CN112268032A - Straight-arm lorry-mounted crane converging multi-way valve device and working method thereof - Google Patents
Straight-arm lorry-mounted crane converging multi-way valve device and working method thereof Download PDFInfo
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- CN112268032A CN112268032A CN202011303146.5A CN202011303146A CN112268032A CN 112268032 A CN112268032 A CN 112268032A CN 202011303146 A CN202011303146 A CN 202011303146A CN 112268032 A CN112268032 A CN 112268032A
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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
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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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- 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
-
- 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/205—Systems with pumps
- F15B2211/20576—Systems with pumps with multiple 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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/78—Control of multiple output members
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Automation & Control Theory (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
A straight-arm lorry-mounted crane confluence multi-way valve device and a working method thereof. Relates to the technical field of hydraulic pressure of straight-arm lorry-mounted cranes, in particular to a confluence multi-way valve device of a straight-arm lorry-mounted crane and a working method thereof. The converging multi-way valve device of the straight-arm lorry-mounted crane and the working method thereof are high in action efficiency of the straight-arm lorry-mounted crane, and can be used for avoiding the problems that an engine is suppressed to be extinguished, the rotation action is not stable during converging in a rotation linkage operation state and the like. A straight-arm lorry-mounted crane confluence multi-way valve device comprises a first pump oil inlet control link, a telescopic reversing link, a winch reversing link, a variable amplitude reversing link, a confluence control link, a rotary reversing link and a second pump oil inlet control link; the first pump oil inlet control union comprises a three-way flow valve I and a load sensitive LS oil path pressure limiting overflow valve. The invention realizes the requirements of light load large flow and heavy load small flow and has the advantages of micromotion and high efficiency.
Description
Technical Field
The invention relates to the technical field of hydraulic pressure of straight-arm lorry-mounted cranes, in particular to a confluence multi-way valve device of a straight-arm lorry-mounted crane and a working method thereof.
Background
The straight arm lorry-mounted crane is a multipurpose machine which is arranged on an automobile chassis and can load and unload heavy objects in a certain range, has the characteristics of quickness, flexibility, convenience and integration of hoisting and transportation, and is widely applied to the fields of hoisting and transportation such as equipment loading and unloading, landscaping, municipal construction and the like. In recent years, with the development of markets and technologies, the times of concepts such as high efficiency, high speed, energy conservation and the like are becoming the technical development trend of lorry-mounted cranes.
The main operation actions of the straight-arm lorry-mounted crane comprise stretching, winding, amplitude variation and rotation, and the multi-way valve for getting on the crane is a core element of the hydraulic action control systems. At present, a single oil pump oil supply and proportional multi-way valve control system is adopted in a main stream of a straight boom lorry-mounted crane, requirements for system flow and pressure are greatly different due to main operation actions of the straight boom crane, an existing single pump oil supply system cannot meet requirements for high efficiency, low energy consumption and accurate control, and meanwhile, due to the limitation of the power characteristics of a chassis engine, a large-displacement single pump system cannot solve the problem of engine pressure-holding flameout under high load pressure.
In the prior patent document, as an invention patent document published by the national office in 2020 and 9 months, named as a confluence proportion multi-way reversing valve for a straight-arm lorry-mounted crane and a working method, the invention patent with the application number of 2020104249733 discloses a confluence proportion multi-way reversing valve for a straight-arm lorry-mounted crane and a working method, load pressure signals are collected from two output working oil ports of a winch combined reversing valve, a multi-way valve device and a working method that a first oil pump and a second oil pump are confluent and the rest states are not confluent during the winch action are adopted, the confluence of two pumps during the winch action can only be realized, the pressure of two sides where the first pump and the second pump are located is required to be the same, otherwise, when the set pressure at one side of the rotary joint is low, the LS oil line pressure at one side of the combined state hoisting joint is reduced by the pressure at one side of the rotary joint, so that the pressure of the whole system in the combined state is not increased; when the pressure settings on the hoisting connection side and the revolving connection side are both high enough, the engine of the chassis may be suppressed to stall due to insufficient output power or torque.
The prior patent document, such as an invention patent document disclosed by the national office in 2017, 12 months, is named as a multi-way reversing device of a lorry-mounted crane, and has the application number of 201710947089.6; the variable-amplitude reversing valve and the telescopic reversing valve are connected with two ends of the oil inlet path in parallel, the rotary reversing valve, the functional module and the oil inlet path are connected in series, and the telescopic reversing valve and the functional module are connected with the oil inlet path in series in sequence after confluence. The switch type multi-way valve is the object related in the device, but not the proportional core multi-way valve, the working connection of the device can not be subjected to any composite operation, the action over-control performance, the flow matching performance and the energy consumption are poor, and the requirements of the technical development of the lorry-mounted crane product at the present stage can not be met.
Disclosure of Invention
Aiming at the problems, the invention provides the straight-arm lorry-mounted crane confluence multi-way valve device and the working method thereof, wherein the straight-arm lorry-mounted crane has high action efficiency, and the problems of engine pressure build-up flameout, unstable rotation action during confluence in a rotation linkage operation state and the like are avoided.
