CN111115448A

CN111115448A - Crane hydraulic system and working method

Info

Publication number: CN111115448A
Application number: CN201811289896.4A
Authority: CN
Inventors: 王江; 陈懿; 梁兆环; 郭安罗; 郭小飞
Original assignee: South China Marine Machinery Co Ltd
Current assignee: South China Marine Machinery Co Ltd
Priority date: 2018-10-31
Filing date: 2018-10-31
Publication date: 2020-05-08

Abstract

The invention relates to a crane, in particular to a crane hydraulic system and a working method thereof, wherein the crane hydraulic system comprises a hydraulic oil tank, a main pump assembly, a switch assembly, a rotary system for driving a rotary mechanism, a main hoisting system for driving a main hoisting winch, an auxiliary hoisting system for driving an auxiliary hoisting winch, an amplitude-changing system for driving an amplitude-changing winch and a cable-stabilizing system for driving a cable-stabilizing winch; the input end of the main pump assembly is connected with a hydraulic oil tank, and the output end of the main pump assembly supplies oil to the amplitude varying system, the main lifting system, the auxiliary lifting system, the rotary system and the cable stabilizing system through the switch assembly; the invention reduces the influence of impacting the crane hydraulic system when the load swings and shakes, balances the pressure of the crane hydraulic system and improves the safety and stability of the crane hydraulic system.

Description

Crane hydraulic system and working method

Technical Field

The invention relates to a crane, in particular to a crane hydraulic system and a working method.

Background

The marine crane is a special crane for carrying out transportation operation in the marine environment, and is mainly used for important tasks of transportation and transfer of goods among ships, marine supply, throwing and recovering of underwater operation equipment and the like. Marine cranes are typically controlled using a crane hydraulic system. In the working process, the ship body pitches, rolls and ascends and descends along with sea waves, the motions lead to the load to swing and shake, the load swings and shakes to form huge impact on a hydraulic system, and the crane hydraulic system is unstable.

The hydraulic system of the crane provides power and brake for the main hoisting winch, the auxiliary main hoisting winch, the amplitude-variable winch and the rotary platform. When the oil pressure is suddenly increased and the pressure of a hydraulic system of the crane is unbalanced, hydraulic elements can be out of work or damaged, oil leakage of an oil pipe can be caused, and even the oil pipe is cracked, so that the safety of operation can be seriously threatened. If the hydraulic element fails or is damaged, the pressure of a hydraulic system can be suddenly relieved, and the safety accident of falling of goods occurs. Therefore, the safety performance and the stability of the hydraulic system of the marine crane are improved, and the method has great significance.

Disclosure of Invention

In order to solve the problems in the prior art, the invention provides a crane hydraulic system and a working method thereof, which can reduce the influence of impact on the crane hydraulic system when a load swings and shakes, balance the pressure of the crane hydraulic system and improve the safety and stability of the crane hydraulic system.

In order to achieve the purpose, the technical scheme of the invention is as follows: a hydraulic system of a crane comprises a hydraulic oil tank, a main pump assembly, a switch assembly, a rotary system for driving a rotary mechanism, a main hoisting system for driving a main hoisting winch, an auxiliary hoisting system for driving an auxiliary hoisting winch, an amplitude-changing system for driving an amplitude-changing winch and a cable-stabilizing system for driving a cable-stabilizing winch; the hydraulic oil tank provides hydraulic oil for the whole crane hydraulic system, the main pump assembly provides hydraulic oil for the whole crane hydraulic system, and the switch assembly, the rotating system, the main lifting system, the auxiliary lifting system, the amplitude varying system and the cable stabilizing system are mutually matched to drive each action mechanism to finish various actions of lifting, moving and putting down goods of the crane.

The input end of the main pump assembly is connected with a hydraulic oil tank, and the output end of the main pump assembly supplies oil to the amplitude varying system, the main lifting system, the auxiliary lifting system, the rotary system and the cable stabilizing system through the switch assembly; therefore, the main pump assembly absorbs hydraulic oil from the hydraulic oil tank, converts mechanical energy into hydraulic pressure energy and provides power for each system.

The main pump assembly comprises more than one main hydraulic pump, and all the main hydraulic pumps are driven by the same motor; the multiple main hydraulic pumps are used for providing larger power for a crane hydraulic system, and the multiple main hydraulic pumps are driven by the same motor, so that the rotating speeds of the main hydraulic pumps are the same, and stable hydraulic oil pressure can be provided.

The switch assembly is a hydraulic control proportional multi-way valve; the hydraulic control proportional multi-way valve controls the actions of a plurality of control systems according to the requirements of a crane hydraulic system, and has compact structure and long service life.

The rotary system comprises a first rotary hydraulic motor, a second rotary hydraulic motor, a first rotary balance valve bank, a second rotary balance valve bank and a rotary brake pipeline; the hydraulic control proportional multi-way valve is respectively connected with one end of a first rotary hydraulic motor and one end of a second rotary hydraulic motor through a right oil supply pipeline, the hydraulic control proportional multi-way valve is respectively connected with the other end of the first rotary hydraulic motor and the other end of the second rotary hydraulic motor through a left oil supply pipeline, a first rotary balance valve group is arranged between the right oil supply pipeline of the first rotary hydraulic motor and the left oil supply pipeline of the second rotary hydraulic motor, a second rotary balance valve group is arranged between the left oil supply pipeline of the first rotary hydraulic motor and the right oil supply pipeline of the second rotary hydraulic motor, the first rotary hydraulic motor and the second rotary hydraulic motor are respectively provided with a rotary brake mechanism, a rotary brake pipeline is arranged between the first rotary balance valve group and the rotary brake mechanism, and a rotary brake pressure reducing valve is sequentially arranged on the rotary brake pipeline, a rotary brake reversing valve and a rotary brake speed regulating valve; the hydraulic control proportional multi-way valve controls the flow direction of hydraulic oil of the rotary system in a right oil supply pipeline and a left oil supply pipeline, so that the rotation directions of the first rotary hydraulic motor and the second rotary hydraulic motor are controlled, and the rotary mechanism rotates leftwards or rightwards; the first rotary balance valve group and the second rotary balance valve group adjust the pressure and flow of the first rotary hydraulic motor and the second rotary hydraulic motor in the right oil supply pipeline and the left oil supply pipeline, and ensure the stable pressure and flow entering the first rotary hydraulic motor and the second rotary hydraulic motor, so that the first rotary hydraulic motor and the second rotary hydraulic motor simultaneously act, the rotating speeds are consistent, and the rotary mechanism acts stably; the rotary brake pipeline obtains hydraulic oil through the input end of the first rotary balance valve group, the hydraulic oil is decompressed through the rotary brake pressure reducing valve to prevent overlarge pressure and adjust the oil pressure input to the rotary brake mechanism, when the control end of the rotary brake reversing valve has the output hydraulic oil from the rotary brake pressure reducing valve, the rotary brake reversing valve is automatically connected with the rotary brake speed regulating valve in a transposition mode, the rotary brake speed regulating valve is used for adjusting the flow passing through, the speed of the rotary brake mechanism for releasing the brake is accurately controlled, and meanwhile, the influence of the change of the rotary brake mechanism on the flow is eliminated; when the rotary brake mechanism needs to stop, the rotary brake pipeline stops supplying oil to the rotary brake reversing valve, the rotary brake reversing valve resets, hydraulic oil of the rotary brake mechanism flows back to an oil tank from the rotary brake reversing valve through the rotary brake speed regulating valve to play a role in unloading oil, braking in the rotary process until the rotary brake mechanism stops is realized, and the rotary brake mechanism plays a role in back pressure on the unloading oil of the rotary brake mechanism due to the arrangement of the rotary brake speed regulating valve in the oil unloading process, so that the rotary brake mechanism is prevented from rapidly braking due to rapid oil unloading of the rotary brake mechanism, the phenomenon of sudden stop is avoided, and a crane hydraulic system is better protected.

The main lifting system comprises a main lifting motor, a main pump assembly supplies oil to the main lifting motor through a hydraulic control proportional multi-way valve, the hydraulic control proportional multi-way valve is connected with one end of the main lifting motor through a main hook lifting pipeline, and the hydraulic control proportional multi-way valve is connected with the other end of the main lifting motor through a main hook descending pipeline; a back pressure balance valve is connected between the main lifting motor and the main hook lifting pipeline; the main lifting motor is provided with a main lifting motor brake mechanism, and an oil circuit of the main lifting motor brake mechanism is connected into a main hook ascending pipeline and a main hook descending pipeline through a main lifting shuttle valve; a main lifting brake pressure reducing valve and a main lifting brake reversing valve are sequentially arranged on an oil circuit of the main lifting motor brake mechanism; and a main lifting one-way valve is connected in parallel with the main lifting brake pressure reducing valve and the main lifting reversing valve. The main pump assembly provides hydraulic oil for the hydraulic control proportional multi-way valve, and the hydraulic control proportional multi-way valve controls the flowing direction of the hydraulic oil entering the main hook ascending pipeline and the main hook descending pipeline, so that the rotating direction of the main lifting motor is controlled, and ascending and descending actions of the main hook are realized. When the main hook descends, the overflow valve is arranged in the backpressure balance valve, the overflow valve is connected with the one-way valve in parallel, when the main hook descends, hydraulic oil coming out of the main lifting motor can only pass through the overflow valve, the overflow valve can provide certain backpressure, and therefore the main hook can be prevented from descending quickly due to quick oil unloading of the main lifting motor, and the heavy object can descend quickly, so that the heavy object can descend stably. The main hoisting motor brake mechanism always stops the main hoisting winch from acting when the main hoisting winch does not act, so that the safety accident caused by the sudden failure of the main hoisting system is prevented; the main lifting motor brake mechanism oil circuit can obtain hydraulic oil through the main lifting shuttle valve no matter the main lifting motor brake mechanism oil circuit is fed through the main lifting shuttle valve into the main hook lifting pipeline and the main hook descending pipeline, the hydraulic oil obtained from the main lifting motor brake mechanism oil circuit is decompressed through the main lifting brake decompression valve, the hydraulic oil of the main lifting motor brake mechanism oil circuit controls the main lifting brake reversing valve to automatically shift to enable the hydraulic oil to enter the main lifting motor brake mechanism, the main lifting motor brake mechanism obtains the power of pushing the brake, and the main lifting winch can work after the brake is pushed. The main lifting brake pressure reducing valve and the main lifting reversing valve are connected in parallel with a main lifting one-way valve, when the oil pressure from the main lifting reversing valve is too large, the main lifting one-way valve is pushed open, and part of hydraulic oil flows back to the pressure reducing input end of the main lifting brake pressure reducing valve to be reduced in pressure through the main lifting pressure reducing valve, so that a main lifting system is further protected.

The auxiliary lifting system comprises an auxiliary lifting hydraulic motor and an anti-shake valve; the hydraulic control proportional multi-way valve is connected with one end of the auxiliary lifting hydraulic motor through an auxiliary hook ascending pipeline, the hydraulic control proportional multi-way valve is connected with the other end of the auxiliary lifting hydraulic motor through an auxiliary hook descending pipeline, and an anti-shake valve is arranged between the auxiliary hook descending pipeline and the auxiliary lifting hydraulic motor; the auxiliary lifting hydraulic motor is provided with an auxiliary lifting motor brake mechanism and a disc brake mechanism, an oil circuit of the auxiliary lifting motor brake mechanism is connected into an auxiliary hook lifting pipeline and an auxiliary hook descending pipeline through an auxiliary lifting shuttle valve, and an auxiliary lifting brake pressure reducing valve and an auxiliary lifting brake reversing valve are sequentially arranged on an oil circuit of the auxiliary lifting brake mechanism; the two ends of the series connection of the auxiliary lifting brake pressure reducing valve and the auxiliary lifting brake reversing valve are connected in parallel with an auxiliary lifting one-way valve; a disc brake control system is arranged between the hydraulic oil tank and the disc brake mechanism and is respectively communicated with the auxiliary hook ascending pipeline and the auxiliary hook descending pipeline through a disc brake shuttle valve; the anti-shake valve comprises a valve core, a valve body arranged in the valve core, a spring and a push block, wherein the valve core is provided with an A port and a B port, a valve cavity communicated with the A port and the B port is formed in the valve core, the A port is communicated with an auxiliary lifting hydraulic motor, the B port is communicated with an auxiliary hook descending pipeline, the push block is arranged in the valve cavity, the spring is arranged between the valve core and the push block, the valve core is blocked at the B port under the action of the spring in a non-working state, and the A port is communicated with the valve cavity. The hydraulic control proportional multi-way valve controls the flowing direction of hydraulic oil entering the auxiliary hook ascending pipeline and the auxiliary hook descending pipeline, so that the rotating direction of the auxiliary lifting hydraulic motor is controlled, and the ascending and descending actions of the auxiliary hook are realized. The auxiliary hoisting motor brake mechanism and the disc brake mechanism always stop the action of the auxiliary hoisting winch when the auxiliary hoisting winch does not act, so that safety accidents of an auxiliary hoisting system are prevented; the oil circuit of the auxiliary lifting brake mechanism obtains hydraulic oil through an auxiliary lifting shuttle valve, so that the oil circuit of the auxiliary lifting motor brake mechanism can obtain the hydraulic oil no matter the oil is fed into an auxiliary hook lifting pipeline or an auxiliary hook descending pipeline, the hydraulic oil passing through the auxiliary lifting shuttle valve is decompressed through an auxiliary lifting brake decompression valve, the hydraulic oil from the auxiliary lifting brake decompression valve enables an auxiliary lifting brake reversing valve to automatically shift to input the hydraulic oil into the auxiliary lifting motor brake mechanism, the auxiliary lifting motor brake mechanism obtains power for pushing away a brake, and simultaneously a disc brake control system is started to control the disc brake mechanism to be opened, and after the auxiliary lifting motor brake mechanism and the disc brake mechanism are released, the auxiliary lifting winch can work; and the auxiliary lifting brake pressure reducing valve and the auxiliary lifting reversing valve are connected in parallel with an auxiliary lifting one-way valve, and when the oil pressure from the auxiliary lifting brake reversing valve is too large, the auxiliary lifting one-way valve is pushed to return to the pressure reducing input end of the auxiliary lifting brake pressure reducing valve for pressure reduction, so that an auxiliary lifting system is further protected. When the crane rises, hydraulic oil enters the auxiliary lifting hydraulic motor and then enters the valve cavity through the anti-shake valve port A, when the hydraulic oil pressure in the valve cavity is smaller than the elastic force of the spring, the valve body is blocked at the port B under the action of the spring, the hydraulic oil cannot be discharged from the port B, when the hydraulic oil pressure in the valve cavity is larger than the elastic force of the spring, the hydraulic oil acts on the push block, the push block drives the spring to move towards the push block, the acting force of the spring on the valve body is reduced or eliminated, the valve body is opened under the pressure action of the hydraulic oil, the port A is communicated with the port B, the purposes of controlling the return flow rate of the hydraulic oil, controlling the speed and the like are achieved, and the phenomenon that the auxiliary hook is unstable or shakes. If the hydraulic oil enters from the port B and is discharged from the port A, the hydraulic oil can push the valve body open by overcoming the elastic force of the spring, and the oil control effect is achieved.

