, the oil pressure that guide proportion reducing valve 6b exports the control port of main balance cock 6a to is also larger, and now, the opening of the mutative damp element of main balance cock 6a is also comparatively large, and the fall velocity of amplitude oil cylinder 1,4 is larger; Otherwise when the electric current passing into electromagnet Y4 is less, the oil pressure that guide proportion reducing valve 6b exports the control port of main balance cock 6a to is also smaller, now, the opening of the mutative damp element of main balance cock 6a is also less, and the fall velocity of amplitude oil cylinder 1,4 is less.
As shown in Figure 2, when change-over valve is proportional reversing valve 8, principal arm luffing control system also comprises controllable capacity pump 10, pressure-compensated valve 9 and shuttle valve 7, wherein: on the oil circuit between the oil inlet P that pressure-compensated valve 9 is arranged at controllable capacity pump 10 and proportional reversing valve 8; Two oil inlets of shuttle valve 7 respectively with the first actuator port B of proportional reversing valve and the control port conducting of rod chamber balance cock 2,3, the oil outlet of shuttle valve 7 and pressure-compensated valve 9 and controllable capacity pump 10 conducting respectively.
Controllable capacity pump 10 provides required hydraulic fluid flow rate for hydraulic efficiency pressure system, and it has pressure adjusting function, can according to the pressure of system condition demand regulation.Pressure-compensated valve 9 can make delivery rate and its spool aperture proportional of proportional reversing valve 8.The pressure of two actuator ports A, B of shuttle valve 7 comparative example change-over valve 8 compares, and pressure is comparatively fed back to pressure-compensated valve 9 and controllable capacity pump 10 in Gao mono-tunnel, regulates accordingly according to feedback pressure to make pressure-compensated valve 9 and controllable capacity pump 10.
As shown in Figure 3, in an alternate embodiment of the present invention where, when change-over valve is switch change-over valve 8 ', principal arm luffing control system also comprises the proportional variable pump 10 ' with the oil inlet P conducting of switch change-over valve 8 '.The delivery rate of proportional variable pump 10 ' is directly proportional to the control electric current of its electromagnet Y5, adopts this structure, and pressure-compensated valve and shuttle valve can correspondingly be cancelled.
When super-tonnage crane adopt gravity transfer mode transfer principal arm time, recharging oil device can continue in the rod chamber of amplitude oil cylinder 1,4, to fill into hydraulic oil to prevent from inhaling sky, and, because rod chamber balance cock 2,3 is closed, hydraulic oil in the rod chamber of amplitude oil cylinder 1,4 is locked, therefore, the piston rod avoiding amplitude oil cylinder 1,4 is pulled out by Chao Qi mechanism.When principal arm hoist, rod chamber balance cock 2,3 open time, because the rod chamber pressure of amplitude oil cylinder 1,4 equals oil compensation pressure, therefore, hydraulic oil in the rod chamber of amplitude oil cylinder 1,4 can not abrupt release, this considerably reduce principal arm to hoist suffered impact, thus improve smooth operation and the safety of hoisting crane.Adopt the technical scheme of the embodiment of the present invention, first can transfer mode with power and transfer principal arm, and then transfer mode with gravity and transfer principal arm and support to principal arm supported body; Also all can transfer mode with gravity to transfer principal arm and support to principal arm supported body.
In addition, when principal arm gravity is transferred, the hydraulic oil filled in rod chamber due to amplitude oil cylinder 1,4 is low-pressure hydraulic oil, oil pressure when pressure is transferred well below power, therefore, adopt gravity to transfer mode and transfer principal arm, the extruding of principal arm to supporting mechanism can be greatly reduced, reduce the distortion of supporting mechanism.