The technical scheme of the invention is as follows: a straight-arm lorry-mounted crane confluence multi-way valve device comprises a first pump oil inlet control link, a telescopic reversing link, a winch reversing link, a variable amplitude reversing link, a confluence control link, a rotary reversing link and a second pump oil inlet control link;
the first pump oil inlet control joint comprises a three-way flow valve I and a load sensitive LS oil path pressure limiting overflow valve;
the telescopic reversing valve comprises a telescopic reversing valve and a two-way pressure matching valve II;
the winch reversing connection comprises a winch reversing valve and a two-way pressure matching valve III;
the variable amplitude reversing connection comprises a variable amplitude reversing valve and a two-way pressure matching valve;
the confluence control union comprises a main oil path hydraulic control switching valve, a one-way valve, a load sensitive LS oil path hydraulic control switching valve and a shuttle valve;
the rotary reversing joint comprises a rotary reversing valve and a two-way pressure matching valve;
the second pump oil inlet joint comprises a three-way flow valve II and a pressure control valve;
the first working oil port of the three-way flow valve, the first working oil port of the telescopic reversing valve, the first working oil port of the winch reversing valve, the first working oil port of the variable amplitude reversing valve, the two working oil ports of the one-way valve, the two working oil ports of the confluence control switching valve, the first working oil port of the rotary reversing valve, the first working oil port of the three-way flow valve and the first working oil port of the pressure control valve are all communicated with an oil inlet P1 of the first pump oil inlet joint and an oil inlet P2 of the second pump oil inlet joint;
the other working oil port of the first three-way flow valve, one oil port of the pilot overflow valve, the second working oil port of the telescopic reversing valve, the second working oil port of the winch reversing valve, the second working oil port of the variable amplitude reversing valve, the second working oil port of the rotary reversing valve, the other working oil port of the second three-way flow valve and the other working oil port of the pressure control valve are all communicated with an oil return port T1 of the first pump oil inlet joint and an oil return port T2 of the second pump oil inlet joint;
the control port of the three-way flow valve I, the control oil port of the two-way pressure matching valve I, the control oil port of the working oil port I, the control oil port of the two-way pressure matching valve II, the working oil port I and the control oil port of the two-way pressure matching valve III are respectively communicated with the working oil port I through the two working oil ports of the hydraulic control switching valve and the control oil port of the two-way pressure matching valve, and are communicated with the oil port MLS1 and the oil port MLS2 to form a load sensitive LS oil path;
the other two working oil ports of the telescopic reversing valve are communicated with the two working oil ports of the pressure matching valve and the other control port;
the other two working oil ports of the winch reversing valve are communicated with the two working oil ports of the pressure matching valve and the other control port;
the other two working oil ports of the variable amplitude reversing valve are communicated with the two working oil ports of the pressure matching valve and the other control port;
the other two working oil ports of the rotary reversing valve are communicated with the two working oil ports of the pressure matching valve and the other control port;
oil outlets A4 and B4 of the rotary control joint are respectively connected with oil inlets at two sides of the shuttle valve, and an oil outlet in the middle of the shuttle valve is communicated with oil passages between a hydraulic control switching valve control oil port and a load sensitive LS oil passage hydraulic control switching valve control oil port.
The pressure control valve is a second pump main oil path pressure limiting valve.
The pressure control valve is an unloading valve or a remote control pressure limiting valve;
and a pilot control oil port of the unloading valve or a pilot control oil port of the remote control pressure limiting valve is communicated with an LS control oil port of the three-way flow valve II.
The MLS1 control oil path is communicated with the oil return port T1 through a damping hole.
And a filter is also arranged between the MLS1 control oil path and the damping hole.
The MLS2 control oil passage is in communication with the oil return port T2 through a damping orifice.
The telescopic reversing valve further comprises a pressure limiting overflow valve I and a pressure limiting overflow valve II;
an oil inlet of the first pressure limiting overflow valve and an oil inlet of the second pressure limiting overflow valve are respectively communicated with the telescopic reversing valve;
and the oil outlet of the first pressure limiting overflow valve and the oil outlet of the second pressure limiting overflow valve are respectively communicated with the valve body oil return port T1 and the valve body oil return port T2.
A working method of a confluence multi-way valve device of a straight-arm lorry-mounted crane,
when the crane is in an idle state:
the telescopic reversing connection, the winch reversing connection, the amplitude-variable reversing connection, the confluence control connection and the rotary reversing connection do not work; the main oil circuit hydraulic control switching valve and the load sensitive LS oil circuit hydraulic control switching valve in the confluence control joint are respectively communicated due to respective normally open functions; hydraulic oil of a first oil pump in the first oil pumping control unit is converged in the multi-way valve through an oil port P1, and hydraulic oil of a second oil pump in the second oil pumping control unit is converged through an oil port P2; because the load-sensitive LS oil circuit has no feedback pressure, the three-way flow valve I and the three-way flow valve II are opened for unloading, so that hydraulic oil of the two oil pumps flows back to the oil tank through the oil return port T1 and the oil return port T2;
when the rotary reversing connection works independently and the telescopic reversing connection, the winch reversing connection and the amplitude-variable reversing connection do not work:
the confluence control joint middle shuttle valve respectively acquires the load pressures of a working oil port A4 and a working oil port B4 of the rotary reversing valve, selects high-pressure signals of the working oil port A4 and the working oil port B4 and inputs the high-pressure signals of the working oil port A4 and the working oil port B4 to a main oil path hydraulic control switching valve and a switching valve to control the oil ports, controls the main oil path switching valve and the load sensitive LS oil path hydraulic control switching valve to simultaneously disconnect oil paths, enables a P2 oil port of a second oil;