The amplitude varying system comprises a first amplitude varying hydraulic motor, a second amplitude varying hydraulic motor, a first amplitude varying balance valve and a second amplitude varying balance valve; the hydraulic control proportional multi-way valve is respectively connected with one end of the first variable-amplitude hydraulic motor and one end of the second variable-amplitude hydraulic motor through a variable-amplitude ascending oil supply pipeline, the hydraulic control proportional multi-way valve is respectively connected with the other end of the first variable-amplitude hydraulic motor and the other end of the second variable-amplitude hydraulic motor through a variable-amplitude descending oil supply pipeline, a first variable-amplitude balance valve is arranged on the variable-amplitude ascending oil supply pipeline communicated with the first variable-amplitude hydraulic motor, and a second variable-amplitude balance valve is arranged on the variable-amplitude ascending oil supply pipeline communicated with the second variable-amplitude hydraulic; the first amplitude-variable hydraulic motor and the second amplitude-variable hydraulic motor are provided with amplitude-variable motor brake mechanisms, oil passages of the amplitude-variable motor brake mechanisms are connected into an amplitude-variable ascending oil supply pipeline and an amplitude-variable descending oil supply pipeline through amplitude-variable shuttle valves, and amplitude-variable brake pressure reducing valves and amplitude-variable brake reversing valves are sequentially arranged on the oil passages of the amplitude-variable brake mechanisms; two ends of the amplitude-variable brake pressure-reducing valve and the amplitude-variable brake reversing valve which are connected in series are connected in parallel with an amplitude-variable one-way valve. The hydraulic control proportional multi-way valve controls the flow direction of hydraulic oil entering the amplitude-variable ascending oil supply pipeline and the amplitude-variable descending oil supply pipeline, so that the rotation directions of the first amplitude-variable hydraulic motor and the second amplitude-variable hydraulic motor are controlled, and the ascending and descending actions of the suspension arm are realized; the first amplitude-variable balance valve and the second amplitude-variable balance valve ensure that the flow rates of hydraulic oil entering the first amplitude-variable hydraulic motor and the second amplitude-variable hydraulic motor are consistent, so that the rotating speeds of the first amplitude-variable hydraulic motor and the second amplitude-variable hydraulic motor are controlled to be consistent; the amplitude-variable motor braking mechanism always stops the amplitude-variable winch from acting when the amplitude-variable winch does not act, so that safety accidents of an amplitude-variable system are prevented; the hydraulic path of the variable-amplitude motor brake mechanism obtains hydraulic oil through the variable-amplitude shuttle valve, so that no matter the hydraulic oil enters from the variable-amplitude ascending oil supply pipeline or the variable-amplitude descending oil supply pipeline, the hydraulic oil on the variable-amplitude brake mechanism can be obtained, the hydraulic oil passing through the variable-amplitude shuttle valve is decompressed through the variable-amplitude brake decompression valve, the control end of the variable-amplitude brake reversing valve is controlled by the decompressed hydraulic oil to be automatically transposed, so that the hydraulic oil enters the variable-amplitude motor brake mechanism from the variable-amplitude brake reversing valve, the variable-amplitude motor brake mechanism obtains the power of pushing the brake, and the variable-amplitude winch can; the amplitude-variable brake pressure-reducing valve and the amplitude-variable brake reversing valve are connected in parallel with an amplitude-variable one-way valve, and when the oil pressure from the amplitude-variable reversing valve is too high, the amplitude-variable one-way valve is pushed to return to the input end of the amplitude-variable brake pressure-reducing valve for pressure reduction, so that an amplitude-variable system is further protected.

The cable stabilizing system comprises a cable stabilizing hydraulic motor, a cable stabilizing balance valve and a cable stabilizing hydraulic motor rotating speed control system; the hydraulic control proportional multi-way valve is connected with one end of the cable-stabilizing hydraulic motor through a retracting oil supply pipeline, the hydraulic control proportional multi-way valve is connected with the other end of the cable-stabilizing hydraulic motor through an exhausting oil supply pipeline, and a cable-stabilizing balance valve is arranged between the cable-stabilizing hydraulic motor and the retracting oil supply pipeline; the speed control system of the cable-stabilized hydraulic motor controls the speed of releasing the cable-stabilized hydraulic motor by controlling the displacement of the cable-stabilized hydraulic motor. The hydraulic control proportion multi-way valve controls the flow direction of hydraulic oil entering the retracting oil supply pipeline and the releasing oil supply pipeline, thereby controlling the rotation direction of the cable stabilizing hydraulic motor and realizing the retracting and releasing actions of a cable stabilizing; the swing amplitude of the main hook is controlled through the speed control of the retraction of the cable stabilizer, and the speed of the cable stabilizer hydraulic motor rotating speed control system is used for accurately controlling the speed of releasing the cable stabilizer according to the swing amplitude of the on-site main hook, so that the phenomenon that the main hook shakes too much when lifting goods is prevented.

Furthermore, more than one right confluence valve block is connected between the right oil supply pipe of the first rotary hydraulic motor and the right oil supply pipe of the second rotary hydraulic motor, and more than one left confluence valve block is connected between the left oil supply pipe of the first rotary hydraulic motor and the left oil supply pipe of the second rotary hydraulic motor. The centralized oil supply and the centralized oil return are realized through the rightward confluence valve block and the leftward confluence valve block, the pressure of the rightward oil supply pipe is consistent, the pressure of the leftward oil supply pipe is consistent, and the first rotary hydraulic motor and the second rotary hydraulic motor are guaranteed to obtain consistent driving pressure, so that the first rotary hydraulic motor and the second rotary hydraulic motor work synchronously.

Furthermore, four main lifting motors are arranged, main hook ascending pipelines of the four main lifting motors are communicated with each other through a first main lifting confluence valve block, and main hook descending pipelines of the four main lifting motors are communicated with each other through a second main lifting confluence valve block. Four main lifting motors are arranged to drive the main lifting winch, so that the main lifting winch obtains higher lifting capacity; the first main lifting confluence valve block and the second main lifting confluence valve block realize centralized oil supply and centralized oil return, and the four main lifting motors obtain the same driving force, so that the four main lifting motors work synchronously and drive the main lifting winch to work stably.

Furthermore, the two auxiliary lifting hydraulic motors are arranged, the auxiliary hook ascending pipelines of the two auxiliary lifting hydraulic motors are communicated with each other through the first auxiliary lifting confluence valve block, and the auxiliary hook descending pipelines of the two auxiliary lifting hydraulic motors are communicated with each other through the second auxiliary lifting confluence valve block. Two sets of auxiliary lifting hydraulic motors are arranged to drive the auxiliary lifting winches, the lifting capacity of the auxiliary lifting winches is improved, the first auxiliary lifting confluence valve block and the second auxiliary lifting confluence valve block are used for supplying oil and returning oil in a centralized mode, the auxiliary lifting hydraulic motors obtain the same driving force, the auxiliary lifting hydraulic motors are synchronous in work, and the auxiliary lifting winches are driven to work stably.

Further, the disc brake control system comprises a disc brake hydraulic pump, a disc brake reversing valve group, a disc brake control shuttle valve, a disc brake energy accumulator valve block, a disc brake energy accumulator, a Y-shaped three-position four-way reversing valve, a disc brake hydraulic control reversing valve, a disc brake oil inlet and oil outlet shuttle valve and a three-way valve; the input end of a disc brake hydraulic pump is communicated with a hydraulic oil tank, the output end of the disc brake hydraulic pump is communicated with a disc brake reversing valve group, two input ends of a disc brake control shuttle valve are communicated with the disc brake reversing valve group, the output end of the disc brake control shuttle valve is communicated with a disc brake energy accumulator valve block, a disc brake energy accumulator is communicated with the disc brake energy accumulator valve block, the output end of the disc brake energy accumulator valve block is respectively communicated with the 1 end of a three-way valve and the P port of a Y-shaped three-position four-way reversing valve, the A port of the Y-shaped three-position four-way reversing valve is communicated with the first end of a disc brake oil inlet and oil outlet shuttle valve, the B port of the Y-shaped three-position four-way reversing valve is communicated with the 2 port of the disc brake hydraulic control reversing valve, the 3 port of the disc brake hydraulic control reversing valve is communicated with the second end of the disc brake oil inlet and oil outlet shuttle valve, the 4 port of the disc brake hydraulic oil control reversing valve is communicated with the hydraulic oil, the disc brake oil inlet and outlet shuttle valve is communicated with the 3 end of the three-way valve, and the 2 end of the three-way valve is communicated with the disc brake mechanism. The disc brake hydraulic pump extracts hydraulic oil from a hydraulic oil tank, converts mechanical energy into hydraulic energy, pushes a disc brake control shuttle valve out of a disc brake reversing valve group, enters a disc brake energy accumulator valve block and then is divided into two paths, one path is connected with the disc brake energy accumulator for storing energy, the other path enters a Y-shaped three-position four-way reversing valve from the output end of the disc brake energy accumulator valve block, when an auxiliary hoisting winch hoists goods, a P port and an A port of the Y-shaped three-position four-way reversing valve are communicated, the hydraulic oil enters the A port from the P port and then pushes a disc brake oil inlet and unloading shuttle valve, then enters a2 port from a 3 port of a three-way valve and finally enters a disc brake mechanism to brake, and braking of the auxiliary hoisting winch is relieved; when an auxiliary hoisting winch is needed to hoist a person, the port P and the port B of the Y-shaped three-position four-way reversing valve are communicated, hydraulic oil enters the port B from the port P and then enters the disc brake hydraulic control reversing valve, if the disc brake hydraulic control reversing valve receives a hydraulic control signal, the disc brake hydraulic control reversing valve is switched, the port 2 and the port 3 of the disc brake hydraulic control reversing valve are communicated, the hydraulic oil pushes the disc brake oil inlet and oil discharge shuttle valve to enter the disc brake mechanism through the three-way valve to brake, the brake on the auxiliary hoisting winch is released, and the auxiliary hoisting winch can work; once the auxiliary lifting hydraulic motor works, hydraulic oil is input into the auxiliary hook lifting pipeline or the auxiliary hook descending pipeline, hydraulic oil is input into the disc brake shuttle valve, the hydraulic oil passing through the disc brake shuttle valve enters the control end of the disc brake hydraulic control reversing valve to enable the disc brake hydraulic control reversing valve to change the position, and if the control end of the disc brake hydraulic control reversing valve does not have the hydraulic oil, the disc brake hydraulic control reversing valve resets. If the pressure release suddenly takes place for vice lifting system, do not have hydraulic oil on vice hook ascending pipeline or vice hook downcomer promptly, the hydraulic control switching-over valve of dish brake loses the pilot-operated signal, the hydraulic control switching-over valve transposition of dish brake, 3 mouthfuls and 4 mouthfuls of intercommunication of the hydraulic control switching-over valve of dish brake, the hydraulic oil of the mechanism of dish brake returns hydraulic tank fast through the three-way valve, the oil inlet oil discharge shuttle valve of dish brake and the hydraulic control switching-over valve of dish brake, the vice hoisting winch that rises of quick braking after the pressure release of the mechanism of dish brake, prevent like this that the people from dropping from the sky suddenly. When the Y-shaped three-position four-way reversing valve breaks down, the port 1 and the port 2 of the three-way valve can be communicated through the handle, so that the disc brake mechanism obtains oil pressure to release the brake, the auxiliary hoisting winch works, and the emergency function is achieved.

Further, the disc brake energy accumulator valve block comprises an energy storage check valve, an energy storage hydraulic control reversing valve, a first switch, a second switch, an energy storage overflow valve and a disc brake overflow valve, wherein the input end of the energy storage check valve is communicated with the output end of the disc brake control shuttle valve, the output end of the energy storage check valve is communicated with the control end of the energy storage hydraulic control reversing valve, meanwhile, the output end of the energy storage check valve is communicated with the 1 end of the three-way valve and the P port of the Y-type three-position four-way reversing valve, the output end of the energy storage check valve is communicated with the disc brake energy accumulator through the first switch, the disc brake energy accumulator is communicated with the hydraulic oil tank through the energy storage overflow valve, the disc brake energy accumulator is communicated with the hydraulic oil tank through the second switch, the input end of the energy storage check valve is communicated with the hydraulic oil tank through. The hydraulic oil enters the disc brake energy accumulator valve block from the output end of the disc brake control shuttle valve, when the entering pressure exceeds the set pressure of the energy storage hydraulic control reversing valve, the energy storage hydraulic control reversing valve is switched to communicate the X end in the disc brake overflow valve with the oil tank, at the moment, part of the hydraulic oil overflows from the disc brake overflow valve, and the purpose of controlling the oil pressure entering the disc brake mechanism and the disc brake energy accumulator is achieved. The normally open setting of first switch is converted the energy in the control system of disc brake into compression energy at appropriate opportunity and is stored, when the control system needs of disc brake, converts compression energy into hydraulic energy again and releases, mends the control system of disc brake again, and when the control system of disc brake pressure increase in the twinkling of an eye, it can absorb this partial energy to guarantee that entire system pressure is normal. If the pressure in the disc brake energy accumulator exceeds the set pressure of the energy storage overflow valve, the energy storage overflow valve is connected with the hydraulic oil tank to control the oil pressure of the disc brake energy accumulator, and the disc brake energy accumulator has a safety protection effect. The second switch is normally closed, and when the energy of the disc brake energy accumulator needs to be released or an emergency overpressure condition occurs, the second switch is opened and communicated with the hydraulic oil tank for unloading, so that the disc brake control system is protected from overpressure.

Furthermore, the rotation speed control system of the cable-stabilizing hydraulic motor comprises a first cable-stabilizing overflow valve, a first cable-stabilizing two-position three-way hydraulic control reversing valve and a second cable-stabilizing overflow valve which are sequentially connected; a P port of the first cable-stabilizing overflow valve is connected with a retracting oil supply pipeline through a tension valve block, a T port of the first cable-stabilizing overflow valve is connected with an discharging oil supply pipeline, an X port of the first cable-stabilizing overflow valve is connected with a first cable-stabilizing two-position three-way hydraulic control reversing valve, the first cable-stabilizing two-position three-way hydraulic control reversing valve is connected with a second cable-stabilizing overflow valve, and the second cable-stabilizing overflow valve is connected with a hydraulic oil tank; an X port of the first cable stabilizing overflow valve is connected between the tension valve block and the cable stabilizing balance valve through a bidirectional throttle valve; a cable-stabilizing shuttle valve is connected between the oil supply retracting pipeline and the oil supply discharging pipeline, the outlet end of the cable-stabilizing shuttle valve is connected with a cable-stabilizing pressure reducing valve, the outlet end of the cable-stabilizing pressure reducing valve is connected to the control end of the cable-stabilizing hydraulic motor, the outlet end of the cable-stabilizing pressure reducing valve is connected with a cable-stabilizing electromagnetic valve, the cable-stabilizing electromagnetic valve is connected to the control end of the first cable-stabilizing two-position three-way hydraulic control reversing valve, and meanwhile, the cable-stabilizing electromagnetic valve is. The cable-stabilizing balance valve is arranged, when the hydraulic oil drives the cable-stabilizing hydraulic motor from the oil supply outlet pipeline, back pressure can be provided through the cable-stabilizing balance valve, and quick oil discharge of the cable-stabilizing hydraulic motor is avoided. Under the condition that the cable-stabilizing electromagnetic valve is not electrified, the first cable-stabilizing two-position three-way hydraulic control reversing valve does not act, and in the state, when the oil pressure of the retracting oil supply pipeline exceeds the set pressure of the first cable-stabilizing overflow valve, the first cable-stabilizing overflow valve is communicated with the releasing oil supply pipeline to discharge oil, the stability of the oil pressure of the retracting oil supply pipeline is ensured, and the cable-stabilizing hydraulic motor is protected. The rotating speed control system of the cable-stabilized hydraulic motor obtains control hydraulic oil through a cable-stabilized shuttle valve, the pressure of the output hydraulic oil is ensured to be stable through the pressure reduction of a cable-stabilized pressure reducing valve, the pressure required by the control end of the cable-stabilized hydraulic motor is obtained, and the cable-stabilized hydraulic motor is controlled. If the cable stabilizing electromagnetic valve obtains an electric signal, the cable stabilizing electromagnetic valve is switched to be communicated with the control end of the first cable stabilizing two-position three-way hydraulic control reversing valve, the first cable stabilizing two-position three-way hydraulic control reversing valve obtains a hydraulic control signal for switching, the first cable stabilizing two-position three-way hydraulic control reversing valve is switched to be communicated with the X port of the first cable stabilizing overflow valve, hydraulic oil flows back to the hydraulic oil tank after passing through the second cable stabilizing overflow valve, the flow of the hydraulic oil flowing back to the hydraulic oil tank is controlled by adjusting the second cable stabilizing overflow valve, and the oil pressure entering the cable stabilizing hydraulic motor is controlled, so that the purpose. Therefore, the main hook is stabilized by controlling the tightness of the stable cable, and the situation that the goods hoisted by the main hook are greatly shaken to cause safety accidents is prevented.

Further, the hydraulic control proportional multi-way valve comprises a first reversing valve and a second reversing valve for controlling a first rotary hydraulic motor and a second rotary hydraulic motor in a rotary system, a third reversing valve and a fourth reversing valve for controlling a main hoisting motor in a main hoisting system, a fifth reversing valve and a sixth reversing valve for controlling an auxiliary hoisting hydraulic motor in an auxiliary hoisting system, a seventh reversing valve and an eighth reversing valve for controlling a first luffing hydraulic motor and a second luffing hydraulic motor in a luffing system, and a ninth reversing valve for controlling a cable-stabilizing hydraulic motor in a cable-stabilizing system; the first, second, third, fourth, fifth, sixth, seventh, eighth and ninth are three-position seven-way hydraulic control reversing valves. Different systems are controlled through different reversing valves respectively, the mutual influence is avoided, one system fails, and other systems can still work.

