CN104477798B - 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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- CN104477798B CN104477798B CN201410756088.XA CN201410756088A CN104477798B CN 104477798 B CN104477798 B CN 104477798B CN 201410756088 A CN201410756088 A CN 201410756088A CN 104477798 B CN104477798 B CN 104477798B
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- 239000003921 oil Substances 0.000 claims abstract description 225
- 239000010720 hydraulic oil Substances 0.000 claims abstract description 34
- 230000005484 gravity Effects 0.000 claims abstract description 30
- 239000012530 fluid Substances 0.000 claims description 9
- 239000002828 fuel tank Substances 0.000 claims description 9
- 238000005303 weighing Methods 0.000 claims 1
- 230000001502 supplementing effect Effects 0.000 abstract 3
- 230000007246 mechanism Effects 0.000 description 18
- 238000000034 method Methods 0.000 description 7
- 230000008569 process Effects 0.000 description 7
- 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
- 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
- 230000007423 decrease Effects 0.000 description 1
- 230000005611 electricity Effects 0.000 description 1
- 230000006872 improvement 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 the principal arm luffing control system of a kind of crane and a kind of crane.
Background technology
As shown in Figure 1a, the structure of existing super-tonnage crane generally includes: swing arm 100, hoisting rope 110, setting-up steel wire rope 120, principal arm 130 and amplitude oil cylinder 140, and wherein, one end of principal arm 130 is hinged with vehicle frame 150, and the other end is hinged with swing arm 100；Amplitude oil cylinder 140 is used for driving the luffing of principal arm 130 to hoist and luffing is transferred；Hoisting rope 110 is set around on the arm head pulley of swing arm 100, is used for the weight that hoists；Setting-up steel wire rope 120 hangs force-bearing situation and the balance quality of principal arm 130 when carrying operation for improvement.As shown in Figure 1 b, returning 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 the most dynamic transferring and is transferred two ways with gravity.
As illustrated in figure 1 c, use power to transfer mode to transfer the luffing control system of principal arm and specifically include that amplitude oil cylinder 140, rodless cavity balanced valve 202, guide proportion air relief valve 203, rod chamber balanced valve 204 and reversal valve 205.When power transfers principal arm, rod chamber balanced valve 204 cuts out, the high-pressure oil passage of hydraulic system turns on the rod chamber of amplitude oil cylinder 140, the piston rod of amplitude oil cylinder 140 is compressed rodless cavity by the action of gravity of principal arm and the pressure effect of hydraulic oil, making amplitude oil cylinder 140 fall after rise to pack up, principal arm is transferred to supporting mechanism.But, when the principal arm that again hoists, unlatching rod chamber balanced valve 204, the rod chamber of amplitude oil cylinder 140 can be by rod chamber balanced valve 204 and reversal valve 205 and fuel tank transient switching, the rod chamber moment pressure release of amplitude oil cylinder 140 can produce bigger impact to hydraulic system, thus cause principal arm to rebound, badly influence stationarity and the safety of lifting operation.If additionally, principal arm has transferred to horizontal level, and operator stop power lowering operation the most in time, the supporting mechanism of vehicle frame is likely to by principal arm crimp.
As shown in Figure 1 d, the luffing control system using mode of transferring of conducting oneself with dignity to transfer principal arm specifically includes that amplitude oil cylinder 140, rodless cavity balanced valve 202, guide proportion air relief valve 203 and reversal valve 205.When gravity transfers principal arm, the rod chamber of amplitude oil cylinder 140 turns on fuel tank, and the piston rod of amplitude oil cylinder 140 is not by the pressure effect of hydraulic oil, and principal arm is transferred under gravity to supporting mechanism, and amplitude oil cylinder 140 falls after rise and packs up simultaneously.For super-tonnage crane, setting-up mechanism can apply one to principal arm makes it to the active force of layback, transfers mode according to deadweight and transfers principal arm, and the piston rod of amplitude oil cylinder 140 is probably pulled out suddenly cylinder body, thus causes the most serious security incident.
Therefore, how to improve stationarity and the safety of crane hanging component operation, be technical problem the most urgently to be resolved hurrily.
