CN111285257B - Hydraulic control system of crane - Google Patents
Hydraulic control system of crane Download PDFInfo
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- CN111285257B CN111285257B CN202010073552.0A CN202010073552A CN111285257B CN 111285257 B CN111285257 B CN 111285257B CN 202010073552 A CN202010073552 A CN 202010073552A CN 111285257 B CN111285257 B CN 111285257B
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- valve
- hydraulic control
- lifting
- amplitude
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C13/00—Other constructional features or details
- B66C13/18—Control systems or devices
- B66C13/20—Control systems or devices for non-electric drives
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
- B66C15/00—Safety gear
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
- F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
- F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
- F15B13/08—Assemblies of units, each for the control of a single servomotor only
- F15B13/0803—Modular units
- F15B13/0807—Manifolds
Abstract
The utility model provides a hoist hydraulic control system belongs to the hydraulic control field. When the crane is lifted and amplitude-variable action is linked, the lifting and amplitude-variable motor works. The lifting overflow valve is communicated with a control port of the variable amplitude hydraulic control proportional reversing valve, an outlet of the lifting overflow valve is communicated with a P port of the m-type lifting hydraulic control reversing valve, an A port of the m-type lifting hydraulic control reversing valve is communicated with an oil tank, and a control port of the m-type lifting hydraulic control reversing valve is communicated with an A port of the lifting hydraulic control proportional reversing valve. The oil liquid flowing out of the lifting hydraulic control proportional reversing valve is larger than the set pressure of the m-type lifting hydraulic control reversing valve, the pressure of a control port of the variable amplitude hydraulic control proportional reversing valve is controlled to be the pressure of a lifting overflow valve, the power required by the variable amplitude pump cannot be too high, the variable amplitude module, the rotary pump and the rotary module run in similar oil paths, motors driving the lifting pump, the variable amplitude pump and the rotary pump cannot be in an excess working state, the motors cannot be damaged or shut down due to overheating, and the working efficiency of the crane is ensured.
Description
Technical Field
The disclosure relates to the field of hydraulic control, in particular to a crane hydraulic control system.
Background
The crane is a common mechanical device for lifting or carrying heavy objects, the crane generally has three actions of lifting, amplitude-changing and rotating, the crane is provided with a lifting pump, an amplitude-changing pump and a rotary pump which correspondingly move in lifting, amplitude-changing and rotating, and the lifting pump, the amplitude-changing pump and the rotary pump respectively control a lifting motor, an amplitude-changing motor and a rotary motor to move. In part of cranes, the hoisting pump, the amplitude transformer pump and the rotary pump are connected in series, and the hoisting pump, the amplitude transformer pump and the rotary pump are driven by one crane.
However, when the crane works, the lifting action, the amplitude variation action and the rotation action are linked, and at the moment, if the speed of the crane during lifting, amplitude variation or rotation is too high, the motor is easily damaged or stopped due to too high power, so that the working efficiency of the crane is influenced.
Disclosure of Invention
The embodiment of the disclosure provides a hydraulic control system of a crane, which can avoid the condition that a motor does not have too much power when the crane is in linkage of lifting action, amplitude variation action and rotation action. The technical scheme is as follows:
the embodiment of the disclosure provides a hydraulic control system of a crane, which comprises a lifting module, a variable amplitude module, a rotation module and an oil tank,
the lifting module comprises a lifting pump, a lifting hydraulic control proportional reversing valve, a lifting motor, a lifting shuttle valve, a lifting overflow valve and an m-type lifting hydraulic control reversing valve, the amplitude changing module comprises an amplitude changing pump, an amplitude changing hydraulic control proportional reversing valve, an amplitude changing motor and an amplitude changing shuttle valve, the rotation module comprises a rotary pump, a rotary hydraulic control proportional reversing valve, a rotary motor and a rotary shuttle valve,
the input end of the lifting pump is communicated with the oil tank, the output end of the lifting pump is communicated with a port P of the lifting hydraulic control proportional reversing valve, a port A of the lifting hydraulic control proportional reversing valve is communicated with a port A of the lifting motor, a port B of the lifting motor is communicated with a port B of the lifting hydraulic control proportional reversing valve, a port T of the lifting hydraulic control proportional reversing valve is communicated with the oil tank, an outlet of the lifting shuttle valve is communicated with the control end of the lifting pump, two inlets of the lifting shuttle valve are respectively communicated with the port A and the port B of the lifting motor, an inlet of the lifting overflow valve is communicated with one control port of the amplitude-variable proportional reversing valve, an outlet of the lifting overflow valve is communicated with the port P of the m-type lifting hydraulic control reversing valve, the port A of the m-type lifting hydraulic control reversing valve is communicated with the oil tank, and the port T of the m-type lifting hydraulic control reversing valve is communicated with the oil tank,
the input end of the amplitude-variable pump is communicated with the oil tank, the output end of the amplitude-variable pump is communicated with the port P of the amplitude-variable hydraulic control proportional reversing valve, the port A of the amplitude-variable hydraulic control proportional reversing valve is communicated with the port A of the amplitude-variable motor, the port B of the amplitude-variable motor is communicated with the port B of the amplitude-variable hydraulic control proportional reversing valve, the outlet of the amplitude-variable shuttle valve is communicated with the control end of the amplitude-variable pump, two inlets of the amplitude-variable shuttle valve are respectively communicated with the port A and the port B of the amplitude-variable motor, the input end of the amplitude-variable pump is communicated with the oil tank, the connection relationship among the rotary pump, the rotary hydraulic control proportional reversing valve, the rotary motor, the rotary shuttle valve and the oil tank is correspondingly the same as the connection relationship among the amplitude-variable pump, the amplitude-variable hydraulic control proportional reversing valve, the amplitude-variable motor, the amplitude shuttle valve and the oil tank, the lifting pump, the variable amplitude pump and the rotary pump are all load-sensitive variable pumps, and the lifting pump, the variable amplitude pump and the rotary pump are all driven by the same motor.