The working method of the hydraulic system of the crane comprises a working method of a rotary system, a working method of a main hoisting system, a working method of an auxiliary hoisting system, a working method of a luffing system and a working method of a cable stabilizing system;

the working method of the rotary system comprises a left rotary working method and a right rotary working method;

the left-turn working method comprises the following steps: firstly, starting a motor, driving a main hydraulic pump to work by the motor, and pumping hydraulic oil into input ends of hydraulic control proportional multi-way valves of a first rotary hydraulic motor and a second rotary hydraulic motor in a control rotary system under the action of the main hydraulic pump; then giving a left-turning signal to the hydraulic control proportional multi-way valve of the first rotary hydraulic motor and the second rotary hydraulic motor in the control rotary system, controlling the hydraulic control proportional multi-way valve of the first rotary hydraulic motor and the second rotary hydraulic motor in the rotary system to open, respectively entering hydraulic oil into the first rotary hydraulic motor and the second rotary hydraulic motor from the hydraulic control proportional multi-way valve of the first rotary hydraulic motor and the second rotary hydraulic motor in the control rotary system to the left oil supply pipeline, returning the hydraulic oil passing through the first rotary hydraulic motor and the second rotary hydraulic motor from the right oil supply pipeline to the hydraulic oil tank through the hydraulic control proportional multi-way valve of the first rotary hydraulic motor and the second rotary hydraulic motor in the control rotary system, and entering a part of the left oil supply pipeline into the rotary brake pipeline while the first rotary hydraulic motor and the second rotary hydraulic motor work, hydraulic oil entering the rotary brake pipeline enters the rotary brake reversing valve through the rotary brake pressure reducing valve, the rotary brake reversing valve is switched under the action of the hydraulic oil in the rotary brake pipeline, the hydraulic oil in the rotary brake pipeline enters the rotary brake mechanism from the rotary brake reversing valve and the rotary brake speed regulating valve, and the rotary brake mechanism is opened; if the hydraulic control proportional multi-way valve for controlling the first rotary hydraulic motor and the second rotary hydraulic motor in the rotary system is reset, the first rotary hydraulic motor and the second rotary hydraulic motor stop working, meanwhile, oil supply is stopped on the rotary brake pipeline, the rotary brake reversing valve is reset, hydraulic oil in the rotary brake mechanism is removed from the rotary brake reversing valve through the rotary brake speed regulating valve, and the rotary brake mechanism is reset to limit the first rotary hydraulic motor and the second rotary hydraulic motor to rotate;

the right-turn working method comprises the following steps: firstly, starting a motor, driving a main hydraulic pump to work by the motor, and pumping hydraulic oil into input ends of hydraulic control proportional multi-way valves of a first rotary hydraulic motor and a second rotary hydraulic motor in a control rotary system under the action of the main hydraulic pump; then giving a right-turn signal to the hydraulic control proportional multi-way valve of the first rotary hydraulic motor and the second rotary hydraulic motor in the control rotary system, controlling the hydraulic control proportional multi-way valve of the first rotary hydraulic motor and the second rotary hydraulic motor in the rotary system to open, respectively entering hydraulic oil into the first rotary hydraulic motor and the second rotary hydraulic motor from the hydraulic control proportional multi-way valve of the first rotary hydraulic motor and the second rotary hydraulic motor in the control rotary system to the right oil supply pipeline, returning the hydraulic oil passing through the first rotary hydraulic motor and the second rotary hydraulic motor from the left oil supply pipeline to the hydraulic oil tank through the hydraulic control proportional multi-way valve of the first rotary hydraulic motor and the second rotary hydraulic motor in the control rotary system, and entering a part of the right oil supply pipeline into the rotary brake pipeline while the first rotary hydraulic motor and the second rotary hydraulic motor work, hydraulic oil entering the rotary brake pipeline enters the rotary brake reversing valve through the rotary brake pressure reducing valve, the rotary brake reversing valve is switched under the action of the hydraulic oil in the rotary brake pipeline, the hydraulic oil in the rotary brake pipeline enters the rotary brake mechanism from the rotary brake reversing valve and the rotary brake speed regulating valve, and the rotary brake mechanism is opened; if the hydraulic control proportional multi-way valve for controlling the first rotary hydraulic motor and the second rotary hydraulic motor in the rotary system is reset, the first rotary hydraulic motor and the second rotary hydraulic motor stop working, meanwhile, oil supply is stopped on the rotary brake pipeline, the rotary brake reversing valve is reset, hydraulic oil in the rotary brake mechanism is removed from the rotary brake reversing valve through the rotary brake speed regulating valve, and the rotary brake mechanism is reset to limit the first rotary hydraulic motor and the second rotary hydraulic motor to rotate;

the working method of the main hoisting system comprises a main hoisting working method and a main descending working method;

the main lifting working method comprises the following steps: firstly, starting a motor, driving a main hydraulic pump to work by the motor, and pumping hydraulic oil to an input end of a hydraulic control proportional multi-way valve for controlling a main lifting motor in a main lifting system under the action of the main hydraulic pump; then, a lifting signal is given to a hydraulic control proportional multi-way valve for controlling a main lifting motor in the main lifting system, the hydraulic control proportional multi-way valve of the main lifting motor in the main lifting system is controlled to be opened, hydraulic oil enters the main lifting motor from the hydraulic control proportional multi-way valve for controlling the main lifting motor in the main lifting system through a main hook lifting pipeline and a back pressure balance valve, the hydraulic oil passing through the main lifting motor returns to a hydraulic oil tank from a main hook descending pipeline through the hydraulic control proportional multi-way valve for controlling the main lifting motor in the main lifting system, when the main lifting motor works, a part of the hydraulic oil in the main hook lifting pipeline opens a shuttle valve, the hydraulic oil entering the shuttle valve enters a main lifting brake reversing valve through a main lifting brake reducing valve, the hydraulic oil reaching the main lifting brake reversing valve enables the main lifting brake valve to be transposed through a control end of the main lifting brake reversing valve, and the hydraulic oil entering the main lifting brake reversing valve enters the main lifting brake mechanism through the main lifting brake, opening a main lifting brake mechanism; if the hydraulic control proportional multi-way valve of the main lifting motor in the main lifting system is controlled to reset, the main lifting motor stops working, meanwhile, oil supply on a brake pipeline of the main lifting motor is stopped, the main lifting brake reversing valve resets, hydraulic oil in the main lifting brake mechanism is removed through the main lifting brake reversing valve, and the main lifting motor brake mechanism resets to limit the main lifting motor to rotate;

the main descending working method comprises the following steps: firstly, starting a motor, driving a main hydraulic pump to work by the motor, and pumping hydraulic oil to an input end of a hydraulic control proportional multi-way valve for controlling a main lifting motor in a main lifting system under the action of the main hydraulic pump; then giving a descending signal to a hydraulic control proportional multi-way valve for controlling a main lifting motor in the main lifting system, controlling the hydraulic control proportional multi-way valve of the main lifting motor in the main lifting system to open, enabling hydraulic oil to enter the main lifting motor from the hydraulic control proportional multi-way valve for controlling the main lifting motor in the main lifting system through a main hook descending pipeline, enabling the hydraulic oil passing through the main lifting motor to return to a hydraulic oil tank from a main hook of a back pressure balance valve and a main hook ascending pipeline through the hydraulic control proportional multi-way valve for controlling the main lifting motor in the main lifting system, opening a shuttle valve by a part of the hydraulic oil in the main hook descending pipeline when the main lifting motor works, enabling the hydraulic oil entering the shuttle valve to enter the main lifting brake reversing valve through a main braking pressure reducing valve, enabling the hydraulic oil of the main lifting brake reversing valve to change positions through a control end of the main lifting brake reversing valve, and enabling the hydraulic oil entering the main lifting brake reversing valve to enter the main lifting brake mechanism through the main lifting, opening a main lifting brake mechanism; if the hydraulic control proportional multi-way valve of the main lifting motor in the main lifting system is controlled to reset, the main lifting motor stops working, meanwhile, oil supply on a brake pipeline of the main lifting motor is stopped, the main lifting brake reversing valve resets, hydraulic oil in the main lifting brake mechanism is removed through the main lifting brake reversing valve, and the main lifting motor brake mechanism resets to limit the main lifting motor to rotate;

the working method of the auxiliary hoisting system comprises an auxiliary hoisting working method and an auxiliary descending working method:

the auxiliary lifting working method comprises the following steps: firstly, starting a motor, driving a main hydraulic pump to work by the motor, and pumping hydraulic oil into an input end of a hydraulic control proportional multi-way valve for controlling an auxiliary lifting hydraulic motor in an auxiliary lifting system under the action of the main hydraulic pump; then giving a lifting signal to a hydraulic control proportional multi-way valve for controlling an auxiliary lifting hydraulic motor in the auxiliary lifting system, opening the hydraulic control proportional multi-way valve for controlling the auxiliary lifting hydraulic motor in the auxiliary lifting system, enabling hydraulic oil to enter the auxiliary lifting hydraulic motor from the hydraulic control proportional multi-way valve for controlling the auxiliary lifting hydraulic motor in the auxiliary lifting system through an auxiliary hook lifting pipeline, enabling the hydraulic oil of at least one auxiliary lifting hydraulic motor to return to a hydraulic oil tank from the hydraulic control proportional multi-way valve for controlling the auxiliary lifting hydraulic motor in the auxiliary lifting system through an anti-shake valve, and enabling the hydraulic oil of other auxiliary lifting hydraulic motors to return to the hydraulic oil tank through the hydraulic control proportional multi-way valve for controlling the auxiliary lifting hydraulic motor in the auxiliary lifting; when the auxiliary lifting hydraulic motor works, a part of hydraulic oil of the auxiliary hook lifting pipeline opens the auxiliary lifting shuttle valve, the hydraulic oil entering the auxiliary lifting shuttle valve enters the auxiliary lifting brake reversing valve through the auxiliary lifting brake pressure reducing valve, the hydraulic oil reaching the auxiliary lifting brake reversing valve is transposed through the control end of the auxiliary lifting brake reversing valve, the hydraulic oil entering the auxiliary lifting brake reversing valve enters the auxiliary lifting motor brake mechanism through the auxiliary lifting brake reversing valve, the auxiliary lifting motor brake mechanism is opened, and the disc brake mechanism is opened through the disc brake control system; if the hydraulic control proportional multi-way valve of the auxiliary lifting hydraulic motor in the auxiliary lifting system is controlled to reset, the auxiliary lifting hydraulic motor stops working, meanwhile, oil supply on a brake pipeline of the auxiliary lifting motor is stopped, the auxiliary lifting brake reversing valve resets, hydraulic oil in a brake mechanism of the auxiliary lifting motor is removed through the auxiliary lifting brake reversing valve, meanwhile, hydraulic oil of a disc brake mechanism is removed through the disc brake control system, and the auxiliary lifting motor brake mechanism and the disc brake mechanism reset to limit the auxiliary lifting hydraulic motor to rotate;

the auxiliary descending working method comprises the following steps: firstly, starting a motor, driving a main hydraulic pump to work by the motor, and pumping hydraulic oil into an input end of a hydraulic control proportional multi-way valve for controlling an auxiliary lifting hydraulic motor in an auxiliary lifting system under the action of the main hydraulic pump; then giving a descending signal to a hydraulic control proportional multi-way valve for controlling an auxiliary lifting hydraulic motor in the auxiliary lifting system, opening the hydraulic control proportional multi-way valve for controlling the auxiliary lifting hydraulic motor in the auxiliary lifting system, and allowing hydraulic oil to enter the auxiliary lifting hydraulic motor from the hydraulic control proportional multi-way valve for controlling the auxiliary lifting hydraulic motor in the auxiliary lifting system through an auxiliary hook descending pipeline, wherein the hydraulic oil of at least one auxiliary lifting hydraulic motor flows in from an anti-shake valve, and the hydraulic oil passing through the auxiliary lifting hydraulic motor returns to a hydraulic oil tank from the hydraulic control proportional multi-way valve for controlling the auxiliary lifting hydraulic motor in the auxiliary lifting system; when the auxiliary lifting hydraulic motor works, a part of hydraulic oil of the auxiliary hook descending pipeline opens the auxiliary lifting shuttle valve, the hydraulic oil entering the auxiliary lifting shuttle valve enters the auxiliary lifting brake reversing valve through the auxiliary lifting brake pressure reducing valve, the hydraulic oil reaching the auxiliary lifting brake reversing valve is transposed through the control end of the auxiliary lifting brake reversing valve, the hydraulic oil entering the auxiliary lifting brake reversing valve enters the auxiliary lifting motor brake mechanism through the auxiliary lifting brake reversing valve, the auxiliary lifting motor brake mechanism is opened, and the disc brake mechanism is opened through the disc brake control system; if the hydraulic control proportional multi-way valve of the auxiliary lifting hydraulic motor in the auxiliary lifting system is controlled to reset, the auxiliary lifting hydraulic motor stops working, meanwhile, oil supply on a brake pipeline of the auxiliary lifting motor is stopped, the auxiliary lifting brake reversing valve resets, hydraulic oil in a brake mechanism of the auxiliary lifting motor is removed through the auxiliary lifting brake reversing valve, meanwhile, hydraulic oil of a disc brake mechanism is removed through the disc brake control system, and the auxiliary lifting motor brake mechanism and the disc brake mechanism reset to limit the auxiliary lifting hydraulic motor to rotate;

the working method of the amplitude variation system comprises an amplitude variation ascending working method and an amplitude variation descending working method:

the working method of amplitude-variable ascending comprises the following steps: firstly, starting a motor, driving a main hydraulic pump to work by the motor, and pumping hydraulic oil into input ends of hydraulic control proportional multi-way valves of a first variable amplitude hydraulic motor and a second variable amplitude hydraulic motor in a control variable amplitude system under the action of the main hydraulic pump; then raising signals are given to the hydraulic control proportional multi-way valves of the first variable amplitude hydraulic motor and the second variable amplitude hydraulic motor in the control variable amplitude system, the hydraulic control proportional multi-way valves of the first variable amplitude hydraulic motor and the second variable amplitude hydraulic motor in the control variable amplitude system are opened, hydraulic oil enters the first variable amplitude hydraulic motor and the second variable amplitude hydraulic motor from the hydraulic control proportional multi-way valves of the first variable amplitude hydraulic motor and the second variable amplitude hydraulic motor in the control variable amplitude system through a raising oil supply pipeline, and the hydraulic oil passing through the first variable amplitude hydraulic motor and the second variable amplitude hydraulic motor returns to a hydraulic oil tank through the hydraulic control proportional multi-way valves of the first variable amplitude hydraulic motor and the second variable amplitude hydraulic motor in the control variable amplitude system; when the first amplitude-variable hydraulic motor and the second amplitude-variable hydraulic motor work, a part of hydraulic oil in the ascending oil supply pipeline opens the amplitude-variable shuttle valve, the hydraulic oil entering the amplitude-variable shuttle valve enters the amplitude-variable brake reversing valve through the amplitude-variable brake pressure reducing valve, the hydraulic oil reaching the amplitude-variable brake reversing valve shifts positions of the amplitude-variable brake reversing valve through the control end of the amplitude-variable brake reversing valve, and the hydraulic oil entering the amplitude-variable brake reversing valve enters the amplitude-variable motor brake mechanism through the amplitude-variable brake reversing valve to open the amplitude-variable motor brake mechanism; if the hydraulic control proportional multi-way valve of the first amplitude-varying hydraulic motor and the second amplitude-varying hydraulic motor in the amplitude-varying system is controlled to reset, the first amplitude-varying hydraulic motor and the second amplitude-varying hydraulic motor stop working, meanwhile, oil supply is stopped on a brake oil circuit of the amplitude-varying motor, the amplitude-varying brake reversing valve resets, hydraulic oil in a brake mechanism of the amplitude-varying motor is removed through the amplitude-varying brake reversing valve, and the amplitude-varying motor brake mechanism resets to limit the first amplitude-varying hydraulic motor and the second amplitude-varying hydraulic motor to rotate;