Summary of the invention
Embodiments provide the principal arm luffing control system of a kind of crane and a kind of crane, to improve smooth operation and the safety of crane.
The principal arm luffing control system of the crane that the embodiment of the present invention is provided, including reversal valve, amplitude oil cylinder, rod chamber balanced valve, stop valve and recharging oil device, wherein:
Described reversal valve, has and controls the first operating position that amplitude oil cylinder falls after rise, and control the second operating position that amplitude oil cylinder hoists, and described reversal valve includes the first actuator port, the second actuator port, oil-in and oil return opening；In described first operating position, the oil-in of reversal valve turns on to the first actuator port, and the second actuator port of reversal valve to oil return opening turns on；In described second operating position, the oil-in of reversal valve turns on to the second actuator port, and the first actuator port of reversal valve to oil return opening turns on；
Described rod chamber balanced valve, 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 stop valve, is arranged on the oil circuit between the first actuator port of reversal valve and rod chamber balanced valve, for the conducting when principal arm power is transferred and ends when principal arm gravity is transferred；
Described recharging oil device, is arranged on the oil circuit between the oil return opening of reversal valve and rod chamber balanced valve, for when principal arm gravity is transferred, fills into hydraulic oil to the rod chamber of amplitude oil cylinder.
Preferably, described recharging oil device includes slippage pump and repairing counterbalance valve, wherein:
The oil-in of described slippage pump turns on fuel tank, and the oil-out of described slippage pump accesses the oil circuit between oil return opening and the rod chamber balanced valve of reversal valve；
The oil-in of described repairing counterbalance valve turns on fuel tank, and the oil-out of described repairing counterbalance valve accesses the oil circuit between oil return opening and the rod chamber balanced valve of reversal valve.
More excellent, described recharging oil device also include the oil return opening of reversal valve to rod chamber balanced valve between the repairing check valve of oil circuit one-way conduction.
Preferably, principal arm luffing control system also includes: rodless cavity balanced valve, 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 includes main transformer width balanced valve, is arranged on the oil circuit between the second actuator port of reversal valve and rodless cavity balanced valve, including main balanced valve and guide proportion air relief valve, wherein:
Two actuator ports of described main balanced valve respectively with the second actuator port of reversal valve, and rodless cavity balanced valve turns on, for opening when amplitude oil cylinder falls and the cut out when amplitude oil cylinder hoists away from the actuator port of amplitude oil cylinder rodless cavity；
The oil-out of described guide proportion air relief valve turns on the control port of the control port of rodless cavity balanced valve and main balanced valve respectively, for controlling rodless cavity balanced valve and the open and-shut mode of main balanced valve, and controls hydraulic oil flow velocity when main balanced valve is opened.
Optionally, when described reversal valve is proportional reversing valve, described principal arm luffing control system also includes variable pump, pressure-compensated valve and shuttle valve, wherein:
Described pressure-compensated valve is arranged on the oil circuit between variable pump and the oil-in of proportional reversing valve；
Two oil-ins of described shuttle valve turn on the first actuator port of proportional reversing valve and the control port of rod chamber balanced valve respectively, and the oil-out of described shuttle valve is respectively turned on pressure-compensated valve and variable pump.
Optionally, when described reversal valve is for switch reversal valve, described principal arm luffing control system also includes the proportional variable pump of the oil-in conducting with switch reversal valve.
Preferably, principal arm luffing control system also includes the control device being connected with the stop valve signal of telecommunication, for receive when principal arm power transfers instruction control stop valve conducting, and control stop valve conducting when principal arm gravity transfers instruction receiving, and control stop valve cut-off when principal arm gravity transfers instruction receiving.
More excellent, described control device, it is additionally operable to when receiving principal arm and transferring instruction, controls stop valve and first turn in the first stroke that principal arm is transferred, then end in the second stroke that principal arm is transferred.