when the rotary reversing connection does not work and any one of the telescopic reversing connection, the winch reversing connection and the variable amplitude reversing connection works:
the shuttle valve in the confluence control union cannot detect a high-pressure signal, the main oil circuit hydraulic control switching valve and the load sensitive LS oil circuit hydraulic control switching valve do not act and are respectively in a conduction state due to respective normally open functions, so that hydraulic oil of a first oil pump and hydraulic oil of a second oil pump through an oil port P2 are converged in the multi-way valve through an oil port P1, a load sensitive LS oil circuit pressure limiting overflow valve acquires the highest load pressure in a telescopic reversing union, a winch reversing union and a variable amplitude reversing union, the highest load pressure is transmitted to control oil ports of a three-way flow valve I and a three-way flow valve II at the same time, the first oil pump and the second oil pump are simultaneously converged to supply oil, and the pressure of the converged oil supply is increased along with the increase;
the pressure-limiting overflow valve in the first pump oil inlet joint is generally higher than the pressure setting of the pressure-limiting overflow valve in the second pump oil inlet joint, so that when the system pressure is increased and reaches the pressure setting of the pressure-limiting overflow valve in the second pump oil inlet joint, the pressure-limiting overflow valve in the second pump oil inlet joint firstly acts to limit the continuous increase of the output pressure of the second pump, meanwhile, the one-way valve in the confluence joint is closed, the working confluence state of the first pump and the second pump is changed into the shunting state, the first pump oil inlet joint, the telescopic reversing valve joint, the variable amplitude reversing joint and the winch reversing joint are not limited by the pressure setting of the pressure-limiting overflow valve in the second pump oil inlet joint, and the pressure of the first pump system can still continuously increase along with the increase of the load until the pressure setting of the load-sensitive LS oil path pressure-limiting overflow valve in the first pump oil inlet joint is reached;
when the rotary reversing linkage works and at least one of the telescopic reversing linkage, the winch reversing linkage and the amplitude-variable reversing linkage works:
a shuttle valve in the confluence control union acquires the load pressure of a working oil port A4 and a working oil port B4 of a rotary reversing valve, high-pressure signals of the two are selected to be input to a main oil path hydraulic control switching valve and a load sensitive LS oil path hydraulic control switching valve to control oil ports, the main oil path hydraulic control switching valve and the load sensitive LS oil path hydraulic control switching valve are controlled to simultaneously disconnect oil paths, a P2 oil port of a second oil pump supplies oil and is independently used for a rotary reversing union to carry out crane rotary operation, and a P1 oil port of a first oil pump supplies oil and is independently used for working union operation in a telescopic reversing union, a winch reversing union and a variable amplitude reversing union.
The invention achieves the following beneficial effects:
compared with a single-pump control system, the single large-displacement oil pump is selected for meeting all action requirements, on one hand, the hydraulic oil flow requirement is small during the rotation joint operation, the control micro-mobility and the flow matching property are poor, and the system energy consumption is large; on the other hand, when other linkages except the slewing linkage act, the flow demand on the hydraulic system is high in order to improve the working efficiency, and under the condition that the output power and the output torque of the chassis engine are constant, the displacement selected by the large pump cannot be further increased in order to ensure that the system is not subjected to pressure-holding and flameout. The present invention provides a method that solves both of the above-mentioned problems.
The invention preferentially ensures the stability of the operation and control of the rotary joint and eliminates the impact of the split-combined flow of the double pumps of the system on the operation of the rotary joint.
For the telescopic link, the variable amplitude link and the winch link, the multi-way valve device is essentially primary system power control under the condition of double-pump confluence and the medium-pressure overflow pressure limiting (or low-pressure unloading) of the second oil pump, can fully exert the capacity of chassis equipment, realizes the requirements of light load large flow and heavy load small flow, and takes the micromotion property and high efficiency into consideration.
Drawings
Figure 1 is a schematic diagram of the principle structure of the invention,
figure 2 is a schematic diagram of the principle structure of the invention two,
in the figure, 1 is a first pump oil inlet control link, 11 is a three-way flow valve I, 12 is a filter, 13 is a damping hole, 14 is a load-sensitive LS oil path pressure-limiting overflow valve, 2 is a telescopic reversing link, 21 is a telescopic reversing valve, 22 is a two-way pressure matching valve I, 23 is a pressure-limiting overflow valve, 24 is a pressure-limiting overflow valve, 3 is a winch reversing link, 31 is a winch reversing valve, 32 is a two-way pressure matching valve II, 33 is a pressure-limiting overflow valve, 34 is a pressure-limiting overflow valve, 4 is an amplitude-changing reversing link, 41 is an amplitude-changing reversing valve, 42 is a two-way pressure matching valve III, 43 is a pressure-limiting overflow valve, 44 is a pressure-limiting overflow valve, 5 is a confluence control link, 51 is a main oil path hydraulic control switching valve, 52 is a one-way valve, 53 is a load-sensitive LS oil path hydraulic control switching valve, 54 is a shuttle valve, 6 is a rotary reversing link, 61 is a rotary reversing, And 64 is a pressure-limiting overflow valve, 7 is a second pump oil inlet joint, 71 is a three-way flow valve II, 72 is a damping hole, 73-1 is a second pump main oil way pressure-limiting overflow valve, and 73-2 is an unloading valve.
Detailed Description
Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.
In the following, referring to fig. 1 and fig. 2, MLS1 and MLS2 are respectively pressure measuring oil ports for load-sensitive oil paths according to the embodiment of the present invention; p1 is a first oil supply port, P2 is a second oil supply port; MP1 is a first oil pump pressure measuring port, MP2 is a second oil pump pressure measuring port; A1-A4 and B1-B4 are respectively working oil ports of each reversing link; t1 and T2 are oil return ports, respectively.