the amplitude-variable descending working method comprises the following steps: firstly, starting a motor, driving a main hydraulic pump to work by the motor, and pumping hydraulic oil into input ends of hydraulic control proportional multi-way valves of a first variable amplitude hydraulic motor and a second variable amplitude hydraulic motor in a control variable amplitude system under the action of the main hydraulic pump; then giving a descending signal to the hydraulic control proportional multi-way valves of the first variable amplitude hydraulic motor and the second variable amplitude hydraulic motor in the control variable amplitude system, controlling the hydraulic control proportional multi-way valves of the first variable amplitude hydraulic motor and the second variable amplitude hydraulic motor in the control variable amplitude system to be opened, respectively allowing hydraulic oil to enter the first variable amplitude hydraulic motor and the second variable amplitude hydraulic motor from the hydraulic control proportional multi-way valves of the first variable amplitude hydraulic motor and the second variable amplitude hydraulic motor in the control variable amplitude system through a descending oil supply pipeline, and returning the hydraulic oil passing through the first variable amplitude hydraulic motor and the second variable amplitude hydraulic motor to a hydraulic oil tank through the hydraulic control proportional multi-way valves of the first variable amplitude hydraulic motor and the second variable amplitude hydraulic motor in the control variable amplitude system; when the first amplitude-variable hydraulic motor and the second amplitude-variable hydraulic motor work, a part of hydraulic oil in the descending oil supply pipeline opens the amplitude-variable shuttle valve, the hydraulic oil entering the amplitude-variable shuttle valve enters the amplitude-variable brake reversing valve through the amplitude-variable brake pressure reducing valve, the hydraulic oil reaching the amplitude-variable brake reversing valve shifts positions of the amplitude-variable brake reversing valve through the control end of the amplitude-variable brake reversing valve, and the hydraulic oil entering the amplitude-variable brake reversing valve enters an amplitude-variable motor brake mechanism through the amplitude-variable brake reversing valve to open the amplitude-variable motor brake mechanism; if the hydraulic control proportional multi-way valve of the first amplitude-varying hydraulic motor and the second amplitude-varying hydraulic motor in the amplitude-varying system is controlled to reset, the first amplitude-varying hydraulic motor and the second amplitude-varying hydraulic motor stop working, meanwhile, oil supply is stopped on a brake oil circuit of the amplitude-varying motor, the amplitude-varying brake reversing valve resets, hydraulic oil in a brake mechanism of the amplitude-varying motor is removed through the amplitude-varying brake reversing valve, and the amplitude-varying motor brake mechanism resets to limit the first amplitude-varying hydraulic motor and the second amplitude-varying hydraulic motor to rotate;

the working method of the cable stabilizing system comprises a cable stabilizing retracting working method and a cable stabilizing releasing working method;

the working method for retracting the stabilizing rope comprises the following steps: firstly, starting a motor, driving a main hydraulic pump to work by the motor, and pumping hydraulic oil to an input end of a hydraulic control proportional multi-way valve for controlling a cable-stabilizing hydraulic motor in a cable-stabilizing system under the action of the main hydraulic pump; then, a signal is received by a hydraulic control proportional multi-way valve for controlling a cable-stabilizing hydraulic motor in the cable-stabilizing system, the hydraulic control proportional multi-way valve for controlling the cable-stabilizing hydraulic motor in the cable-stabilizing system is opened, hydraulic oil enters the cable-stabilizing hydraulic motor from the hydraulic control proportional multi-way valve for controlling the cable-stabilizing hydraulic motor in the cable-stabilizing system through a receiving oil supply pipeline and a cable-stabilizing balance valve, and the hydraulic oil passing through the cable-stabilizing hydraulic motor returns to a hydraulic oil tank from the hydraulic control proportional multi-way valve for controlling the cable-stabilizing hydraulic motor in the cable-stabilizing system through a discharging oil supply pipeline; meanwhile, the displacement of the cable-stabilizing hydraulic motor is controlled by a rotating speed control system of the cable-stabilizing hydraulic motor to control the speed of retracting the cable-stabilizing hydraulic motor;

the stable cable releasing working method comprises the following steps: firstly, starting a motor, driving a main hydraulic pump to work by the motor, and pumping hydraulic oil to an input end of a hydraulic control proportional multi-way valve for controlling a cable-stabilizing hydraulic motor in a cable-stabilizing system under the action of the main hydraulic pump; and then, a signal is sent to a hydraulic control proportional multi-way valve for controlling a cable-stabilizing hydraulic motor in the cable-stabilizing system, the hydraulic control proportional multi-way valve for controlling the cable-stabilizing hydraulic motor in the cable-stabilizing system is opened, hydraulic oil enters the cable-stabilizing hydraulic motor from the hydraulic control proportional multi-way valve for controlling the cable-stabilizing hydraulic motor in the cable-stabilizing system through an oil supply outlet pipeline, and the hydraulic oil passing through the cable-stabilizing hydraulic motor returns to a hydraulic oil tank from the hydraulic control proportional multi-way valve for controlling the cable-stabilizing hydraulic motor in the cable-stabilizing system through a cable-stabilizing balance valve and an oil supply outlet pipeline.

Compared with the prior art, the invention has the following beneficial effects:

1. the main hoisting winch, the auxiliary main hoisting winch, the amplitude-variable winch, the swing mechanism and the cable-stabilizing winch are all controlled by independent hydraulic systems, so that the independence is good, and the reliability is high;

2. the main hoisting winch, the auxiliary main hoisting winch, the amplitude-variable winch, the swing mechanism and the cable-stabilizing winch are all provided with brake mechanisms, so that the safe operation of the crane is ensured.

3. The crane main hook is stabilized by the cable stabilizing system, the main hook is prevented from shaking when the goods are lifted, impact on a crane hydraulic system caused by shaking of the goods is reduced, and the safety of the crane hydraulic system is improved.

4. The rotary system, the main lifting system and the auxiliary lifting system are all provided with confluence valve blocks, so that the hydraulic motors of the same system can work synchronously, and the stability of the hydraulic system of the crane is improved.

5. The auxiliary lifting hydraulic system is provided with a disc brake control system, so that when the crane lifts a person, the personal safety of the lifted person is further ensured.

Drawings

FIG. 1 is a first piping diagram of the hydraulic system of the present invention.

FIG. 2 is a second piping diagram of the hydraulic system of the present invention.

Fig. 3 is a schematic diagram of a rotary system.

Fig. 4 is a schematic diagram of a main hoisting system.

Fig. 5 is a schematic diagram of the auxiliary lifting system.

FIG. 6 is a schematic diagram of a luffing system.

Fig. 7 is a schematic diagram of a fuse system.

FIG. 8 is a drive schematic diagram and a cooling system schematic diagram of the disc brake control system.

Fig. 9 is a schematic diagram of a disc brake control system.

Fig. 10 is a schematic diagram of a back pressure balancing valve.

Fig. 11 is a schematic view of an anti-shake valve.

Fig. 12 is a schematic view of a disc brake accumulator valve block.

Fig. 13 is a schematic view of a disc brake reversing valve set.

Fig. 14 is a schematic view of the connection of the motor to the main hydraulic pump.

FIG. 15 is a schematic diagram of a pilot operated proportional multi-way valve.

FIG. 16 is a schematic view of first, second, seventh and eighth directional control valves.

FIG. 17 is a schematic view of third, fourth, fifth, sixth and ninth directional control valves.

Fig. 18 is a schematic diagram of connection between a main lifting motor and a main lifting motor brake mechanism.

Fig. 19 is a hydraulic schematic diagram of a main lifting motor brake mechanism.

Detailed Description

The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.

As shown in fig. 1 to 8, a hydraulic system of a crane includes a hydraulic oil tank 1, a main pump assembly 2, a switch assembly 3, a swing system 4 for driving a swing mechanism, a main hoisting system 5 for driving a main hoisting winch, an auxiliary hoisting system 6 for driving an auxiliary hoisting winch, a luffing system 7 for driving a luffing winch, a cable stabilizing system 8 for driving a cable stabilizing winch, and a cooling system 9 for cooling hydraulic oil.

The hydraulic oil tank 1 provides hydraulic oil for a whole crane hydraulic system, the main pump assembly 2 provides main hydraulic oil for the whole crane hydraulic system, and the switch assembly 3, the rotation system 4, the main hoisting system 5, the auxiliary hoisting system 6, the amplitude varying system 7 and the cable stabilizing system 8 are matched with each other to drive each action mechanism to finish various actions of hoisting, moving and putting down goods of the crane. The cooling system cools 9 the hydraulic oil to ensure that the temperature of the hydraulic oil in the hydraulic oil tank 1 is not too high.

The input end of the main pump component 2 is connected with the hydraulic oil tank 1, and the output end of the main pump component supplies oil to the amplitude changing system 4, the main lifting system 5, the auxiliary lifting system 6, the rotary system 7 and the cable stabilizing system 8 through the switch component 3; therefore, the main pump assembly 2 sucks hydraulic oil from the hydraulic oil tank 1, converts mechanical energy into hydraulic pressure energy and provides power for various systems.

As shown in fig. 1 and 13, the main pump assembly 2 includes two main hydraulic pumps 21, and the two main hydraulic pumps 21 are driven by the same motor 200; the output ends of the two main hydraulic pumps 21 are provided with main pump check valves 22 for preventing the hydraulic oil from flowing reversely, and the output ends of the two main pump check valves are respectively P1 and P2. The main hydraulic pump 21 provides more power for the crane hydraulic system and provides kinetic energy for different hydraulic systems.

The switch component 3 is a hydraulic control proportional multi-way valve 30. As shown in fig. 2 and 14 to 16, the pilot-controlled proportional multi-way valve 30 comprises a first reversing valve 31 and a second reversing valve 32 for controlling the rotary system, a third reversing valve 33 and a fourth reversing valve 34 for controlling the main hoisting system, a fifth reversing valve 35 and a sixth reversing valve 36 for controlling the auxiliary hoisting system, a seventh reversing valve 37 and an eighth reversing valve 38 for controlling the luffing system, and a ninth reversing valve 39 for controlling the cable stabilizer system; the first, second, third, fourth, fifth, sixth, seventh, eighth and ninth are three-position seven-way hydraulic control reversing valves, P1 and P2 are collected and then connected with input ends of all the reversing valves, and an oil return end of each reversing valve is connected with a hydraulic oil tank through a T1 connecting point. Different systems are controlled through different reversing valves respectively, the mutual influence is avoided, one system fails, and other systems can still work. The hydraulic control proportional multi-way valve 30 controls the actions of a plurality of control systems according to the requirements of a crane hydraulic system, and has compact structure and long service life.

As shown in fig. 2, the first directional valve 31 has a line connection point of SA1 and SB1, the second directional valve 32 has a line connection point of SA2 and SB2, and the swing system has a SLL return line connection point connected to the hydraulic tank through T2. The third diverter valve 33 has MWA1 and MWB1 line connections and the fourth diverter valve 34 has MWA2 and MWB2 line connections and has a WMX swing hydraulic motor control connection and a MWL1 return connection to the hydraulic tank via T2 in the main hoist system. The fifth directional valve 35 has an AWA1 and AWB1 line connection point and the sixth directional valve 36 has an AWA2 and AWB2 line connection point and in the secondary lift system has an AWL return line connection point connected to the hydraulic tank through T2. The seventh diverter valve 37 has LWA1 and LWB1 line connections and the eighth diverter valve 38 has LWA2 and LWB2 line connections and in the luffing system has a LWL return line connection to a hydraulic tank via T2. The ninth directional valve 39 has a TWA and TWB line connection point and in a cable system has a TWL return connection point connected to a hydraulic tank via T2. The "connection point" described above may be a connection joint, but in the present invention, since the entire hydraulic system cannot be expressed in the same drawing in the drawings of the specification, only the line connection corresponding to the symbol in each drawing is shown.

As shown in fig. 3, the swing system 4 includes a first swing hydraulic motor 41, a second swing hydraulic motor 42, a first swing balancing valve group 43, a second swing balancing valve group 44, and a swing brake pipe 45; SA1 of the first direction switching valve 31 and SA2 of the second direction switching valve 32 and SA1 and SA2 of the corresponding right oil supply pipe 46 are connected to one ends of the first rotary hydraulic motor 41 and the second rotary hydraulic motor 42, respectively, SB1 of the first direction switching valve 31 and SB2 of the second direction switching valve 32 and SB1 and SB2 of the corresponding left oil supply pipe 47 are connected to the other ends of the first rotary hydraulic motor 41 and the second rotary hydraulic motor 42, respectively, a first rotary balance valve group 43 is provided between the right oil supply pipe 46 of the first rotary hydraulic motor 41 and the left oil supply pipe 47 of the second rotary hydraulic motor 42, a second rotary balance valve group 44 is provided between the left oil supply pipe 47 of the first rotary hydraulic motor 41 and the right oil supply pipe 46 of the second rotary hydraulic motor 42, rotary brake mechanisms 413 are provided to the first rotary hydraulic motor 41 and the second rotary hydraulic motor 42, respectively, a rotary brake line 45 is provided between the first rotary balance valve group 43 and the rotary brake mechanisms 413, that is, the swing brake line 45 is connected between the right oil supply line 46 and the left oil supply line 47, and the swing brake line 45 is supplied with hydraulic oil regardless of whether the right oil supply line 46 or the left oil supply line 47 is supplied with oil. A rotary brake pressure reducing valve 48, a rotary brake reversing valve 49 and a rotary brake speed regulating valve 40 are sequentially arranged on the rotary brake pipeline 45; the rotary brake reversing valve 49 is a two-position three-way hydraulic control reversing valve with a control end connected to the inlet of the rotary brake reversing valve 49, oil drain ports of the first rotary hydraulic motor 41 and the second rotary hydraulic motor 42 are connected with an oil drain pipeline 100, the oil drain pipeline 100 is connected with the hydraulic oil tank 1, the rotary brake pressure reducing valve 48 and the rotary brake reversing valve 49 are provided with oil return pipelines connected with the oil drain pipeline 100, the first reversing valve 31 and the second reversing valve 32 control the flowing direction of hydraulic oil of the rotary system 4 in the right oil supply pipe 46 and the left oil supply pipe 47, so that the rotating directions of the first rotary hydraulic motor 41 and the second rotary hydraulic motor 42 are controlled, and the rotary mechanism rotates left and right. The first and second rotary balance valve groups 43 and 44 regulate the pressure and flow rate in the right and left oil supply pipes of the first and second rotary hydraulic motors 41 and 42, and ensure stable pressure and flow rate entering the first and second rotary hydraulic motors 41 and 42, so that the first and second rotary hydraulic motors 41 and 42 operate simultaneously at the same speed, and the rotary speeds are the same, so that the rotary mechanisms operate stably; the rotary brake pipeline 45 obtains hydraulic oil through the input end of the first rotary balance valve group 43, the hydraulic oil is decompressed through the rotary brake decompression valve 48, the pressure is prevented from being overlarge, the oil pressure input to the rotary brake mechanism 413 is adjusted, when the control end of the rotary brake reversing valve 49 is provided with the hydraulic oil output from the rotary brake decompression valve 48, the rotary brake reversing valve 49 is automatically connected with the rotary brake speed regulating valve 40 in a transposition mode, the rotary brake speed regulating valve 40 is used for regulating the flow passing through, the speed of braking of the rotary brake mechanism 413 is accurately controlled, and meanwhile, the influence of the change of the rotary brake mechanism 413 on the flow is eliminated; when the rotary brake mechanism 413 needs to stop, the rotary brake pipeline 45 stops supplying oil to the rotary brake reversing valve 49, the rotary brake reversing valve 49 resets, hydraulic oil of the rotary brake mechanism 413 flows back to an oil tank from the rotary brake reversing valve 49 through the rotary brake speed regulating valve 40 to play a role in unloading oil, braking in the rotary process until stopping is achieved, and the rotary brake mechanism 413 plays a role in back pressure on unloading oil of the rotary brake mechanism 413 due to the fact that the rotary brake speed regulating valve 40 is arranged in the oil unloading process, so that the rotary brake mechanism 413 is prevented from being rapidly braked due to rapid oil unloading of the rotary brake mechanism 413, the emergency stop phenomenon is avoided, and a crane hydraulic system is better protected.

One or more right confluence valve blocks 411 are connected between the right oil supply pipe 46 of the first turning hydraulic motor 41 and the right oil supply pipe 46 of the second turning hydraulic motor 42, and one or more left confluence valve blocks 412 are connected between the left oil supply pipe 47 of the first turning hydraulic motor 41 and the left oil supply pipe 47 of the second turning hydraulic motor 42. Centralized oil supply and centralized oil return are realized through the rightward confluence valve block 411 and the leftward confluence valve block 412, the pressure of the rightward oil supply pipe 46 is consistent, the pressure of the leftward oil supply pipe 47 is consistent, and the first rotary hydraulic motor and the second rotary hydraulic motor are guaranteed to obtain consistent driving pressure, so that the first rotary hydraulic motor and the second rotary hydraulic motor work synchronously.

As shown in fig. 4, the main lifting system 5 includes four main lifting motors 51, the main pump assembly 2 supplies oil to the four main lifting motors 51 through the pilot-controlled proportional multi-way valve 30, the third directional valve 33 and the fourth directional valve 34 are connected with one ends of the four main lifting motors through a main hook lifting pipeline 52, and the third directional valve 33 and the fourth directional valve 34 are connected with the other ends of the four main lifting motors 51 through a main hook descending pipeline 53; the main hook lifting lines 52 of the four main lifting motors communicate with each other through a first main lifting confluence valve block 54a, and the main hook descending lines 53 of the four main lifting motors 51 communicate with each other through a second main lifting confluence valve block 54 b. Four main hoisting motors 51 are arranged to drive the main hoisting winch, so that the main hoisting winch has higher hoisting capacity; the first main lifting confluence valve block 54a and the second main lifting confluence valve block 54b realize centralized oil supply and centralized oil return, and the four main lifting motors 51 obtain the same driving force, so that the four main lifting motors work synchronously and drive the main lifting winch to work stably.