When super-tonnage crane use gravity transfer mode transfer principal arm time, recharging oil device can continue to fill into hydraulic oil in the rod chamber of amplitude oil cylinder to prevent from being emptied, and, owing to rod chamber balanced valve cuts out, hydraulic oil in the rod chamber of amplitude oil cylinder is locked, therefore, it is to avoid the piston rod of amplitude oil cylinder is pulled out by setting-up mechanism.When principal arm hoist, rod chamber balanced valve open time, owing to the rod chamber pressure of amplitude oil cylinder is equal to oil compensation pressure, therefore, hydraulic oil in the rod chamber of amplitude oil cylinder will not abrupt release, this considerably reduce principal arm to hoist suffered impact, thus improve smooth operation and the safety of crane.Use the technical scheme of the embodiment of the present invention, first can transfer mode with power and quickly transfer principal arm, transfer mode with gravity the most again and transfer principal arm to the support of principal arm supported body；Also all can transfer mode with gravity and transfer principal arm to the support of principal arm supported body.
Additionally, when principal arm gravity is transferred, the hydraulic oil owing to filling in the rod chamber of amplitude oil cylinder is low-pressure hydraulic oil, pressure well below power transfer time oil pressure, therefore, it can the extruding greatly reducing principal arm to supporting mechanism, reduce the deformation of supporting mechanism.
The crane that the embodiment of the present invention is provided, including the principal arm luffing control system described in aforementioned any embodiment, the smooth operation of this crane is preferable, and safety is higher, and supporting mechanism is difficult to be deformed.
Accompanying drawing explanation
Fig. 1 a is the structural representation of super-tonnage crane；
Fig. 1 b is that crane returns the vehicle to the garage and knock off view；
Fig. 1 c is to use power to transfer mode to transfer the luffing control system schematic diagram of principal arm；
Fig. 1 d is to use gravity to transfer mode to transfer the luffing control system schematic diagram of principal arm；
The principal arm luffing control system schematic diagram of the crane that Fig. 2 provides for one embodiment of the invention；
The principal arm luffing control system schematic diagram of the crane that Fig. 3 provides for another embodiment of the present invention.
Reference:
Prior art reference:
100-swing arm；110-hoisting rope；120-setting-up steel wire rope；130-principal arm；140-amplitude oil cylinder；
150-vehicle frame；160-supporting mechanism；202-rodless cavity balanced valve；203-guide proportion air relief valve；
204-rod chamber balanced valve；205-reversal valve.
Embodiment of the present invention reference:
1,4-amplitude oil cylinder；2,3-rod chamber balanced valve；5,15-rodless cavity balanced valve；
6-main transformer width balanced valve；The main balanced valve of 6a-；6b-guide proportion air relief valve；7-shuttle valve；
8-proportional reversing valve；8 '-switch reversal valve；9-pressure-compensated valve；10-variable pump；
10 '-proportional variable pump；11-slippage pump；12-repairing counterbalance valve；13-repairing check valve；
14-stop valve；14a-pressure-compensated valve element；14b-inserted valve element；14c-solenoid directional control valve element；
14d-shuttle valve member.
Detailed description of the invention
In order to improve smooth operation and the safety of crane, embodiments provide the principal arm luffing control system of a kind of crane and a kind of crane.In the technical scheme of the embodiment of the present invention, principal arm luffing control system, including reversal valve, amplitude oil cylinder, rod chamber balanced valve, stop valve and recharging oil device, when super-tonnage crane use gravity transfer mode transfer principal arm time, recharging oil device can continue to fill into hydraulic oil in the rod chamber of amplitude oil cylinder to prevent from being emptied, and, owing to rod chamber balanced valve cuts out, hydraulic oil in the rod chamber of amplitude oil cylinder is locked, therefore, it is to avoid the piston rod of amplitude oil cylinder is pulled out by setting-up mechanism.When principal arm hoist, rod chamber balanced valve open time, owing to the rod chamber pressure of amplitude oil cylinder is equal to oil compensation pressure, therefore, hydraulic oil in the rod chamber of amplitude oil cylinder will not abrupt release, this considerably reduce principal arm to hoist suffered impact, thus improve smooth operation and the safety of crane.Below with specific embodiment and be described with reference to the accompanying drawings the present invention.
