CN203319595U - Crane and winch hydraulic system thereof - Google Patents
Crane and winch hydraulic system thereof Download PDFInfo
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- CN203319595U CN203319595U CN201320390335XU CN201320390335U CN203319595U CN 203319595 U CN203319595 U CN 203319595U CN 201320390335X U CN201320390335X U CN 201320390335XU CN 201320390335 U CN201320390335 U CN 201320390335U CN 203319595 U CN203319595 U CN 203319595U
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Abstract
The utility model provides a winch hydraulic system of a crane. The winch hydraulic system comprises a winch hydraulic motor (4), a winch brake (8) and a winch normal-reverse transfer control valve (3), wherein a hydraulic control cavity (5f) of a winch balance valve (5) is hydraulically connected with a hydraulic control oil pressure releasing oil line (20), and the hydraulic control oil pressure releasing oil line (20) is connected to an oil tank or a second branch oil returning line (25) through an on-off control valve (7). In addition, the utility model further provides a crane comprising the winch hydraulic system. According to the winch hydraulic system of the crane, provided by the utility model, through a simple oil line structure improvement, namely, through additionally arranging the hydraulic control oil pressure releasing oil line with the on-off control valve, operations among the winch normal-reverse transfer control valve, the winch balance valve and the winch brake are mutually matched to form a control sequence relationship capable of eliminating the defect of the prior art, thus operation accidents such as impact of a hydraulic system, hook slipping and the like are favorably reduced, and the reliability and safety of winch operation are improved.
Description
Technical field
The utility model relates to crane hydraulic system, particularly, relates to a kind of crane hoisting hydraulic efficiency pressure system.In addition, the utility model also relates to a kind of hoisting crane that comprises described crane hoisting hydraulic efficiency pressure system.
Background technology
Crane tool, especially large-tonnage crane tool extensively adopt hydraulic winch structure (typically being the electric-controlled hydraulic hoisting mechanism), the hydraulic winch structure comprises hoisting crane hydraulic pressure hoisting hydraulic system, this hoisting crane hydraulic pressure hoisting hydraulic system is by fluid motor-driven winching barrel (reel) folding and unfolding steel rope, with lifting heavy or make weight descend.Hoisting crane hydraulic pressure hoisting hydraulic system generally comprises the elevator balance cock that is connected in HM Hydraulic Motor, and the Main Function of elevator balance cock is to prevent HM Hydraulic Motor suction sky and decline speed limit.
Particularly, shown in Figure 1, Figure 1 shows that in prior art the hydraulic schematic diagram of typical crane hoisting hydraulic efficiency pressure system.Described crane hoisting hydraulic efficiency pressure system mainly comprises hoisting electricity proportional pressure-reducing valve 1, elevator descend electric proportional pressure-reducing valve 2, elevator rotating reversing control valve 3, elevator HM Hydraulic Motor 4, elevator balance cock 5, brake control valve 6 and hoist brake 8 etc., letter in Fig. 1 is mainly used in helping to understand hydraulic schematic diagram, it must not represent the hydraulic fluid port of practical structures in the crane hoisting hydraulic efficiency pressure system, main is to play the suggesting effect of relevant oil circuit to technical personnel, and wherein P1 points out main oil-feed oil circuit 9; P2 prompting braking oil-feed oil circuit 21(should brake in the general 30bar of oil pressure on oil-feed oil circuit 21, in 3MPa); P3 and P4 point out respectively hoisting hydraulic control oil-feed oil circuit 22 and elevator decline hydraulic control oil-feed oil circuit 23, elevator rotating control cock 3 in Fig. 1 is pilot operated directional control valve, hoisting hydraulic control oil-feed oil circuit 22 and elevator decline hydraulic control oil-feed oil circuit 23 are for answering hydraulic control oil to the hydraulic control confession of elevator rotating control cock 3 both sides as required, at this, it should be noted that, hoisting hydraulic control oil-feed oil circuit 22 and elevator decline hydraulic control oil-feed oil circuit 23, all for supplying hydraulic control oil, generally can share hydraulic oil source; T points out oil return circuit 17, know ground for the Hydraulic Field technical personnel, oil return circuit 17 in hydraulic efficiency pressure system can have various forms, it can comprise many independent oil return oil circuits that are connected in fuel tank, also can comprise a main oil return circuit that is connected in fuel tank, connect some branches oil return circuit etc. on this main oil return circuit, the utility model is not restricted for the concrete pipeline layout of oil return circuit 17; Y prompting repairing oil circuit 14, for those skilled in the art knownly, repairing oil circuit 14 is mainly used at the rotating speed of elevator HM Hydraulic Motor 4 too fast and cause on main oil-feed oil circuit 9 hydraulic oil of supply can not meet requirements the time, elevator HM Hydraulic Motor 4 via repairing oil circuit 14 from fuel tank the aspirated liquid force feed to supplement hydraulic oil.
In prior art shown in Fig. 1, typical crane hoisting hydraulic efficiency pressure system mainly has three mode of operations:
The first, hoisting.Under this mode of operation, operating personal operation hoisting operating handle, make the proportion electro-magnet of hoisting electricity proportional pressure-reducing valve 1 obtain the electric current progressively increased, hydraulic control oil on hoisting hydraulic control oil-feed oil circuit 22 reaches the hydraulic control mouth of elevator rotating reversing control valve 3 one sides via hoisting electricity proportional pressure-reducing valve 1 and hoisting hydraulic control oil circuit 10, elevator rotating control cock 3 commutates to the right position shown in Fig. 1, thereby the hydraulic oil on main oil-feed oil circuit 9 is via elevator rotating reversing control valve 3, the first working oil path 12 and balance cock 5 are to elevator HM Hydraulic Motor 4 fuel feeding, shown in Figure 1, the balance cock hydraulic control oil circuit 15 that the hydraulic control mouth X of elevator balance cock 5 connects is communicated with the second working oil path 13, and under this state, the second working oil path 13 is communicated with oil return circuit 17 via elevator rotating reversing control valve 3, now the hydraulic control mouth X of elevator balance cock 5 does not set up oil pressure, elevator balance cock 5 plays the effect of check valve, hydraulic oil on the first working oil path 12 backs down the main inner elements of check valve in elevator balance cock 5, hydraulic oil is fed to the first hydraulic fluid port A of elevator HM Hydraulic Motor 4, backhaul hydraulic oil from the second hydraulic fluid port B of elevator HM Hydraulic Motor 4 via the second working oil path 13, elevator rotating reversing control valve 3 and oil return circuit 17 oil returns, thereby elevator HM Hydraulic Motor 4 is rotated and be with movable reel to rotate, so that the reel Wound steel rope has been realized lift operations.In addition, under this state, know for those skilled in the art ground, brake control valve 6 switches to braking oil-feed oil circuit 21 and the state of braking working oil path 16 conductings of making, thereby braking oil-feed oil circuit 21 is fed to hoist brake 8 via brake control valve 6 and braking working oil path 16 by hydraulic oil, the braking that makes hoist brake 8 remove hoisting mechanism.With regard to hoist brake 8, hoist brake 8 mainly comprises brake cylinder, in braking working oil path 16 not under the state of the rod chamber supply hydraulic fluid of brake cylinder, stretch out under the effect of the retracing spring of the piston rod of brake cylinder in the rodless cavity of brake cylinder and hoisting mechanism is implemented to braking, braking working oil path 16 under the state of the rod chamber supply hydraulic fluid of brake cylinder, the piston rod of brake cylinder overcomes the resistance of retracing spring and retracts under the driving of hydraulic oil, thus the brake off state.Relevant hoist brake is known ground for those skilled in the art, hereinafter this is repeated no more.