A back pressure balance valve 55 is connected between the main lifting motor 51 and the main hook lifting pipeline 52; as shown in fig. 10 and 18, the back pressure balancing valve 55 includes a back pressure overflow valve 5501 and a back pressure check valve 5502, an input end of the back pressure overflow valve 5501 is connected to one end of the main hoisting motor 51, an output end of the back pressure check valve 5502 is connected to one end of the main hoisting motor 51, and the back pressure overflow valve 5501 and the back pressure check valve 5502 are connected in parallel. A main lifting motor brake mechanism 56 is arranged on the main lifting motor 51, and an oil path 57 of the main lifting motor brake mechanism is connected into the main hook lifting pipeline 52 and the main hook descending pipeline 53 through a main lifting shuttle valve 58; as shown in fig. 4 and 19, a main lifting brake pressure reducing valve 59 and a main lifting brake reversing valve 510 are sequentially arranged on the main lifting motor brake mechanism oil path 57; a main lifting one-way valve 511 is connected in parallel with the main lifting brake pressure reducing valve 59 and the main lifting reversing valve 510 which are connected in series; the main lifting brake reversing valve 510 is a two-position three-way hydraulic control reversing valve with a control end connected to the input end of the main lifting brake reversing valve 510, oil drain ports of four main lifting motors 51 are connected with an oil drain pipeline 100 through an oil drain multi-way body valve block 512, and the main lifting brake pressure reducing valve 59 and the main lifting brake reversing valve 510 are provided with oil return pipelines connected with the oil drain multi-way body valve block 512; the centralized oil return pipeline is simply and conveniently managed through the oil drainage multi-way valve block 512. The main pump assembly 2 provides hydraulic oil for the hydraulic control proportional multi-way valve 30, and the hydraulic control proportional multi-way valve 30 controls the flowing direction of the hydraulic oil entering the main hook ascending pipeline 52 and the main hook descending pipeline 53, so that the rotating direction of the main lifting motor 51 is controlled, and the ascending and descending actions of the main hook are realized; when the main hook descends, the backpressure overflow valve 5501 is arranged in the backpressure balance valve 55, and the backpressure check valve 5502 is connected to the backpressure overflow valve 5501 in parallel, so that when the main hook descends, hydraulic oil from the main lifting motor 51 can only pass through the backpressure overflow valve 5501, and the backpressure overflow valve 5501 can provide a certain backpressure, and therefore the main hook can be prevented from descending quickly due to quick oil discharge of the main lifting motor, and a heavy object can descend stably; the main lifting motor brake mechanism 56 always stops the main lifting winch from acting when the main lifting winch does not act, so that safety accidents of a main lifting system are prevented; because the main lifting motor brake mechanism oil path 57 is connected with the main hook ascending pipeline 52 and the main hook descending pipeline 53 through the main lifting shuttle valve 58, no matter the main hook ascending pipeline 52 or the main hook descending pipeline 53 is fed with oil, the main lifting motor brake mechanism oil path 57 can obtain hydraulic oil through the main lifting shuttle valve 58, the main lifting motor brake mechanism oil path 57 obtains the hydraulic oil and then reduces the pressure through the main lifting brake pressure reducing valve 59, then the main lifting brake reversing valve 510 is controlled by the hydraulic oil of the main lifting motor brake mechanism oil path to automatically shift to enable the hydraulic oil to enter the main lifting motor brake mechanism 56, the main lifting motor brake mechanism 56 obtains the power for pushing the brake, and the main lifting winch can work after the brake is pushed. The main lifting brake pressure reducing valve 59 and the main lifting reversing valve 510 are connected in parallel with a main lifting one-way valve 511, and when the oil pressure from the main lifting reversing valve 510 is too high, the main lifting one-way valve 511 is pushed open, so that part of the hydraulic oil flows back to the input end of the main lifting brake pressure reducing valve 59 and is reduced in pressure through the main lifting pressure reducing valve, and the main lifting system is further protected.

As shown in fig. 5, the secondary hoist system 6 includes two secondary hoist hydraulic motors 61 and an anti-shake valve 62. AWA1 and AWA2 corresponding to the fifth direction switching valve 35 and the sixth direction switching valve 36 are connected to one end of the auxiliary lifting hydraulic motor 61 through an auxiliary hook ascending pipe 63, AWB1 and AWB2 corresponding to the fifth direction switching valve 36 and the sixth direction switching valve 36 are connected to the other end of the auxiliary lifting hydraulic motor 61 through an auxiliary hook descending pipe 64, the auxiliary hook ascending pipes 63 of the two auxiliary lifting hydraulic motors 61 are communicated with each other through a first auxiliary lifting confluence valve block 65, and the auxiliary hook descending pipes 64 of the two auxiliary lifting hydraulic motors 61 are communicated with each other through a second auxiliary lifting confluence valve block 66. Two sets of auxiliary lifting hydraulic motors 61 are arranged to drive the auxiliary lifting winches, the lifting capacity of the auxiliary lifting winches is improved, the first auxiliary lifting confluence valve block 65 and the second auxiliary lifting confluence valve block 66 are used for centralized oil supply and centralized oil return, and the auxiliary lifting hydraulic motors 61 obtain the same driving force, so that the auxiliary lifting winches are synchronous in work and are driven to work stably. The fifth direction changing valve 35 and the sixth direction changing valve 36 control the flow direction of the hydraulic oil entering the auxiliary hook ascending pipeline 63 and the auxiliary hook descending pipeline 64, thereby controlling the rotation direction of the auxiliary lifting hydraulic motor and realizing the ascending and descending actions of the auxiliary hook.

In the present embodiment, an anti-shake valve 62 is provided between the auxiliary hook descent line 64 and one of the auxiliary lifting hydraulic motors 61; the auxiliary lifting hydraulic motor 61 is provided with an auxiliary lifting motor brake mechanism 67 and a disc brake mechanism 68, an auxiliary lifting motor brake mechanism oil path 69 is connected to the auxiliary hook lifting pipeline 63 and the auxiliary hook descending pipeline 64 through an auxiliary lifting shuttle valve 610, and an auxiliary lifting brake pressure reducing valve 611 and an auxiliary lifting brake reversing valve 612 are sequentially arranged on the auxiliary lifting brake mechanism oil path 69; an auxiliary lifting one-way valve 613 is connected in parallel at two ends of the series connection of the auxiliary lifting brake pressure reducing valve 611 and the auxiliary lifting brake reversing valve 612; the auxiliary lifting brake reversing valve 612 is a two-position three-way hydraulic control reversing valve with a control end connected to the input end of the auxiliary lifting brake reversing valve 612, oil drain ports of the two auxiliary lifting motors 61 are connected with the oil drain pipeline 100, and the auxiliary lifting brake pressure reducing valve 611 and the auxiliary lifting brake reversing valve 612 are provided with oil return pipelines connected with the oil drain pipeline 100; the auxiliary hoisting motor brake mechanism 67 and the disc brake mechanism 68 always stop the action of the auxiliary hoisting winch when the auxiliary hoisting winch does not act, so that the safety accident of the auxiliary hoisting system is prevented; the auxiliary lifting brake mechanism oil path 69 obtains hydraulic oil through the auxiliary lifting shuttle valve 610, so that the auxiliary lifting motor brake mechanism oil path 69 can obtain hydraulic oil no matter the auxiliary hook lifting pipeline 63 or the auxiliary hook descending pipeline 64 is fed with oil, the hydraulic oil passing through the auxiliary lifting shuttle valve 610 is decompressed through the auxiliary lifting brake decompression valve 611, the hydraulic oil from the auxiliary lifting brake decompression valve 611 enables the auxiliary lifting brake reversing valve 612 to automatically shift to input the hydraulic oil into the auxiliary lifting motor brake mechanism 67, the auxiliary lifting motor brake mechanism 67 obtains power for pushing away a brake, and simultaneously a disc brake control system is started to control the disc brake mechanism to be opened, and when the auxiliary lifting motor brake mechanism and the disc brake mechanism are released, the auxiliary lifting winch can work; an auxiliary lifting one-way valve 613 is connected in parallel to the auxiliary lifting brake pressure reducing valve 611 and the auxiliary lifting reversing valve 612, and when the oil pressure from the auxiliary lifting brake reversing valve is too high, the auxiliary lifting one-way valve is pushed to return to the pressure reducing input end of the auxiliary lifting brake pressure reducing valve for pressure reduction, so that the auxiliary lifting system is further protected. As shown in fig. 1 and 2, and fig. 8 and 9, a disc brake control system 60 is provided between the hydraulic oil tank 1 and the disc brake mechanism 68, and the disc brake control system 60 is respectively communicated with the sub-hook ascending conduit 63 and the sub-hook descending conduit 64 through a disc brake shuttle valve 610.

As shown in fig. 11, the anti-shake valve includes a valve core 6201, a valve body 6202 arranged in the valve core, a spring 6203 and a pushing block 6204, the valve core has an opening a and an opening B, the valve core 6201 has a valve cavity 6205 communicated with the opening a and the opening B, the opening a is communicated with the auxiliary lifting hydraulic motor 61, the opening B is communicated with the auxiliary hook descending pipeline, the pushing block 6204 is arranged in the valve cavity 6205, the spring 6203 is arranged between the valve core 6201 and the pushing block 6204, in a non-working state, the valve core 6201 is blocked at the opening B under the action of the spring 6203, and the opening a is communicated with the valve cavity 6205; when the auxiliary hoisting winch rises, hydraulic oil enters the auxiliary hoisting hydraulic motor and then enters the valve cavity through the anti-shake valve port A, when the hydraulic oil pressure in the valve cavity is smaller than the elastic force of the spring, the valve body is blocked at the port B under the action of the spring, the hydraulic oil cannot be discharged from the port B, when the hydraulic oil pressure in the valve cavity is larger than the elastic force of the spring, the hydraulic oil acts on the push block, the push block drives the spring to move towards the push block, the acting force of the spring on the valve body is reduced or eliminated, the valve body is opened under the pressure action of the hydraulic oil, the port A is communicated with the port B, the purposes of controlling the return flow rate and the speed of the hydraulic oil are achieved, and the phenomenon that the auxiliary hook is unstable in hoisting or shakes due to. If the hydraulic oil enters from the port B and is discharged from the port A, the hydraulic oil can push the valve body open by overcoming the elastic force of the spring, and the oil control effect is achieved.

As shown in fig. 1 and 2, 8 and 9, the disc brake control system 60 includes a disc brake hydraulic pump 6001, a disc brake directional valve set 6002, a disc brake control shuttle valve 6003, a disc brake accumulator valve block 6004, a disc brake accumulator 6005, a Y-shaped three-position four-way directional valve 6006, a disc brake hydraulic directional valve 6007, a disc brake oil inlet and outlet shuttle valve 6008 and a three-way valve 6009.

The input end of a disc brake hydraulic pump 6001 is communicated with a hydraulic oil tank 1, the output end of the disc brake hydraulic pump 6001 is communicated with a disc brake reversing valve set 6002, the two input ends of a disc brake control shuttle valve 6003 are communicated with the disc brake reversing valve set 6002, the output end of the disc brake control shuttle valve 6003 is communicated with a disc brake accumulator valve block 6004, a disc brake accumulator 6005 is communicated with the disc brake accumulator valve block 6004, the output end of the disc brake accumulator valve block 6004 is respectively communicated with the 1 end of a three-way valve 6009 and the P port of a Y-shaped three-position four-way reversing valve 6006, the A port of the Y-shaped three-position four-way reversing valve 6006 is communicated with the first end of a disc brake oil inlet and oil outlet shuttle valve 6008, the B port of the Y-shaped three-position four-way reversing valve 6006 is communicated with the 2 ports of a disc brake hydraulic control pilot control reversing valve 6007, the 3 port of the disc brake reversing valve 6007 is communicated with the second end of the disc brake oil outlet shuttle valve 6008, the 4 port of the disc brake oil outlet valve 6007 is, the control end of the disc brake hydraulic control reversing valve 6007 is communicated with the output end of the disc brake shuttle valve 610, the disc brake oil inlet and outlet shuttle valve 6008 is communicated with the 3 ends of the three-way valve 6009, and the 2 ends of the three-way valve 6009 are communicated with the disc brake mechanism 68.

The disc brake hydraulic pump 6001 extracts hydraulic oil from a hydraulic oil tank 1, converts mechanical energy into hydraulic energy, pushes a disc brake control shuttle valve 6003 away from a disc brake reversing valve set 6002, enters a disc brake energy accumulator valve block 6004 and then is divided into two paths, one path is connected with the disc brake energy accumulator 6005 for storing energy, the other path enters a Y-shaped three-position four-way reversing valve 6006 from the output end of the disc brake energy accumulator 6005 valve block, when the auxiliary hoisting winch hoists goods, a port P and a port A of the Y-shaped three-position four-way reversing valve 6006 are communicated, the hydraulic oil enters the port A from the port P and then pushes a disc brake oil inlet and oil outlet shuttle valve 6008 away to enter a disc brake mechanism 68 for brake release, and the brake on the auxiliary hoisting winch is released; when an auxiliary hoisting winch is needed to hoist a person, the port P and the port B of the Y-shaped three-position four-way reversing valve 6006 are communicated, hydraulic oil enters the port B from the port P and flows out to enter the disc brake hydraulic control reversing valve 6007, if the disc brake hydraulic control reversing valve 6007 receives a hydraulic control signal, the disc brake hydraulic control reversing valve 6007 is transposed, the port 2 and the port 3 of the disc brake hydraulic control reversing valve 6007 are communicated, the hydraulic oil pushes the disc brake oil inlet and outlet shuttle valve 6008 to enter the disc brake mechanism 68 through the three-way valve 6009 to brake, the brake on the auxiliary hoisting winch is released, and the auxiliary hoisting winch can work; in the process of lifting a person, if the auxiliary hoisting system suddenly breaks down and releases pressure, the disc brake hydraulic control reversing valve 6007 loses a hydraulic control signal, the disc brake hydraulic control reversing valve 6007 is switched, 3 ports and 4 ports of the disc brake hydraulic control reversing valve 6007 are communicated, hydraulic oil of the disc brake mechanism 68 quickly returns to a hydraulic oil tank through the three-way valve 6009 and the disc brake hydraulic control reversing valve 6007, and the auxiliary hoisting winch is quickly braked after the pressure of the disc brake mechanism 68 is released, so that the person is prevented from suddenly dropping from a half space, and personal safety is protected. When the Y-shaped three-position four-way reversing valve 6006 fails, the 1 port and the 2 ports of the three-way valve 6009 can be communicated through the handle, so that the disc brake mechanism 68 obtains oil pressure to release the brake, and the auxiliary hoisting winch works.

As shown in fig. 9 and 12, the disc brake accumulator valve block 6004 includes an energy storage check valve H01, an energy storage pilot-operated directional valve H02, a first switch H03, a second switch H04, an energy storage overflow valve H05, and a disc brake overflow valve H06. The input end of an energy storage one-way valve H01 is communicated with the output end of a disc brake control shuttle valve 6003, the output end of an energy storage one-way valve H01 is communicated with the control end of an energy storage hydraulic control reversing valve H02, meanwhile, the output end of an energy storage one-way valve H01 is communicated with the 1 end of a three-way valve 6009 and the P port of a Y-shaped three-position four-way reversing valve 6006, the output end of an energy storage one-way valve H01 is communicated with a disc brake energy storage device 6005 through a first switch H03, the disc brake energy storage device 6005 is communicated with a hydraulic oil tank 1 through an energy storage overflow valve H05, the disc brake energy storage device 6005 is communicated with the hydraulic oil tank 1 through a second switch H04, the input end of an energy storage one-way valve H01 is communicated with the hydraulic oil tank 1 through a disc brake overflow valve H06, and the X end of the disc brake overflow valve H06 is communicated with the hydraulic oil tank 1 through a hydraulic oil control. In the invention, the set pressure of the energy storage hydraulic control reversing valve is smaller than the set pressure of the disc brake overflow valve, so that the energy storage hydraulic control reversing valve is firstly switched, the overflow is realized through the disc brake overflow valve, if the energy storage hydraulic control reversing valve fails, the input end of the energy storage check valve has larger pressure in time, but if the pressure is larger than the set pressure of the disc brake overflow valve, the overflow can be realized, and the disc brake control system is effectively protected. The normally open setting of first switch is converted the energy in the control system of disc brake into compression energy at appropriate opportunity and is stored, when the control system needs of disc brake, converts compression energy into hydraulic energy again and releases, mends the control system of disc brake again, and when the control system of disc brake pressure increase in the twinkling of an eye, it can absorb this partial energy to guarantee that entire system pressure is normal. If the pressure in the disc brake energy accumulator exceeds the set pressure of the energy storage overflow valve, the energy storage overflow valve is connected with the hydraulic oil tank to control the oil pressure of the disc brake energy accumulator, and the disc brake energy accumulator has a safety protection effect. The second switch is normally closed, and when the energy of the disc brake energy accumulator needs to be released or an emergency overpressure condition occurs, the second switch is opened and communicated with the hydraulic oil tank for unloading, so that the disc brake control system is protected from overpressure.