As shown in Figure 2, the principal arm luffing control system of the crane that one embodiment of the invention provides, including reversal valve (this embodiment reversal valve is specially proportional reversing valve 8), amplitude oil cylinder 1,4, rod chamber balanced valve 2,3, stop valve 14 and recharging oil device (this embodiment recharging oil device specifically includes slippage pump 11, repairing counterbalance valve 12 and repairing check valve 13), wherein:
Reversal valve, have and control the first operating position (when i.e. the electric magnet Y2 of reversal valve obtains electric) that amplitude oil cylinder 1,4 falls after rise, and controlling the second operating position (when i.e. the electric magnet Y1 of reversal valve obtains electric) that amplitude oil cylinder 1,4 hoists, reversal valve includes the first actuator port B, the second actuator port A, oil inlet P and oil return inlet T；In the first operating position, the oil inlet P of reversal valve turns on to the first working oil B mouth, and the second actuator port A of reversal valve to oil return inlet T turns on；In the second operating position, the oil inlet P of reversal valve turns on to the second actuator port A, and the first actuator port B of reversal valve to oil return inlet T turns on；
Rod chamber balanced valve 2,3, is respectively arranged on the rod chamber hydraulic fluid port oil circuit of amplitude oil cylinder 1,4, for closing when amplitude oil cylinder 1,4 falls after rise and opening when amplitude oil cylinder 1,4 hoists；
Stop valve 14, is arranged on the oil circuit between the first actuator port (i.e. B mouth) and the rod chamber balanced valve 2,3 of reversal valve, for the conducting when principal arm power is transferred and ends when principal arm gravity is transferred；
Recharging oil device, is arranged on the oil circuit between oil return opening (i.e. T mouth) and the rod chamber balanced valve 2,3 of reversal valve, and 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 crane does not limits, such as, can be medium and small tonnage crane, it is also possible to for the hoister in large tonnage with setting-up mechanism.In hoister in large tonnage, the quantity of amplitude oil cylinder is usually 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 reversal valve does not limits, embodiment illustrated in fig. 2 concrete adoption rate reversal valve 8.In other embodiments of the invention (as shown in Figure 3), reversal valve can also use switch reversal valve 8 ', such as switch electromagnetic valve or pilot operated directional control valve etc..Reversal valve generally includes 4 hydraulic fluid ports, respectively oil inlet P, oil return inlet T, the first actuator port B and the second actuator port A.
As in figure 2 it is shown, rod chamber balanced valve 2,3 is separately positioned on the rod chamber hydraulic fluid port oil circuit of amplitude oil cylinder 1,4, in its closed mode, in hydraulic oil can only flow into the rod chamber of amplitude oil cylinder 1,4 by one-way valve element and locked cannot flow out；Hydraulic oil in its opening, 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 balanced valve 2,3 can be controlled by the pressure of the second actuator port A of reversal valve, and when amplitude oil cylinder 1,4 hoists, the second actuator port A of reversal valve flows out hydraulic oil, and now rod chamber balanced valve 2,3 is opened；Otherwise, when amplitude oil cylinder 1,4 falls after rise, the second actuator port A of reversal valve flows into low pressure oil, and now rod chamber balanced valve 2,3 cuts out.
Stop valve can realize conducting and the cut-off of CD oil circuit, and its specific constructive form does not limits.As in figure 2 it is shown, in this embodiment, stop valve 14 includes 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 electric magnet Y3 not electric time, the spring cavity of inserted valve element 14b and fuel tank turn on, and inserted valve element 14b opens under oil pressure effect, and the oil-in C and oil-out D of stop valve 14 turns on.When the electric magnet Y3 of solenoid directional control valve element 14c obtains electric, inserted valve element 14b closes, and is not turned between the oil-in C and oil-out D of stop valve 14.
The specific constructive form of recharging oil device does not limits.Continuing referring to shown in Fig. 2, in this embodiment, recharging oil device includes slippage pump 11, repairing counterbalance valve 12 and repairing check valve 13.Wherein: the oil-in of slippage pump 11 turns on fuel tank, the oil-out of slippage pump 11 accesses the oil circuit between oil return inlet T and the rod chamber balanced valve 2,3 of reversal valve；The oil-in of repairing counterbalance valve 12 turns on fuel tank, and the oil-out of repairing counterbalance valve 12 accesses the oil circuit between oil return inlet T and the rod chamber balanced valve 2,3 of reversal valve；Repairing check valve 13 is directly accessed in the oil circuit between the oil return inlet T of reversal valve and rod chamber balanced valve 2,3, by the oil circuit one-way conduction between the oil return inlet T of reversal valve to rod chamber balanced valve 2,3.