In a preferred embodiment of the invention, principal arm luffing control system also comprises the control setup (not shown in Fig. 2 and Fig. 3 embodiment) be connected with shutoff valve 14 electric signal, for controlling shutoff valve 14 conducting receiving when principal arm power transfers instruction, and control shutoff valve 14 when principal arm gravity transfers instruction and end receiving.Understandable, control setup can also be connected with the electric signal such as change-over valve, guide proportion reducing valve, controls, improve accuracy and the convenience of operation with a series of electricity operations realizing hoisting crane.
In a more excellent embodiment of the present invention, control setup, also for when receiving principal arm and transferring instruction, controls shutoff valve 14 first conducting in the first stroke that principal arm is transferred, then ends in the second stroke that principal arm is transferred.In the first stroke that principal arm is transferred, shutoff valve 14 conducting, principal arm can be transferred mode by power and be transferred fast, reposefully, and the controllability of lowering velocity is better; In the second stroke that principal arm is transferred, shutoff valve 14 ends, and principal arm is transferred mode by gravity and transferred, and greatly reduces the extruding of principal arm to supporting mechanism, thus decreases the distortion of supporting mechanism.When principal arm hoists again, the hydraulic oil in the rod chamber of amplitude oil cylinder can not abrupt release, and therefore, principal arm can comparatively hoist by pulsation-free, and smooth operation and the safety of hoisting crane are higher.
Below for embodiment illustrated in fig. 2, describe the working process of principal arm luffing control system in detail:
In the first stroke that principal arm is transferred, adopt power to transfer mode and transfer principal arm, the electromagnet Y4 of the electromagnet Y2 of proportional reversing valve 8 and the guide proportion reducing valve 6b of main transformer width balance cock 6 obtains electric, the oil inlet P of proportional reversing valve 8 and the first actuator port B conducting.Because of the electromagnet Y3 dead electricity of shutoff valve 14, therefore oil circuit C-D conducting, hydraulic oil enters the rod chamber of amplitude oil cylinder 1,4 through oil circuit B-F, the pilot pressure that electromagnet Y4 controls simultaneously promotes rodless cavity balance cock 15,5, and main transformer width balance cock 6 the spool of main balance cock 6a open, principal arm realizes power and transfers action.In said process, electromagnet Y2 and electromagnet Y4 synchronous proportional increase or synchronous proportional reduces, and principal arm lowering velocity is also relevant to this ratio.The outlet of repairing check valve 13 and oil circuit BF conducting, because oil circuit BF is high-pressure oil passage, therefore repairing check valve 13 exports and is shut, oil circuit W-E not conducting.
In the second stroke that principal arm is transferred, adopt gravity to transfer mode and transfer principal arm, the electromagnet Y4 of the electromagnet Y2 of proportional reversing valve 8, the guide proportion reducing valve 6b of main transformer width balance cock 6, and the electromagnet Y3 of shutoff valve 14 obtains electric, the oil inlet P of proportional reversing valve 8 and the first actuator port B conducting.Because the electromagnet Y3 of shutoff valve 14 obtains electric, therefore oil circuit C-D ends.The pilot pressure that electromagnet Y4 controls promotes rodless cavity balance cock 15,5 simultaneously, and the main balance cock 6a of main transformer width balance cock 6 opens, and principal arm realizes transferring under Gravitative Loads power.The piston rod of amplitude oil cylinder 1,4 moves downward, the hydraulic oil in rodless cavity respectively through rodless cavity balance cock 15,5, the main balance cock 6a of main transformer width balance cock 6, and the second actuator port A of proportional reversing valve 8, arrive oil circuit T-V after oil return inlet T.In above process, the rod chamber of amplitude oil cylinder 1,4 has is inhaled empty trend, but the system oil return of slippage pump 11 and arrival oil circuit T-V can under the effect of repairing back pressure valve 12, continue to oil circuit E-F repairing through repairing check valve 13, repairing source enters the rod chamber of amplitude oil cylinder 1,4 respectively after rod chamber balance cock 2,3, thus prevents the rod chamber of amplitude oil cylinder 1,4 to be inhaled sky.In said process, the control signal of electromagnet