As shown in fig. 13, the disc brake directional valve set 6002 includes a disc brake two-position four-way electromagnetic directional valve G01 and a disc brake directional valve overflow valve G02, a port P of the disc brake directional valve set 6002 is connected to an output end of the disc brake hydraulic pump 6001, a port T of the disc brake directional valve set 6002 is connected to a hydraulic tank, a port a of the disc brake directional valve set 6002 is connected to a disc brake accumulator valve block 6004, a port B of the disc brake directional valve set 6002 is connected to the cooling system 9, a port P1 of the disc brake two-position four-way electromagnetic directional valve G01 and a port 1 of the disc brake directional valve overflow valve G02 are connected to a port P of the disc brake directional valve set 6002, a port a 5639 of the disc brake two-position four-way electromagnetic directional valve G01 and a port 2 of the disc brake directional overflow valve G02 are connected to a port a of the disc brake directional valve set 6002, and a port, the 3 end and the 4 end of the overflow valve G02 of the disk brake reversing valve group are connected with the T port of the disk brake reversing valve group 6002, and the B1 port of the disk brake two-position four-way electromagnetic reversing valve G01 is connected with the B port of the disk brake reversing valve group 6002. Therefore, when the disc brake reversing valve bank is in overpressure, the disc brake control system is stabilized by unloading through an overflow valve G02 of the disc brake reversing valve bank.

As shown in fig. 8, the cooling system 9 includes a cooling hydraulic pump 91 and two coolers 92, and the cooling hydraulic pump 91 and a disc brake hydraulic pump 6001 are driven by a motor 200. The hydraulic tank 1 is connected to cooling hydraulic pump 91 input, and the cooling hydraulic pump 91 output is connected with the input of two coolers 92, and hydraulic tank 1 is connected to the output of cooler 92. The cooler 92 is driven by a cooling hydraulic motor 93, and an input end of the cooling hydraulic motor 93 is connected with a port B of the disc brake reversing valve set 6002. The input of the chiller hydraulic motor is also connected between the disc brake reversing valve block 6002 and the disc brake accumulator valve block 6004 by a disc brake control shuttle valve 6003. The cooling hydraulic pump 91 thus sucks hydraulic oil from the hydraulic oil tank 1, cools the hydraulic oil 92 by the two coolers, and returns the hydraulic oil to the hydraulic oil tank 1. When the temperature of hydraulic oil is high, accelerated cooling is needed, the disc brake two-position four-way electromagnetic directional valve G01 is controlled to be switched through the electromagnetic valve, the hydraulic oil drives the cooling hydraulic motor 93 to rotate after passing through the two-position four-way electromagnetic directional valve G01, the cooler 91 is driven to be cooled quickly, and the hydraulic oil is prevented from being over-heated to cause the crane hydraulic system to break down.

As shown in fig. 6, the luffing system 7 comprises a first luffing hydraulic motor 71, a second luffing hydraulic motor 72, a first luffing balancing valve 73 and a second luffing balancing valve 74; the seventh reversing valve 37 and the eighth reversing valve 38 are respectively connected with one end of the first luffing hydraulic motor 71 and one end of the second luffing hydraulic motor 72 through a luffing ascending oil supply pipeline 75, the seventh reversing valve and the eighth reversing valve are respectively connected with the other end of the first luffing hydraulic motor 71 and the other end of the second luffing hydraulic motor 72 through a luffing descending oil supply pipeline 76, a first luffing balance valve 73 is arranged on the luffing ascending oil supply pipeline 75 communicated with the first luffing hydraulic motor 71 to provide back pressure, and a second luffing balance valve 74 is arranged on the luffing ascending oil supply pipeline 75 communicated with the second luffing hydraulic motor 72 to provide back pressure; the first luffing hydraulic motor 71 and the second luffing hydraulic motor 72 are provided with a luffing motor brake mechanism 77, an oil path 78 of the luffing motor brake mechanism is connected to the luffing ascending oil supply pipeline 75 and the luffing descending oil supply pipeline 76 through a luffing shuttle valve 79, and a luffing brake pressure reducing valve 710 and a luffing brake reversing valve 711 are sequentially arranged on the oil path 78 of the luffing brake mechanism; a variable amplitude one-way valve 712 is connected in parallel at two ends of the series variable amplitude brake pressure reducing valve 710 and the variable amplitude brake reversing valve 711; the amplitude-variable brake reversing valve 711 is a two-position three-way hydraulic control reversing valve with a control end connected to the input end of the amplitude-variable brake reversing valve 711, oil drainage ports of the first amplitude-variable hydraulic motor 71 and the second amplitude-variable hydraulic motor 72 are connected with the oil drainage pipeline 100, and the amplitude-variable brake pressure reducing valve 710 and the amplitude-variable brake reversing valve 711 are provided with oil return pipelines connected with the oil drainage pipeline 100; the seventh reversing valve 37 and the eighth reversing valve 38 control the flow direction of the hydraulic oil entering the amplitude ascending oil supply pipeline 75 and the amplitude descending oil supply pipeline 76, so as to control the rotation direction of the first amplitude hydraulic motor 71 and the second amplitude hydraulic motor 72 and realize the ascending and descending actions of the boom; the first amplitude-variable balance valve and the second amplitude-variable balance valve ensure that the flow rates of hydraulic oil entering the first amplitude-variable hydraulic motor and the second amplitude-variable hydraulic motor are consistent, so that the rotating speeds of the first amplitude-variable hydraulic motor and the second amplitude-variable hydraulic motor are controlled to be consistent; the amplitude-variable motor braking mechanism always stops the amplitude-variable winch from acting when the amplitude-variable winch does not act, so that safety accidents of an amplitude-variable system are prevented; the hydraulic path of the variable-amplitude motor brake mechanism obtains hydraulic oil through the variable-amplitude shuttle valve, so that no matter the hydraulic oil enters from the variable-amplitude ascending oil supply pipeline or the variable-amplitude descending oil supply pipeline, the hydraulic oil on the variable-amplitude brake mechanism can be obtained, the hydraulic oil passing through the variable-amplitude shuttle valve is decompressed through the variable-amplitude brake decompression valve, the control end of the variable-amplitude brake reversing valve is controlled by the decompressed hydraulic oil to be automatically transposed, so that the hydraulic oil enters the variable-amplitude motor brake mechanism from the variable-amplitude brake reversing valve, the variable-amplitude motor brake mechanism obtains the power of pushing the brake, and the variable-amplitude winch can; the amplitude-variable brake pressure-reducing valve and the amplitude-variable brake reversing valve are connected in parallel with an amplitude-variable one-way valve, and when the oil pressure from the amplitude-variable reversing valve is too high, the amplitude-variable one-way valve is pushed to return to the input end of the amplitude-variable brake pressure-reducing valve for pressure reduction, so that an amplitude-variable system is further protected.

As shown in fig. 7, the cable stabilizing system 8 comprises a cable stabilizing hydraulic motor 81, a cable stabilizing balance valve 82 and a cable stabilizing hydraulic motor speed control system 83; the ninth reversing valve 39 is connected with one end of the cable-stabilized hydraulic motor 81 through a retracting oil supply pipeline 84, the ninth reversing valve 38 is connected with the other end of the cable-stabilized hydraulic motor 81 through a releasing oil supply pipeline 85, and a cable-stabilized balance valve 82 is arranged between the cable-stabilized hydraulic motor 81 and the retracting oil supply pipeline 84 and plays a role in providing back pressure; the stabilizer hydraulic motor speed control system 83 controls the speed of the stabilizer release by controlling the displacement of the stabilizer hydraulic motor 81. The hydraulic control proportional multi-way valve controls the flow direction of hydraulic oil entering the retracting oil supply pipeline 84 and the releasing oil supply pipeline 85, so that the rotation direction of the cable stabilizing hydraulic motor 81 realizes the retracting and releasing actions of a cable stabilizing; the swing amplitude of the main hook is controlled through the speed control of the retraction of the cable stabilizer, and the speed of the cable stabilizer hydraulic motor rotating speed control system 83 is used for accurately controlling the speed of releasing the cable stabilizer according to the swing amplitude of the on-site main hook, so that the phenomenon that the main hook shakes too much when lifting goods is prevented.

The rotation speed control system 83 of the cable-stabilizing hydraulic motor comprises a first cable-stabilizing overflow valve 8301, a first cable-stabilizing two-position three-way hydraulic control reversing valve 8302 and a second cable-stabilizing overflow valve 8303 which are connected in sequence; a P port of the first cable stabilizing overflow valve 8301 is connected with the retracting oil supply pipeline 84 through a tension valve block 86, a T port of the first cable stabilizing overflow valve 8301 is connected with the discharging oil supply pipeline 85, an X port of the first cable stabilizing overflow valve 8301 is connected with a first cable stabilizing two-position three-way hydraulic control reversing valve 8302, the first cable stabilizing two-position three-way hydraulic control reversing valve 8302 is connected with a second cable stabilizing overflow valve 8303, and the second cable stabilizing overflow valve 8303 is connected with a hydraulic oil tank; an X port of the first rope stabilizing overflow valve 8301 is connected between the tension valve block 86 and the rope stabilizing balance valve 82 through a two-way throttle valve 87; a cable stabilizing shuttle valve 88 is connected between the retracting oil supply pipeline 84 and the releasing oil supply pipeline 85, the outlet end of the cable stabilizing shuttle valve 88 is connected with a cable stabilizing pressure reducing valve 89, the outlet end of the cable stabilizing pressure reducing valve 89 is connected to the control end of the cable stabilizing hydraulic motor 81, the outlet end of the cable stabilizing pressure reducing valve 89 is connected with a cable stabilizing electromagnetic valve 810, the cable stabilizing electromagnetic valve 810 is connected to the control end of the first cable stabilizing two-position three-way hydraulic control reversing valve 8302, and meanwhile, the cable stabilizing electromagnetic valve 810 is connected to a hydraulic oil tank. The cable-stabilizing balance valve is arranged, when the hydraulic oil drives the cable-stabilizing hydraulic motor from the oil supply outlet pipeline, back pressure can be provided through the cable-stabilizing balance valve, and quick oil discharge of the cable-stabilizing hydraulic motor is avoided. Under the condition that the cable-stabilizing electromagnetic valve is not electrified, the first cable-stabilizing two-position three-way hydraulic control reversing valve does not act, and in the state, when the oil pressure of the retracting oil supply pipeline exceeds the set pressure of the first cable-stabilizing overflow valve, the first cable-stabilizing overflow valve is communicated with the releasing oil supply pipeline to discharge oil, the stability of the oil pressure of the retracting oil supply pipeline is ensured, and the cable-stabilizing hydraulic motor is protected. The rotating speed control system of the cable-stabilized hydraulic motor obtains control hydraulic oil through a cable-stabilized shuttle valve, the pressure of the output hydraulic oil is ensured to be stable through the pressure reduction of a cable-stabilized pressure reducing valve, the pressure required by the control end of the cable-stabilized hydraulic motor is obtained, and the cable-stabilized hydraulic motor is controlled. If the cable stabilizing electromagnetic valve obtains an electric signal, the cable stabilizing electromagnetic valve is switched to be communicated with the control end of the first cable stabilizing two-position three-way hydraulic control reversing valve, the first cable stabilizing two-position three-way hydraulic control reversing valve obtains a hydraulic control signal for switching, the first cable stabilizing two-position three-way hydraulic control reversing valve is switched to be communicated with the X port of the first cable stabilizing overflow valve, hydraulic oil flows back to the hydraulic oil tank after passing through the second cable stabilizing overflow valve, the flow of the hydraulic oil flowing back to the hydraulic oil tank is controlled by adjusting the second cable stabilizing overflow valve, and the oil pressure entering the cable stabilizing hydraulic motor is controlled, so that the purpose. Therefore, the main hook is stabilized by controlling the tightness of the stable cable, and the situation that the goods hoisted by the main hook are greatly shaken to cause safety accidents is prevented.

The working method of the hydraulic system of the crane comprises a working method of the rotary system 4, a working method of the main hoisting system 5, a working method of the auxiliary hoisting system 6, a working method of the amplitude varying system 7 and a working method of the cable stabilizing system 8;

the working method of the rotating system 4 comprises a left rotating working method and a right rotating working method;

the left-turn working method comprises the following steps: firstly, starting the motor 200, driving the main hydraulic pump 21 to work by the motor 200, and pumping hydraulic oil into the input ends of the hydraulic control proportional multi-way valves 30 of the first rotary hydraulic motor 41 and the second rotary hydraulic motor 42 in the control rotary system 4 under the action of the main hydraulic pump 21; then, a left turn signal is given to the pilot-operated proportional multi-way valve 30 for controlling the first and second rotary hydraulic motors 41 and 42 in the swing system 4, the pilot-operated proportional multi-way valve 30 for controlling the first and second rotary hydraulic motors 41 and 42 in the swing system 4 is opened, hydraulic oil is fed from the pilot-operated proportional multi-way valve 30 for controlling the first and second rotary hydraulic motors 41 and 42 in the swing system 4 to the first and second rotary hydraulic motors 41 and 42 through the left oil supply line 47, respectively, hydraulic oil passing through the first and second rotary hydraulic motors 41 and 42 is returned from the left oil supply line 46 to the hydraulic oil tank 1 through the pilot-operated proportional multi-way valve 30 for controlling the first and second rotary hydraulic motors 41 and 42 in the swing system 4, and, while the first and second rotary hydraulic motors 41 and 42 are operating, a part of hydraulic oil in the left oil supply pipeline 47 enters a rotary brake pipeline, the hydraulic oil entering the rotary brake pipeline enters a rotary brake reversing valve 49 through a rotary brake pressure reducing valve 48, the rotary brake reversing valve 49 is shifted under the action of the hydraulic oil in the rotary brake pipeline, the hydraulic oil in the rotary brake pipeline enters the rotary brake mechanism 413 from the rotary brake reversing valve 49 and the rotary brake speed regulating valve 40, and the rotary brake mechanism 413 is opened; if the hydraulic control proportional multi-way valve 30 for controlling the first rotary hydraulic motor 41 and the second rotary hydraulic motor 42 in the rotary system 4 is reset, the first rotary hydraulic motor 41 and the second rotary hydraulic motor 42 stop working, meanwhile, oil supply is stopped on the rotary brake pipeline, the rotary brake reversing valve 49 is reset, hydraulic oil in the rotary brake mechanism 413 is discharged from the rotary brake reversing valve 49 through the rotary brake speed regulating valve 40, and the rotary brake mechanism 413 is reset to limit the first rotary hydraulic motor 41 and the second rotary hydraulic motor 42 to rotate;

the right-turn working method comprises the following steps: firstly, starting the motor 200, driving the main hydraulic pump 21 to work by the motor 200, and pumping hydraulic oil into the input ends of the hydraulic control proportional multi-way valves 30 of the first rotary hydraulic motor 41 and the second rotary hydraulic motor 42 in the control rotary system 4 under the action of the main hydraulic pump 21; then, a right turn signal is given to the pilot-operated proportional multi-way valve 30 for controlling the first and second rotary hydraulic motors 41 and 42 in the swing system 4, the pilot-operated proportional multi-way valves 30 for controlling the first and second rotary hydraulic motors 41 and 42 in the swing system 4 are opened, hydraulic oil is fed from the pilot-operated proportional multi-way valves 30 for controlling the first and second rotary hydraulic motors 41 and 42 in the swing system 4 to the first and second rotary hydraulic motors 41 and 42 through the right oil supply line 46, respectively, hydraulic oil passed through the first and second rotary hydraulic motors 41 and 42 is returned from the left oil supply line 47 to the hydraulic oil tank 1 through the pilot-operated proportional multi-way valves 30 for controlling the first and second rotary hydraulic motors 41 and 42 in the swing system 4, and, while the first and second rotary hydraulic motors 41 and 42 are operating, a part of hydraulic oil in the right oil supply pipeline 46 enters a rotary brake pipeline, the hydraulic oil entering the rotary brake pipeline enters a rotary brake reversing valve 49 through a rotary brake pressure reducing valve 48, the rotary brake reversing valve 49 is shifted under the action of the hydraulic oil in the rotary brake pipeline, the hydraulic oil in the rotary brake pipeline enters the rotary brake mechanism 413 from the rotary brake reversing valve 49 and the rotary brake speed regulating valve 40, and the rotary brake mechanism 413 is opened; if the hydraulic control proportional multi-way valve 30 for controlling the first rotary hydraulic motor 41 and the second rotary hydraulic motor 42 in the rotary system 4 is reset, the first rotary hydraulic motor 41 and the second rotary hydraulic motor 42 stop working, meanwhile, oil supply is stopped on the rotary brake pipeline, the rotary brake reversing valve 49 is reset, hydraulic oil in the rotary brake mechanism 413 is discharged from the rotary brake reversing valve 49 through the rotary brake speed regulating valve 40, and the rotary brake mechanism 413 is reset to limit the first rotary hydraulic motor 41 and the second rotary hydraulic motor 42 to rotate;