The second, meta keeps.Under this mode of operation, the descend elevator step-down operation handle of electric proportional pressure-reducing valve 2 of the hoisting operating handle of operating personal inoperation hoisting electricity proportional pressure-reducing valve 1 and elevator, the hoisting operating handle of hoisting electricity proportional pressure-reducing valve 1 and elevator descend the elevator step-down operation handle of electric proportional pressure-reducing valve 2 in initial position, thereby elevator rotating reversing control valve 3 is in the meta state, do not have hydraulic oil to be fed to elevator HM Hydraulic Motor 4, simultaneously, brake control valve 6 switches to and makes braking oil-feed oil circuit 21 and brake the mutual cut-off of working oil path 16 and braking working oil path 16 state with the oil return circuit mutual conduction, thereby the hydraulic oil in hoist brake 8 is via braking oil-feed oil circuit 21 and brake control valve 6 oil returns, the braking mode that makes hoist brake 8 keep hoisting mechanism.Typically, under the braking mode of hoist brake 8, the slipper of hoist brake 8 is embraced the outer peripheral face of the output shaft of elevator HM Hydraulic Motor 4, thereby it is motionless to make weight remain on for a long time a position.
The 3rd, elevator descends.Under this state, operating personal operation elevator step-down operation handle, make the descend proportion electro-magnet of electric proportional pressure-reducing valve 2 of elevator obtain the electric current progressively increased, in the aperture process from small to large of elevator step-down operation handle, because the elevator intensity of current that the proportion electro-magnet of electric proportional pressure-reducing valve 2 obtains that descends increases gradually, the descend oil pressure of hydraulic control oil of electric proportional pressure-reducing valve 2 outputs of elevator increases gradually, hydraulic control oil on elevator decline hydraulic control oil-feed oil circuit 23 is fed to the opposite side hydraulic control mouth of elevator rotating reversing control valve 3 via the elevator electric proportional pressure-reducing valve 2 that descends, thereby drive elevator rotating reversing control valve 3 to be switched to the left position shown in Fig. 1, hydraulic oil on main oil-feed oil circuit 9 is fed to the second hydraulic fluid port B of elevator HM Hydraulic Motor 4 via elevator rotating reversing control valve 3 and the second working oil path 13, simultaneously because balance cock hydraulic control oil circuit 15 is communicated with the second working oil path 13, balance cock hydraulic control oil circuit 15 is incorporated into the hydraulic oil on the second working oil path 13 the hydraulic control mouth X of elevator balance cock 5, thereby the hydraulic control mouth X of elevator balance cock 5 sets up oil pressure, elevator balance cock 5 is opened (in the hydraulic schematic diagram shown in Fig. 1, being switched to left position state) under the oil pressure effect of hydraulic control oil, backhaul hydraulic oil from the first hydraulic fluid port A of elevator HM Hydraulic Motor 4 via elevator balance cock 4, the first working oil path 12, elevator rotating reversing control valve 3 and oil return circuit 17 oil returns.After above-mentioned driving elevator rotating reversing control valve 3 is switched to the left position shown in Fig. 1, need to control brake control valve 6 and switch to braking oil-feed oil circuit 21 and the state of braking working oil path 16 conductings of making, thereby make hoist brake 8 remove the braking mode to hoisting mechanism under the effect of braking the hydraulic oil on working oil path 16, so that the elevator HM Hydraulic Motor can reverse to be with the movable reel upset, make thus reel discharge steel rope and realize step-down operation.In this step-down operation process, especially need to prevent that the weight descending speed is too fast, need to realize the decline speed limit by elevator balance cock 4, the speed limit principle of relevant elevator balance cock 4 is known ground for those skilled in the art, at this, only simply describes.Particularly, in above-mentioned step-down operation process, speed reversal once elevator HM Hydraulic Motor 4 too fast (being that the weight descending speed is too fast), hydraulic oil on main oil-feed oil circuit 9 can not meet requirements, thereby oil pressure reduces, correspondingly the oil pressure of the hydraulic control mouth X of elevator balance cock 5 reduces, the main valve plug of elevator balance cock 5 makes the through-flow aperture of elevator balance cock 5 diminish under the oil pressure effect of the first hydraulic fluid port A of main valve plug retracing spring and elevator HM Hydraulic Motor 4, thereby make the flow of backhaul hydraulic oil reduce, make thus the speed reversal of elevator HM Hydraulic Motor 4 descend, realize thus the speed limit effect of elevator balance cock 4.In addition, in elevator step-down operation process, before weight drops to the position of requirement, operating personal operation elevator step-down operation handle, make the aperture of elevator step-down operation handle from big to small, in this case, the elevator oil pressure that electric proportional pressure-reducing valve 2 outputs to the hydraulic control oil in elevator decline hydraulic control 11 that descends reduces, thereby make the spool of elevator rotating reversing control valve 3 move and cause through-flow aperture to reduce towards meta, therefore the oil mass that is fed to the second hydraulic fluid port B of elevator HM Hydraulic Motor 4 reduces, when the through-flow aperture of elevator rotating reversing control valve 3 is very little, control brake control valve 6 switch to make braking oil-feed oil circuit 21 and braking working oil path 16 mutually the state of cut-off and braking working oil path 16 and oil return circuit mutual conduction (in Fig. 1, brake control valve 6 is two position, three-way electromagnetic change valve, make brake control valve 6 dead electricity), thereby make hoist brake 8 in braking mode, step-down operation stops.
Operating process by the above-mentioned hydraulic efficiency pressure system of the crane hoisting to prior art can be readily seen that, under the elevator descent mode, when the elevator step-down operation starts, after operating personal manipulation elevator step-down operation handle makes 3 commutations of elevator rotating reversing control valve, just controlling brake control valve 6 obtains electric and makes braking oil-feed oil circuit 21 and brake working oil path 16 conductings, make hoist brake 8 brake offs, but due to the unlatching of elevator rotating reversing control valve 3 releasing early than the braking mode of hoist brake 8, before the braking mode of hoist brake 8 is removed, elevator HM Hydraulic Motor 4 can not be rotated, now the hydraulic oil on the second working oil path 13 can only be via balance cock hydraulic control oil circuit 15, the second damping hole 5b oil return on the first damping hole 5a and bypass damping oil circuit 19, apparently, the through-flow bore of the first damping hole 5a and the second damping hole 5b is all very little, hydraulic oil just can make because of forming relative blocked state the oil pressure of the second hydraulic fluid port B of elevator HM Hydraulic Motor 4 very high like this, correspondingly, oil pressure between the first damping hole 5a and the second damping hole 5b also can be very high, be that the oil pressure set up of the hydraulic control mouth X place of elevator balance cock 5 is very high, this oil pressure is as the response pressure of elevator balance cock 5, its oil pressure is larger, the increase time is shorter, elevator balance cock 4 is opened faster, like this, after hoist brake 8 unclamps, because elevator balance cock 4 is switched to rapidly large through-flow openings state, thereby make elevator HM Hydraulic Motor 4 rotate suddenly, state in a kind of moment Acceleration of starting rotation, be that hoisting mechanism descends suddenly, this can cause the oil pressure of the second hydraulic fluid port B of elevator HM Hydraulic Motor 4 to descend suddenly, thereby make the through-flow aperture of elevator balance cock 4 also diminish and make step-down operation not steady.