Y4 is ratio control signal, thus the ratio that can realize the main balance cock 6a of main transformer width balance cock 6 is opened, and realizes the control to principal arm lowering velocity.In principal arm conducts oneself with dignity the process transferred, the hydraulic oil that the rod chamber due to amplitude oil cylinder 1,4 enters is low pressure repairing source, system pressure when pressure is transferred well below principal arm power, and therefore, the squeese pressure that vehicle frame of being rivals in a contest under principal arm gravity produces is less.In like manner, carry out principal arm hoist action time, when rod chamber balance cock 2,3 is opened, pressure due to the rod chamber of amplitude oil cylinder 1,4 originally just equals the benefit oil supply pressure of system, therefore, rod chamber can not pressure release suddenly, this considerably reduces the vibration of principal arm when luffing hoists.In said process, regardless of the fall velocity of amplitude oil cylinder 1,4, piston area due to rodless cavity is greater than the piston area of rod chamber, flow needed for the reality that when therefore principal arm is at the uniform velocity transferred, the system oil return of oil circuit T-V is greater than the rod chamber filling into amplitude oil cylinder 1,4 always.Due to the effect of repairing back pressure valve 12, the system oil return of oil circuit T-V can overcome the rod chamber of the resistance arrival amplitude oil cylinder 1,4 of pipeline and rod chamber balance cock 2,3 under setting pressure, therefore, in the at the uniform velocity decentralization process of principal arm, repairing source is sufficient all the time.Slippage pump 11 can ensure extra sufficient oil sources the moment, when principal arm luffing is not operating also can to the rod chamber of amplitude oil cylinder 1,4 produce one initiatively repairing flow (when system reality not demand time, can release from repairing back pressure valve 12), thus the problem of the instantaneous oil suction deficiency of rod chamber of amplitude oil cylinder 1,4 when solving instantaneous starting and when acceleration is transferred, ensure that the rod chamber of amplitude oil cylinder 1,4 there will not be emptying phenomenon in principal arm decentralization process.
The embodiment of the present invention additionally provides a kind of hoisting crane, comprises the principal arm luffing control system of aforementioned any embodiment, and the smooth operation of this hoisting crane is better, and safety is higher, and supporting mechanism is not easily extruded distortion.
Obviously, those skilled in the art can carry out various change and modification to the present invention and not depart from the spirit and scope of the present invention.Like this, if these amendments of the present invention and modification belong within the scope of the claims in the present invention and equivalent technologies thereof, then the present invention is also intended to comprise these change and modification.
Claims (10)
1. a principal arm luffing control system for hoisting crane, is characterized in that, comprises change-over valve, amplitude oil cylinder, rod chamber balance cock, shutoff valve and recharging oil device, wherein:
Described change-over valve, has the first control position controlling amplitude oil cylinder and fall after rise, and the second control position that control amplitude oil cylinder hoists, and described change-over valve comprises the first actuator port, the second actuator port, oil inlet and return opening; At described first control position, oil inlet to the first actuator port conducting of change-over valve, the second actuator port of change-over valve is to return opening conducting; At described second control position, oil inlet to the second actuator port conducting of change-over valve, the first actuator port of change-over valve is to return opening conducting;
Described rod chamber balance cock, is arranged on the rod chamber hydraulic fluid port oil circuit of amplitude oil cylinder, for closing when amplitude oil cylinder falls after rise and opening when amplitude oil cylinder hoists;
Described shutoff valve, is arranged on the oil circuit between the first actuator port of change-over valve and rod chamber balance cock, ends for the conducting when principal arm power is transferred and when principal arm gravity is transferred;
Described recharging oil device, is arranged on the oil circuit between the return opening of change-over valve and rod chamber balance cock, and for when principal arm gravity is transferred, the rod chamber to amplitude oil cylinder fills into hydraulic oil.