Specifically, slippage pump 11 can be gear pump, for providing hydraulic oil to systems stay.Repairing counterbalance valve 12 can limit slippage pump 11 and provide the pressure of hydraulic oil to system, and its setup pressure value generally ratio is relatively low, ensure that hydraulic oil that slippage pump 11 provides and system oil return be enough to enter the rod chamber of amplitude oil cylinder 1,4, prevents vacuum and is as the criterion.Repairing check valve 13 may insure that the hydraulic oil and the rod chamber of system oil return unidirectional inflow amplitude oil cylinder 1,4 that slippage pump 11 provides, without there is reverse flow.
In embodiment illustrated in fig. 2, rod chamber and rodless cavity for making amplitude oil cylinder 1,4 reach pressure balance, principal arm luffing control system also includes: rodless cavity balanced valve 15,5, it is respectively arranged on the rodless cavity hydraulic fluid port oil circuit 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 opening and closing principle of rodless cavity balanced valve 5,15 is similar with rod chamber balanced valve 2,3, is not repeated herein and repeats.
More excellent, principal arm luffing control system also includes main transformer width balanced valve 6, it is arranged on the oil circuit between the second actuator port A of reversal valve and rodless cavity balanced valve 15,5, including main balanced valve 6a and guide proportion air relief valve 6b, wherein: two actuator ports of main balanced valve 6a respectively with the second actuator port A of reversal valve, and rodless cavity balanced valve 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-out of guide proportion air relief valve 6b turns on the control port of the control port of rodless cavity balanced valve 15,5 and main balanced valve 6a respectively, for controlling rodless cavity balanced valve 15,5 and the open and-shut mode of main balanced valve 6a, and control hydraulic oil flow velocity when main balanced valve 6a opens.
The structure of main balanced valve 6a is similar with rod chamber balanced valve 2,3 and rodless cavity balanced valve 15,5, but its damping element is mutative damp element.Main transformer width balanced valve 6 can be 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 the electric magnet Y4 being passed through guide proportion air relief valve 6b.When the electric current being passed through electric magnet Y4 is bigger, guide proportion air relief valve 6b output is the biggest to the oil pressure of the control port of main balanced valve 6a, and now, the opening of the mutative damp element of main balanced valve 6a is the biggest, and the fall velocity of amplitude oil cylinder 1,4 is bigger；Otherwise, when the electric current being passed through electric magnet Y4 is less, guide proportion air relief valve 6b output is smaller to the oil pressure of the control port of main balanced valve 6a, and now, the opening of the mutative damp element of main balanced valve 6a is the least, and the fall velocity of amplitude oil cylinder 1,4 is less.
As in figure 2 it is shown, when reversal valve is proportional reversing valve 8, principal arm luffing control system also includes variable pump 10, pressure-compensated valve 9 and shuttle valve 7, wherein: pressure-compensated valve 9 is arranged on the oil circuit between the oil inlet P of variable pump 10 and proportional reversing valve 8；Two oil-ins of shuttle valve 7 turn on the first actuator port B of proportional reversing valve and the control port of rod chamber balanced valve 2,3 respectively, and the oil-out of shuttle valve 7 is respectively turned on pressure-compensated valve 9 and variable pump 10.
Variable pump 10 is the hydraulic fluid flow rate needed for hydraulic system offer, and it has pressure adjusting function, can be according to the pressure of system condition demand regulation.Pressure-compensated valve 9 can make output flow and its spool aperture proportional of proportional reversing valve 8.The pressure of two actuator ports A, B of shuttle valve 7 comparative example reversal valve 8 compares, and pressure relatively Gao mono-tunnel is fed back to pressure-compensated valve 9 and variable pump 10, so that pressure-compensated valve 9 and variable pump 10 regulate accordingly according to feedback pressure.
