CN204727511U - A kind of luffing range of cantilever support hydraulic efficiency pressure system and hoisting crane - Google Patents
A kind of luffing range of cantilever support hydraulic efficiency pressure system and hoisting crane Download PDFInfo
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- CN204727511U CN204727511U CN201520484018.3U CN201520484018U CN204727511U CN 204727511 U CN204727511 U CN 204727511U CN 201520484018 U CN201520484018 U CN 201520484018U CN 204727511 U CN204727511 U CN 204727511U
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Abstract
The utility model discloses a kind of luffing range of cantilever support hydraulic efficiency pressure system, comprise main pump, main valve, amplitude oil cylinder, the first oil circuit, the second oil circuit, first oil circuit is connected with the first chamber hydraulic fluid port of amplitude oil cylinder, second oil circuit is connected with the second chamber hydraulic fluid port of amplitude oil cylinder, first oil circuit is connected with the first actuator port of main valve, second oil circuit is connected with the second actuator port of main valve, and main pump is connected with the oil inlet of main valve, in the first oil circuit, be provided with pressure-gradient control valve.Also comprise servopump and servo oil circuit, servopump is to servo oil circuit fuel feeding, and servo oil circuit is connected with guide's hydraulic fluid port of pressure-gradient control valve, in servo oil circuit, be provided with hydraulic valve, the aperture of hydraulic valve control presssure control cock.The utility model solves the jib that the frequent opening and closing of balance cock in the past causes and rocks, and improves luffing range of cantilever support manipulation stationarity and fine motion.
Description
Technical field
The utility model relates to engineering machinery field, particularly a kind of luffing range of cantilever support hydraulic efficiency pressure system and hoisting crane.
Background technology
In the luffing range of cantilever support operation of construction machinery and equipment, such as, in car hosit, actuating unit is generally amplitude oil cylinder, is carrying out falling in arm operation, and the closed loop control of general employing hydraulic pressure transferred by jib, and the balance cock that namely the large chamber of amplitude oil cylinder is installed opens oil sources from loculus.But can find in actual applications, due to difference and the jib angle difference of load, in jib decentralization process, often there will be jib fiercely rock, the problems such as fine motion difference.Trace it to its cause, because balance cock opens oil sources from loculus, in decentralization process, main pump delivery rate is to amplitude oil cylinder loculus and the first guide cavity of balance cock, along with little cavity pressure raises, balance cock aperture increases, and then jib lowering velocity is accelerated, but along with the quickening of jib lowering velocity, little cavity pressure is again in minimizing, balance cock aperture and then minimizing, amplitude oil cylinder speed slows down, therefore in whole jib decentralization process, constantly repeat the process of balance cock opening and closing, and then cause jib to rock, and main pump flowrate variation mode is difficult to meet all operating modes, therefore manipulation stationarity and fine motion is had a strong impact on.
Utility model content
In view of this, the utility model proposes a kind of luffing range of cantilever support hydraulic efficiency pressure system and hoisting crane, in jib decentralization process, often there will be jib fiercely rock to solve, have a strong impact on the problem of manipulation stationarity and fine motion.
On the one hand, the utility model provides a kind of luffing range of cantilever support hydraulic efficiency pressure system, comprise main pump, main valve, amplitude oil cylinder, first oil circuit, second oil circuit, first oil circuit is connected with the first chamber hydraulic fluid port of amplitude oil cylinder, second oil circuit is connected with the second chamber hydraulic fluid port of amplitude oil cylinder, first oil circuit is connected with the first actuator port of main valve, second oil circuit is connected with the second actuator port of main valve, main pump is connected with the oil inlet of main valve, pressure-gradient control valve is provided with in the first oil circuit, also comprise servopump and servo oil circuit, servopump is to servo oil circuit fuel feeding, servo oil circuit is connected with guide's hydraulic fluid port of pressure-gradient control valve, hydraulic valve is provided with in servo oil circuit, the aperture of hydraulic valve control presssure control cock.