2. the system as claimed in claim 1, is characterized in that, described recharging oil device comprises slippage pump and repairing back pressure valve, wherein:
The oil inlet of described slippage pump and fuel tank conducting, the oil circuit between the return opening of the oil outlet access change-over valve of described slippage pump and rod chamber balance cock;
The oil inlet of described repairing back pressure valve and fuel tank conducting, the oil circuit between the return opening of the oil outlet access change-over valve of described repairing back pressure valve and rod chamber balance cock.
3. the system as claimed in claim 1, is characterized in that, the repairing check valve of the oil circuit one-way conduction between described recharging oil device also comprises the return opening of change-over valve to rod chamber balance cock.
4. the system as claimed in claim 1, is characterized in that, also comprises:
Rodless cavity balance cock, is arranged on the rodless cavity hydraulic fluid port oil circuit of amplitude oil cylinder, for opening when amplitude oil cylinder falls after rise and closing when amplitude oil cylinder hoists.
5. system as claimed in claim 4, is characterized in that, also comprise:
Main transformer width balance cock, is arranged on the oil circuit between the second actuator port of change-over valve and rodless cavity balance cock, comprises main balance cock and guide proportion reducing valve, wherein:
Two actuator ports of described main balance cock respectively with the second actuator port of change-over valve, and rodless cavity balance cock is away from the actuator port conducting of amplitude oil cylinder rodless cavity, for opening when amplitude oil cylinder falls after rise and closing when amplitude oil cylinder hoists;
The oil outlet of described guide proportion reducing valve respectively with the control port of rodless cavity balance cock and the control port conducting of main balance cock, for controlling the open and-shut mode of rodless cavity balance cock and main balance cock, and control hydraulic oil flow velocity when main balance cock is opened.
6. the system as claimed in claim 1, is characterized in that, when described change-over valve is proportional reversing valve, described principal arm luffing control system also comprises controllable capacity pump, pressure-compensated valve and shuttle valve, wherein:
Described pressure-compensated valve is arranged on the oil circuit between controllable capacity pump and the oil inlet of proportional reversing valve;
Two oil inlets of described shuttle valve respectively with the first actuator port of proportional reversing valve and the control port conducting of rodless cavity balance cock, the oil outlet of described shuttle valve and pressure-compensated valve and controllable capacity pump conducting respectively.
7. the system as claimed in claim 1, is characterized in that, when described change-over valve is switch change-over valve, described principal arm luffing control system also comprises the proportional variable pump with the oil inlet conducting of switch change-over valve.
8. the system as described in any one of claim 1 ~ 7, is characterized in that, also comprises:
The control setup be connected with shutoff valve electric signal, for controlling shutoff valve conducting receiving when principal arm power transfers instruction, and controls shutoff valve cut-off receiving when principal arm gravity transfers instruction.
9. system as claimed in claim 8, is characterized in that, described control setup, also for when receiving principal arm and transferring instruction, controls shutoff valve first conducting in the first stroke that principal arm is transferred, then ends in the second stroke that principal arm is transferred.
10. a hoisting crane, is characterized in that, comprises the principal arm luffing control system as described in any one of claim 1 ~ 9.