As it is shown on figure 3, in an alternate embodiment of the present invention where, when reversal valve is for switch reversal valve 8 ', principal arm luffing control system also includes the proportional variable pump 10 ' of the oil inlet P conducting with switch reversal valve 8 '.The output flow of proportional variable pump 10 ' is directly proportional to the control electric current of its electric magnet Y5, uses this structure, pressure-compensated valve and shuttle valve to cancel accordingly.
When super-tonnage crane use gravity transfer mode transfer principal arm time, recharging oil device can continue to fill into hydraulic oil in the rod chamber of amplitude oil cylinder 1,4 to prevent from being emptied, and, owing to rod chamber balanced valve 2,3 cuts out, hydraulic oil in the rod chamber of amplitude oil cylinder 1,4 is locked, therefore, it is to avoid the piston rod of amplitude oil cylinder 1,4 is pulled out by setting-up mechanism.When principal arm hoist, rod chamber balanced valve 2,3 open time, owing to the rod chamber pressure of amplitude oil cylinder 1,4 is equal to oil compensation pressure, therefore, hydraulic oil in the rod chamber of amplitude oil cylinder 1,4 will not abrupt release, this considerably reduce principal arm to hoist suffered impact, thus improve smooth operation and the safety of crane.Use the technical scheme of the embodiment of the present invention, first can transfer mode with power and transfer principal arm, transfer mode with gravity the most again and transfer principal arm to the support of principal arm supported body；Also all can transfer mode with gravity and transfer principal arm to the support of principal arm supported body.
In addition, when principal arm gravity is transferred, hydraulic oil owing to filling in the rod chamber of amplitude oil cylinder 1,4 is low-pressure hydraulic oil, pressure well below power transfer time oil pressure, therefore, use gravity to transfer mode and transfer principal arm, the principal arm extruding to supporting mechanism can be greatly reduced, reduce the deformation of supporting mechanism.
In a preferred embodiment of the invention, principal arm luffing control system also includes the control device (not shown in Fig. 2 and Fig. 3 embodiment) being connected with stop valve 14 signal of telecommunication, turn on for controlling stop valve 14 when receiving principal arm power and transferring instruction, and control stop valve 14 ends when receiving principal arm gravity and transferring instruction.Can also be connected with the signal of telecommunication such as reversal valve, guide proportion air relief valve it should be understood that control device, to realize a series of electrically operated control of crane, improve the accuracy and convenience operated.
In a more excellent embodiment of the present invention, control device, be additionally operable to when receiving principal arm and transferring instruction, control stop valve 14 and first turn in the first stroke that principal arm is transferred, then end in the second stroke that principal arm is transferred.In the first stroke that principal arm is transferred, stop valve 14 turns on, and principal arm can transfer mode quickly, smoothly transfer by power, and the controllability of lowering velocity is preferable；In the second stroke that principal arm is transferred, stop valve 14 ends, and principal arm is transferred mode by gravity and transferred, and greatly reduces the principal arm extruding to supporting mechanism, thus decreases the deformation of supporting mechanism.When principal arm hoists again, the hydraulic oil in the rod chamber of amplitude oil cylinder will not abrupt release, therefore, principal arm can hoist more smoothly, and smooth operation and the safety of crane are higher.
Below as a example by embodiment illustrated in fig. 2, the work process of detailed description principal arm luffing control system:
In the first stroke that principal arm is transferred, using power to transfer mode and transfer principal arm, the electric magnet Y4 of the electric magnet Y2 of proportional reversing valve 8 and the guide proportion air relief valve 6b of main transformer width balanced valve 6 obtains electric, the oil inlet P of proportional reversing valve 8 and the first actuator port B conducting.Electric magnet Y3 dead electricity because of stop 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 electric magnet Y4 controls simultaneously promotes rodless cavity balanced valve 15,5, and main transformer width balanced valve 6 the spool of main balanced valve 6a open, principal arm realizes power and transfers action.In said process, electric magnet Y2 increases with electric magnet Y4 synchronous proportional or synchronous proportional reduces, and principal arm lowering velocity is also relevant to this ratio.The outlet of repairing check valve 13 turns on oil circuit BF, and owing to oil circuit BF is high-pressure oil passage, therefore repairing check valve 13 exports and shut, and oil circuit W-E is not turned on.