Further, in order to prevent amplitude oil cylinder second chamber, inhale empty below jib in process, comprise controller and pressure sensor, pressure sensor is arranged on amplitude oil cylinder or the second oil circuit, pressure sensor detects the second chamber hydraulic fluid port pressure of amplitude oil cylinder, and controller obtains pressure sensor signal, controls discharge of main pump.
Further, if pressure sensor detects the second chamber hydraulic fluid port pressure be less than setting value, controller increases discharge of main pump, if pressure sensor detects the second chamber hydraulic fluid port pressure be greater than setting value, controller reduces discharge of main pump.
Further, in jib decentralization process, the first oil circuit is oil return circuit, and the second oil circuit is oil-feed oil circuit; Upwards lift in process at jib, the first oil circuit is oil-feed oil circuit, and the second oil circuit is oil return circuit.
Further, pressure-gradient control valve is balance cock, and guide's hydraulic fluid port of balance cock is connected with servo oil circuit, and the oil inlet and outlet of balance cock is connected with the first oil circuit.
Further, hydraulic valve is electric proportional pressure-reducing valve or electric proportional pressure control valve or proportional reversing valve, and hydraulic valve regulates the guide oil mouth pressure of pressure-gradient control valve.
Further, main valve is three position four-way directional control valve, and three position four-way directional control valve meta function is Y type.
Further, comprise fuel tank, fuel tank is connected with the return opening of main valve, and the second chamber of amplitude oil cylinder is rod chamber, and the first chamber of amplitude oil cylinder is rodless cavity.
In addition, the utility model additionally provides a kind of hoisting crane, comprises above-mentioned luffing range of cantilever support hydraulic efficiency pressure system.
Further, comprise body and jib, jib and body hinged, cylinder barrel and the body of amplitude oil cylinder are hinged, and piston rod and the jib of amplitude oil cylinder are hinged.
The utility model proposes a kind of luffing range of cantilever support hydraulic efficiency pressure system and hoisting crane, solve in jib decentralization process and often there will be jib and fiercely rock, have a strong impact on the problem of manipulation stationarity and fine motion.First through repeatedly analyzing and test the reason that have found jib and fiercely rock, and proposition solves the technical scheme that jib fiercely rocks.Solution of the present utility model is: by the openings of sizes of the hydraulic valve control presssure control cock in servo oil circuit.Hydraulic valve can be electric proportional pressure-reducing valve or electric proportional pressure control valve or proportional reversing valve etc., and pressure-gradient control valve can be pilot overflow valve, balance cock, one way sequence valve, reducing valve equipressure control cock.Hydraulic valve regulates the guide oil mouth pressure of pressure-gradient control valve.Thus control amplitude oil cylinder oil return speed, avoid the jib that the frequent opening and closing of balance cock in the past causes and rock, improve luffing range of cantilever support manipulation stationarity and fine motion.
In addition, pressure-gradient control valve also can be arranged in the first oil circuit and the second oil circuit simultaneously.Each pressure-gradient control valve all adopts the hydraulic valve in a servo oil circuit to regulate the guide oil mouth pressure of pressure-gradient control valve.
In further technical scheme, in order to prevent amplitude oil cylinder second chamber, inhale empty below jib in process.Detect amplitude oil cylinder second cavity pressure by pressure sensor, regulate main pump delivery rate in real time, guarantee that amplitude oil cylinder is in friction speed jib decentralization process, the second cavity pressure is stable does not inhale sky.
Luffing range of cantilever support hydraulic efficiency pressure system of the present utility model can be applied to hoisting crane, also can be applied in other machinery, such as: in the equipment such as concrete pump truck, ladder truck, fire extinguishing tanker.
Accompanying drawing explanation
The accompanying drawing forming a part of the present utility model is used to provide further understanding of the present utility model, and schematic description and description of the present utility model, for explaining the utility model, is not formed improper restriction of the present utility model.In the accompanying drawings:
Fig. 1 is the utility model luffing range of cantilever support Hydraulic System Principle schematic diagram.
Detailed description of the invention
It should be noted that, when not conflicting, the embodiment in the utility model and the feature in embodiment can combine mutually.Below with reference to the accompanying drawings and describe the utility model in detail in conjunction with the embodiments.