A straight-arm lorry-mounted crane confluence multi-way valve device comprises a first pump oil inlet control joint 1, a telescopic reversing joint 2, a winch reversing joint 3, a variable amplitude reversing joint 4, a confluence control joint 5, a rotary reversing joint 6 and a second pump oil inlet control joint 7;
the first pump oil inlet control unit 1 comprises a three-way flow valve I11 and a load sensitive LS oil path pressure limiting overflow valve 14;
the telescopic reversing valve 2 comprises a telescopic reversing valve 21 and a two-way pressure matching valve II 22;
the winch reversing connection 3 comprises a winch reversing valve 31 and a two-way pressure matching valve III 32;
the variable amplitude reversing connection 4 comprises a variable amplitude reversing valve 41 and a two-way pressure matching valve 42;
the confluence control block 5 comprises a main oil line hydraulic control switching valve 51, a one-way valve 52, a load sensitive LS oil line hydraulic control switching valve 53 and a shuttle valve 54;
the rotary reversing joint 6 comprises a rotary reversing valve 61 and a two-way pressure matching valve six 62;
the second pump oil inlet joint 7 comprises a three-way flow valve II 71 and a pressure control valve;
the first working oil port of the three-way flow valve 11, the first working oil port of the telescopic reversing valve 21, the first working oil port of the winch reversing valve 31, the first working oil port of the amplitude-variable reversing valve 41, the two working oil ports of the one-way valve 52, the two working oil ports of the confluence control switching valve 51, the first working oil port of the rotary reversing valve 61, the first working oil port of the three-way flow valve 71 and the first working oil port of the pressure control valve are all communicated with an oil inlet P1 of the first pump oil inlet joint 1 and an oil inlet P2 of the second pump oil inlet joint 7;
the other working oil port of the three-way flow valve I11, one oil port of the pilot overflow valve 14, the second working oil port of the telescopic reversing valve 21, the second working oil port of the winch reversing valve 31, the second working oil port of the variable amplitude reversing valve 41, the second working oil port of the rotary reversing valve 61, the other working oil port of the three-way flow valve II 71 and the other working oil port of the pressure control valve are all communicated with an oil return port T1 of the first pump oil inlet connection 1 and an oil return port T2 of the second pump oil inlet connection 7;
the control port of the three-way flow valve I11, the control oil port of the two-way pressure matching valve I22 and the working oil port I, the control oil port of the two-way pressure matching valve II 32 and the working oil port I, and the control oil port and the working oil port I of the two-way pressure matching valve III 42 are respectively communicated with the control oil port and the working oil port I of the two-way pressure matching valve 62 through the two working oil ports of the hydraulic control switching valve 53 and are communicated with the oil port MLS1 and the oil port MLS2 to form a load sensitive LS oil path;
further optimization, a plurality of pressure limiting overflow valves such as a pressure limiting overflow valve I23, a pressure limiting overflow valve II 24, a pressure limiting overflow valve III 33, a pressure limiting overflow valve IV 34, a pressure limiting overflow valve V43, a pressure limiting overflow valve VI 44, a pressure limiting overflow valve VII 63 and a pressure limiting overflow valve VIII 64 can be assembled and selectively at working oil ports of the telescopic reversing valve, the hoisting reversing valve, the amplitude-changing reversing valve and the rotary reversing valve, such as A1, B1, A2, B2, A3, B3, A4 and B4; the oil inlet of the pressure-limiting overflow valve of each oil port of the reversing connection is communicated with the working oil port of the corresponding reversing connection reversing valve, and the oil return port of the pressure-limiting overflow valve is communicated with the oil return ports T1 and T2 of the valve body.
The other two working oil ports of the telescopic reversing valve 21 are communicated with the two working oil ports of the pressure matching valve 22 and the other control port;
the other two working oil ports of the winch reversing valve 31 are communicated with the two working oil ports of the pressure matching valve 32 and the other control port;
the other two working oil ports of the variable amplitude reversing valve 41 are communicated with the two working oil ports of the pressure matching valve 42 and the other control port;
the other two working oil ports of the rotary reversing valve 61 are communicated with the two working oil ports of the pressure matching valve 62 and the other control port;
oil outlets A4 and B4 of the rotary control unit 6 are respectively connected with oil inlets at two sides of the shuttle valve 54, and a middle oil outlet of the shuttle valve 54 is communicated with oil passages between a control oil port of the hydraulic control switching valve 51 and a control oil port of the load sensitive LS oil passage hydraulic control switching valve 53.
As shown in fig. 1, the pressure control valve is a second pump main oil passage pressure-limiting valve 73-1.
The pressure control valve is an unloading valve (shown in figure 2) or a remote control pressure limiting valve;
and a pilot control oil port of the unloading valve or a pilot control oil port of the remote control pressure limiting valve is communicated with an LS control oil port of the three-way flow valve II 71.
The MLS1 control oil passage is communicated with the oil return port T1 through a damping hole 13.
And a filter 12 is also arranged between the MLS1 control oil path and the damping hole 13.
The MLS2 control oil passage communicates with the oil return T2 through the orifice 72.