In addition, as mentioned above, in elevator step-down operation process, before weight drops to the position of requirement, operating personal operation elevator step-down operation handle, make the aperture of elevator step-down operation handle from big to small, in this case, when the through-flow aperture of elevator rotating reversing control valve 3 is very little, control brake control valve 6 and switch to the state (making brake control valve 6 dead electricity) that makes braking oil-feed oil circuit 21 and the mutual cut-off of braking working oil path 16 and braking working oil path 16 and oil return circuit mutual conduction, thereby make hoist brake 8 in braking mode.That is to say, in this decline shut-down operation process, even brake control valve 6 is made hoist brake 8 in braking mode at elevator rotating reversing control valve 3 during in little through-flow state with regard to switching, but, although it is very little now to be fed to the hydraulic pressure oil mass of the second hydraulic fluid port B of elevator HM Hydraulic Motor 4, because elevator HM Hydraulic Motor 4 can not be rotated, therefore the hydraulic oil at the second hydraulic fluid port 4 places of elevator HM Hydraulic Motor 4 can only be via balance cock hydraulic control oil circuit 15, the second damping hole 5b on the first damping hole 5a and bypass damping oil circuit 19, as mentioned above, the through-flow bore of the first damping hole 5a and the second damping hole 5b is all very little, therefore hydraulic oil just can make because of forming relative blocked state the oil pressure of the second hydraulic fluid port B of elevator HM Hydraulic Motor 4 very high, correspondingly, oil pressure between the first damping hole 5a and the second damping hole 5b also can be very high, be that the oil pressure set up of the hydraulic control mouth X place of elevator balance cock 5 is very high, therefore elevator balance cock 5 under the oil pressure effect at hydraulic control mouth X place in opening, so just, can make the first hydraulic fluid port A of elevator HM Hydraulic Motor 4 can flow back to fuel tank by elevator balance cock 5 with the hydraulic oil be connected on oil circuit between elevator balance cock 5, now elevator balance cock 5 can not play the effect that ends running of hydraulic power oil, if now hoist brake 8 breaks down, can cause weight to produce slipping hook, produce serious work accident.In addition, due to the braking of hoist brake 8 with remove braking and need the regular hour, (for example in the step-down operation stopped process, frequently carry out the keying operation of hoist brake 8) under some working conditions, even brake control valve 6 dead electricity, but hoist brake 8 often can not be very soon in braking mode (slipper that is hoist brake 8 not be held motor output shaft very soon tightly), simultaneously for the fuel feeding still now of the Hydraulic Pump to main oil-feed oil circuit 9 fuel feeding, although extensively adopt load sensitive pump in the crane hoisting hydraulic efficiency pressure system, but the response regulation of the fuel supply flow rate of load sensitive pump needs the time, and load sensitive pump is mainly to change and carry out the fuel supply flow rate adjusting according to the caused oil pressure of load variations, it can not directly regulate fuel supply flow rate according to the handle aperture of operating personal, get back to meta not yet fully and under through-flow state, (motion of the spool of elevator rotating change-over valve 3 also needs the regular hour in low discharge at the spool of elevator rotating change-over valve 3, the hysteresis that it is certain with respect to the lever operated existence of operating personal), hydraulic oil still can constantly be fed to the second hydraulic fluid port B of elevator HM Hydraulic Motor, this causes the oil pressure of the second hydraulic fluid port B of elevator HM Hydraulic Motor still can be very high, elevator balance cock 5 can be still now to open, weight still can descend like this, this feels to be exactly that elevator step-down operation handle has been got back to initial position to the operator's, the a bit of distance but weight still will descend.
Because the above-mentioned defect of prior art need to provide a kind of novel hoisting crane cigarette hydraulic efficiency pressure system, to overcome or to alleviate the above-mentioned defect of prior art.
The utility model content
Technical problem to be solved in the utility model is to provide a kind of crane hoisting hydraulic efficiency pressure system, and this crane hoisting hydraulic efficiency pressure system can be improved the stationarity of elevator step-down operation effectively, and strengthens reliability and the safety of elevator step-down operation.
In addition, technical problem to be solved in the utility model is to provide a kind of hoisting crane, and this hoisting crane can improve the stationarity of elevator step-down operation effectively, and strengthens reliability and the safety of elevator step-down operation.
In order to solve the problems of the technologies described above, the utility model provides a kind of crane hoisting hydraulic efficiency pressure system, comprise the elevator HM Hydraulic Motor, hoist brake and the elevator rotating reversing control valve that is connected in main oil-feed oil circuit and main oil return circuit, the first hydraulic fluid port of wherein said elevator HM Hydraulic Motor is connected in described elevator rotating reversing control valve by the first working oil path via the elevator balance cock, the second hydraulic fluid port is connected in described elevator rotating reversing control valve by the second working oil path, can realize by this elevator rotating reversing control valve the rotating oil circuit commutation control of described elevator HM Hydraulic Motor, be connected with balance cock hydraulic control oil circuit on described the second working oil path, this balance cock hydraulic control oil circuit is connected to the liquid controling cavity of described elevator balance cock via the first damping hole, and the balance cock hydraulic control oil circuit between the liquid controling cavity of the liquid controling cavity of described elevator balance cock or this elevator balance cock and described the first damping hole partly is connected in the arrival end of bypass damping oil circuit, this bypass damping oil circuit is connected in fuel tank or first branch's oil return circuit via the second damping hole, and described hoist brake is connected in braking oil-feed oil circuit and braking oil return circuit by the braking working oil path via brake control valve, wherein, balance cock hydraulic control oil circuit between the liquid controling cavity of the liquid controling cavity of described elevator balance cock or this elevator balance cock and described the first damping hole partly go up or described bypass damping oil circuit be connected with hydraulic control oil release oil circuit on the bypass damping oil circuit part between described arrival end and described the second damping hole, this hydraulic control oil release oil circuit is connected in fuel tank or second branch's oil return circuit via on-off control valve.
Particularly, described balance cock hydraulic control oil circuit comprises external balance valve hydraulic control oil circuit and inner hydraulic control oil duct, described external balance valve hydraulic control oil circuit is connected between the hydraulic control mouth of described the second working oil path and described elevator balance cock, described inner hydraulic control oil duct extends to the liquid controling cavity of described elevator balance cock from the hydraulic control mouth of described elevator balance cock via described the first damping hole, thereby the hydraulic control oil circuit between the liquid controling cavity of described elevator balance cock and described the first damping hole is partly the part of described inner hydraulic control oil duct, and the inside oil duct that at least a portion of described bypass damping oil circuit is described elevator balance cock.
Preferably, also be provided with damping oil circuit check valve on described bypass damping oil circuit, described the second damping hole is between the arrival end and described damping oil circuit check valve of described bypass damping oil circuit, the forward port of this damping oil circuit check valve is communicated with described the second damping hole, and reverse port is communicated with described fuel tank or first branch's oil return circuit.
Particularly, described the first working oil path comprises change-over valve linkage section and motor linkage section, described change-over valve linkage section is connected between the first working port of described elevator rotating reversing control valve and described elevator balance cock, and described motor linkage section is connected between the first working port of the second working port of described elevator balance cock and described elevator HM Hydraulic Motor.
Typically, comprise control plunger, main valve plug and main check valve in described elevator balance cock, the forward port of wherein said main check valve is communicated with described the first working port, and the reverse port of this main check valve is communicated with described the second working port, and the opposite side relative with a described liquid controling cavity side of living in of described elevator balance cock is formed with main valve plug retracing spring chamber, in this main valve plug retracing spring chamber, the main valve plug retracing spring that applies elastic forepressure for the end to described main valve plug is installed, one end end face of described control plunger is exposed in the liquid controling cavity of described elevator balance cock, driving described control plunger to move by the hydraulic control oil entered in described liquid controling cavity, and promote by this control plunger the resistance that the other end of described main valve plug drives this main valve plug to overcome described main valve plug retracing spring and move, thereby make described the first working port and described the second working port be interconnected.
Preferably, described main valve plug retracing spring chamber is communicated with the first hydraulic fluid port of described elevator HM Hydraulic Motor via the 3rd damping hole, and the 3rd damping hole also is parallel with check valve, the forward port of this check valve is communicated with described main valve plug retracing spring chamber, and reverse port is communicated with the first hydraulic fluid port of described elevator HM Hydraulic Motor.