In the second stroke that principal arm is transferred, use gravity to transfer mode and transfer principal arm, the electric magnet Y2 of proportional reversing valve 8, the electric magnet Y4 of guide proportion air relief valve 6b of main transformer width balanced valve 6, and the electric magnet Y3 of stop valve 14 obtains electric, the oil inlet P of proportional reversing valve 8 and the first actuator port B conducting.Owing to the electric magnet Y3 of stop valve 14 obtains electric, therefore oil circuit C-D cut-off.The pilot pressure that electric magnet Y4 controls promotes rodless cavity balanced valve 15,5 simultaneously, and the main balanced valve 6a of main transformer width balanced valve 6 opens, and principal arm realizes transferring under Gravitative Loads power.The piston rod of amplitude oil cylinder 1,4 moves downward, and the hydraulic oil in rodless cavity, respectively through rodless cavity balanced valve 15,5, arrives oil circuit T-V after the main balanced valve 6a of main transformer width balanced valve 6, and the second actuator port A of proportional reversing valve 8, oil return inlet T.In above process, the rod chamber of amplitude oil cylinder 1,4 has the trend being emptied, but the system oil return of slippage pump 11 and arrival oil circuit T-V can be under the effect of repairing counterbalance valve 12, continue to oil circuit E-F repairing through repairing check valve 13, repairing source respectively enters the rod chamber of amplitude oil cylinder 1,4 after rod chamber balanced valve 2,3, thus prevents the rod chamber of amplitude oil cylinder 1,4 to be emptied.In said process, the control signal of electric magnet Y4 is ratio control signal, such that it is able to the ratio realizing the main balanced valve 6a of main transformer width balanced valve 6 is opened, it is achieved the control to principal arm lowering velocity.Principal arm deadweight transfer during, due to amplitude oil cylinder 1,4 rod chamber enter hydraulic oil be low pressure repairing source, pressure well below principal arm power transfer time system pressure, therefore, vehicle frame of being rivals in a contest under principal arm gravity produce extruding force less.In like manner, carry out principal arm hoist action time, when rod chamber balanced valve 2,3 is opened, owing to the pressure of the rod chamber of amplitude oil cylinder 1,4 is originally equal to the benefit oil supply pressure of system, therefore, rod chamber will not pressure release suddenly, this considerably reduce the vibration of principal arm when luffing hoists.In said process, fall velocity regardless of amplitude oil cylinder 1,4, piston area due to rodless cavity is more than the piston area of rod chamber, and when therefore principal arm is at the uniform velocity transferred, the system oil return of oil circuit T-V is always more than the actually required flow of the rod chamber filling into amplitude oil cylinder 1,4.Due to the effect of repairing counterbalance valve 12, the system oil return of oil circuit T-V can overcome the resistance of pipeline and rod chamber balanced valve 2,3 to arrive the rod chamber of amplitude oil cylinder 1,4 under setting pressure, and 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, also the rod chamber of amplitude oil cylinder 1,4 can be produced the flow of an active repairing when principal arm luffing is not operating (when system reality not demand, can release at repairing counterbalance valve 12), thus the problem that the instantaneous oil suction of rod chamber of amplitude oil cylinder 1,4 is not enough when solving instantaneous starting and when acceleration is transferred, it is ensured that the rod chamber of amplitude oil cylinder 1,4 does not haves emptying phenomenon in principal arm decentralization process.
The embodiment of the present invention additionally provides a kind of crane, and including the principal arm luffing control system of aforementioned any embodiment, the smooth operation of this crane is preferable, and safety is higher, and supporting mechanism is difficult to be deformed.