Optionally, the lifting module further comprises a lifting sequence valve, an inlet of the lifting sequence valve is communicated with the A of the lifting hydraulic control proportional reversing valve, an outlet of the lifting sequence valve is communicated with a control port of the m-type lifting hydraulic control reversing valve, a control port of the lifting sequence valve is communicated with an inlet of the lifting sequence valve, and a set pressure of the lifting sequence valve is greater than a set pressure of the m-type lifting hydraulic control reversing valve.
Optionally, the lifting module further includes a lifting speed regulating valve, and the lifting speed regulating valve is arranged between a control port of the m-type lifting hydraulic control directional valve and an outlet of the lifting sequence valve.
Optionally, the amplitude module further comprises an amplitude-variable overflow valve and an m-type amplitude-variable hydraulic control reversing valve, an inlet of the amplitude-variable overflow valve is communicated with one control port of the amplitude-variable hydraulic control proportional reversing valve, an outlet of the amplitude-variable overflow valve is communicated with a P port of the m-type amplitude-variable hydraulic control reversing valve, an a port of the m-type amplitude-variable hydraulic control reversing valve is communicated with the oil tank, a T port of the m-type amplitude-variable hydraulic control reversing valve is communicated with the oil tank, and a control port of the m-type amplitude-variable hydraulic control reversing valve is communicated with the a port of the amplitude-variable hydraulic control proportional reversing valve.
Optionally, the amplitude-variable module further includes an amplitude-variable sequence valve, an inlet of the amplitude-variable sequence valve is communicated with an output end of the hoisting pump, an outlet of the amplitude-variable sequence valve is communicated with a control port of the m-type amplitude-variable hydraulic-control reversing valve, a control port of the amplitude-variable sequence valve is communicated with an inlet of the amplitude-variable sequence valve, a set pressure of the amplitude-variable sequence valve is equal to a set pressure of the hoisting sequence valve, and the set pressure of the amplitude-variable sequence valve is greater than the set pressure of the m-type amplitude-variable hydraulic-control reversing valve.
Optionally, the rotary module further includes a rotary overflow valve and an m-type rotary hydraulic control directional control valve, an inlet of the rotary overflow valve is communicated with one control port of the rotary hydraulic control proportional directional control valve, an outlet of the rotary overflow valve is communicated with a port P of the m-type rotary hydraulic control directional control valve, a port a of the m-type rotary hydraulic control directional control valve is communicated with the oil tank, a port T of the m-type rotary hydraulic control directional control valve is communicated with the oil tank, and a control port of the m-type rotary hydraulic control directional control valve is communicated with the port a of the rotary hydraulic control proportional directional control valve.
Optionally, the crane hydraulic control system further comprises a selection valve group, the selection valve group comprises a first m-type hydraulic control directional valve and a second m-type hydraulic control directional valve, a P port of the first m-type hydraulic control directional valve is communicated with the two control ports of the variable amplitude hydraulic control proportional directional valve, an a port of the first m-type hydraulic control directional valve is communicated with an inlet of the variable amplitude overflow valve, a control port of the first m-type hydraulic control directional valve is communicated with an output end of the rotary pump, a T port of the first m-type hydraulic control directional valve is communicated with the oil tank,
the P port of the second m-type hydraulic control reversing valve is communicated with the two control ports of the rotary hydraulic control proportional reversing valve, the A port of the second m-type hydraulic control reversing valve is communicated with the inlet of the rotary overflow valve, the control port of the second m-type hydraulic control reversing valve is communicated with the output end of the amplitude variable pump, and the T port of the second m-type hydraulic control reversing valve is communicated with the oil tank.
Optionally, the set pressure of the first m-type hydraulic control reversing valve is greater than the set pressure of the variable amplitude overflow valve, and the set pressure of the second m-type hydraulic control reversing valve is greater than the set pressure of the rotary overflow valve.
Optionally, the selector valve group further comprises a check valve, and the check valve is arranged between the port P of the first m-type hydraulic control reversing valve and one control port of the luffing hydraulic control proportional reversing valve.
Optionally, the set pressure of the lifting overflow valve is greater than the set pressures of the amplitude-variable overflow valve and the rotary overflow valve.
