CN114688115A - Compound action control hydraulic system and method for loader - Google Patents
Compound action control hydraulic system and method for loader Download PDFInfo
- Publication number
- CN114688115A CN114688115A CN202210620505.2A CN202210620505A CN114688115A CN 114688115 A CN114688115 A CN 114688115A CN 202210620505 A CN202210620505 A CN 202210620505A CN 114688115 A CN114688115 A CN 114688115A
- Authority
- CN
- China
- Prior art keywords
- control valve
- oil
- control
- valve
- hydraulic
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- 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
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/225—Control of steering, e.g. for hydraulic motors driving the vehicle tracks
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
- E02F9/2267—Valves or distributors
-
- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02F—DREDGING; SOIL-SHIFTING
- E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
- E02F9/20—Drives; Control devices
- E02F9/22—Hydraulic or pneumatic drives
- E02F9/2278—Hydraulic circuits
- E02F9/2292—Systems with 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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
-
- 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
-
- 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
-
- 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
- F15B13/16—Special measures for feedback, e.g. by a follow-up device
-
- 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
- F15B2211/2053—Type of pump
- F15B2211/20538—Type of pump constant capacity
-
- 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
- F15B2211/2053—Type of pump
- F15B2211/20546—Type of pump variable capacity
-
- 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
Abstract
The invention discloses a composite action control hydraulic system and a composite action control hydraulic method for a loader. The first hydraulic pump absorbs oil from the hydraulic oil tank, the first hydraulic pump is connected with a first control valve, and the first control valve is connected with a movable arm oil cylinder; the second hydraulic pump absorbs oil from the hydraulic oil tank, the second hydraulic pump is connected with a third control valve, and the third control valve is respectively connected with a steering gear and a fourth control valve; the steering gear is connected with the right steering oil cylinder and the left steering oil cylinder; the fourth control valve is respectively connected with the second control valve and the first control valve; the second control valve is connected with the tipping bucket oil cylinder; the third control valve preferentially supplies oil to the steering gear, and the redundant flow is supplied to the fourth control valve; the fourth control valve preferentially supplies oil to the second control valve and the excess flow to the first control valve. The invention realizes the compound action of the movable arm oil cylinder and the tipping bucket oil cylinder, the two molecular systems can be independently controlled, the operation controllability is stronger, the pressure and the operation speed of the two molecular systems can be independently set, and the overlarge impact during unloading is avoided.
Description
Technical Field
The invention relates to the technical field of engineering machinery, in particular to a composite action control hydraulic system and a composite action control hydraulic method for a loader.
Background
In the process of shovel loading operation, in order to improve the operation efficiency, the loader often uses the compound action of the movable arm and the tipping bucket to cooperate to carry out high-efficiency operation. The operation efficiency can be greatly reduced by completing one action and then performing the other action, and the two actions are completed simultaneously, so that the operation time can be greatly saved.
Most of the control valves currently used by a loader hydraulic system are of a series structure, and boom lifting or lowering control and bucket tipping or receiving actions cannot be performed simultaneously, so that the continuity of loader operation and the operation efficiency of loading and unloading actions are affected.
Because the traditional double-pump confluence hydraulic system of the loader is difficult to realize compound action, in order to realize the simultaneous action of a movable arm and a bucket of the loader, a load sensitive system is mostly adopted in the prior industry, but the load sensitive system still has the defects while realizing the compound action:
the accurate control of the two valve cores of the control valve is difficult to realize through the operation of inclining the single handle by 45 degrees;
although the valve core of the first control valve and the valve core of the second control valve can be controlled independently through pilot double-handle operation, the common control valve only has one oil inlet, and the flow entering the movable arm combined bucket joint is difficult to control accurately.
Disclosure of Invention
In order to solve the technical problem, the invention provides a composite action control hydraulic system and a composite action control hydraulic method for a loader. The invention solves the problem that the movable arm and the bucket can not carry out compound action or can not be controlled more accurately by adopting a simpler, more reliable and more economic method.