Below in conjunction with Fig. 1; preferred embodiment of the present utility model is described in further detail; the luffing range of cantilever support hydraulic efficiency pressure system of this preferred embodiment, the first often there will be jib with solution and fiercely rocks in jib decentralization process, has a strong impact on the problem of manipulation stationarity and fine motion.
As shown in Figure 1, luffing range of cantilever support hydraulic efficiency pressure system specifically comprises: main pump 5, main valve 4, amplitude oil cylinder 1, fuel tank, first oil circuit, second oil circuit, first oil circuit is connected with the first chamber hydraulic fluid port of amplitude oil cylinder 1, second oil circuit is connected with the second chamber hydraulic fluid port of amplitude oil cylinder 1, first oil circuit is connected with the first actuator port B of main valve 4, second oil circuit is connected with the second actuator port A of main valve 4, main pump 5 is connected with the oil inlet P of main valve 4, fuel tank is connected with the oil return inlet T of main valve 4, pressure-gradient control valve 2 is provided with in the first oil circuit, pressure-gradient control valve 2 oil inlet and outlet A, B is connected with the first oil circuit.In this hydraulic efficiency pressure system, main pump 5, main valve 4, amplitude oil cylinder 1, fuel tank, the first oil circuit, the second oil circuit form open type hydraulic system.The hydraulic power source of the expanding-contracting action of amplitude oil cylinder 1 is from the hydraulic oil of main pump 5.
In the present embodiment, the second chamber of amplitude oil cylinder 1 is rod chamber, and the first chamber of amplitude oil cylinder 1 is rodless cavity.Rod chamber refers to the chamber of piston rod, and rodless cavity refers to the chamber of piston-rodless.Also loculus is claimed, because rodless cavity volume greatly also claims large chamber because rod chamber volume is little.
When main valve 4 is in right position, first oil circuit is oil return circuit, second oil circuit is oil-feed oil circuit, the hydraulic oil of main pump 5 enters in the second chamber through main valve 4, second oil circuit, hydraulic oil in amplitude oil cylinder 1 first chamber is by the first oil circuit, pressure-gradient control valve 2, main valve 4 oil sump tank, and now jib is transferred under the effect of deadweight.Can control presssure control cock 2 openings of sizes be passed through, control the return oil pressure of the first oil circuit.
When main valve 4 is in left position, the first oil circuit is oil-feed oil circuit, and the second oil circuit is oil return circuit.The hydraulic oil of main pump 5 enters in the first chamber through main valve 4, pressure-gradient control valve 2, first oil circuit, and the hydraulic oil in amplitude oil cylinder 1 second chamber is by the second oil circuit, main valve 4 oil sump tank, and now jib upwards lifts, and pressure-gradient control valve 2 is in one-way conduction state.
Pressure-gradient control valve 2 of the present utility model is balance cock, also can be pilot overflow valve, one way sequence valve, reducing valve equipressure control cock.Pressure-gradient control valve 2 is the valve general names controlling inlet and outlet pressure.
In prior art amplitude oil cylinder hydraulic efficiency pressure system, the pressure oil of guide's hydraulic fluid port X of balance cock comes from the second oil circuit, and the pressure in the second oil circuit changes with the change of jib lowering velocity, and the jib causing the frequent opening and closing of balance cock to cause rocks.In jib decentralization process, often there will be jib fiercely rock to solve, have a strong impact on the problem of manipulation stationarity and fine motion.The utility model adopts outside oil circuit control presssure control cock 2 openings of sizes.As shown in Figure 1, comprise servopump (not shown) and servo oil circuit, servopump is to servo oil circuit fuel feeding, and servo oil circuit is connected with guide's hydraulic fluid port X of pressure-gradient control valve 2, hydraulic valve 3 is provided with, the aperture of hydraulic valve 3 control presssure control cock 2 in servo oil circuit.Hydraulic valve 3 can be electric proportional pressure-reducing valve or electric proportional pressure control valve or proportional reversing valve, and hydraulic valve 3 regulates guide's hydraulic fluid port X pressure of pressure-gradient control valve 2.The oil inlet and outlet of hydraulic valve 3 is connected with P, A servo oil circuit, and the oil return inlet T of hydraulic valve 3 is connected with fuel tank.