The beneficial effect that technical scheme that this disclosure embodiment provided brought includes at least: when the crane performs lifting action and simultaneously performs amplitude variation action if needed, in a hydraulic control system of the crane, a lifting pump in a lifting module and an amplitude variation pump in an amplitude variation module extract oil from an oil tank, so that the oil flows out through ports A of a lifting hydraulic control proportional reversing valve and an amplitude variation hydraulic control proportional reversing valve and enters a lifting motor and an amplitude variation motor to enable the crane to complete lifting and amplitude variation action. Because the inlet of the lifting overflow valve is communicated with one control port of the amplitude-variable hydraulic control proportional reversing valve, the outlet of the lifting overflow valve is communicated with the P port of the m-type lifting hydraulic control proportional reversing valve, the A port of the m-type lifting hydraulic control reversing valve is communicated with the oil tank, the T port of the m-type lifting hydraulic control reversing valve is communicated with the oil tank, the control port of the m-type lifting hydraulic control reversing valve is communicated with the A port of the amplitude-variable hydraulic control proportional reversing valve, when the oil liquid flowing out of the A port of the lifting hydraulic control proportional reversing valve is greater than the set pressure of the m-type lifting hydraulic control reversing valve, the P port of the m-type lifting hydraulic control reversing valve is communicated with the A port of the m-type lifting hydraulic control proportional reversing valve, the control port of the amplitude-variable hydraulic control proportional reversing valve is communicated with the oil circuit of the oil tank, the pressure of the control port of the amplitude-variable hydraulic control proportional reversing valve is controlled to be the set pressure of the lifting overflow valve, the valve core opening of the amplitude-variable hydraulic control proportional reversing valve is stabilized at a fixed value, the flow and the rotating speed of the amplitude-variable motor are also stabilized at one value, the amplitude-variable shuttle valve feeds back the required oil of the amplitude-variable motor to the amplitude-variable pump to enable the amplitude-variable pump to work at a proper flow, the required power of the amplitude-variable pump cannot be too high, the output pressure of the amplitude-variable pump in the corresponding amplitude-variable module is limited by an amplitude-variable overflow valve, the output pressure of the rotary pump in the rotary module is limited by a rotary overflow valve, and when the set pressure of the lifting overflow valve, the amplitude-variable overflow valve and the rotary overflow valve is adjusted to enable the lifting pump, the amplitude-variable pump and the rotary pump to work, the motor driving the lifting pump, the amplitude-variable pump and the rotary pump cannot be in an excess working state, the motor cannot be damaged by overheating or shut down, and the working efficiency of the crane is ensured.
Drawings
Fig. 1 is a schematic diagram of a hydraulic control system of a crane according to an embodiment of the disclosure.
Detailed Description
To make the objects, technical solutions and advantages of the present disclosure more apparent, embodiments of the present disclosure will be described in detail with reference to the accompanying drawings.
Fig. 1 is a schematic diagram of a hydraulic control system of a crane according to an embodiment of the present disclosure, and as shown in fig. 1, the hydraulic control system of the crane includes a hoisting module 1, a luffing module 2, a rotation module 3, and an oil tank 4.
The hoisting module 1 comprises a hoisting pump 101, a hoisting hydraulic control proportional reversing valve 102, a hoisting motor 103, a hoisting shuttle valve 104, a hoisting overflow valve 105 and an m-shaped hoisting hydraulic control reversing valve 106, the amplitude changing module 2 comprises an amplitude changing pump 201, an amplitude changing hydraulic control proportional reversing valve 202, an amplitude changing motor 203 and an amplitude changing shuttle valve 204, and the rotation module 3 comprises a rotation pump 301, a rotation hydraulic control proportional reversing valve 302, a rotation motor 303 and a rotation shuttle valve 304.
The input end of a lifting pump 101 is communicated with an oil tank 4, the output end of the lifting pump 101 is communicated with a port P of a lifting hydraulic control proportional reversing valve 102, a port A of the lifting hydraulic control proportional reversing valve 102 is communicated with a port A of a lifting motor 103, a port B of the lifting motor 103 is communicated with a port B of the lifting hydraulic control proportional reversing valve 102, a port T of the lifting hydraulic control proportional reversing valve 102 is communicated with the oil tank 4, the outlet of a lifting shuttle valve 104 is communicated with the control end of the lifting pump 101, two inlets of the lifting shuttle valve 104 are respectively communicated with the port A and the port B of the lifting motor 103, the inlet of a lifting overflow valve 105 is communicated with one control port of a variable amplitude proportional reversing valve 202, the outlet of the lifting overflow valve 105 is communicated with the port P of an m-type lifting hydraulic control reversing valve 106, the port A of the m-type lifting hydraulic control reversing valve 106 is communicated with the oil tank 4, and the port T of the m-type lifting hydraulic control reversing valve 106 is communicated with the oil tank 4.
The input end of the variable amplitude pump 201 is communicated with the oil tank 4, the output end of the variable amplitude pump 201 is communicated with the port P of the variable amplitude hydraulic control proportional reversing valve 202, the port A of the variable amplitude hydraulic control proportional reversing valve 202 is communicated with the port A of the variable amplitude motor 203, the port B of the variable amplitude motor 203 is communicated with the port B of the variable amplitude hydraulic control proportional reversing valve 202, the outlet of the variable amplitude shuttle valve 204 is communicated with the control end of the variable amplitude pump 201, two inlets of the variable amplitude shuttle valve 204 are respectively communicated with the port A and the port B of the variable amplitude motor 203, the input end of the variable amplitude pump 201 is communicated with the oil tank 4, the connection relations among the rotary pump 301, the rotary hydraulic control proportional reversing valve 302, the rotary motor 303, the rotary shuttle valve 304 and the oil tank 4 are correspondingly the same as the connection relations among the variable amplitude pump 201, the variable amplitude hydraulic control proportional reversing valve 202, the variable amplitude motor 203, the variable amplitude shuttle valve 204 and the oil tank 4, and the lifting pump 101, the variable amplitude pump 201 and the rotary pump 301 are load-sensitive variable amplitude pump, and the lifting pump 101, the amplitude transformer 201 and the rotary pump 301 are all driven by the same motor 10.