The invention is realized by the following technical scheme: a combined action control hydraulic system of a loader is characterized in that a first hydraulic pump absorbs oil from a hydraulic oil tank, the first hydraulic pump is connected with a first control valve, and the first control valve is connected with a movable arm oil cylinder;
the second hydraulic pump absorbs oil from the hydraulic oil tank, the second hydraulic pump is connected with a third control valve, and the third control valve is respectively connected with a steering gear and a fourth control valve; the steering gear is connected with the right steering oil cylinder and the left steering oil cylinder; the fourth control valve is respectively connected with the second control valve and the first control valve; the second control valve is connected with the tipping bucket oil cylinder;
the third control valve preferentially supplies oil to the steering gear, and redundant flow is supplied to the fourth control valve; the fourth control valve preferentially supplies oil to the second control valve and excess flow to the first control valve.
It further comprises the following steps: the second control valve is a closed-center three-position seven-way valve, an oil inlet P5 of the second control valve is connected with an oil outlet CF2 of the fourth control valve, a feedback oil port LS2 of the second control valve is connected with a control port Y2 of the fourth control valve, and an oil outlet EF2 of the fourth control valve is connected with the first control valve;
when the second control valve is in a working position, hydraulic oil enters the second control valve from the oil inlet P5 and then enters the skip bucket oil cylinder; at this time, a load signal is fed back from the feedback port LS2, and hydraulic oil flows to the fourth control valve control port Y2 through the feedback port LS2, thereby controlling the movement of the spool of the fourth control valve and preferentially supplying hydraulic oil to the second control valve.
The oil inlet P2 of the third control valve is connected with the second hydraulic pump, the oil outlet EF1 of the third control valve is connected with the oil inlet P4 of the fourth control valve, the oil outlet CF1 of the third control valve is connected with the steering gear, and the feedback oil port LS1 of the steering gear is connected with the control port Y1 of the third control valve;
when the valve core of the third control valve is in a left position, hydraulic oil enters the third control valve from the oil inlet P2 and then enters the steering gear; at this time, the feedback oil port LS1 feeds back a load signal, and hydraulic oil flows to the third control valve control port Y1 through the feedback oil port LS1, thereby controlling the third control valve spool to move and preferentially supplying hydraulic oil to the steering gear.
The valve core of the first control valve is of an open center type, the first control valve and the second control valve are of an integral valve group structure, and the first control valve and the second control valve are provided with independent oil inlets.
The first hydraulic pump is a gear pump, a vane pump or a plunger pump; the second hydraulic pump is a gear pump, a vane pump or a plunger pump.
An oil inlet of the first control valve is connected with a first overflow valve; the oil inlet of the second control valve is connected with a second overflow valve; and adjusting the pressure of the first overflow valve and the second overflow valve according to the requirements of working conditions, thereby distributing the power of the hydraulic system.
The first control valve and the second control valve are correspondingly connected with the first operating lever and the second operating lever through mechanical flexible shafts respectively.
The first control valve and the second control valve are respectively and correspondingly connected with the first operating lever and the second operating lever through pilot valves.
A composite action control method for a loader comprises the following steps:
when the steering and the movable arm lifting actions are carried out simultaneously;
pushing a first control lever to control a first control valve, so that a valve core of the first control valve is reversed, and at the moment, a first hydraulic pump directly supplies oil to a rodless cavity or a rod cavity of a movable arm oil cylinder to realize the lifting or descending action of a movable arm;
meanwhile, the steering wheel is controlled to operate the inner valve core of the steering gear to rotate and change direction, when the inner valve core of the steering gear rotates, a load signal is output from a feedback oil port LS1 of the steering gear and enters a control port Y1 of a third control valve to push the valve core of the third control valve to move right, so that the second hydraulic pump directly supplies oil to the steering gear through the third control valve and then enters a left steering oil cylinder or a right steering oil cylinder through an L port or an R port of the steering gear to realize steering of the whole machine;
when the actions of lifting the movable arm and tipping the bucket are carried out simultaneously;
pushing a first control lever to control a first control valve, so that a valve core of the first control valve moves rightwards and reverses, and at the moment, a first hydraulic pump directly supplies oil to a rodless cavity of a movable arm oil cylinder to realize the lifting action of a movable arm;