Obviously, those skilled in the art can carry out various change and modification without departing from the spirit and scope of the present invention to the present invention.So, 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. the principal arm luffing control system of a crane, it is characterised in that include reversal valve, luffing
Oil cylinder, rod chamber balanced valve, stop valve and recharging oil device, wherein:
Described reversal valve, has and controls the first operating position that amplitude oil cylinder falls after rise, and controls luffing oil
The second operating position that cylinder hoists, described reversal valve include the first actuator port, the second actuator port,
Oil-in and oil return opening；In described first operating position, the oil-in of reversal valve is to the first actuator port
Conducting, the second actuator port of reversal valve to oil return opening turns on；In described second operating position, commutation
The oil-in of valve turns on to the second actuator port, and the first actuator port of reversal valve to oil return opening turns on；
Described rod chamber balanced valve, is arranged on the rod chamber hydraulic fluid port oil circuit of amplitude oil cylinder, for becoming
Close when width oil cylinder falls after rise and open when amplitude oil cylinder hoists；
Described stop valve, is arranged at the oil between the first actuator port of reversal valve and rod chamber balanced valve
Lu Shang, for the conducting when principal arm power is transferred and ends when principal arm gravity is transferred；
Described recharging oil device, is arranged on the oil circuit between the oil return opening of reversal valve and rod chamber balanced valve,
For when principal arm gravity is transferred, filling into hydraulic oil to the rod chamber of amplitude oil cylinder.
2. the system as claimed in claim 1, it is characterised in that described recharging oil device includes slippage pump
With repairing counterbalance valve, wherein:
The oil-in of described slippage pump turns on fuel tank, and the oil-out of described slippage pump accesses reversal valve
Oil circuit between oil return opening and rod chamber balanced valve；
The oil-in of described repairing counterbalance valve turns on fuel tank, and the oil-out of described repairing counterbalance valve accesses
Oil circuit between oil return opening and the rod chamber balanced valve of reversal valve.
3. the system as claimed in claim 1, it is characterised in that described recharging oil device also includes changing
The repairing check valve of the oil circuit one-way conduction between the oil return opening of valve to rod chamber balanced valve.
4. the system as claimed in claim 1, it is characterised in that also include:
Rodless cavity balanced valve, is arranged on the rodless cavity hydraulic fluid port oil circuit of amplitude oil cylinder, at luffing oil
Open when cylinder falls after rise and close when amplitude oil cylinder hoists.
5. system as claimed in claim 4, it is characterised in that also include:
Main transformer width balanced valve, is arranged between the second actuator port of reversal valve and rodless cavity balanced valve
On oil circuit, including main balanced valve and guide proportion air relief valve, wherein:
Two actuator ports of described main balanced valve respectively with the second actuator port of reversal valve, Yi Jiwu
Bar chamber balanced valve turns on away from the actuator port of amplitude oil cylinder rodless cavity, for when amplitude oil cylinder falls after rise
Open and close when amplitude oil cylinder hoists；
The oil-out of described guide proportion air relief valve respectively with control port and the master of rodless cavity balanced valve
The control port conducting of balanced valve, for controlling rodless cavity balanced valve and the open and-shut mode of main balanced valve,
And control hydraulic oil flow velocity when main balanced valve is opened.
6. the system as claimed in claim 1, it is characterised in that when described reversal valve is ratio commutation
During valve, described principal arm luffing control system also includes variable pump, pressure-compensated valve and shuttle valve, wherein:
Described pressure-compensated valve is arranged on the oil circuit between variable pump and the oil-in of proportional reversing valve；
Two oil-ins of described shuttle valve are flat with the first actuator port of proportional reversing valve and rod chamber respectively
The control port conducting of weighing apparatus valve, the oil-out of described shuttle valve is respectively turned on pressure-compensated valve and variable pump.
7. the system as claimed in claim 1, it is characterised in that when described reversal valve is switch commutation
During valve, described principal arm luffing control system also includes that the ratio of the oil-in conducting with switch reversal valve becomes
Amount pump.
8. the system as described in any one of claim 1～7, it is characterised in that also include:
The control device being connected with the stop valve signal of telecommunication, for when receiving principal arm power and transferring instruction
Control stop valve conducting, and control stop valve cut-off when principal arm gravity transfers instruction receiving.
9. system as claimed in claim 8, it is characterised in that described control device, is additionally operable to
Receive principal arm when transferring instruction, control stop valve and first turn in the first stroke that principal arm is transferred,
Then end in the second stroke that principal arm is transferred.
10. a crane, it is characterised in that include the master as described in any one of claim 1～9
Arm luffing control system.
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