If the crane needs to perform amplitude variation while performing lifting action, in the hydraulic control system of the crane, the lifting pump 101 in the lifting module 1 and the amplitude variation pump 201 in the amplitude variation module 2 extract oil from the oil tank 4, so that the oil flows out through the openings a of the lifting hydraulic control proportional reversing valve 102 and the amplitude variation hydraulic control proportional reversing valve 202 and enters the lifting motor 103 and the amplitude variation motor 203 to enable the crane to complete lifting and amplitude variation actions. Because the inlet of the lifting overflow valve 105 is communicated with one control port of the variable amplitude hydraulic control proportional reversing valve 202, the outlet of the lifting overflow valve 105 is communicated with the P port of the m-type lifting hydraulic control reversing valve 106, the A port of the m-type lifting hydraulic control reversing valve 106 is communicated with the oil tank 4, and the T port of the m-type lifting hydraulic control reversing valve 106 is communicated with the oil tank 4, when the oil liquid flowing out of the A port of the lifting hydraulic control proportional reversing valve 102 is greater than the set pressure of the m-type lifting hydraulic control reversing valve 106, the P port of the m-type lifting hydraulic control reversing valve 106 is communicated with the A port of the m-type lifting hydraulic control reversing valve 106, the oil path between one control port of the variable amplitude proportional reversing valve 202 and the lifting overflow valve 105 and the oil tank 4 is communicated, the pressure of the control port of the variable amplitude hydraulic control proportional reversing valve 202 is controlled to be the set pressure of the lifting overflow valve 105, the valve core opening of the variable amplitude hydraulic control proportional reversing valve 202 is stabilized at a fixed value, the flow and the rotating speed of the amplitude motor 203 are also stabilized at a value, the amplitude shuttle valve 204 feeds the oil liquid required by the amplitude motor 203 back to the amplitude pump 201, so that the amplitude pump 201 works at a proper flow, and the power required by the amplitude pump 201 is not too high. The output pressure of the amplitude transformer 201 in the corresponding amplitude transformer module 2 is limited by the amplitude transformer overflow valve 205, the output pressure of the rotary pump 301 in the rotary module 3 is limited by the rotary overflow valve 305, and the set pressure of the lifting overflow valve 105, the amplitude transformer overflow valve 205 and the rotary overflow valve 206 is adjusted to ensure that when the lifting pump 101, the amplitude transformer 201 and the rotary pump 301 work, the motors driving the lifting pump 101, the amplitude transformer 201 and the rotary pump 301 are not in an excess working state, the motors are not damaged or shut down due to overheating, and the working efficiency of the crane is ensured.
When the lifting action and the rotation action of the crane are linked, the output pressure of the rotation pump 301 in the rotation module 3 is limited by the rotation overflow valve 305, so that the motors driving the lifting pump 101, the amplitude-change pump 201 and the rotation pump 301 can not be in an excess working state when the lifting action and the rotation action are linked, and the motors can not be damaged by overheating or stopped.
When the oil pressure entering the control port of the lifting hydraulic control proportional directional valve 102 is smaller, the oil pressure entering the control port of the lifting hydraulic control proportional directional valve 102 is lower than the set pressure of the m-type lifting hydraulic control directional valve 106, the PA oil path of the control port of the m-type lifting hydraulic control directional valve 106 is not conducted, and the lifting overflow valve 105 does not work. At this time, the hoisting pump 101 is not limited by the current, and the load of the hydraulic control system of the crane can be reduced. And no matter what working state the crane hydraulic control system is in, the lifting motor 103 in the lifting module 1 can not be limited by current and pressure, thus ensuring the lifting efficiency of the crane.
And the valves used in the crane hydraulic control system are all hydraulic control valves, so that the electric valves are prevented from working, the whole work is stable, and accidents are not easy to happen.
It should be noted that the lifting hydraulic control proportional reversing valve 102, the amplitude variation hydraulic control proportional reversing valve 202 and the rotary hydraulic control proportional reversing valve 302 are three-position four-way proportional reversing valves, and each has two hydraulic control ports. When the lifting hydraulic control proportional reversing valve 102, the amplitude variation hydraulic control proportional reversing valve 202 and the rotary hydraulic control proportional reversing valve 302 respectively work at the left position and the right position, the lifting hydraulic control proportional reversing valve corresponds to the positive rotation and the negative rotation of the lifting motor 103, the amplitude variation motor 203 and the rotary motor 303.
Note that, due to space limitations, reference numerals for the ports P and T of the rotary fluid-controlled proportional directional valve 302 are omitted in fig. 1.
As shown in fig. 1, the group of lifting pumps 101 further comprises a lifting sequence valve 107, an inlet of the lifting sequence valve 107 is communicated with a of the lifting hydraulic control proportional directional control valve 102, an outlet of the lifting sequence valve 107 is communicated with a control port of the m-type lifting hydraulic control directional control valve 106, a control port of the lifting sequence valve 107 is communicated with an inlet of the lifting sequence valve 107, and the set pressure of the lifting sequence valve 107 is greater than the set pressure of the m-type lifting hydraulic control directional control valve 106.
The lifting sequence valve 107 can play a role in buffering, impact on the m-type lifting hydraulic control reversing valve 106 can be reduced, and the set pressure of the lifting sequence valve 107 can be adjusted to a large value to serve as a judgment standard for judging whether the motor 10 can work excessively or not.
As shown in fig. 1, the lifting module 1 may further include a lifting speed regulating valve 108, and the lifting speed regulating valve 108 is disposed between the control port of the m-type lifting hydraulic control directional valve 106 and the outlet of the lifting sequence valve 107.
The lifting speed regulating valve 108 can regulate the speed of oil entering the m-type lifting hydraulic control reversing valve 106, reduce the impact on the m-type lifting hydraulic control reversing valve 106 and regulate the reversing time of the m-type lifting hydraulic control reversing valve 106.
Optionally, the hoisting module 1 may further include a hoisting damping plate 109, and the hoisting damping plate 109 is disposed between the control port of the m-type hoisting hydraulic control directional valve 106 and the outlet of the hoisting sequence valve 107.
The lifting damping plate 109 can further reduce the impact on the m-type lifting hydraulic control directional valve 106, and ensure the stable use of the m-type lifting hydraulic control directional valve 106.