meanwhile, a second control lever is pushed to control the valve core of the second control valve to move rightwards and change direction, so that the valve core of the second control valve is in a left position, and hydraulic oil of the second hydraulic pump enters a third control valve; at the moment, if the whole machine does not perform steering action, hydraulic oil cannot enter the steering gear to push the valve core of the third control valve to move left, so that the valve core of the third control valve is positioned at the right position, and the hydraulic oil of the second hydraulic pump enters the oil inlet P4 of the fourth control valve through the oil outlet EF1 of the third control valve; a valve core of the second control valve in the left position outputs a load signal from a feedback oil port LS2 of the second control valve to a control port Y2 of a fourth control valve to push the valve core of the fourth control valve to move upwards, so that the valve core of the fourth control valve is in the lower position, hydraulic oil entering from an oil inlet P4 of the fourth control valve enters an oil inlet P5 of the second control valve through an oil outlet CF2 of the fourth control valve and then enters a rod cavity of a tipping bucket oil cylinder, and tipping bucket action is realized;
when the dump bucket cylinder does not fully use the flow output by the second hydraulic pump, and the pressure of the oil outlet CF2 of the fourth control valve is greater than the pressure of the control port Y2 and the return spring of the fourth control valve, the valve core of the fourth control valve moves downwards; because the dump cylinder still acts, a valve core of the fourth control valve is in a neutral position, hydraulic oil which is output by the second hydraulic pump and enters from a fourth control valve oil inlet P4 partially flows from an oil outlet CF2 to enter the second control valve to realize the dump action, and the rest flows are output from an oil outlet EF2 and are converged with the hydraulic oil output by the first hydraulic pump to enter the first control valve to realize the boom action.
It further comprises the following steps:
when the turning direction and the tipping bucket do not move;
the pressure of the oil outlet CF2 of the fourth control valve is greater than the sum of the pressure of the control port Y2 and the pressure of a return spring of the fourth control valve, and the valve core of the fourth control valve moves downwards to enable the valve core of the fourth control valve to be positioned at the upper position; the hydraulic oil output by the second hydraulic pump and entering from the fourth control valve oil inlet P4 is output from the oil outlet EF2, and is converged with the hydraulic oil output by the first hydraulic pump to enter the oil inlet P1 of the first control valve, so that the maximization of the efficiency of the boom oil cylinder is realized, and the boom can be lifted quickly.
Compared with the prior art, the invention has the beneficial effects that:
1. the compound action of the movable arm oil cylinder and the tipping bucket oil cylinder can be realized; the third control valve controls the oil way of the second hydraulic pump to make the steering preferential, and the redundant flow can be controlled to enter the skip bucket oil cylinder through the fourth control valve; when the tipping bucket action applies a small flow, the redundant flow can be converged with the flow of the first hydraulic pump and supplied to the boom cylinder, and the lifting speed of the boom cylinder is increased. The realization of the composite action can greatly improve the operation production efficiency and the continuity of the operation of the loader;
2. when the movable arm oil cylinder and the tipping bucket oil cylinder act simultaneously, the two molecular systems can be independently controlled without mutual influence, the operation controllability is stronger, the pressure and the operation speed of the two molecular systems can be independently set, and overlarge impact during unloading is avoided;
3. the whole process of the first hydraulic pump does not participate in the action of the tipping bucket oil cylinder, so that the flow of the second hydraulic pump is smaller than that of a traditional double-pump confluence system and can meet the working condition of a bucket for shoveling materials, and the consumed engine power is smaller when the tipping bucket works; meanwhile, according to the working condition requirement, the second overflow valve can be adjusted, the digging force of the bucket is increased independently, and other working systems are not affected.
Drawings
FIG. 1 is a schematic diagram of a hydraulic system of the present invention;
FIG. 2 is a schematic diagram of a second control valve of the present invention;
in the figure: 1. the hydraulic control system comprises a hydraulic oil tank, 2, a first hydraulic pump, 3, a fourth control valve, 4, a second hydraulic pump, 5, a third control valve, 6, a steering gear, 7, a right steering oil cylinder, 8, a left steering oil cylinder, 9, a first overflow valve, 10, a second operating rod, 11, a first operating rod, 12, a first control valve, 13, a movable arm oil cylinder, 14, a tipping bucket oil cylinder, 15, a second control valve and 16, wherein the hydraulic oil tank is connected with the first hydraulic pump through a first hydraulic pump.
Detailed Description
The invention will be further explained with reference to the drawings.