Jib is in decentralization process, also claim to fall in arm process, the jib arm speed that falls is determined by luffing electric control handle, along with luffing electric control handle aperture increases, the electric current of hydraulic valve 3 increases, and delivery pressure increases, and then the aperture of pressure-gradient control valve 2 increases, impel amplitude oil cylinder 1 first chamber oil return flow to increase, jib lowering velocity is accelerated.If luffing electric control handle aperture reduces, the electric current of hydraulic valve 3 reduces, and the aperture of pressure-gradient control valve 2 reduces, and impel amplitude oil cylinder 1 first chamber oil return flow to reduce, jib lowering velocity slows down.Therefore, the lowering velocity of jib is determined by luffing electric control handle completely, the size of current of hydraulic valve 3.
Jib is in decentralization process, if jib lowering velocity is too fast, amplitude oil cylinder 1 second chamber can be caused to inhale empty, because pressure-gradient control valve 2 adopts hydraulic pressure opened loop control, namely the unlatching oil sources of balance cock is from hydraulic valve 3, and whole process arm rest frame deadweight realizes amplitude oil cylinder 1 and transfers.Now, amplitude oil cylinder 1 loculus only needs main pump 5 repairing to ensure not inhale sky, and the oil return speed (jib lowering velocity) in large chamber depends on the aperture of balance cock completely.Balance cock plays the effect of dead lock for safety and throttling governing, avoids the problem of the frequent opening and closing of traditional control method balance cock.
Inhale empty problem to solve amplitude oil cylinder 1 second chamber, the utility model also comprises controller and pressure sensor 6, and pressure sensor 6 is arranged in amplitude oil cylinder 1, also can be arranged on the second oil circuit.Pressure sensor 6 detects the loculus hydraulic fluid port pressure of amplitude oil cylinder 1, and controller obtains pressure sensor 6 signal, controls main pump 5 discharge capacity.If pressure sensor 6 detects the second chamber hydraulic fluid port pressure be less than setting value, that is, jib lowering velocity is too fast, and sky may be inhaled in the second chamber, and controller sends to main pump 5 increases the instruction of main pump 5 discharge capacity, and main pump 5 discharge capacity is increased.If pressure sensor 6 detects the second chamber hydraulic fluid port pressure be greater than setting value, controller sends to main pump 5 and reduces the instruction of main pump 5 discharge capacity, and main pump 5 discharge capacity is reduced.
The utility model additionally provides a kind of hoisting crane: comprise body and jib and above-mentioned luffing range of cantilever support hydraulic efficiency pressure system, jib and body hinged, cylinder barrel and the body of amplitude oil cylinder 1 are hinged, and piston rod and the jib of amplitude oil cylinder 1 are hinged.
Luffing range of cantilever support hydraulic efficiency pressure system of the present utility model also can be applied in other machinery, such as: in the equipment such as concrete pump truck, ladder truck, fire extinguishing tanker.
The foregoing is only preferred embodiment of the present utility model; not in order to limit the utility model; all within spirit of the present utility model and principle, any amendment done, equivalent replacement, improvement etc., all should be included within protection domain of the present utility model.
Claims (10)
1. a luffing range of cantilever support hydraulic efficiency pressure system, comprise main pump (5), main valve (4), amplitude oil cylinder (1), first oil circuit, second oil circuit, first oil circuit is connected with the first chamber hydraulic fluid port of amplitude oil cylinder (1), second oil circuit is connected with the second chamber hydraulic fluid port of amplitude oil cylinder (1), first oil circuit is connected with the first actuator port of main valve (4), second oil circuit is connected with the second actuator port of main valve (4), main pump (5) is connected with the oil inlet of main valve (4), pressure-gradient control valve (2) is provided with in the first oil circuit, it is characterized in that, also comprise servopump and servo oil circuit, servopump is to servo oil circuit fuel feeding, servo oil circuit is connected with guide's hydraulic fluid port of pressure-gradient control valve (2), hydraulic valve (3) is provided with in servo oil circuit, the aperture of hydraulic valve (3) control presssure control cock (2).