As shown in fig. 1, the variable amplitude module 2 may further include a variable amplitude relief valve 205 and an m-type variable amplitude hydraulic control directional valve 206, an inlet of the variable amplitude relief valve 205 is communicated with one control port of the variable amplitude hydraulic control proportional directional valve 202, an outlet of the variable amplitude relief valve 205 is communicated with a port P of the m-type variable amplitude hydraulic control directional valve 206, a port a of the m-type variable amplitude hydraulic control directional valve 206 is communicated with the oil tank 4, a port T of the m-type variable amplitude hydraulic control directional valve 206 is communicated with the oil tank 4, and a control port of the m-type variable amplitude hydraulic control directional valve 206 is communicated with a port a of the variable amplitude hydraulic control proportional directional valve 202.
The lifting overflow valve 105 and the m-type lifting hydraulic control reversing valve 106 can control the opening amplitude of the variable amplitude hydraulic control reversing valve 206, the variable amplitude overflow valve 205 and the m-type variable amplitude hydraulic control reversing valve 206 added in the variable amplitude module 2 can also control the opening amplitude of the variable amplitude hydraulic control reversing valve 206 according to the output pressure of the lifting pump 101, and finally control the output pressure of the variable amplitude pump 201, and both control the variable amplitude pump 201, so that when the lifting pump 101 and the variable amplitude pump 201 work simultaneously, the motor cannot be overheated.
As shown in fig. 1, the swing module 3 may further include a swing relief valve 305 and an m-type swing pilot-controlled directional valve 306, an inlet of the swing relief valve 305 is communicated with one control port of the swing pilot-controlled proportional directional valve 302, an outlet of the swing relief valve 305 is communicated with a port P of the m-type swing pilot-controlled directional valve 306, a port a of the m-type swing pilot-controlled directional valve 306 is communicated with the oil tank 4, a port T of the m-type swing pilot-controlled directional valve 306 is communicated with the oil tank 4, and a control port of the m-type swing pilot-controlled directional valve 306 is communicated with the port a of the swing pilot-controlled proportional directional valve 302.
The safety factor of the motor 10 can be further improved by arranging the rotary overflow valve 305 and the m-shaped rotary hydraulic control reversing valve 306.
Alternatively, the set pressure of the lift relief valve 105 may be greater than the set pressures of the luffing relief valve 205 and the swing relief valve 305.
The set pressure of the hoisting overflow valve 105 can be larger than the set pressure of the luffing overflow and rotary overflow valve 305, so that the openings of the m-type luffing hydraulic control reversing valve 206 and the m-type rotary hydraulic control reversing valve 306 can be smaller than the opening of the m-type hoisting hydraulic control reversing valve 106, the working speeds of the luffing motor 203 and the rotary motor 303 are smaller than that of the hoisting motor 103, and the stable luffing action and the rotary action can be ensured while the main hoisting operation of the crane is not influenced.
As shown in fig. 1, the lifting module 1 further includes a two-position two-way lifting hydraulic control directional control valve 110, an inlet of the two-position two-way lifting hydraulic control directional control valve 110 is communicated with an output end of the lifting pump 101, an outlet of the two-position two-way lifting hydraulic control directional control valve 110 is communicated with an a port of the lifting motor 103, and a control port of the two-position two-way lifting hydraulic control directional control valve 110 is communicated with a B port of the lifting motor 103.
A two-position two-way lift hydraulic control directional valve 110 is disposed between the lift motor 103 and the output of the lift pump 101. When the lifting motor 103 is stalled when descending, the two-position two-way lifting hydraulic control reversing valve 110 can be used for reversing to adjust the oil pressure of the lifting motor 103, and the lifting motor 103 is ensured to rotate at a stable rotating speed.
As shown in fig. 1, the amplitude module 2 may further include an amplitude sequence valve 207, an inlet of the amplitude sequence valve 207 is communicated with an output end of the hoisting pump 101, an outlet of the amplitude sequence valve 207 is communicated with a control port of the m-type amplitude hydraulic control reversing valve 206, a control port of the amplitude sequence valve 207 is communicated with an inlet of the amplitude sequence valve 207, a set pressure of the amplitude sequence valve 207 is equal to a set pressure of the hoisting sequence valve 107, and the set pressure of the amplitude sequence valve 207 is greater than the set pressure of the m-type amplitude hydraulic control reversing valve 206.
The setting of the amplitude-varying sequence valve 207 in the amplitude-varying module 2 can enable the amplitude-varying sequence valve 207 in the amplitude-varying module 2 to be conducted when the pressure at the output end of the lifting pump 101 is overlarge (the lifting motor 103 has high speed and high power consumption), the set pressure of the amplitude-varying sequence valve 207 is greater than the set pressure of the m-type amplitude-varying pilot-controlled reversing valve 206, and the m-type amplitude-varying pilot-controlled reversing valve 206 is conducted again, so that the amplitude-varying action can be normally carried out while the lifting efficiency of the crane is maximized.
Optionally, a luffing speed regulating valve 208 and a luffing damping plate 209 may also be disposed in the luffing module 2 between the m-type luffing pilot operated directional control valve 206 and the luffing sequence valve 207. For reducing buffering, which the present disclosure does not limit.
Illustratively, the amplitude module 2 further comprises a two-position two-way amplitude-changing hydraulic control reversing valve 210, wherein an inlet of the two-position two-way amplitude-changing hydraulic control reversing valve 210 is communicated with the output end of the amplitude pump 201, an outlet of the two-position two-way amplitude-changing hydraulic control reversing valve 210 is communicated with the port A of the amplitude motor 203, and a control port of the two-position two-way amplitude-changing hydraulic control reversing valve 210 is communicated with the port B of the amplitude motor 203. Stalling of the luffing motor 203 is avoided.