Example one
As shown in fig. 1 and 2, a compound action control hydraulic system of a loader,
an oil suction port of the first hydraulic pump 2 is connected with the hydraulic oil tank 1 through a pipeline, an oil outlet of the first hydraulic pump 2 is connected with an oil inlet P1 of the first control valve 12, and the first operating lever 11 can control the action of a valve core of the first control valve 12. The port a1 of the first control valve 12 is connected to the rodless chamber of the boom cylinder 13, the port B1 of the first control valve 12 is connected to the rod chamber of the boom cylinder 13, and the port T1 of the first control valve 12 is connected to the hydraulic oil tank 1.
An oil suction port of the second hydraulic pump 4 is connected with the hydraulic oil tank 1 through a pipeline, and an oil outlet of the second hydraulic pump 4 is connected with an oil inlet P2 of the third control valve 5. An oil outlet EF1 of the third control valve 5 is connected with an oil inlet P4 of the fourth control valve 3, an oil inlet CF1 of the third control valve 5 is connected with an oil inlet P3 of the steering gear 6, a control port Y1 of the third control valve 5 is connected with a feedback oil port LS1 of the steering gear 6, and a port T2 of the third control valve 5 is connected with the hydraulic oil tank 1; an L port of the steering gear 6 is connected with a rodless cavity of the right steering oil cylinder 7 and a rod cavity of the left steering oil cylinder 8, and an R port of the steering gear 6 is connected with a rod cavity of the right steering oil cylinder 7 and a rodless cavity of the left steering oil cylinder 8;
an oil outlet EF2 of the fourth control valve 3 is connected with an oil inlet P1 of the first control valve 12, an oil outlet CF2 of the fourth control valve 3 is connected with an oil inlet P5 of the second control valve 12, a control port Y2 of the fourth control valve 3 is connected with a feedback oil port LS2 of the second control valve 15, and a port T4 of the fourth control valve is connected with the hydraulic oil tank 1. The port a2 of the second control valve 15 is connected to the rodless chamber of the dump cylinder 14, the port B2 of the second control valve 15 is connected to the rod chamber of the dump cylinder 14, the port T5 of the second control valve 15 is connected to the hydraulic tank 1, and the second joystick 10 can control the operation of the spool of the second control valve 15.
The third control valve 5 preferentially supplies oil to the steering gear 6, and the redundant flow is supplied to the fourth control valve 3; the fourth control valve 3 preferentially supplies oil to the second control valve 15, and the redundant flow rate supplies oil to the first control valve 12;
specifically, the method comprises the following steps:
when the third control valve 5 is in a left position, hydraulic oil enters the third control valve 5 from the oil inlet P2 and then enters the steering gear 6; at this time, the feedback oil port LS1 feeds back a load signal, and hydraulic oil flows to the control port Y1 of the third control valve 5 through the feedback oil port LS1, so that the spool of the third control valve 5 is controlled to move, and the hydraulic oil is preferentially supplied to the steering gear 6;
when the second control valve 15 is at the working position, hydraulic oil enters the second control valve 15 from the oil inlet P5 and then enters the skip bucket oil cylinder 14; at this time, a load signal is fed back from the feedback oil port LS2, and hydraulic oil flows to the control port Y2 of the fourth control valve 3 through the feedback oil port LS2, thereby controlling the movement of the spool of the fourth control valve 3, and the hydraulic oil is preferentially supplied to the second control valve 15, thereby controlling the direction and speed of the operation of the dump cylinder.
The first hydraulic pump 2 and the second hydraulic pump 4 are gear pumps, vane pumps or plunger pumps. An oil inlet of the first control valve 12 is connected with a first overflow valve 9; the oil inlet of the second control valve 15 is connected with a second overflow valve 16. According to the requirements of working conditions, the pressure of the first overflow valve 9 and the pressure of the second overflow valve 16 can be adjusted, so that the power of the hydraulic system is distributed, and the working capacity and the working efficiency can be improved.
The second control valve 15 is a closed-center three-position seven-way valve, and the valve core of the first control valve 12 is an open-center type. The first control valve 12 and the second control valve 15 may adopt an integral valve group structure, and the first control valve 12 and the second control valve 15 have independent oil inlets.