Preferably, described elevator balance cock also is integrated with by pass valve, and the input port hydraulic connecting of this by pass valve is communicated with in the first hydraulic fluid port of described elevator HM Hydraulic Motor, and the output port hydraulic connecting is in fuel tank or described second branch's oil return circuit.
Typically, also be connected with motor repairing oil circuit on described the second working oil path, this motor repairing oil circuit is provided with back pressure valve.
Preferably, described on-off control valve is automatically controlled on-off control valve.
Particularly, described brake control valve is two position three way directional control valve, three hydraulic fluid ports of this two position three way directional control valve are connected to described braking working oil path, braking oil-feed oil circuit and oil return circuit, can make by the commutation of this two position three way directional control valve described braking working oil path, optionally with described braking oil-feed oil circuit or oil return circuit, are communicated with.
Particularly, the main valve plug of described elevator rotating change-over valve control cock has meta, the first control position and the second control position, and this elevator rotating change-over valve control cock has a plurality of hydraulic fluid ports, described main oil-feed oil circuit, main oil return circuit, the first working oil path and the second working oil path are connected to the different hydraulic fluid ports of this elevator rotating change-over valve control cock, wherein, under the state of main valve plug in meta of described elevator rotating change-over valve control cock, described main oil-feed oil circuit all ends with described the first working oil path and the second working oil path; Under the state of main valve plug in described the first control position of described elevator rotating change-over valve control cock, described main oil-feed oil circuit and described the first working oil path are interconnected and described main oil return circuit and described the second working oil path are interconnected; Under the state of main valve plug in described the second control position of described elevator rotating change-over valve control cock, described main oil-feed oil circuit and described the second working oil path are interconnected and described main oil return circuit and described the first working oil path are interconnected.
Typically, described elevator rotating change-over valve control cock is pilot operated directional control valve, one side hydraulic control mouth of this pilot operated directional control valve is connected in hoisting electricity proportional pressure-reducing valve by hoisting hydraulic control oil circuit, and this hoisting electricity proportional pressure-reducing valve is connected in hoisting oil-feed oil circuit and hydraulic control oil oil return circuit; And the opposite side hydraulic control mouth of described pilot operated directional control valve is connected in the elevator electric proportional pressure-reducing valve that descends by elevator decline hydraulic control oil circuit, this elevator electric proportional pressure-reducing valve that descends is connected in elevator decline oil-feed oil circuit and hydraulic control oil oil return circuit.
On the basis of the technical scheme of above-mentioned crane hoisting hydraulic efficiency pressure system, the utility model also provides a kind of hoisting crane, and wherein, this hoisting crane comprises according to above-mentioned arbitrary crane hoisting hydraulic efficiency pressure system.
Pass through technique scheme, crane hoisting hydraulic efficiency pressure system of the present utility model is improved by simple oil channel structures, be provided with the hydraulic control oil release oil circuit of on-off control valve by increase, make the operation between elevator rotating reversing control valve, elevator balance cock and hoist brake mutually mate, formation can be eliminated the control sequence relation of prior art defect, this is conducive in reducing Impact in Hydraulic System, prevents from slipping the work accidents such as hook, has improved reliability and the safety of elevator operation.In general, when hoisting crane cigarette hydraulic efficiency pressure system of the present utility model has reduced elevator decline startup, the system pressure peak value, make the operation descended while starting more steady; And, this practicality has newly formed hydraulic pressure and the double braking of mechanical braking when elevator descends braking, make brake system more reliable, system pressure peak value when it has reduced elevator decline braking, prevented that the generations such as the malfunctioning and frequent operation of hoist brake from slipping the risk of hook, the service life that is conducive to improve hoist brake.In addition, hoisting crane of the present utility model comprises above-mentioned crane hoisting hydraulic efficiency pressure system, so it has above-mentioned advantage equally.
Other feature and advantage of the present utility model will partly be described in detail in the specific embodiment subsequently.
The accompanying drawing explanation
Following accompanying drawing is used to provide further understanding of the present utility model; and form the part of specification sheets; itself and the following specific embodiment one are used from explanation the utility model, but protection domain of the present utility model is not limited to following the drawings and the specific embodiments.In the accompanying drawings:
Fig. 1 is the hydraulic schematic diagram of a kind of typical crane hoisting hydraulic efficiency pressure system in prior art.
Fig. 2 is the hydraulic schematic diagram of the crane hoisting hydraulic efficiency pressure system of the utility model specific embodiment.
Fig. 3 is the local structure schematic diagram of the balance cock in Fig. 2, wherein for clear demonstration has adopted, analyses and observe display format.
Description of reference numerals:
The specific embodiment
Below in conjunction with accompanying drawing, the specific embodiment of the present utility model is elaborated; should be understood that; the specific embodiment described herein is only for description and interpretation the utility model, and protection domain of the present utility model is not limited to the following specific embodiment.
Crane hoisting hydraulic efficiency pressure system of the present utility model belongs to Hydraulic Field, and its substantive technical conceive is the improvement of hydraulic circuit relation, and does not lie in concrete physical construction.For example, crane hoisting hydraulic efficiency pressure system of the present utility model is partly improved mainly for the hydraulic control oil circuit of elevator balance cock, but the elevator balance cock is not limited to the elevator balance cock of the ad hoc structure form shown in Fig. 2, any elevator balance cock, as long as it possesses the oil channel structures that in Fig. 2, elevator balance cock left side liquid controling cavity connects, it all can adopt technical conceive of the present utility model.In addition; although crane hoisting hydraulic efficiency pressure system of the present utility model mainly adopts automatically controlled mode to control relevant hydraulic valve in a preferred embodiment; but in technical conceive scope of the present utility model; technical conceive of the present utility model also is confined to adopt automatically controlled form; but can adopt hydraulic control form, automatically controlled and hydraulic control combining form, even manual control form, these all belong to protection domain of the present utility model.
Shown in Figure 2, similar with the hoisting hydraulic system of describing above with reference to Fig. 1, crane hoisting hydraulic efficiency pressure system of the present utility model comprises elevator HM Hydraulic Motor 4, hoist brake 8 and the elevator rotating reversing control valve 3 that is connected in main oil-feed oil circuit 9 and main oil return circuit 17, the first hydraulic fluid port A of elevator HM Hydraulic Motor 4 is connected in elevator rotating reversing control valve 3 by the first working oil path 12 via elevator balance cock 5, the second hydraulic fluid port B is connected in elevator rotating reversing control valve 3 by the second working oil path 13, can realize by elevator rotating reversing control valve 3 the rotating oil circuit commutation control of elevator HM Hydraulic Motor 4.Be connected with balance cock hydraulic control oil circuit 15 on the second working oil path 13, this balance cock hydraulic control oil circuit 15 is connected to the liquid controling cavity 5f of elevator balance cock 5 via the first damping hole 5a, and the balance cock hydraulic control oil circuit between the liquid controling cavity 5f of elevator balance cock 5 or the liquid controling cavity 5f of this elevator balance cock 5 and the first damping hole 5a partly is connected in the arrival end 5h of bypass damping oil circuit 19, this bypass damping oil circuit 19 is connected in fuel tank or first branch's oil return circuit 24 via the second damping hole 5b.Hoist brake 8 is connected in braking oil-feed oil circuit 21 and braking oil return circuit by braking working oil path 16 via brake control valve 6.