Illustratively, the swing module 3 may further include a swing sequence valve 307, an inlet of the swing sequence valve 307 is communicated with an output end of the lift pump 101, an outlet of the swing sequence valve 307 is communicated with a control port of the m-type swing pilot-controlled directional valve 306, the control port of the swing sequence valve 307 is communicated with an inlet of the swing sequence valve 307, a set pressure of the swing sequence valve 307 is equal to a set pressure of the lift sequence valve 107, and the set pressure of the swing sequence valve 307 is greater than the set pressure of the m-type swing pilot-controlled directional valve 306.
The arrangement of the rotary sequence valve 307 in the rotary module 3 can enable the rotary sequence valve 307 in the rotary module 3 to be conducted when the pressure at the output end of the lifting pump 101 is too large (the lifting motor 103 has high speed and high power consumption), the set pressure of the rotary sequence valve 307 is greater than the set pressure of the m-type rotary hydraulic control reversing valve 306, and the m-type rotary hydraulic control reversing valve 306 is conducted again, so that the rotary action can be normally carried out while the lifting of the crane can be enabled to be maximally efficient.
Optionally, a swing speed valve 308 and a swing damping plate 309 may also be provided in the swing module 3 between the m-type swing pilot-operated directional valve 306 and the swing sequence valve 307. For reducing buffering, which the present disclosure does not limit.
As shown in fig. 1, the rotary module 3 may also include a two-position two-way rotary fluid-operated directional valve 310, an inlet of the two-position two-way rotary fluid-operated directional valve 310 is communicated with an output end of the rotary pump 301, an outlet of the two-position two-way rotary fluid-operated directional valve 310 is communicated with the port a of the rotary motor 303, and a control port of the two-position two-way rotary fluid-operated directional valve 310 is communicated with the port B of the rotary motor 303. Avoiding rotating stall.
Optionally, in the swing module 3, a two-position two-way swing pilot-controlled directional valve 310 may also be provided between the output end of the swing pump 301 and the port B of the swing motor 303.
The speed is limited in two directions of the rotation of the crane.
As shown in fig. 1, the crane hydraulic control system further includes a selection valve group 5, the selection valve group 5 includes a first m-type hydraulic control directional valve 501 and a second m-type hydraulic control directional valve 502, a P port of the first m-type hydraulic control directional valve 501 is communicated with two control ports of the variable amplitude hydraulic control proportional directional valve 202, an a port of the first m-type hydraulic control directional valve 501 is communicated with an inlet of the variable amplitude overflow valve 205, a control port of the first m-type hydraulic control directional valve 501 is communicated with an output end of the rotary pump 301, and a T port of the first m-type hydraulic control directional valve 501 is communicated with the oil tank 4.
The P port of the second m-type hydraulic control reversing valve 502 is communicated with two control ports of the rotary hydraulic control proportional reversing valve 302, the A port of the second m-type hydraulic control reversing valve 502 is communicated with the inlet of the rotary overflow valve 305, the control port of the second m-type hydraulic control reversing valve 502 is communicated with the output end of the variable amplitude pump 201, and the T port of the second m-type hydraulic control reversing valve 502 is communicated with the oil tank 4.
The first m-shaped hydraulic control reversing valve 501 and the second m-shaped hydraulic control reversing valve 502 can respectively increase buffer time between the variable amplitude overflow valve 205 and the variable amplitude pump 201 and between the rotary overflow valve 305 and the rotary pump 301, so that stable use of a hydraulic control system of the crane is ensured.
Alternatively, the set pressure of the first m-type pilot operated directional control valve 501 may be greater than the set pressure of the luffing relief valve 205, and the set pressure of the second m-type pilot operated directional control valve 502 may be greater than the set pressure of the rotary relief valve 305.
The set pressure of the first m-type hydraulic control reversing valve 501 is greater than that of the variable amplitude overflow valve 205, and the set pressure of the second m-type hydraulic control reversing valve 502 is greater than that of the rotary overflow valve 305, so that the oil impact on the variable amplitude overflow valve 205 and the rotary overflow valve 305 can be reduced.
As shown in fig. 1, the selector valve group 5 may further include a check valve 503, and the check valve 503 is disposed between the port P of the first m-type pilot-controlled directional control valve 501 and one control port of the luffing pilot-controlled proportional directional control valve 202. The inlet of the one-way valve 503 is communicated with a control port of the variable amplitude hydraulic control proportional reversing valve 202.
The check valve 503 prevents the oil from flowing backward.
As shown in fig. 1, the crane hydraulic control system may further include a control valve group 6, the control valve group 6 includes a control pump 601, an input end of the control pump 601 is communicated with the oil tank 4, and an output end of the control pump 601 is communicated with the two control ports of the lifting hydraulic control proportional directional valve 102, the two control ports of the variable amplitude hydraulic control proportional directional valve 202, and the two control ports of the rotation hydraulic control proportional directional valve 302. The control is convenient to realize.
The control valve group 6 further comprises a lifting handle valve 602, an amplitude-variable handle valve 603 and a rotary handle valve 604, and the control pump 601 is connected with and disconnected from the two control ports of the lifting hydraulic control proportional directional control valve 102, the two control ports of the amplitude-variable hydraulic control proportional directional control valve 202 and the two control ports of the rotary hydraulic control proportional directional control valve 302, and can be controlled by the lifting handle valve 602, the amplitude-variable handle valve 603 and the rotary handle valve 604 respectively.
A control overflow valve 605 can be added between the control pump 601 and the lifting handle valve 602. The oil pressure of the control oil way is protected from being too high.