The telescopic reversing valve 2 further comprises a first pressure limiting overflow valve 23 and a second pressure limiting overflow valve 24;
the oil inlet of the first pressure limiting overflow valve 23 and the oil inlet of the second pressure limiting overflow valve 24 are respectively communicated with the telescopic reversing valve 21;
the oil outlet of the first pressure limiting overflow valve 23 and the oil outlet of the second pressure limiting overflow valve 24 are respectively communicated with a valve body oil return port T1 and a valve body oil return port T2.
The winch reversing connection 3 further comprises a third pressure limiting overflow valve 33 and a fourth pressure limiting overflow valve 34;
the oil inlet of the third pressure limiting overflow valve 33 and the oil inlet of the fourth pressure limiting overflow valve 34 are respectively communicated with the winch reversing valve 31;
and the oil outlet of the third pressure limiting overflow valve 33 and the oil outlet of the fourth pressure limiting overflow valve 34 are respectively communicated with a valve body oil return port T1 and a valve body oil return port T2.
The amplitude-variable reversing connection 4 also comprises a pressure-limiting overflow valve five 43 and a pressure-limiting overflow valve six 44;
the oil inlet of the pressure limiting overflow valve five 43 and the oil inlet of the pressure limiting overflow valve six 44 are respectively communicated with the amplitude-variable reversing valve 41;
the oil outlet of the pressure limiting overflow valve five 43 and the oil outlet of the pressure limiting overflow valve six 44 are respectively communicated with a valve body oil return port T1 and a valve body oil return port T2;
the rotary reversing joint 6 comprises a pressure-limiting overflow valve seven 63 and a pressure-limiting overflow valve eight 64;
the oil inlet of the pressure limiting overflow valve seven 63 and the oil inlet of the pressure limiting overflow valve eight 64 are respectively communicated with the rotary reversing valve 61;
the oil outlet of the pressure limiting overflow valve seven 63 and the oil outlet of the pressure limiting overflow valve eight 64 are respectively communicated with a valve body oil return port T1 and a valve body oil return port T2.
A working method of a confluence multi-way valve device of a straight-arm lorry-mounted crane,
when the crane is in an idle state:
the telescopic reversing connection 2, the winch reversing connection 3, the amplitude-variable reversing connection 4, the confluence control connection 5 and the rotary reversing connection 6 do not work; the main oil line hydraulic control switching valve 51 and the load sensitive LS oil line hydraulic control switching valve 53 in the confluence control unit 5 are respectively communicated due to respective normally open functions; hydraulic oil of a first oil pump in the first oil pumping control unit 1 flows through an oil port P1, and hydraulic oil of a second oil pump in the second oil pumping control unit 7 flows through an oil port P2 in the multi-way valve respectively; because the load-sensitive LS oil path has no feedback pressure, the three-way flow valve I11 and the three-way flow valve II 71 are opened for unloading, so that the hydraulic oil of the two oil pumps flows back to the oil tank through the oil return port T1 and the oil return port T2; the system only maintains a very low standby pressure.
When the rotary reversing connection 6 works independently and the telescopic reversing connection 2, the winch reversing connection 3 and the amplitude-variable reversing connection 4 do not work:
the shuttle valve 54 in the confluence control joint 5 respectively acquires the load pressures of a working oil port A4 and a working oil port B4 of the rotary reversing valve 61, selects high-pressure signals of the two to input to control oil ports of the main oil path hydraulic control switching valve 51 and the load-sensitive LS oil path hydraulic control switching valve 53, controls the main oil path switching valve 51 and the load-sensitive LS oil path hydraulic control switching valve 53 to simultaneously disconnect oil paths, enables a P2 oil port of a second oil pump to supply oil, and is independently used for the rotary reversing joint 6 to perform crane rotary operation;
when the rotary reversing connection 6 does not work, and any one of the telescopic reversing connection 2, the winch reversing connection 3 and the variable amplitude reversing connection 4 works:
the shuttle valve 54 in the confluence control link 5 cannot detect a high-pressure signal, the main oil path hydraulic control switching valve 51 and the load sensitive LS oil path hydraulic control switching valve 53 do not act and are respectively in a conduction state due to respective normally open functions, so that hydraulic oil of a first oil pump and hydraulic oil of a second oil pump through an oil port P2 are converged in the multi-way valve, the load sensitive LS oil path pressure limiting overflow valve 14 acquires the highest load pressure in the telescopic reversing link 2, the winch reversing link 3 and the variable amplitude reversing link 4, the highest load pressure is transmitted to the control oil ports of the three-way flow valve I11 and the three-way flow valve II 71 at the same time, the first oil pump and the second oil pump are converged at the same time, and the pressure of the converged oil supply is increased along with the increase of the system pressure;
because the set pressure of the pressure-limiting overflow valve 14 in the first pumping oil inlet joint 1 is generally higher than the set pressure of the pressure control valve in the second pumping oil inlet joint 7, therefore, as the system pressure increases and the set pressure of the pressure control valve in the second pumping manifold 7 is reached, the pressure control valve in the second pump inlet manifold 7 acts first to limit the continuous increase of the output pressure of the second pump, meanwhile, the one-way valve in the confluence couple 5 is closed, the working confluence state of the first pump and the second pump is changed into a shunting state, the first pump oil inlet couple 1, the telescopic reversing valve couple 2, the amplitude-variable reversing couple 3 and the winch reversing couple 4 are not limited by the set pressure of the pressure control valve in the second pump oil inlet couple 7, and the pressure of the first pump system can still continuously increase along with the rise of the load until the set pressure of the load-sensitive LS oil path pressure-limiting overflow valve 14 in the first pump oil inlet couple 1 is reached;
when the rotary reversing linkage 6 works and at least one of the telescopic reversing linkage 2, the winch reversing linkage 3 and the amplitude-variable reversing linkage 4 works:
the shuttle valve 54 in the confluence control joint 5 acquires the load pressure of the working oil port A4 and the working oil port B4 of the rotary reversing valve 61, selects high-pressure signals of the two to input to the control oil ports of the main oil path hydraulic control switching valve 51 and the load sensitive LS oil path hydraulic control switching valve 53, controls the main oil path hydraulic control switching valve 51 and the load sensitive LS oil path hydraulic control switching valve 53 to simultaneously cut off oil paths, and enables the P2 oil port of the second oil pump to supply oil which is independently used for the rotary reversing joint 6 to perform crane rotary operation, and the P1 oil port of the first oil pump to supply oil which is independently used for the working joint operation in the telescopic reversing joint 2, the winch reversing joint 3 and the luffing reversing joint.