the working method of the main hoisting system 5 comprises a main hoisting working method and a main descending working method;

the main lifting working method comprises the following steps: firstly, starting a motor 200, driving a main hydraulic pump 21 to work by the motor 200, and pumping hydraulic oil to an input end of a hydraulic control proportional multi-way valve 30 for controlling a main lifting motor in a main lifting system 5 under the action of the main hydraulic pump 21; then, a lifting signal is given to a hydraulic control proportional multi-way valve 30 for controlling a main lifting motor in the main lifting system 5, the hydraulic control proportional multi-way valve 30 for controlling the main lifting motor in the main lifting system 5 is controlled to be opened, hydraulic oil enters the main lifting motor 51 from the hydraulic control proportional multi-way valve 30 for controlling the main lifting motor in the main lifting system 5 through a main hook lifting pipeline 52 and a back pressure balance valve 55, the hydraulic oil passing through the main lifting motor 51 returns to the hydraulic oil tank 1 from a main hook descending pipeline 53 through the hydraulic control proportional multi-way valve 30 for controlling the main lifting motor 51 in the main lifting system 5, when the main lifting motor 51 works, a part of the hydraulic oil in the main hook lifting pipeline 52 opens the main lifting shuttle valve 58, the hydraulic oil entering the main lifting shuttle valve 58 enters the main lifting brake reversing valve 510 through a main lifting brake pressure reducing valve 59, and the hydraulic oil of the main lifting brake reversing valve 510 shifts the position of the main lifting brake valve 510 through a control end of the main lifting brake reversing valve, the hydraulic oil entering the main lifting brake reversing valve 510 enters the main lifting brake mechanism 56 through the main lifting brake reversing valve 510, and the main lifting brake mechanism 56 is opened; if the hydraulic control proportional multi-way valve 30 of the main lifting motor 51 in the main lifting system 5 is controlled to reset, the main lifting motor 51 stops working, meanwhile, oil supply on a brake pipeline of the main lifting motor is stopped, the main lifting brake reversing valve 510 resets, hydraulic oil in the main lifting brake mechanism 56 is removed through the main lifting brake reversing valve 510, and the main lifting motor brake mechanism resets to limit the main lifting motor 51 to rotate;

the main descending working method comprises the following steps: firstly, starting a motor 200, driving a main hydraulic pump 21 to work by the motor 200, and pumping hydraulic oil to an input end of a hydraulic control proportional multi-way valve 30 for controlling a main lifting motor 51 in a main lifting system 5 under the action of the main hydraulic pump 21; then, a descending signal is given to a hydraulic control proportional multi-way valve 30 for controlling a main lifting motor 51 in the main lifting system 5, the hydraulic control proportional multi-way valve 30 for controlling the main lifting motor 51 in the main lifting system 5 is controlled to be opened, hydraulic oil enters the main lifting motor 51 from the hydraulic control proportional multi-way valve 30 for controlling the main lifting motor 51 in the main lifting system 5 through a main hook descending pipeline 53, the hydraulic oil passing through the main lifting motor 51 returns to the hydraulic oil tank 1 from a back pressure balance valve 55 and a main hook ascending pipeline 52 through the hydraulic control proportional multi-way valve 30 for controlling the main lifting motor 51 in the main lifting system 5, when the main lifting motor 51 works, a part of the hydraulic oil in the main hook descending pipeline 53 opens the main lifting shuttle valve 58, the hydraulic oil entering the main lifting shuttle valve 58 enters the main lifting brake reversing valve 510 through a main lifting pressure reducing valve 59, and the hydraulic oil of the main lifting brake reversing valve 510 shifts the position of the main lifting brake valve 510 through a control end of the main lifting brake, the hydraulic oil entering the main lifting brake reversing valve 510 enters the main lifting brake mechanism 56 through the main lifting brake reversing valve 510, and the main lifting brake mechanism 56 is opened; if the hydraulic control proportional multi-way valve 30 of the main lifting motor 51 in the main lifting system 5 is controlled to reset, the main lifting motor 51 stops working, meanwhile, oil supply on a brake pipeline of the main lifting motor is stopped, the main lifting brake reversing valve 510 resets, hydraulic oil in the main lifting brake mechanism 56 is removed through the main lifting brake reversing valve 510, and the main lifting motor 51 is reset to limit the rotation of the main lifting motor 51;

the working method of the auxiliary hoisting system 6 comprises an auxiliary hoisting working method and an auxiliary descending working method:

the auxiliary lifting working method comprises the following steps: firstly, starting a motor 200, driving a main hydraulic pump 21 to work by the motor 200, and pumping hydraulic oil into an input end of a hydraulic control proportional multi-way valve 30 for controlling an auxiliary lifting hydraulic motor in an auxiliary lifting system 6 under the action of the main hydraulic pump 21; then, giving a lifting signal to a hydraulic control proportional multi-way valve 30 for controlling an auxiliary lifting hydraulic motor in the auxiliary lifting system 6, controlling the hydraulic control proportional multi-way valve 30 for controlling the auxiliary lifting hydraulic motor in the auxiliary lifting system 6 to open, allowing hydraulic oil to enter the auxiliary lifting hydraulic motor 61 from the hydraulic control proportional multi-way valve 30 for controlling the auxiliary lifting hydraulic motor in the auxiliary lifting system 6 through an auxiliary hook lifting pipeline 63, returning hydraulic oil of at least one auxiliary lifting hydraulic motor 61 to the hydraulic oil tank 1 from the hydraulic control proportional multi-way valve 30 for controlling the auxiliary lifting hydraulic motor 61 in the auxiliary lifting system 6 through an anti-shake valve, and returning hydraulic oil of other auxiliary lifting hydraulic motors 61 to the hydraulic oil tank 1 through the hydraulic control proportional multi-way valve 30 for controlling the auxiliary lifting hydraulic motor 61 in the auxiliary lifting system 6; when the auxiliary lifting hydraulic motor 61 works, a part of hydraulic oil in the auxiliary hook lifting pipeline 63 opens the auxiliary lifting shuttle valve 610, the hydraulic oil entering the auxiliary lifting shuttle valve 610 enters the auxiliary lifting brake reversing valve 612 through the auxiliary lifting brake pressure reducing valve 611, the hydraulic oil reaching the auxiliary lifting brake reversing valve 612 shifts the position of the auxiliary lifting brake reversing valve 612 through the control end of the auxiliary lifting brake reversing valve 612, the hydraulic oil entering the auxiliary lifting brake reversing valve 612 enters the auxiliary lifting motor brake mechanism 67 through the auxiliary lifting brake reversing valve 612, the auxiliary lifting motor brake mechanism 67 is opened, and the disc brake mechanism is opened through the disc brake control system; if the hydraulic control proportional multi-way valve 30 of the auxiliary lifting hydraulic motor 61 in the auxiliary lifting system 6 is controlled to reset, the auxiliary lifting hydraulic motor 61 stops working, meanwhile, oil supply is stopped on a brake pipeline of the auxiliary lifting hydraulic motor, the auxiliary lifting brake reversing valve 612 resets, hydraulic oil in the auxiliary lifting motor brake mechanism 67 is removed through the auxiliary lifting brake reversing valve 612, hydraulic oil of the disc brake mechanism is removed through the disc brake control system, and the auxiliary lifting motor brake mechanism 67 and the disc brake mechanism reset to limit the auxiliary lifting hydraulic motor 61 to rotate;

the auxiliary descending working method comprises the following steps: firstly, starting a motor 200, driving a main hydraulic pump 21 to work by the motor 200, and pumping hydraulic oil into an input end of a hydraulic control proportional multi-way valve 30 for controlling an auxiliary lifting hydraulic motor 61 in an auxiliary lifting system 6 under the action of the main hydraulic pump 21; then, a descending signal is given to a hydraulic control proportional multi-way valve 30 for controlling an auxiliary lifting hydraulic motor 61 in the auxiliary lifting system 6, the hydraulic control proportional multi-way valve 30 for controlling the auxiliary lifting hydraulic motor 61 in the auxiliary lifting system 6 is opened, hydraulic oil enters the auxiliary lifting hydraulic motor 61 from the hydraulic control proportional multi-way valve 30 for controlling the auxiliary lifting hydraulic motor 61 in the auxiliary lifting system 6 through an auxiliary hook descending pipeline 64, wherein the hydraulic oil of at least one auxiliary lifting hydraulic motor 61 flows in from an anti-shake valve, and the hydraulic oil passing through the auxiliary lifting hydraulic motor 61 returns to the hydraulic oil tank 1 from the hydraulic control proportional multi-way valve 30 for controlling the auxiliary lifting hydraulic motor 61 in the auxiliary lifting system 6; when the auxiliary lifting hydraulic motor 61 works, a part of hydraulic oil in the auxiliary hook descending pipeline 64 opens the auxiliary lifting shuttle valve 610, the hydraulic oil entering the auxiliary lifting shuttle valve 610 enters the auxiliary lifting brake reversing valve 612 through the auxiliary lifting brake pressure reducing valve 611, the hydraulic oil reaching the auxiliary lifting brake reversing valve 612 shifts the position of the auxiliary lifting brake reversing valve 612 through the control end of the auxiliary lifting brake reversing valve 612, the hydraulic oil entering the auxiliary lifting brake reversing valve 612 enters the auxiliary lifting motor brake mechanism 67 through the auxiliary lifting brake reversing valve 612, the auxiliary lifting motor brake mechanism 67 is opened, and the disc brake mechanism 68 is opened through the disc brake control system; if the hydraulic control proportional multi-way valve 30 of the auxiliary lifting hydraulic motor 61 in the auxiliary lifting system 6 is controlled to reset, the auxiliary lifting hydraulic motor 61 stops working, meanwhile, oil supply is stopped on a brake pipeline of the auxiliary lifting motor, the auxiliary lifting brake reversing valve 612 resets, hydraulic oil in the auxiliary lifting motor brake mechanism 67 is removed through the auxiliary lifting brake reversing valve 612, hydraulic oil in the disc brake mechanism 68 is removed through the disc brake control system, and the auxiliary lifting motor brake mechanism 67 and the disc brake mechanism 68 reset to limit the auxiliary lifting hydraulic motor 61 to rotate;

the working method of the amplitude variation system 7 comprises an amplitude variation ascending working method and an amplitude variation descending working method:

the working method of amplitude-variable ascending comprises the following steps: firstly, starting the motor 200, driving the main hydraulic pump 21 to work by the motor 200, and pumping hydraulic oil into the input ends of the hydraulic control proportional multi-way valves 30 of the first variable amplitude hydraulic motor 71 and the second variable amplitude hydraulic motor 72 in the control variable amplitude system 7 under the action of the main hydraulic pump 21; then, raising signals are given to the hydraulic control proportional multi-way valve 30 for controlling the first amplitude hydraulic motor 71 and the second amplitude hydraulic motor 72 in the amplitude varying system 7, the hydraulic control proportional multi-way valve 30 for controlling the first amplitude hydraulic motor 71 and the second amplitude hydraulic motor 72 in the amplitude varying system 7 is opened, hydraulic oil enters the first amplitude hydraulic motor 71 and the second amplitude hydraulic motor 72 from the hydraulic control proportional multi-way valve 30 for controlling the first amplitude hydraulic motor 71 and the second amplitude hydraulic motor 72 in the amplitude varying system 7 through an amplitude raising oil supply pipeline 75, and the hydraulic oil passing through the first amplitude hydraulic motor 71 and the second amplitude hydraulic motor 72 returns to the hydraulic oil tank 1 through the hydraulic control proportional multi-way valve 30 for controlling the first amplitude hydraulic motor 71 and the second amplitude hydraulic motor 72 in the amplitude varying system 7; when the first amplitude-varying hydraulic motor 71 and the second amplitude-varying hydraulic motor 72 work, a part of hydraulic oil in the amplitude-varying ascending oil supply pipeline 75 opens the amplitude-varying shuttle valve 79, the hydraulic oil entering the amplitude-varying shuttle valve 79 enters the amplitude-varying brake reversing valve 711 through the amplitude-varying brake pressure reducing valve 710, the hydraulic oil reaching the amplitude-varying brake reversing valve 711 shifts the position of the amplitude-varying brake reversing valve 711 through the control end of the amplitude-varying brake reversing valve 711, the hydraulic oil entering the amplitude-varying brake reversing valve 711 enters the amplitude-varying motor braking mechanism 77 through the amplitude-varying brake reversing valve 711, and the amplitude-varying motor braking mechanism 77 is opened; if the hydraulic control proportional multi-way valve 30 of the first amplitude hydraulic motor 71 and the second amplitude hydraulic motor 72 in the amplitude varying system 7 is controlled to reset, the first amplitude varying hydraulic motor and the second amplitude varying hydraulic motor stop working, meanwhile, oil supply stops on a brake oil circuit of the amplitude varying motor, the amplitude varying brake reversing valve 711 resets, hydraulic oil in the amplitude varying motor braking mechanism 77 is removed through the amplitude varying brake reversing valve 711, and the amplitude varying motor braking mechanism 77 resets to limit the rotation of the first amplitude varying hydraulic motor 72 and the second amplitude varying hydraulic motor 72;

the amplitude-variable descending working method comprises the following steps: firstly, starting the motor 200, driving the main hydraulic pump 21 to work by the motor 200, and pumping hydraulic oil into the input ends of the hydraulic control proportional multi-way valves 30 of the first variable amplitude hydraulic motor 71 and the second variable amplitude hydraulic motor 72 in the control variable amplitude system 7 under the action of the main hydraulic pump 21; then, a descending signal is given to the pilot-controlled proportional multi-way valve 30 for controlling the first variable amplitude hydraulic motor 71 and the second variable amplitude hydraulic motor 72 in the variable amplitude system 7, the pilot-controlled proportional multi-way valves 30 for controlling the first variable amplitude hydraulic motor 71 and the second variable amplitude hydraulic motor 72 in the variable amplitude system 7 are opened, hydraulic oil enters the first variable amplitude hydraulic motor 71 and the second variable amplitude hydraulic motor 72 from the pilot-controlled proportional multi-way valve 30 for controlling the first variable amplitude hydraulic motor 71 and the second variable amplitude hydraulic motor 72 in the variable amplitude system 7 through the variable amplitude descending oil supply pipeline 76, and the hydraulic oil passing through the first variable amplitude hydraulic motor 71 and the second variable amplitude hydraulic motor 72 returns to the hydraulic oil tank 1 through the pilot-controlled proportional multi-way valves 30 for controlling the first variable amplitude hydraulic motor 71 and the second variable amplitude hydraulic motor 72 in the variable amplitude system 7; when the first amplitude-varying hydraulic motor 71 and the second amplitude-varying hydraulic motor 72 work, a part of hydraulic oil in the amplitude-varying descending oil supply pipeline 76 opens the amplitude-varying shuttle valve 79, the hydraulic oil entering the amplitude-varying shuttle valve 79 enters the amplitude-varying brake reversing valve 711 through the amplitude-varying brake pressure reducing valve 710, the hydraulic oil reaching the amplitude-varying brake reversing valve 711 shifts the position of the amplitude-varying brake reversing valve 711 through the control end of the amplitude-varying brake reversing valve 711, the hydraulic oil entering the amplitude-varying brake reversing valve 711 enters the amplitude-varying motor braking mechanism 77 through the amplitude-varying brake reversing valve 711, and the amplitude-varying motor braking mechanism 77 is opened; if the hydraulic control proportional multi-way valve 30 of the first amplitude hydraulic motor 71 and the second amplitude hydraulic motor 72 in the amplitude varying system 7 is controlled to reset, the first amplitude varying hydraulic motor and the second amplitude varying hydraulic motor stop working, meanwhile, oil supply stops on a brake oil circuit of the amplitude varying motor, the amplitude varying brake reversing valve 711 resets, hydraulic oil in the amplitude varying motor braking mechanism 77 is removed through the amplitude varying brake reversing valve 711, and the amplitude varying motor braking mechanism 77 resets to limit the rotation of the first amplitude varying hydraulic motor 72 and the second amplitude varying hydraulic motor 72;