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| CN201410756088.XA CN104477798B (en) | 2014-12-10 | 2014-12-10 | Main arm variable amplitude control system of crane and crane |
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| CN105366569A (en) * | 2015-11-19 | 2016-03-02 | 湖北海洋工程装备研究院有限公司 | A-shaped frame amplitude varying mechanism and control system thereof |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09273503A (en) * | 1996-04-02 | 1997-10-21 | Kayaba Ind Co Ltd | Fluid pressure control device |
| JP2000230505A (en) * | 1999-02-15 | 2000-08-22 | Yutani Heavy Ind Ltd | Hydraulic tuning circuit for construction machine |
| CN2748677Y (en) * | 2003-12-30 | 2005-12-28 | 贺勍 | Balance valve |
| CN102502433A (en) * | 2011-10-08 | 2012-06-20 | 武汉船用机械有限责任公司 | Variable amplitude hydraulic system of dual-oil-cylinder variable amplitude crane |
| CN202322125U (en) * | 2011-10-21 | 2012-07-11 | 四川宏华石油设备有限公司 | Hydraulic control system with adjustable amplitude for articulated lifting device |
| CN102887447A (en) * | 2012-10-17 | 2013-01-23 | 中联重科股份有限公司 | Hydraulic control loop of variable amplitude hydraulic cylinder, crane and variable amplitude control method |
-
2014
- 2014-12-10 CN CN201410756088.XA patent/CN104477798B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH09273503A (en) * | 1996-04-02 | 1997-10-21 | Kayaba Ind Co Ltd | Fluid pressure control device |
| JP2000230505A (en) * | 1999-02-15 | 2000-08-22 | Yutani Heavy Ind Ltd | Hydraulic tuning circuit for construction machine |
| CN2748677Y (en) * | 2003-12-30 | 2005-12-28 | 贺勍 | Balance valve |
| CN102502433A (en) * | 2011-10-08 | 2012-06-20 | 武汉船用机械有限责任公司 | Variable amplitude hydraulic system of dual-oil-cylinder variable amplitude crane |
| CN202322125U (en) * | 2011-10-21 | 2012-07-11 | 四川宏华石油设备有限公司 | Hydraulic control system with adjustable amplitude for articulated lifting device |
| CN102887447A (en) * | 2012-10-17 | 2013-01-23 | 中联重科股份有限公司 | Hydraulic control loop of variable amplitude hydraulic cylinder, crane and variable amplitude control method |
Cited By (29)
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| CN105366569A (en) * | 2015-11-19 | 2016-03-02 | 湖北海洋工程装备研究院有限公司 | A-shaped frame amplitude varying mechanism and control system thereof |
| CN106813536A (en) * | 2015-11-27 | 2017-06-09 | 贵州航天天马机电科技有限公司 | A kind of double oil cylinder heavy loads deflecting of carrier rocket plays perpendicular hydraulic control system |
| CN105605001A (en) * | 2016-03-17 | 2016-05-25 | 上海振华重工(集团)股份有限公司 | Hydraulic safety valve set for closed winch |
| CN106672870A (en) * | 2016-12-22 | 2017-05-17 | 徐州海伦哲专用车辆股份有限公司 | Insulated folding arm high-altitude operation car with amplitude limiting control valve and amplitude limiting method |
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| CN106698199A (en) * | 2017-01-23 | 2017-05-24 | 武汉船用机械有限责任公司 | Double-derricking cylinder hydraulic control system |
| CN106698199B (en) * | 2017-01-23 | 2018-08-07 | 武汉船用机械有限责任公司 | A kind of double amplitude oil cylinder hydraulic control systems |
| CN108278229A (en) * | 2018-03-19 | 2018-07-13 | 湖南星邦重工有限公司 | A kind of crank arm type high-altitude operation vehicle connector leveling hydraulic system |
| CN108278229B (en) * | 2018-03-19 | 2024-03-26 | 湖南星邦智能装备股份有限公司 | Crank arm type high-altitude operation vehicle connector leveling hydraulic system |
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| CN112343881B (en) * | 2020-11-13 | 2022-09-23 | 中船华南船舶机械有限公司 | Balanced pressure self preservation protects hydraulic system |
| CN112343881A (en) * | 2020-11-13 | 2021-02-09 | 中船华南船舶机械有限公司 | Balanced pressure self preservation protects hydraulic system |
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| CN112814961B (en) * | 2021-01-15 | 2023-05-30 | 三一汽车制造有限公司 | Boom hydraulic system of working vehicle, control method and working vehicle |
| CN113232719A (en) * | 2021-06-24 | 2021-08-10 | 上海三一重机股份有限公司 | Steering system and loader |
| CN113700687A (en) * | 2021-08-06 | 2021-11-26 | 中际联合（北京）科技股份有限公司 | Hydraulic amplitude changing system of crane and offshore crane |
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