The first oil pump oil inlet connection 1 adopts a load sensitive LS oil path pressure limiting overflow valve 14 to pilot control a three-way flow valve I11, realizes the pressure limiting of a main oil path, and generally sets higher pressure so as to meet the requirement of high load pressure of a telescopic reversing connection 2, a winch reversing connection 3 and a variable amplitude reversing connection 4;
the second oil pump oil inlet connection 7 adopts a main oil path overflow valve for direct pressure limiting, and the generally set pressure is lower, so that the requirement of the actual working pressure of the rotary reversing connection 6 can be met, the control port of a three-way flow valve II 71 on the second oil pump oil inlet connection 7 is directly communicated with a load sensitive LS oil path, when the rotary reversing connection 6 works, the pressure of the load of the rotary reversing connection 6 is fed back, when the rotary reversing connection 6 does not work, the load pressure of other connections except the rotary reversing connection 6 is fed back, the three-way flow valve 71 is also controlled by the pilot pressure limiting of the load sensitive LS oil path pressure limiting overflow valve 14 on the first oil pump oil inlet connection 1 in the multi-way valve confluence state, namely the pressure limiting set pressure of the three-way flow valve 71 is the same as the pressure limiting set pressure of the three-way. When the rotary reversing connection 6 does not work and the multi-way valve is in a confluence state in a drawing, the pressure of an oil port P1 of the first oil pump and an oil port P2 of the second oil pump is increased, when the load pressure is increased to the pressure limiting value of a medium-pressure second pump main oil way pressure limiting overflow valve 73-1 of a main oil way on the second pump oil inlet connection 7, the medium-pressure limiting of the overflow valve (if an unloading valve is adopted, low-pressure unloading is adopted), a main oil way one-way valve 52 in the confluence control connection 5 is cut off, the taken load of the second oil pump such as the power or torque of an engine is not increased, but the pressure of the first oil pump can be continuously increased along with the increase of the load until the high-pressure load sensitive LS oil way pressure limiting overflow valve 14 of the first pump oil inlet connection 1 overflows and the three-way flow valve 11 is triggered to perform pressure limiting action. Therefore, the discharge capacity of the double quantitative pump can be properly increased to obtain the high-speed operation requirement of the crane under no-load or low-load pressure;
if the engine has a phenomenon of immobility, the set pressure of an overflow valve or an unloading valve on the oil inlet joint 7 can be properly reduced, the maximum power or the maximum torque of the second oil pump for taking the engine is reduced, and the balance between the load taken by the hydraulic system and the output of the engine is ensured.
The disclosure of the present application also includes the following points:
1) the drawings of the embodiments disclosed herein only relate to the structures related to the embodiments disclosed herein, and other structures can refer to general designs;
2) in case of conflict, the embodiments and features of the embodiments disclosed in this application can be combined with each other to arrive at new embodiments;
the above embodiments are only embodiments disclosed in the present disclosure, but the scope of the disclosure is not limited thereto, and the scope of the disclosure should be determined by the scope of the claims.