The first control valve 12 and the second control valve 15 are correspondingly connected with the first operating lever 11 and the second operating lever 10 through a mechanical flexible shaft or a pilot valve respectively. The first joystick 11 controls the position of the spool of the first control valve 12, and thus controls the operation direction and the operation speed of the boom cylinder 13. The second joystick 10 controls the position of the spool of the second control valve 15, and thus the operation direction and the operation speed of the hoist cylinder 14. When the pilot valve is used for control, the position of the valve core and the opening degree of the valve port can be controlled through pilot pressure oil; at this time, a pilot oil source needs to be added in the system to provide control pressure for the pilot valve, so that the actions of the first control valve spool and the second control valve spool can be controlled.
When the hydraulic control system works, the first hydraulic pump directly supplies oil to the first control valve, and the first control lever controls the position of a valve core of the first control valve and the opening degree of a valve port to control the action direction and the speed of the movable arm oil cylinder;
the second hydraulic pump supplies oil to the third control valve, and on the premise of priority of steering, the oil is supplied to the steering gear firstly, and redundant flow is supplied to the second control valve through the third control valve. The steering gear controls the action direction and speed of the steering oil cylinder through a pipeline. When the turning motion is not carried out, the hydraulic oil of the second hydraulic pump is preferentially led to the second control valve through the third control valve and the fourth control valve, and the second control rod controls the position of the valve core of the second control valve to control the motion direction and the motion speed of the tipping bucket oil cylinder. When the tipping speed is low and the boom speed is high, hydraulic oil of the second hydraulic pump passes through the third control valve and the fourth control valve, part of flow is led to the second control valve to carry out the tipping bucket oil cylinder action, and the rest of flow is converged with the flow of the first hydraulic pump and enters the first control valve to carry out the boom oil cylinder action;
when the dump bucket is not used even when the steering is not performed, the flow rate of the second hydraulic pump is merged to the first control valve through the third control valve and the fourth control valve, and the flow rate is used for increasing the lifting speed of the boom cylinder.
The composite action control hydraulic system of the loader can realize the independent control of the stretching of the movable arm oil cylinder and the stretching of the tipping bucket oil cylinder of the loader and realize the composite action of the movable arm and the bucket; and secondly, the swing arm oil cylinder and the steering gear are controlled independently, so that the overall steering of the loader and the composite action of a working device are convenient to realize, and the working efficiency of the loader and the continuity and smoothness of the operation are improved.
Example two
On the basis of the first embodiment, the composite action control method of the loader comprises the following steps:
when the steering and the movable arm lifting actions are carried out simultaneously;
pushing the first control lever 11 to control the first control valve 12, so that the valve core of the first control valve 12 is shifted to the right or left to be shifted to the left, and at the moment, the first hydraulic pump 2 directly supplies oil to a rodless cavity or a rod cavity of a movable arm oil cylinder 13 to realize the lifting or descending action of a movable arm;
meanwhile, the steering wheel is controlled to operate the rotation reversing of the valve core in the steering gear 6, when the valve core in the steering gear 6 rotates, a load signal is output from a feedback oil port LS1 of the steering gear 6 and enters a control port Y1 of the third control valve 5 to push the valve core of the third control valve 5 to move right, so that the second hydraulic pump 4 directly supplies oil to the steering gear 6 through the third control valve 5 and then enters the left steering oil cylinder 8 or the right steering oil cylinder 7 through an L port or an R port of the steering gear 6 to realize the steering of the whole machine; therefore, the steering action and the movable arm action of the whole machine can be controlled independently.
When the actions of lifting the movable arm and tipping the bucket are carried out simultaneously;
pushing the first control lever 11 to control the first control valve 12, so that the valve core of the first control valve 12 moves rightwards and reverses, and at the moment, the first hydraulic pump 2 directly supplies oil to a rodless cavity of a movable arm oil cylinder 13, so that the movable arm lifting action is realized;
meanwhile, the second operating lever 10 is pushed to control the valve core of the second control valve 15 to move rightwards and change direction, so that the valve core of the second control valve 15 is in the left position, and hydraulic oil of the second hydraulic pump 4 enters the third control valve 5; at this time, if the whole machine does not perform steering action, hydraulic oil cannot enter the steering gear 6 to further push the valve core of the third control valve 5 to move left, so that the valve core of the third control valve 5 is positioned at the right position, and hydraulic oil of the second hydraulic pump 4 enters the oil inlet P4 of the fourth control valve 3 through the oil outlet EF1 of the third control valve 5; the valve core of the second control valve 15 in the left position outputs a load signal from the feedback oil port LS2 of the second control valve 15 to the control port Y2 of the fourth control valve 3 to push the valve core of the fourth control valve 3 to move upwards, so that the valve core of the fourth control valve 3 is in the lower position, and hydraulic oil entering from the oil inlet P4 of the fourth control valve 3 enters the oil inlet P5 of the second control valve 15 through the oil outlet CF2 of the fourth control valve 3 and enters the rod cavity of the dump cylinder 14, thereby realizing the dump action.