Unlike the prior art, adopted originally hydraulic control oil release oil circuit 20 in above-mentioned crane hoisting hydraulic efficiency pressure system, particularly, this hydraulic control oil release oil circuit 20 can be connected in the liquid controling cavity 5f of elevator balance cock 5, perhaps be connected in the liquid controling cavity 5f of this elevator balance cock 5 and the balance cock hydraulic control oil circuit between the first damping hole 5a and partly go up, or be connected in described bypass damping oil circuit 19 on the bypass damping oil circuit part between arrival end 5h and the second damping hole 5b.No matter which kind of concrete type of attachment hydraulic control oil release oil circuit 20 adopts, if its point of connection be positioned at the first damping hole 5a after, before the second damping hole 5b.In addition, hydraulic control oil release oil circuit 20 is connected in fuel tank or second branch's oil return circuit 25 via on-off control valve 7, as long as can realize oil return.
At this, especially it should be noted that, as mentioned above, in the technique scheme of the utility model crane hoisting hydraulic efficiency pressure system, elevator balance cock 5 is not limited to the balance cock of the specific concrete structure shown in Fig. 2, as long as the liquid controling cavity of this balance cock has said structure, be that balance cock hydraulic control oil circuit 15 is connected to the liquid controling cavity 5f of elevator balance cock 5 via the first damping hole 5a, and the balance cock hydraulic control oil circuit between the liquid controling cavity 5f of elevator balance cock 5 or the liquid controling cavity 5f of this elevator balance cock 5 and the first damping hole 5a partly is connected in the arrival end 5h of bypass damping oil circuit 19, this bypass damping oil circuit 19 is connected in fuel tank or first branch's oil return circuit 24 via the second damping hole 5b, no matter the other parts of this balance cock adopt which kind of version (for example the right side part of the elevator balance cock 5 in Fig. 2 adopts and is different from the structure in Fig. 2), as long as it can realize the function of elevator balance cock, all can adopt above-mentioned technical conceive of the present utility model, correspondingly also just belong to protection domain of the present utility model.
In addition, it should be noted that, the second damping hole 5b on the first damping hole 5a described in above-mentioned basic technical scheme of the present utility model, bypass damping oil circuit 19 and this bypass damping oil circuit 19 can form with the base portion of balance cock the integral type balance cock on the mechanical entities structure, also can adopt the independently primary valve part of dash pot valve, conduit under fluid pressure and balance cock to form the hydraulic connecting relation shown in Fig. 2 by hydraulic connecting.Preferably, the elevator balance cock can form the integral valve form, as shown in Figure 2 and suitably with reference to Fig. 3, balance cock hydraulic control oil circuit 15 comprises external balance valve hydraulic control oil circuit and inner hydraulic control oil duct 5g, wherein said external balance valve hydraulic control oil circuit is connected between the hydraulic control mouth X of the second working oil path 13 and elevator balance cock 5, inner hydraulic control oil duct 5g extends to the liquid controling cavity 5f of elevator balance cock 5 from the hydraulic control mouth X of elevator balance cock 5 via the first damping hole 5a, thereby the hydraulic control oil circuit between the liquid controling cavity 5f of elevator balance cock 5 and the first damping hole 5a is partly the part of inner hydraulic control oil duct 5g, and the inside oil duct that at least a portion of bypass damping oil circuit 19 is elevator balance cock 5.
Shown in Figure 2, also be provided with damping oil circuit check valve 5c on bypass damping oil circuit 19, the second damping hole 5b is between the arrival end 5h and damping oil circuit check valve 5c of bypass damping oil circuit 19, the forward port of this damping oil circuit check valve 5c is communicated with the second damping hole 5b, and reverse port is communicated with fuel tank or first branch's oil return circuit 24.The mechanical entities structure at the liquid controling cavity place of relevant elevator balance cock 5 typically can be with reference to shown in Fig. 3, those skilled in the art contrast the hydraulic schematic diagram shown in Fig. 2 can easily understand the mechanical construction drawing shown in Fig. 3, when wherein the hydraulic control oil of control plunger 5e in being subject to liquid controling cavity 5f drives, the main valve plug (showing in Fig. 3) of this control plunger meeting and then driving elevator balance cock 5.At this, pay particular attention to, in Fig. 3, damping oil circuit check valve 5c do not show, it generally can be arranged on and be connected on the hydraulic tubing that the damping oil circuit connects hydraulic fluid port L.In addition, the buffering spool 5d shown in Fig. 3 belongs to a kind of common structure in balance cock, it is mainly used in making entering of hydraulic control oil more steady, it should be noted that, hydraulic control mouth X is via being normal open between the first damping hole 5a and liquid controling cavity 5f, it is also so that the tapering part of buffering spool 5d shown in Fig. 3 moves right on the ora terminalis that abuts to through hole, the relation that should not show because of view and not think and can cause thus ending between hydraulic control mouth X and liquid controling cavity 5f.
Shown in Figure 2, the first working oil path 12 comprises change-over valve linkage section 12a and motor linkage section 12b, change-over valve linkage section 12a is connected between the first working port C of elevator rotating reversing control valve 3 and elevator balance cock 5, and motor linkage section 12b is connected between the first working port A of the second working port D of elevator balance cock 5 and elevator HM Hydraulic Motor 4.With regard to elevator balance cock 5, at its liquid controling cavity 5f place, have under the situation of above-mentioned oil channel structures, generally speaking, as shown in Figure 2, elevator balance cock 5 is interior can comprise control plunger 5e, main valve plug and main check valve, wherein the forward port of main check valve is communicated with the first working port C, and the reverse port of this main check valve is communicated with the second working port D.The opposite side relative with a liquid controling cavity 5f side of living in of elevator balance cock 5 is formed with main valve plug retracing spring chamber 5i, in this main valve plug retracing spring chamber 5i, the main valve plug retracing spring that applies elastic forepressure for the end to described main valve plug is installed, the end end face of control plunger 5e is exposed in the liquid controling cavity 5f of elevator balance cock 5, driving control plunger 5e to move by the hydraulic control oil entered in liquid controling cavity 5f, and promote by this control plunger 5e the resistance that the other end of main valve plug drives this main valve plug to overcome the main valve plug retracing spring and move, thereby make the first working port C and the second working port D be interconnected.That is to say, when hydraulic oil enters from the first working port C of elevator balance cock 5, if oil pressure is enough, can flow to the second working port D by pushing main check valve open; If but hydraulic oil enters from the second working port D, reverse cutoff function due to main check valve, now only at elevator balance cock 5, by the hydraulic oil that enters liquid controling cavity 5f, undertaken under situation that hydraulic control makes main valve plug move, hydraulic oil could flow to the first working port C from the second working port D.
The right-hand member of the elevator balance cock 5 shown in Fig. 2 also has unique structure, particularly, main valve plug retracing spring chamber 5i is communicated with the first hydraulic fluid port A of elevator HM Hydraulic Motor 4 via the 3rd damping hole 5j, and the 3rd damping hole 5j also is parallel with check valve 5k, the forward port of this check valve 5k is communicated with main valve plug retracing spring chamber 5i, and reverse port is communicated with the first hydraulic fluid port A of elevator HM Hydraulic Motor 4.The balance cock of this concrete form belongs to preferred structure, the oil pressure feedback at its place, chamber of retracing spring by balance cock can make the reaction of main valve plug sensitiveer, the main valve plug retracing spring also can adopt the relatively lightly spring of any simultaneously, but corresponding oil-returning structure or hydraulic oil generally need to be set and shift oil circuit, example by pass valve described as follows or elevator HM Hydraulic Motor can adopt variable hydraulic motor, are closed in hydraulic oil in the retracing spring chamber with the main valve plug that prevents elevator balance cock 5 and stop and can't move.For example, elevator balance cock 5 can be integrated with by pass valve 26, and the input port hydraulic connecting of this by pass valve 26 is in the first hydraulic fluid port A of elevator HM Hydraulic Motor 4, and the output port hydraulic connecting is in fuel tank or second branch's oil return circuit 25.For another example, as shown in Figure 2, described elevator HM Hydraulic Motor 4 can be known variable hydraulic motor.In addition, on described the second working oil path 13, generally also be connected with motor repairing oil circuit 14, this motor repairing oil circuit 14 is provided with back pressure valve 18.