Claims (10)
1. A straight-arm lorry-mounted crane confluence multi-way valve device is characterized by comprising a first pump oil inlet control unit (1), a telescopic reversing unit (2), a winch reversing unit (3), a variable amplitude reversing unit (4), a confluence control unit (5), a rotary reversing unit (6) and a second pump oil inlet control unit (7);
the first pump oil inlet control unit (1) comprises a three-way flow valve I (11) and a load sensitive LS oil path pressure limiting overflow valve (14);
the telescopic reversing valve (2) comprises a telescopic reversing valve (21) and a two-way pressure matching valve II (22);
the winch reversing connection (3) comprises a winch reversing valve (31) and a two-way pressure matching valve III (32);
the amplitude-variable reversing union (4) comprises an amplitude-variable reversing valve (41) and a two-way pressure matching valve (42);
the confluence control union (5) comprises a main oil path hydraulic control switching valve (51), a one-way valve (52), a load sensitive LS oil path hydraulic control switching valve (53) and a shuttle valve (54);
the rotary reversing union (6) comprises a rotary reversing valve (61) and a two-way pressure matching valve six (62);
the second pump oil inlet joint (7) comprises a three-way flow valve II (71) and a pressure control valve;
a first working oil port of the three-way flow valve (11), a first working oil port of the telescopic reversing valve (21), a first working oil port of the winch reversing valve (31), a first working oil port of the amplitude-variable reversing valve (41), two working oil ports of the one-way valve (52), two working oil ports of the confluence control switching valve (51), a first working oil port of the rotary reversing valve (61), a first working oil port of the three-way flow valve (71) and a first working oil port of the pressure control valve are all communicated with an oil inlet P1 of the first pump oil inlet joint (1) and an oil inlet P2 of the second pump oil inlet joint (7);
the other working oil port of the three-way flow valve I (11), one oil port of the pilot overflow valve (14), the second working oil port of the telescopic reversing valve (21), the second working oil port of the winch reversing valve (31), the second working oil port of the amplitude-variable reversing valve (41), the second working oil port of the rotary reversing valve (61), the other working oil port of the three-way flow valve II (71) and the other working oil port of the pressure control valve are all communicated with an oil return port T1 of the first pump oil inlet connection (1) and an oil return port T2 of the second pump oil inlet connection (7);
the control port of the three-way flow valve I (11), the control oil port of the two-way pressure matching valve I (22) and the working oil port I, the control oil port of the two-way pressure matching valve II (32) and the control oil port of the working oil port I and the control oil port I of the two-way pressure matching valve III (42) are respectively communicated with the working oil port I through the two working oil ports of the hydraulic control switching valve (53) and the control oil port of the two-way pressure matching valve (62) and are communicated with the oil ports MLS1 and MLS2 to form a load sensitive LS oil circuit;
the other two working oil ports of the telescopic reversing valve (21) are communicated with the two working oil ports and the other control port of the pressure matching valve (22);
the other two working oil ports of the winch reversing valve (31) are communicated with the two working oil ports and the other control port of the pressure matching valve (32);
the other two working oil ports of the variable amplitude reversing valve (41) are communicated with the two working oil ports and the other control port of the pressure matching valve (42);
the other two working oil ports of the rotary reversing valve (61) are communicated with the two working oil ports of the pressure matching valve (62) and the other control port;
oil outlets A4 and B4 of the rotary control unit (6) are respectively connected with oil inlets at two sides of the shuttle valve (54), and an oil outlet in the middle of the shuttle valve (54) is communicated with oil paths between a control oil port of the hydraulic control switching valve (51) and a control oil port of the load sensitive LS oil path hydraulic control switching valve (53).
2. The confluence multi-way valve device of a straight-arm lorry-mounted crane as claimed in claim 1, wherein the pressure control valve is a second pump main oil circuit pressure limiting valve (73-1).
3. The confluence multi-way valve device of a straight-arm lorry-mounted crane as claimed in claim 1, wherein the pressure control valve is an unloading valve or a remote control pressure limiting valve;
and a pilot control oil port of the unloading valve or a pilot control oil port of the remote control pressure limiting valve is communicated with an LS control oil port of the three-way flow valve II (71).
4. The confluence multi-way valve device for the straight-arm lorry-mounted crane according to claim 1, wherein the MLS1 control oil path is communicated with the oil return port T1 through a damping hole (13).
5. The confluence multi-way valve device for the straight-arm lorry-mounted crane according to claim 4, wherein a filter (12) is further arranged between the MLS1 control oil path and the damping hole (13).
6. The straight arm lorry-mounted crane confluence multi-way valve device as claimed in claim 1, wherein the MLS2 control oil way is communicated with the oil return port T2 through a damping hole (72).
7. The confluence multi-way valve device of the straight-arm lorry-mounted crane as claimed in claim 1, wherein the telescopic reversing valve (2) further comprises a first pressure limiting overflow valve (23) and a second pressure limiting overflow valve (24);
an oil inlet of the pressure limiting overflow valve I (23) and an oil inlet of the pressure limiting overflow valve II (24) are respectively communicated with the telescopic reversing valve (21);
the oil outlet of the pressure limiting overflow valve I (23) and the oil outlet of the pressure limiting overflow valve II (24) are respectively communicated with the valve body oil return port T1 and the valve body oil return port T2.
8. The confluence multi-way valve device of the straight-arm lorry-mounted crane as claimed in claim 1, wherein the winch reversing joint (3) further comprises a third pressure limiting overflow valve (33) and a fourth pressure limiting overflow valve (34);
an oil inlet of the third pressure limiting overflow valve (33) and an oil inlet of the fourth pressure limiting overflow valve (34) are respectively communicated with the winch reversing valve (31);
and the oil outlet of the pressure limiting overflow valve III (33) and the oil outlet of the pressure limiting overflow valve IV (34) are respectively communicated with a valve body oil return port T1 and a valve body oil return port T2.
9. The confluence multi-way valve device of the straight-arm lorry-mounted crane as claimed in claim 1, wherein the amplitude-varying reversing union (4) further comprises a pressure-limiting overflow valve five (43) and a pressure-limiting overflow valve six (44);
the oil inlet of the pressure limiting overflow valve five (43) and the oil inlet of the pressure limiting overflow valve six (44) are respectively communicated with the amplitude-variable reversing valve (41);
the oil outlet of the pressure limiting overflow valve five (43) and the oil outlet of the pressure limiting overflow valve six (44) are respectively communicated with a valve body oil return port T1 and a valve body oil return port T2;
the rotary reversing joint (6) comprises a pressure-limiting overflow valve seven (63) and a pressure-limiting overflow valve eight (64);
the oil inlet of the pressure limiting overflow valve seven (63) and the oil inlet of the pressure limiting overflow valve eight (64) are respectively communicated with the rotary reversing valve (61);
the oil outlet of the pressure limiting overflow valve seven (63) and the oil outlet of the pressure limiting overflow valve eight (64) are respectively communicated with the valve body oil return ports T1 and T2.