In one implementation of the present disclosure, the set pressure of the hoisting sequence valve 107 in the hoisting module 1 may be 10MPa, the set pressure of the hoisting overflow valve 105 may be 2.1MPa, and the set pressure of the m-type hoisting hydraulic control directional valve 106 may be 1.4 MPa.
It should be noted that the lifting action of the crane is linked with the amplitude variation action, if the oil pressure flowing out from the port a of the lifting hydraulic control proportional directional valve 102 is greater than or equal to 10MPa, at this time, the oil pressure flowing out from the port a of the lifting hydraulic control proportional directional valve 102 is higher, the working power of the lifting motor 103 is high, at this time, the opening of the amplitude variation hydraulic control proportional directional valve 202 needs to be controlled to be reduced by the lifting overflow valve 105, the flow is reduced under the condition that the oil pressure is not changed, the speed of the amplitude variation motor 203 is reduced, and overload is avoided.
The set pressure of the amplitude variation sequence valve 207 in the amplitude variation module 2 can be 10MPa, the set pressure of the amplitude variation overflow valve 205 can be 1.5MPa, and the set pressure of the m-type amplitude variation hydraulic control reversing valve 206 can be 1.4 MPa. The set pressure of the first m-type pilot operated directional control valve 501 may be 5.5 MPa.
The set pressure of the swing sequence valve 307 in the swing module 3 may be 10MPa, the set pressure of the swing relief valve 305 may be 1.5MPa, and the set pressure of the m-type swing pilot-operated directional valve 306 may be 1.4 MPa. The set pressure of the second m-type pilot operated directional control valve 502 may be 5.5 MPa.
The above description is intended only to illustrate the preferred embodiments of the present disclosure, and should not be taken as limiting the disclosure, as any modifications, equivalents, improvements and the like which are within the spirit and principle of the present disclosure should be included in the scope of the present disclosure.
Claims (4)
1. A hydraulic control system of a crane comprises a hoisting module (1), a variable amplitude module (2), a rotation module (3) and an oil tank (4), and is characterized in that,
the lifting module (1) comprises a lifting pump (101), a lifting hydraulic control proportional reversing valve (102), a lifting motor (103), a lifting shuttle valve (104), a lifting overflow valve (105) and an m-shaped lifting hydraulic control reversing valve (106), the amplitude changing module (2) comprises an amplitude changing pump (201), an amplitude changing hydraulic control proportional reversing valve (202), an amplitude changing motor (203) and an amplitude changing shuttle valve (204), the rotation module (3) comprises a rotation pump (301), a rotation hydraulic control proportional reversing valve (302), a rotation motor (303) and a rotation shuttle valve (304),
the input end of the lifting pump (101) is communicated with the oil tank (4), the output end of the lifting pump (101) is communicated with the P port of the lifting hydraulic control proportional reversing valve (102), the A port of the lifting hydraulic control proportional reversing valve (102) is communicated with the A port of the lifting motor (103), the B port of the lifting motor (103) is communicated with the B port of the lifting hydraulic control proportional reversing valve (102), the T port of the lifting hydraulic control proportional reversing valve (102) is communicated with the oil tank (4), the outlet of the lifting shuttle valve (104) is communicated with the control end of the lifting pump (101), two inlets of the lifting shuttle valve (104) are respectively communicated with the A port and the B port of the lifting motor (103), the inlet of the overflow valve (105) is communicated with one control port of the variable amplitude hydraulic control proportional reversing valve (202), and the outlet of the overflow valve (105) is communicated with the P port of the m-type lifting reversing valve (106), the opening A of the m-type lifting hydraulic control reversing valve (106) is communicated with the oil tank (4), the opening T of the m-type lifting hydraulic control reversing valve (106) is communicated with the oil tank (4), the lifting module (1) further comprises a lifting sequence valve (107), the inlet of the lifting sequence valve (107) is communicated with the opening A of the lifting hydraulic control proportional reversing valve (102), the outlet of the lifting sequence valve (107) is communicated with the control opening of the m-type lifting hydraulic control reversing valve (106), the control opening of the lifting sequence valve (107) is communicated with the inlet of the lifting sequence valve (107), and the set pressure of the lifting sequence valve (107) is greater than the set pressure of the m-type lifting hydraulic control reversing valve (106),
the input end of the variable amplitude pump (201) is communicated with the oil tank (4), the output end of the variable amplitude pump (201) is communicated with the port P of the variable amplitude hydraulic control proportional reversing valve (202), the port A of the variable amplitude hydraulic control proportional reversing valve (202) is communicated with the port A of the variable amplitude motor (203), the port B of the variable amplitude motor (203) is communicated with the port B of the variable amplitude hydraulic control proportional reversing valve (202), the outlet of the variable amplitude shuttle valve (204) is communicated with the control end of the variable amplitude pump (201), two inlets of the variable amplitude shuttle valve (204) are respectively communicated with the port A and the port B of the variable amplitude motor (203), the connection relationship among the variable amplitude pump (201), the rotary hydraulic control proportional reversing valve (302), the rotary motor (303), the rotary shuttle valve (304) and the oil tank (4) is communicated with the variable amplitude pump (201), the variable amplitude proportional reversing valve (202), The connection relations among the amplitude variation motor (203), the amplitude variation shuttle valve (204) and the oil tank (4) are correspondingly the same, the lifting pump (101), the amplitude variation pump (201) and the rotary pump (301) are all load sensitive variable displacement pumps, and the lifting pump (101), the amplitude variation pump (201) and the rotary pump (301) are all driven by the same motor (10),