As a kind of preferred implementation of the present utility model, crane hoisting hydraulic efficiency pressure system of the present utility model adopts automatically controlled form.
Particularly, shown in Figure 2, described on-off control valve 7 can be automatically controlled on-off control valve, and for example on-off control valve 7 can be two position, three-way electromagnetic change valve, bi-bit bi-pass solenoid directional control valve or electromagnetic switch valve.Above-mentioned brake control valve 6 can be generally two position three way directional control valve, three hydraulic fluid ports of this two position three way directional control valve are connected to braking working oil path 16, braking oil-feed oil circuit 21 and oil return circuit, can make by the commutation of this two position three way directional control valve braking working oil path 16, optionally with braking oil-feed oil circuit 21 or oil return circuit, are communicated with.Under automatically controlled form, similarly, brake control valve 6 can be the two-position three way electric control reversing valve.
Shown in Figure 2, the main valve plug of elevator rotating change-over valve control cock 3 has meta, the first control position and the second control position, and this elevator rotating change-over valve control cock 3 has a plurality of hydraulic fluid ports, main oil-feed oil circuit 9, main oil return circuit 17, the first working oil path 12 and the second working oil path 13 are connected to the different hydraulic fluid ports of this elevator rotating change-over valve control cock 3, wherein, under the state of main valve plug in meta of elevator rotating change-over valve control cock 3, main oil-feed oil circuit 9 and the first working oil path 12 and the second working oil path 13 are all ended; Under the state of main valve plug in the first control position of elevator rotating change-over valve control cock 3, main oil-feed oil circuit 9 is interconnected with described the first working oil path 12 and main oil return circuit 17 is interconnected with described the second working oil path 13; Under the state of main valve plug in the second control position of elevator rotating change-over valve control cock 3, main oil-feed oil circuit 9 and the second working oil path 13 are interconnected and main oil return circuit 17 and the first working oil path 12 are interconnected.
In Fig. 2, what elevator rotating change-over valve control cock 3 adopted is pilot operated directional control valve, one side hydraulic control mouth of this pilot operated directional control valve is connected in hoisting electricity proportional pressure-reducing valve 1 by hoisting hydraulic control oil circuit 10, and this hoisting electricity proportional pressure-reducing valve 1 is connected in hoisting oil-feed oil circuit 22 and hydraulic control oil oil return circuit; The opposite side hydraulic control mouth of described pilot operated directional control valve is connected in the elevator electric proportional pressure-reducing valve 2 that descends by elevator decline hydraulic control oil circuit 11, and this elevator electric proportional pressure-reducing valve 2 that descends is connected in elevator decline oil-feed oil circuit 23 and hydraulic control oil oil return circuit.This preferred form is mainly to control the both sides hydraulic control oil circuit of elevator rotating change-over valve control cock 3 by hoisting electricity proportional pressure-reducing valve 1 and the elevator electric proportional pressure-reducing valve 2 that descends, thereby realizes automatically controlled control.Known ground, the size of the control electric current that electric proportional pressure-reducing valve can be by control inputs is regulated the size of the hydraulic oil pressure of this electricity proportional pressure-reducing valve output, thereby controls the commutation of elevator rotating change-over valve control cock 3 by controlling hydraulic control oil.
Elevator rotating change-over valve control cock 3 generally can adopt three position four-way directional control valve to get final product, but the elevator rotating change-over valve control cock 3 in the crane hoisting hydraulic efficiency pressure system is the change-over valve in the multiple directional control valve of crane hydraulic system normally, elevator rotating change-over valve control cock 3 is not generally three position four-way directional control valve commonly used in this case, generally can will not need the hydraulic fluid port shutoff of using to get final product in this case, for example, in Fig. 2, elevator rotating reversing control valve 3 is three seven logical pilot operated directional control valves, main oil-feed oil circuit 9, oil return circuit 17, the first working oil path 12 and the second working oil path 13 are connected to the different operating hydraulic fluid port of this elevator rotating change-over valve control cock 3, and all the other actuator port shutoff of this elevator rotating reversing control valve 3.
On the basis of the technique scheme of crane hoisting hydraulic efficiency pressure system of the present utility model, the utility model provides a kind of hoisting crane, and this hoisting crane comprises according to above-mentioned crane hoisting hydraulic efficiency pressure system.
By the top description to technical solutions of the utility model, can find out, the difference of the structure of crane hoisting hydraulic efficiency pressure system of the present utility model and existing crane hoisting hydraulic efficiency pressure system mainly has been to increase for example two position, three-way electromagnetic change valve used as on-off control valve in Fig. 2 of on-off control valve 7(), below mainly take the crane hoisting hydraulic efficiency pressure system of taking automatically controlled form shown in Fig. 2 and describe as example, its concrete effect in elevator step-down operation process is as follows:
First, when the elevator step-down operation starts, for controlling the descend aperture process from small to large of operating handle (being elevator step-down operation handle) of electric proportional pressure-reducing valve 2 of elevator, the descend oil pressure of hydraulic control oil of electric proportional pressure-reducing valve 1 output of elevator constantly increases, this hydraulic control oil drives this elevator rotating reversing control valve 3 of elevator rotating reversing control valve 3(to be generally a change-over valve of the multiple directional control valve in crane hydraulic system via elevator decline hydraulic control oil circuit 11) commutation, make afterwards the solenoid directional control valve as on-off control valve 7 in Fig. 2 obtain electric, make hydraulic control oil release oil circuit 20 and oil return circuit 17 conductings, the second damping hole 5b on bypass damping oil circuit 19 can't play shock damping action like this, thereby making the control oil pressure on the control plunger 5e that acts on elevator balance cock 5 is the logical fuel tank of 0(), the hydraulic oil at the second hydraulic fluid port B place of elevator HM Hydraulic Motor 4 is via balance cock hydraulic control oil circuit 15 like this, the hydraulic control mouth X of elevator balance cock 5, the first damping hole 5a and as the solenoid directional control valve oil return of on-off control valve 7, thereby make the oil pressure at the second hydraulic fluid port B place of elevator HM Hydraulic Motor 4 significantly reduce (when being approximately step-down operation in prior art and starting 0.5 times of the second hydraulic fluid port B place oil pressure of elevator HM Hydraulic Motor 4) with respect to prior art, next make the two position, three-way electromagnetic change valve as brake control valve 6 obtain electric, so that braking oil- feed oil circuit 21 and 16 conductings of braking working oil path, thereby make hoist brake 8 start the brake off state, simultaneously in unclamping the process of output shaft of elevator HM Hydraulic Motor 4, the slipper of hoist brake 8 makes the solenoid directional control valve dead electricity as on-off control valve 7, make hydraulic control oil release oil circuit 20 and oil return circuit 17 cut-offs, the oil pressure at the hydraulic control mouth X place of elevator balance cock 5 just can progressively increase like this, thereby the unlatching that makes elevator balance cock 5 is slow and progressively be opened to larger through-flow state along with the releasing of the braking mode of hoist brake, make like this step-down operation of hoisting mechanism can be milder, avoided the unsettled phenomenon of step-down operation of the prior art.