10. A working method of a straight-arm lorry-mounted crane converging multi-way valve device is characterized in that,
when the crane is in an idle state:
the telescopic reversing connection (2), the winch reversing connection (3), the amplitude-variable reversing connection (4), the confluence control connection (5) and the rotary reversing connection (6) do not work; the main oil circuit hydraulic control switching valve (51) and the load sensitive LS oil circuit hydraulic control switching valve (53) in the confluence control joint (5) are respectively communicated due to respective normally open functions; hydraulic oil of a first oil pump in the first oil pumping control unit (1) is converged in the multi-way valve through an oil port P1, and hydraulic oil of a second oil pump in the second oil pumping control unit (7) is converged in the multi-way valve through an oil port P2; because the load-sensitive LS oil circuit has no feedback pressure, the three-way flow valve I (11) and the three-way flow valve II (71) are opened for unloading, so that hydraulic oil of the two oil pumps flows back to the oil tank through the oil return port T1 and the oil return port T2;
when the rotary reversing union (6) works independently, the telescopic reversing union (2), the winch reversing union (3) and the amplitude-variable reversing union (4) do not work:
the shuttle valve (54) in the confluence control link (5) respectively acquires the load pressure of a working oil port A4 and a working oil port B4 of the rotary reversing valve (61), selects high-pressure signals of the two to be input to a main oil way hydraulic control switching valve (51) and a load sensitive LS oil way hydraulic control switching valve (53) to control the oil ports, controls the main oil way switching valve (51) and the load sensitive LS oil way hydraulic control switching valve (53) to simultaneously disconnect the oil ways, enables a P2 oil port of a second oil pump to supply oil, and is independently used for the rotary reversing link (6) to carry out crane rotary operation;
when the rotary reversing connection (6) does not work and any one of the telescopic reversing connection (2), the winch reversing connection (3) and the amplitude-variable reversing connection (4) works:
the shuttle valve (54) in the confluence control link (5) cannot detect a high-pressure signal, the main oil line hydraulic control switching valve (51) and the load-sensitive LS oil line hydraulic control switching valve (53) do not act and are respectively in a conduction state due to respective normally open functions, so that hydraulic oil of a first oil pump and hydraulic oil of a second oil pump through an oil port P2 are converged in the multi-way valve through the oil port P1, and a load-sensitive LS oil line pressure-limiting overflow valve (14) acquires the highest load pressure in the telescopic reversing link (2), the winch reversing link (3) and the variable amplitude reversing link (4), and the highest load pressure is transmitted to the control oil ports of a three-way flow valve I (11) and a three-way flow valve II (71) at the same time, so that the first oil pump and the second oil pump are converged at the same time to supply oil, and the pressure of;
because the set pressure of the pressure-limiting overflow valve (14) in the first pump oil inlet joint (1) is generally higher than the set pressure of the pressure control valve in the second pump oil inlet joint (7), therefore, when the set pressure of the pressure control valve in the second oil pumping connection (7) is reached along with the increase of the system pressure, the pressure control valve in the second pump oil inlet joint (7) acts firstly to limit the output pressure of the second pump from increasing continuously, meanwhile, a one-way valve in the confluence joint (5) is closed, the working confluence state of the first pump and the second pump is changed into a shunting state, the first pump oil inlet joint (1), the telescopic reversing valve joint (2), the amplitude-variable reversing joint (3) and the winch reversing joint (4) are not limited by the set pressure of a pressure control valve in the second pump oil inlet joint (7), and the pressure of the first pump system can still continuously increase along with the increase of the load until the set pressure of a load sensitive LS oil path pressure limiting overflow valve (14) in the first pump oil inlet joint (1) is reached;
when the rotary reversing linkage (6) works and at least one of the telescopic reversing linkage (2), the winch reversing linkage (3) and the amplitude-variable reversing linkage (4) works:
a shuttle valve (54) in the confluence control union (5) acquires the load pressure of a working oil port A4 and a working oil port B4 of a rotary reversing valve (61), selects high-pressure signals of the two to input to a main oil circuit hydraulic control switching valve (51) and a load sensitive LS oil circuit hydraulic control switching valve (53) to control the oil ports, controls the main oil circuit hydraulic control switching valve (51) and the load sensitive LS oil circuit hydraulic control switching valve (53) to simultaneously disconnect the oil circuits, enables a P2 oil port of a second oil pump to supply oil, is independently used for a rotary reversing union (6) to carry out crane rotary operation, and a P1 oil port of a first oil pump to supply oil independently used for the working union operation in a telescopic reversing union (2), a winch reversing union (3) and a variable amplitude reversing union (4).
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011303146.5A CN112268032A (en) | 2020-11-19 | 2020-11-19 | Straight-arm lorry-mounted crane converging multi-way valve device and working method thereof |
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| CN202011303146.5A CN112268032A (en) | 2020-11-19 | 2020-11-19 | Straight-arm lorry-mounted crane converging multi-way valve device and working method thereof |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113007157A (en) * | 2021-03-03 | 2021-06-22 | 中联重科股份有限公司 | Load-sensitive multi-way valve, boom hydraulic control system and concrete pump truck |
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- 2020-11-19 CN CN202011303146.5A patent/CN112268032A/en active Pending
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113007157A (en) * | 2021-03-03 | 2021-06-22 | 中联重科股份有限公司 | Load-sensitive multi-way valve, boom hydraulic control system and concrete pump truck |
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