the amplitude-changing module (2) further comprises an amplitude-changing overflow valve (205), an m-type amplitude-changing hydraulic control reversing valve (206) and an amplitude-changing sequence valve (207), wherein an inlet of the amplitude-changing overflow valve (205) is communicated with one control port of the amplitude-changing hydraulic control proportional reversing valve (202), an outlet of the amplitude-changing overflow valve (205) is communicated with a P port of the m-type amplitude-changing hydraulic control reversing valve (206), an A port of the m-type amplitude-changing hydraulic control reversing valve (206) is communicated with the oil tank (4), a T port of the m-type amplitude-changing hydraulic control reversing valve (206) is communicated with the oil tank (4), an inlet of the amplitude-changing sequence valve (207) is communicated with an output end of the lifting pump (101), an outlet of the amplitude-changing sequence valve (207) is communicated with a control port of the m-type amplitude-changing hydraulic control reversing valve (206), and a control port of the amplitude-changing sequence valve (207) is communicated with an inlet of the amplitude-changing sequence valve (207), the set pressure of the amplitude-variable sequence valve (207) is equal to the set pressure of the lifting sequence valve (107), the set pressure of the amplitude-variable sequence valve (207) is greater than the set pressure of the m-type amplitude-variable hydraulic control reversing valve (206),
the rotary module (3) further comprises a rotary overflow valve (305), an m-type rotary hydraulic control reversing valve (306) and a rotary sequence valve (307), wherein an inlet of the rotary overflow valve (305) is communicated with one control port of the rotary hydraulic control proportional reversing valve (302), an outlet of the rotary overflow valve (305) is communicated with a port P of the m-type rotary hydraulic control reversing valve (306), a port A of the m-type rotary hydraulic control reversing valve (306) is communicated with the oil tank (4), a port T of the m-type rotary hydraulic control reversing valve (306) is communicated with the oil tank (4),
the inlet of the rotary sequence valve (307) is communicated with the output end of the lifting pump (101), the outlet of the rotary sequence valve (307) is communicated with the control port of the m-type rotary hydraulic control reversing valve (306), the control port of the rotary sequence valve (307) is communicated with the inlet of the rotary sequence valve (307), the set pressure of the rotary sequence valve (307) is equal to the set pressure of the lifting sequence valve (107), the set pressure of the rotary sequence valve (307) is larger than the set pressure of the m-type rotary hydraulic control reversing valve (306),
the crane hydraulic control system further comprises a selection valve group (5), the selection valve group (5) comprises a first m-type hydraulic control reversing valve (501) and a second m-type hydraulic control reversing valve (502), a P port of the first m-type hydraulic control reversing valve (501) is communicated with two control ports of the amplitude-variable hydraulic control proportional reversing valve (202), an A port of the first m-type hydraulic control reversing valve (501) is communicated with an inlet of the amplitude-variable overflow valve (205), a control port of the first m-type hydraulic control reversing valve (501) is communicated with an output end of the rotary pump (301), a T port of the first m-type hydraulic control reversing valve (501) is communicated with the oil tank (4),
the P port of the second m-type hydraulic control reversing valve (502) is communicated with two control ports of the rotary hydraulic control proportional reversing valve (302), the A port of the second m-type hydraulic control reversing valve (502) is communicated with the inlet of the rotary overflow valve (305), the control port of the second m-type hydraulic control reversing valve (502) is communicated with the output end of the variable amplitude pump (201), the T port of the second m-type hydraulic control reversing valve (502) is communicated with the oil tank (4), the set pressure of the first m-type hydraulic control reversing valve (501) is greater than the set pressure of the variable amplitude overflow valve (205), and the set pressure of the second m-type hydraulic control reversing valve (502) is greater than the set pressure of the rotary overflow valve (305).
2. A crane hydraulic control system as claimed in claim 1, characterized in that the lifting module (1) further comprises a lifting speed regulating valve (108), and the lifting speed regulating valve (108) is arranged between a control port of the m-type lifting hydraulic control directional control valve (106) and an outlet of the lifting sequence valve (107).
3. The crane hydraulic control system as claimed in claim 1, wherein the selector valve group (5) further comprises a check valve (503), and the check valve (503) is arranged between the port P of the first m-type pilot-controlled directional control valve (501) and one control port of the luffing pilot-controlled proportional directional control valve (202).
4. The crane hydraulic control system as claimed in claim 1 or 2, characterized in that the set pressure of the lifting overflow valve (105) is greater than the set pressure of the luffing overflow valve (205) and the rotary overflow valve (305).
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109292631A (en) * | 2018-10-31 | 2019-02-01 | 中船华南船舶机械有限公司 | A kind of crane control system and control method |
| CN109356893A (en) * | 2018-10-11 | 2019-02-19 | 武汉船用机械有限责任公司 | The hydraulic control system of luffing loop wheel machine |
| CN109809311A (en) * | 2019-01-31 | 2019-05-28 | 武汉船用机械有限责任公司 | The Hydraulic slewing system and crane of crane |
| CN209242509U (en) * | 2018-10-31 | 2019-08-13 | 中船华南船舶机械有限公司 | A kind of crane hydraulic system |
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Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109356893A (en) * | 2018-10-11 | 2019-02-19 | 武汉船用机械有限责任公司 | The hydraulic control system of luffing loop wheel machine |
| CN109292631A (en) * | 2018-10-31 | 2019-02-01 | 中船华南船舶机械有限公司 | A kind of crane control system and control method |
| CN209242509U (en) * | 2018-10-31 | 2019-08-13 | 中船华南船舶机械有限公司 | A kind of crane hydraulic system |
| CN109809311A (en) * | 2019-01-31 | 2019-05-28 | 武汉船用机械有限责任公司 | The Hydraulic slewing system and crane of crane |
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