Second, before when hoisting mechanism, weight being transferred to the approaching position needed, brake operating need to be descended, now operating personal makes elevator step-down operation handle aperture from big to small by operation, thereby drive the through-flow aperture of elevator rotating reversing control valve 3 to reduce, thereby the oil inlet quantity of the second hydraulic fluid port B of elevator HM Hydraulic Motor 4 reduces, (through-flow aperture is very little while showing as the hydraulic control oil introduced from the second hydraulic fluid port B of elevator HM Hydraulic Motor 4 by the first damping hole 5a pressure reduction less when the through-flow aperture that drives elevator rotating reversing control valve 3 is very little, this can carry out decision operation according to elevator step-down operation handle with respect to the aperture of initial position by operating personal), the solenoid directional control valve that operating personal is controlled as on-off control valve 7 obtains electric, thereby make hydraulic control oil release oil circuit 20 and oil return circuit 17 conductings, elevator balance cock 5 can be closed very soon because of hydraulic control mouth X place's decompression like this, and the hydraulic oil at the second hydraulic fluid port B place of elevator HM Hydraulic Motor 4 also can be via balance cock hydraulic control oil circuit 15, the hydraulic control mouth X of elevator balance cock 5, the first damping hole 5a and on-off control valve 7 oil returns, thereby the oil pressure at the second hydraulic fluid port B place of elevator HM Hydraulic Motor 4 can significantly be less than the oil pressure under the same operating mode of prior art under this operating mode, in this case, because elevator balance cock 5 has been closed, elevator HM Hydraulic Motor 4 can't oil return and stall.And then operating personal can operate brake control valve 6 dead electricity, make braking working oil path 16 and oil return circuit conducting, thereby the slipper of hoist brake is embraced the output shaft of elevator HM Hydraulic Motor under the effect of retracing spring reset force, realizes braking mode.So by first hydraulic braking, and then the drg braking, system pressure peak value while having reduced braking, what prevented that hoist brake is malfunctioning and frequent operation produces slips the serious work accident such as hook, the service life that the while can be improved hoist brake 8.
By upper description, can be found out, the utility model advantage is: crane hoisting hydraulic efficiency pressure system of the present utility model is improved by simple oil channel structures, be provided with the hydraulic control oil release oil circuit 18 of on-off control valve 7 by increase, make the operation between elevator rotating reversing control valve 3, elevator balance cock 5 and hoist brake 8 mutually mate, formation can be eliminated the control sequence relation of prior art defect, this is conducive in reducing Impact in Hydraulic System, prevent from slipping the work accidents such as hook, improved reliability and the safety of elevator operation.In general, when hoisting crane cigarette hydraulic efficiency pressure system of the present utility model has reduced elevator decline startup, the system pressure peak value, make the operation descended while starting more steady; And, this practicality has newly formed hydraulic pressure and the double braking of mechanical braking when elevator descends braking, make brake system more reliable, system pressure peak value when it has reduced elevator decline braking, prevented that the generations such as the malfunctioning and frequent operation of hoist brake from slipping the risk of hook, the service life that is conducive to improve hoist brake.In addition, hoisting crane of the present utility model comprises above-mentioned crane hoisting hydraulic efficiency pressure system, so it has above-mentioned advantage equally.
Below describe by reference to the accompanying drawings preferred implementation of the present utility model in detail; but; the utility model is not limited to the detail in above-mentioned embodiment; in technical conceive scope of the present utility model; can carry out multiple simple variant to the technical solution of the utility model, these simple variant all belong to protection domain of the present utility model.
It should be noted that in addition each the concrete technical characterictic described in the above-mentioned specific embodiment, in reconcilable situation, can be combined by any suitable mode.For fear of unnecessary repetition, the utility model is to the explanation no longer separately of various possible array modes.
In addition, between various embodiment of the present utility model, also can carry out combination in any, as long as it is without prejudice to thought of the present utility model, it should be considered as content disclosed in the utility model equally.
Claims (13)
1. the crane hoisting hydraulic efficiency pressure system, comprise elevator HM Hydraulic Motor (4), hoist brake (8) and be connected in main oil-feed oil circuit (9) and the elevator rotating reversing control valve (3) of main oil return circuit (17),
First hydraulic fluid port (A) of wherein said elevator HM Hydraulic Motor (4) is connected in described elevator rotating reversing control valve (3) by the first working oil path (12) via elevator balance cock (5), the second hydraulic fluid port (B) is connected in described elevator rotating reversing control valve (3) by the second working oil path (13), can realize by this elevator rotating reversing control valve (3) the rotating oil circuit commutation control of described elevator HM Hydraulic Motor (4), be connected with balance cock hydraulic control oil circuit (15) on described the second working oil path (13), this balance cock hydraulic control oil circuit (15) is connected to the liquid controling cavity (5f) of described elevator balance cock (5) via the first damping hole (5a), and the balance cock hydraulic control oil circuit between the liquid controling cavity (5f) of described elevator balance cock (5) or the liquid controling cavity (5f) of this elevator balance cock (5) and described the first damping hole (5a) partly is connected in the arrival end (5h) of bypass damping oil circuit (19), this bypass damping oil circuit (19) is connected in fuel tank or first branch's oil return circuit (24) via the second damping hole (5b), and described hoist brake (8) is connected in braking oil-feed oil circuit (21) and brakes oil return circuit via brake control valve (6) by braking working oil path (16), it is characterized in that,
Balance cock hydraulic control oil circuit between the liquid controling cavity (5f) of described elevator balance cock (5) or the liquid controling cavity (5f) of this elevator balance cock (5) and described the first damping hole (5a) is partly gone up or being positioned on the bypass damping oil circuit part between described arrival end (5h) and described the second damping hole (5b) of described bypass damping oil circuit (19) is connected with hydraulic control oil release oil circuit (20), and this hydraulic control oil release oil circuit (20) is connected in fuel tank or second branch's oil return circuit (25) via on-off control valve (7).
2. crane hoisting hydraulic efficiency pressure system according to claim 1, it is characterized in that, described balance cock hydraulic control oil circuit (15) comprises external balance valve hydraulic control oil circuit and inner hydraulic control oil duct (5g), described external balance valve hydraulic control oil circuit is connected between the hydraulic control mouth (X) of described the second working oil path (13) and described elevator balance cock (5), described inner hydraulic control oil duct (5g) extends to the liquid controling cavity (5f) of described elevator balance cock (5) from the hydraulic control mouth (X) of described elevator balance cock (5) via described the first damping hole (5a), thereby the hydraulic control oil circuit between the liquid controling cavity (5f) of described elevator balance cock (5) and described the first damping hole (5a) is partly the part of described inner hydraulic control oil duct (5g), and the inside oil duct that at least a portion of described bypass damping oil circuit (19) is described elevator balance cock (5).
3. crane hoisting hydraulic efficiency pressure system according to claim 1, it is characterized in that, also be provided with damping oil circuit check valve (5c) on described bypass damping oil circuit (19), described the second damping hole (5b) is positioned between the arrival end (5h) and described damping oil circuit check valve (5c) of described bypass damping oil circuit (19), the forward port of this damping oil circuit check valve (5c) is communicated with described the second damping hole (5b), and reverse port is communicated with described fuel tank or first branch's oil return circuit (24).
4. crane hoisting hydraulic efficiency pressure system according to claim 1, it is characterized in that, described the first working oil path (12) comprises change-over valve linkage section (12a) and motor linkage section (12b), described change-over valve linkage section (12a) is connected between first working port (C) of described elevator rotating reversing control valve (3) and described elevator balance cock (5), and described motor linkage section (12b) is connected between first working port (A) of second working port (D) of described elevator balance cock (5) and described elevator HM Hydraulic Motor (4).