the working method of the cable stabilizing system 8 comprises a cable stabilizing retraction working method and a cable stabilizing release working method;

the working method for retracting the stabilizing rope comprises the following steps: firstly, starting a motor 200, driving a main hydraulic pump 21 to work by the motor 200, and pumping hydraulic oil to an input end of a hydraulic control proportional multi-way valve 30 for controlling a cable stabilizing hydraulic motor 81 in a cable stabilizing system 8 under the action of the main hydraulic pump 21; then, a retraction signal is given to the hydraulic control proportional multi-way valve 30 for controlling the cable-stabilizing hydraulic motor 81 in the cable-stabilizing system 8, the hydraulic control proportional multi-way valve 30 for controlling the cable-stabilizing hydraulic motor 81 in the cable-stabilizing system 8 is opened, hydraulic oil enters the cable-stabilizing hydraulic motor 81 from the hydraulic control proportional multi-way valve 30 for controlling the cable-stabilizing hydraulic motor 81 in the cable-stabilizing system 8 through the retraction oil supply pipeline 84 and the cable-stabilizing balance valve 82, and the hydraulic oil passing through the cable-stabilizing hydraulic motor 81 returns to the hydraulic oil tank 1 from the hydraulic control proportional multi-way valve 30 for controlling the cable-stabilizing hydraulic motor 81 in the cable-stabilizing system 8 through the discharge oil supply pipeline 85; meanwhile, the displacement of the cable-stabilizing hydraulic motor 81 is controlled by a rotating speed control system 83 of the cable-stabilizing hydraulic motor 81 to control the speed of retracting the cable-stabilizing;

the stable cable releasing working method comprises the following steps: firstly, starting a motor 200, driving a main hydraulic pump 21 to work by the motor 200, and pumping hydraulic oil to an input end of a hydraulic control proportional multi-way valve 30 for controlling a cable stabilizing hydraulic motor 81 in a cable stabilizing system 8 under the action of the main hydraulic pump 21; then, a signal is sent to the hydraulic control proportional multi-way valve 30 for controlling the cable-stabilizing hydraulic motor 81 in the cable-stabilizing system 8, the hydraulic control proportional multi-way valve 30 for controlling the cable-stabilizing hydraulic motor 81 in the cable-stabilizing system 8 is opened, hydraulic oil enters the cable-stabilizing hydraulic motor 81 from the hydraulic control proportional multi-way valve 30 for controlling the cable-stabilizing hydraulic motor 81 in the cable-stabilizing system 8 through the discharge oil supply pipeline 85, and the hydraulic oil passing through the cable-stabilizing hydraulic motor 81 returns to the hydraulic oil tank 1 from the hydraulic control proportional multi-way valve 30 for controlling the cable-stabilizing hydraulic motor 81 in the cable-stabilizing system 8 through the cable-stabilizing balance valve 82 and the discharge oil supply pipeline 85.

3. Set up the stable system of cable 8 and stabilize the hoist main hook, rock when preventing that the main hook from hoisting the goods, reduce because of the goods rocks the impact to hoist hydraulic system that produces, improve hoist hydraulic system's security.

4. The rotary system 4, the main hoisting system 5 and the auxiliary hoisting system 6 are all provided with confluence valve blocks, so that the hydraulic motors of the same system can work synchronously, and the stability of the hydraulic system of the crane is improved.

Claims

1. A crane hydraulic system is characterized in that: the hydraulic winch comprises a hydraulic oil tank, a main pump assembly, a switch assembly, a rotary system for driving a rotary mechanism, a main hoisting system for driving a main hoisting winch, an auxiliary hoisting system for driving an auxiliary hoisting winch, an amplitude-changing system for driving an amplitude-changing winch and a cable-stabilizing system for driving a cable-stabilizing winch;

the input end of the main pump assembly is connected with a hydraulic oil tank, and the output end of the main pump assembly supplies oil to the amplitude varying system, the main lifting system, the auxiliary lifting system, the rotary system and the cable stabilizing system through the switch assembly;

the main pump assembly comprises more than one main hydraulic pump, and all the main hydraulic pumps are driven by the same motor;

the switch assembly is a hydraulic control proportional multi-way valve;

the rotary system comprises a first rotary hydraulic motor, a second rotary hydraulic motor, a first rotary balance valve bank, a second rotary balance valve bank and a rotary brake pipeline; the hydraulic control proportional multi-way valve is respectively connected with one end of a first rotary hydraulic motor and one end of a second rotary hydraulic motor through a right oil supply pipe, the hydraulic control proportional multi-way valve is respectively connected with the other end of the first rotary hydraulic motor and the other end of the second rotary hydraulic motor through a left oil supply pipe, a first rotary balance valve bank is arranged between the right oil supply pipe of the first rotary hydraulic motor and the left oil supply pipe of the second rotary hydraulic motor, a second rotary balance valve bank is arranged between the left oil supply pipe of the first rotary hydraulic motor and the right oil supply pipe of the second rotary hydraulic motor, the first rotary hydraulic motor and the second rotary hydraulic motor are respectively provided with a rotary brake mechanism, a rotary brake pipeline is arranged between the first rotary balance valve bank and the rotary brake mechanism, and a rotary brake pressure reducing valve, a rotary brake reversing valve and a rotary brake speed regulating valve are sequentially arranged on the rotary brake pipeline;

the main lifting system comprises a main lifting motor, a main pump assembly supplies oil to the main lifting motor through a hydraulic control proportional multi-way valve, the hydraulic control proportional multi-way valve is connected with one end of the main lifting motor through a main hook lifting pipeline, and the hydraulic control proportional multi-way valve is connected with the other end of the main lifting motor through a main hook descending pipeline; a back pressure balance valve is connected between the main lifting motor and the main hook lifting pipeline; the main lifting motor is provided with a main lifting motor brake mechanism, and an oil circuit of the main lifting motor brake mechanism is connected into a main hook ascending pipeline and a main hook descending pipeline through a main lifting shuttle valve; a main lifting brake pressure reducing valve and a main lifting brake reversing valve are sequentially arranged on an oil circuit of the main lifting motor brake mechanism; a main lifting one-way valve is connected in parallel with the main lifting brake pressure reducing valve and the main lifting reversing valve;

the auxiliary lifting system comprises an auxiliary lifting hydraulic motor and an anti-shake valve; the hydraulic control proportional multi-way valve is connected with one end of the auxiliary lifting hydraulic motor through an auxiliary hook ascending pipeline, the hydraulic control proportional multi-way valve is connected with the other end of the auxiliary lifting hydraulic motor through an auxiliary hook descending pipeline, and an anti-shake valve is arranged between the auxiliary hook descending pipeline and the auxiliary lifting hydraulic motor; the auxiliary lifting hydraulic motor is provided with an auxiliary lifting motor brake mechanism and a disc brake mechanism, an oil circuit of the auxiliary lifting motor brake mechanism is connected into an auxiliary hook lifting pipeline and an auxiliary hook descending pipeline through an auxiliary lifting shuttle valve, and an auxiliary lifting brake pressure reducing valve and an auxiliary lifting brake reversing valve are sequentially arranged on an oil circuit of the auxiliary lifting brake mechanism; the two ends of the series connection of the auxiliary lifting brake pressure reducing valve and the auxiliary lifting brake reversing valve are connected in parallel with an auxiliary lifting one-way valve; a disc brake control system is arranged between the hydraulic oil tank and the disc brake mechanism and is respectively communicated with the auxiliary hook ascending pipeline and the auxiliary hook descending pipeline through a disc brake shuttle valve; the anti-shake valve comprises a valve core, a valve body arranged in the valve core, a spring and a push block, wherein the valve core is provided with an A port and a B port, a valve cavity communicated with the A port and the B port is formed in the valve core, the A port is communicated with an auxiliary lifting hydraulic motor, the B port is communicated with an auxiliary hook descending pipeline, the push block is arranged in the valve cavity, the spring is arranged between the valve core and the push block, the valve core is blocked at the B port under the action of the spring in a non-working state, and the A port is communicated with the valve cavity;

the amplitude varying system comprises a first amplitude varying hydraulic motor, a second amplitude varying hydraulic motor, a first auxiliary amplitude varying balance valve and a second amplitude varying balance valve; the hydraulic control proportional multi-way valve is respectively connected with one end of the first variable-amplitude hydraulic motor and one end of the second variable-amplitude hydraulic motor through a variable-amplitude ascending oil supply pipeline, the hydraulic control proportional multi-way valve is respectively connected with the other end of the first variable-amplitude hydraulic motor and the other end of the second variable-amplitude hydraulic motor through a variable-amplitude descending oil supply pipeline, a first variable-amplitude balance valve is arranged on the variable-amplitude ascending oil supply pipeline communicated with the first variable-amplitude hydraulic motor, and a second variable-amplitude balance valve is arranged on the variable-amplitude ascending oil supply pipeline communicated with the second variable-amplitude hydraulic; the first amplitude-variable hydraulic motor and the second amplitude-variable hydraulic motor are provided with amplitude-variable motor brake mechanisms, oil passages of the amplitude-variable motor brake mechanisms are connected into an amplitude-variable ascending oil supply pipeline and an amplitude-variable descending oil supply pipeline through amplitude-variable shuttle valves, and amplitude-variable brake pressure reducing valves and amplitude-variable brake reversing valves are sequentially arranged on the oil passages of the amplitude-variable brake mechanisms; two ends of the amplitude-variable brake pressure reducing valve and the amplitude-variable brake reversing valve which are connected in series are connected in parallel with an amplitude-variable one-way valve;

the cable stabilizing system comprises a cable stabilizing hydraulic motor, a cable stabilizing balance valve and a cable stabilizing hydraulic motor rotating speed control system; the hydraulic control proportional multi-way valve is connected with one end of the cable-stabilizing hydraulic motor through a retracting oil supply pipeline, the hydraulic control proportional multi-way valve is connected with the other end of the cable-stabilizing hydraulic motor through an exhausting oil supply pipeline, and a cable-stabilizing balance valve is arranged between the cable-stabilizing hydraulic motor and the retracting oil supply pipeline; the speed control system of the cable-stabilized hydraulic motor controls the speed of releasing the cable-stabilized hydraulic motor by controlling the displacement of the cable-stabilized hydraulic motor.

2. The crane hydraulic system as claimed in claim 1, wherein: more than one right confluence valve block is connected between the right oil supply pipe of the first rotary hydraulic motor and the right oil supply pipe of the second rotary hydraulic motor, and more than one left confluence valve block is connected between the left oil supply pipe of the first rotary hydraulic motor and the left oil supply pipe of the second rotary hydraulic motor.

3. The crane hydraulic system as claimed in claim 1, wherein: the main hoisting motors are four in number, main hook ascending pipelines of the four main hoisting motors are communicated with each other through a first main hoisting confluence valve block, and main hook descending pipelines of the four main hoisting motors are communicated with each other through a second main hoisting confluence valve block.

4. The crane hydraulic system as claimed in claim 1, wherein: the two auxiliary lifting hydraulic motors are arranged, auxiliary hook ascending pipelines of the two auxiliary lifting hydraulic motors are communicated with each other through a first auxiliary lifting confluence valve block, and auxiliary hook descending pipelines of the two auxiliary lifting hydraulic motors are communicated with each other through a second auxiliary lifting confluence valve block.

5. The crane hydraulic system as claimed in claim 1, wherein: the disc brake control system comprises a disc brake hydraulic pump, a disc brake reversing valve group, a disc brake control shuttle valve, a disc brake energy accumulator valve block, a disc brake energy accumulator, a Y-shaped three-position four-way reversing valve, a disc brake hydraulic control reversing valve, a disc brake oil inlet and oil outlet shuttle valve and a three-way valve; the input end of a disc brake hydraulic pump is communicated with a hydraulic oil tank, the output end of the disc brake hydraulic pump is communicated with a disc brake reversing valve group, two input ends of a disc brake control shuttle valve are communicated with the disc brake reversing valve group, the output end of the disc brake control shuttle valve is communicated with a disc brake energy accumulator valve block, a disc brake energy accumulator is communicated with the disc brake energy accumulator valve block, the output end of the disc brake energy accumulator valve block is respectively communicated with the 1 end of a three-way valve and the P port of a Y-shaped three-position four-way reversing valve, the A port of the Y-shaped three-position four-way reversing valve is communicated with the first end of a disc brake oil inlet and oil outlet shuttle valve, the B port of the Y-shaped three-position four-way reversing valve is communicated with the 2 port of the disc brake hydraulic control reversing valve, the 3 port of the disc brake hydraulic control reversing valve is communicated with the second end of the disc brake oil inlet and oil outlet shuttle valve, the 4 port of the disc brake hydraulic oil control reversing valve is communicated with the hydraulic oil, the disc brake oil inlet and outlet shuttle valve is communicated with the 3 end of the three-way valve, and the 2 end of the three-way valve is communicated with the disc brake mechanism.

6. The crane hydraulic system as claimed in claim 5, wherein: the disc brake energy accumulator valve block comprises an energy storage check valve, an energy storage hydraulic control reversing valve, a first switch, a second switch, an energy storage overflow valve and a disc brake overflow valve, wherein the input end of the energy storage check valve is communicated with the output end of the disc brake control shuttle valve, the output end of the energy storage check valve is communicated with the control end of the energy storage hydraulic control reversing valve, meanwhile, the output end of the energy storage check valve is communicated with the 1 end of the three-way valve and the P port of the Y-shaped three-position four-way reversing valve, the output end of the energy storage check valve is communicated with the disc brake energy accumulator through the first switch, the disc brake energy accumulator is communicated with the hydraulic oil tank through the energy storage overflow valve, the disc brake energy accumulator is communicated with the hydraulic oil tank through the second switch, the input end of the energy storage check valve is communicated with the hydraulic oil.

7. The crane hydraulic system as claimed in claim 1, wherein: the rotation speed control system of the cable-stabilizing hydraulic motor comprises a first cable-stabilizing overflow valve, a first cable-stabilizing two-position three-way hydraulic control reversing valve and a second cable-stabilizing overflow valve which are sequentially connected; a P port of the first cable-stabilizing overflow valve is connected with a retracting oil supply pipeline through a tension valve block, a T port of the first cable-stabilizing overflow valve is connected with an discharging oil supply pipeline, an X port of the first cable-stabilizing overflow valve is connected with a first cable-stabilizing two-position three-way hydraulic control reversing valve, the first cable-stabilizing two-position three-way hydraulic control reversing valve is connected with a second cable-stabilizing overflow valve, and the second cable-stabilizing overflow valve is connected with a hydraulic oil tank; an X port of the first cable stabilizing overflow valve is connected between the tension valve block and the cable stabilizing balance valve through a bidirectional throttle valve; a cable-stabilizing shuttle valve is connected between the oil supply retracting pipeline and the oil supply discharging pipeline, the outlet end of the cable-stabilizing shuttle valve is connected with a cable-stabilizing pressure reducing valve, the outlet end of the cable-stabilizing pressure reducing valve is connected to the control end of the cable-stabilizing hydraulic motor, the outlet end of the cable-stabilizing pressure reducing valve is connected with a cable-stabilizing electromagnetic valve, the cable-stabilizing electromagnetic valve is connected to the control end of the first cable-stabilizing two-position three-way hydraulic control reversing valve, and meanwhile, the cable-stabilizing electromagnetic valve is.

8. The crane hydraulic system as claimed in claim 1, wherein: the hydraulic control proportional multi-way valve comprises a first reversing valve and a second reversing valve for controlling a first rotary hydraulic motor and a second rotary hydraulic motor in a rotary system, a third reversing valve and a fourth reversing valve for controlling a main hoisting motor in a main hoisting system, a fifth reversing valve and a sixth reversing valve for controlling an auxiliary hoisting hydraulic motor in an auxiliary hoisting system, a seventh reversing valve and an eighth reversing valve for controlling a first variable amplitude hydraulic motor and a second variable amplitude hydraulic motor in a variable amplitude system, and a ninth reversing valve for controlling a cable-stabilizing hydraulic motor in a cable-stabilizing system; the first, second, third, fourth, fifth, sixth, seventh, eighth and ninth are three-position seven-way hydraulic control reversing valves.

9. A working method of a hydraulic system of a crane according to any one of claims 1 to 8 comprises a working method of a slewing system, a working method of a main hoisting system, a working method of an auxiliary hoisting system, a working method of a luffing system and a working method of a cable stabilizing system;