2. luffing range of cantilever support hydraulic efficiency pressure system according to claim 1, it is characterized in that, comprise controller and pressure sensor (6), pressure sensor (6) is arranged on amplitude oil cylinder (1) or the second oil circuit, pressure sensor (6) detects the second chamber hydraulic fluid port pressure of amplitude oil cylinder (1), controller obtains pressure sensor (6) signal, controls main pump (5) discharge capacity.
3. luffing range of cantilever support hydraulic efficiency pressure system according to claim 2, it is characterized in that, if pressure sensor (6) detects the second chamber hydraulic fluid port pressure be less than setting value, controller increases main pump (5) discharge capacity, if pressure sensor (6) detects the second chamber hydraulic fluid port pressure be greater than setting value, controller reduces main pump (5) discharge capacity.
4. luffing range of cantilever support hydraulic efficiency pressure system according to claim 3, is characterized in that, in jib decentralization process, the first oil circuit is oil return circuit, and the second oil circuit is oil-feed oil circuit; Upwards lift in process at jib, the first oil circuit is oil-feed oil circuit, and the second oil circuit is oil return circuit.
5. the luffing range of cantilever support hydraulic efficiency pressure system according to Claims 1-4 any one, is characterized in that, pressure-gradient control valve (2) is balance cock, and guide's hydraulic fluid port of balance cock is connected with servo oil circuit, and the oil inlet and outlet of balance cock is connected with the first oil circuit.
6. the luffing range of cantilever support hydraulic efficiency pressure system according to Claims 1-4 any one, it is characterized in that, hydraulic valve (3) regulates the guide oil mouth pressure of pressure-gradient control valve (2) for electric proportional pressure-reducing valve or electric proportional pressure control valve or proportional reversing valve, hydraulic valve (3).
7. the luffing range of cantilever support hydraulic efficiency pressure system according to Claims 1-4 any one, is characterized in that, main valve (4) is three position four-way directional control valve, and three position four-way directional control valve meta function is Y type.
8. the luffing range of cantilever support hydraulic efficiency pressure system according to Claims 1-4 any one, it is characterized in that, comprise fuel tank, fuel tank is connected with the return opening of main valve (4), second chamber of amplitude oil cylinder (1) is rod chamber, and the first chamber of amplitude oil cylinder (1) is rodless cavity.
9. a hoisting crane, is characterized in that, comprises the luffing range of cantilever support hydraulic efficiency pressure system as described in claim 1 to 8 any one.
10. hoisting crane according to claim 9, is characterized in that, comprises body and jib, jib and body hinged, cylinder barrel and the body of amplitude oil cylinder (1) are hinged, and piston rod and the jib of amplitude oil cylinder (1) are hinged.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201520484018.3U CN204727511U (en) | 2015-07-02 | 2015-07-02 | A kind of luffing range of cantilever support hydraulic efficiency pressure system and hoisting crane |
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| CN201520484018.3U CN204727511U (en) | 2015-07-02 | 2015-07-02 | A kind of luffing range of cantilever support hydraulic efficiency pressure system and hoisting crane |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104986675A (en) * | 2015-07-02 | 2015-10-21 | 浙江三一装备有限公司 | Boom variable-amplitude hydraulic system and crane |
| CN110939620A (en) * | 2019-12-31 | 2020-03-31 | 湖南星邦智能装备股份有限公司 | Cantilever crane type aerial working equipment and cantilever crane lifting hydraulic system thereof |
-
2015
- 2015-07-02 CN CN201520484018.3U patent/CN204727511U/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104986675A (en) * | 2015-07-02 | 2015-10-21 | 浙江三一装备有限公司 | Boom variable-amplitude hydraulic system and crane |
| CN110939620A (en) * | 2019-12-31 | 2020-03-31 | 湖南星邦智能装备股份有限公司 | Cantilever crane type aerial working equipment and cantilever crane lifting hydraulic system thereof |
| CN110939620B (en) * | 2019-12-31 | 2022-04-05 | 湖南星邦智能装备股份有限公司 | Cantilever crane type aerial working equipment and cantilever crane lifting hydraulic system thereof |
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