5. crane hoisting hydraulic efficiency pressure system according to claim 4, is characterized in that, comprises control plunger (5e), main valve plug and main check valve in described elevator balance cock (5),
The forward port of wherein said main check valve is communicated with described the first working port (C), and the reverse port of this main check valve is communicated with described the second working port (D); And
The opposite side relative with described liquid controling cavity (5f) side of living in of described elevator balance cock (5) is formed with main valve plug retracing spring chamber (5i), in this main valve plug retracing spring chamber (5i), the main valve plug retracing spring that applies elastic forepressure for the end to described main valve plug is installed, one end end face of described control plunger (5e) is exposed in the liquid controling cavity (5f) of described elevator balance cock (5), driving described control plunger (5e) mobile by the hydraulic control oil entered in described liquid controling cavity (5f), and promote by this control plunger (5e) resistance that the other end of described main valve plug drives this main valve plug to overcome described main valve plug retracing spring and move, thereby make described the first working port (C) and described the second working port (D) be interconnected.
6. crane hoisting hydraulic efficiency pressure system according to claim 5, it is characterized in that, described main valve plug retracing spring chamber (5i) is communicated with first hydraulic fluid port (A) of described elevator HM Hydraulic Motor (4) via the 3rd damping hole (5j), and the 3rd damping hole (5j) also is parallel with check valve (5k), the forward port of this check valve (5k) is communicated with described main valve plug retracing spring chamber (5i), and reverse port is communicated with first hydraulic fluid port (A) of described elevator HM Hydraulic Motor (4).
7. crane hoisting hydraulic efficiency pressure system according to claim 6, it is characterized in that, described elevator balance cock (5) also is integrated with by pass valve (26), the input port hydraulic connecting of this by pass valve (26) is communicated with in first hydraulic fluid port (A) of described elevator HM Hydraulic Motor (4), and the output port hydraulic connecting is in fuel tank or described second branch's oil return circuit (25).
8. crane hoisting hydraulic efficiency pressure system according to claim 1, is characterized in that, also is connected with motor repairing oil circuit (14) on described the second working oil path (13), and this motor repairing oil circuit (14) is provided with back pressure valve (18).
9. according to the described crane hoisting hydraulic efficiency pressure system of any one in claim 1 to 8, it is characterized in that, described on-off control valve (7) is automatically controlled on-off control valve.
10. crane hoisting hydraulic efficiency pressure system according to claim 9, it is characterized in that, described brake control valve (6) is two position three way directional control valve, three hydraulic fluid ports of this two position three way directional control valve are connected to described braking working oil path (16), braking oil-feed oil circuit (21) and oil return circuit, can make by the commutation of this two position three way directional control valve described braking working oil path (16), optionally with described braking oil-feed oil circuit (21) or oil return circuit, are communicated with.
11. crane hoisting hydraulic efficiency pressure system according to claim 9, it is characterized in that, the main valve plug of described elevator rotating change-over valve control cock (3) has meta, the first control position and the second control position, and this elevator rotating change-over valve control cock (3) has a plurality of hydraulic fluid ports, described main oil-feed oil circuit (9), main oil return circuit (17), the first working oil path (12) and the second working oil path (13) are connected to the different hydraulic fluid ports of this elevator rotating change-over valve control cock (3), wherein under the state of main valve plug in meta of described elevator rotating change-over valve control cock (3), described main oil-feed oil circuit (9) all ends with described the first working oil path (12) and the second working oil path (13), under the state of main valve plug in described the first control position of described elevator rotating change-over valve control cock (3), described main oil-feed oil circuit (9) is interconnected with described the first working oil path (12) and described main oil return circuit (17) is interconnected with described the second working oil path (13), under the state of main valve plug in described the second control position of described elevator rotating change-over valve control cock (3), described main oil-feed oil circuit (9) is interconnected with described the second working oil path (13) and described main oil return circuit (17) is interconnected with described the first working oil path (12).
12. crane hoisting hydraulic efficiency pressure system according to claim 11, it is characterized in that, described elevator rotating change-over valve control cock (3) is pilot operated directional control valve, one side hydraulic control mouth of this pilot operated directional control valve is connected in hoisting electricity proportional pressure-reducing valve (1) by hoisting hydraulic control oil circuit (10), and this hoisting electricity proportional pressure-reducing valve (1) is connected in hoisting oil-feed oil circuit (22) and hydraulic control oil oil return circuit; And the opposite side hydraulic control mouth of described pilot operated directional control valve is connected in the elevator electric proportional pressure-reducing valve (2) that descends by elevator decline hydraulic control oil circuit (11), this elevator electric proportional pressure-reducing valve (2) that descends is connected in elevator decline oil-feed oil circuit (23) and hydraulic control oil oil return circuit.
13. hoisting crane, is characterized in that, this hoisting crane comprises according to the described crane hoisting hydraulic efficiency pressure system of any one in claim 1 to 12.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201320390335XU CN203319595U (en) | 2013-07-02 | 2013-07-02 | Crane and winch hydraulic system thereof |
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| CN201320390335XU CN203319595U (en) | 2013-07-02 | 2013-07-02 | Crane and winch hydraulic system thereof |
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| CN201320390335XU Expired - Fee Related CN203319595U (en) | 2013-07-02 | 2013-07-02 | Crane and winch hydraulic system thereof |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN103663221A (en) * | 2013-12-10 | 2014-03-26 | 中联重科股份有限公司 | Crane and system and method for controlling free hook-falling and winching thereof |
| CN104555772A (en) * | 2014-12-31 | 2015-04-29 | 中联重科股份有限公司 | Hydraulic hoist system of crane and crane |
| CN104776080A (en) * | 2015-04-08 | 2015-07-15 | 中联重科股份有限公司 | Damping valve, winching system and engineering machinery |
| CN104925685A (en) * | 2015-06-30 | 2015-09-23 | 中国船舶重工集团公司第七一九研究所 | Winch hydraulic system controlling guide rope through stepless speed regulating constant tension |
| CN105217508A (en) * | 2014-10-30 | 2016-01-06 | 徐州重型机械有限公司 | A kind of hoist brake control system, method and hoisting crane |
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| CN109095367A (en) * | 2018-09-04 | 2018-12-28 | 徐工集团工程机械有限公司 | hydraulic system and crane |
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| CN103663221A (en) * | 2013-12-10 | 2014-03-26 | 中联重科股份有限公司 | Crane and system and method for controlling free hook-falling and winching thereof |
| CN103663221B (en) * | 2013-12-10 | 2016-02-03 | 中联重科股份有限公司 | Hoisting crane and free off the hook winch control system thereof and method |
| CN105217508A (en) * | 2014-10-30 | 2016-01-06 | 徐州重型机械有限公司 | A kind of hoist brake control system, method and hoisting crane |
| CN104555772A (en) * | 2014-12-31 | 2015-04-29 | 中联重科股份有限公司 | Hydraulic hoist system of crane and crane |
| CN104555772B (en) * | 2014-12-31 | 2016-12-14 | 中联重科股份有限公司 | Crane hoisting hydraulic system and crane |
| CN104776080A (en) * | 2015-04-08 | 2015-07-15 | 中联重科股份有限公司 | Damping valve, winching system and engineering machinery |
| CN104925685A (en) * | 2015-06-30 | 2015-09-23 | 中国船舶重工集团公司第七一九研究所 | Winch hydraulic system controlling guide rope through stepless speed regulating constant tension |
| CN107504000A (en) * | 2017-10-12 | 2017-12-22 | 徐州徐工随车起重机有限公司 | A kind of lorry-mounted crane multi-way reversing device |
| CN107504000B (en) * | 2017-10-12 | 2024-01-02 | 徐州徐工随车起重机有限公司 | Multi-way reversing device of lorry-mounted crane |
| CN109095367A (en) * | 2018-09-04 | 2018-12-28 | 徐工集团工程机械有限公司 | hydraulic system and crane |
| CN109516396A (en) * | 2018-12-27 | 2019-03-26 | 江涛 | Hoist engine stand-by power unit |
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