When the dump bucket cylinder 14 does not fully use the flow output by the second hydraulic pump 4, and the pressure of the oil outlet CF2 of the fourth control valve 3 is greater than the pressure of the control port Y2 and the return spring of the fourth control valve 3, the valve core of the fourth control valve 3 moves downwards; because the dump bucket cylinder 14 still operates, the valve core of the fourth control valve 3 is in a middle position, the hydraulic oil which is output by the second hydraulic pump 4 and enters from the oil inlet P4 of the fourth control valve 3 outputs partial flow from the oil outlet CF2 to enter the second control valve 15 to realize the dump bucket operation, and the rest flow is output from the oil outlet EF2 and is converged with the hydraulic oil output by the first hydraulic pump 2 to enter the first control valve 12 to realize the boom operation.
When the movable arm oil cylinder and the tipping bucket oil cylinder act simultaneously, the compound action control hydraulic system of the loader is the action of the tipping bucket oil cylinder with priority;
therefore, when the dump cylinder needs to fully use the flow output by the second hydraulic pump, the feedback pressure of the feedback oil port LS2 of the second control valve 15 and the return spring of the fourth control valve 3 jointly push the spool of the fourth control valve 3 to move upwards, i.e. return to the lower position; the hydraulic oil which is output by the second hydraulic pump 4 and enters from the fourth control valve oil inlet P4 outputs all flow from the oil outlet CF2 to enter the second control valve 15, so that the rapid action of the tipping bucket is realized.
The loader lifts a heavy object in situ, and the loader does not turn or dump the heavy object;
the pressure of an oil outlet CF2 port of the fourth control valve 3 is greater than the sum of the pressure of a control port Y2 and the pressure of a return spring of the fourth control valve 3, and a valve core of the fourth control valve 3 moves downwards to enable the valve core of the fourth control valve 3 to be positioned at an upper position; the hydraulic oil which is output by the second hydraulic pump 4 and enters from the oil inlet P4 of the fourth control valve 3 is output from the oil outlet EF2, and is converged with the hydraulic oil output by the first hydraulic pump 2 to enter the oil inlet P1 of the first control valve 12, so that the efficiency maximization of the boom oil cylinder 13 is realized, and the boom can be lifted quickly.
In this embodiment, first overflow valve and second overflow valve can set up different pressures according to the requirement of operating mode to realize bigger operating capacity and faster work efficiency.
In the embodiment, the first hydraulic pump completely supplies oil to the movable arm oil cylinder, the second hydraulic pump preferentially supplies oil to the steering gear, preferentially supplies oil to the tipping bucket oil cylinder, and then supplies oil to the movable arm oil cylinder in a confluence manner with the first hydraulic pump; under the standard requirement, the displacement of the first hydraulic pump can be reduced, and the design cost of a hydraulic system is reduced;
when a driver needs to perform movable arm action and steering action at the same time according to specific working conditions, the composite action of lifting or lowering the movable arm and steering can be realized only by the first operating lever and the steering wheel;
when the turning is not carried out and the tipping bucket action and the movable arm action are required to be carried out simultaneously, the first control rod and the second control rod are operated to realize the action of tipping bucket or receiving bucket while lifting or lowering the movable arm, at the moment, the action of the tipping bucket oil cylinder and the action of the movable arm oil cylinder are two independent control systems, and the simultaneous action of the two oil cylinders can be realized under any working condition, namely the composite action of the loader working device;
when the turning and the tipping bucket cylinder do not act, the flow of the second hydraulic pump and the flow of the first hydraulic pump are converged and simultaneously supplied to the movable arm cylinder, so that the quick lifting of the movable arm cylinder can be realized.
The above is only a preferred embodiment of the present invention, and is not particularly limited thereto, and on the basis of this, specific and targeted adjustments may be made according to actual needs, so as to obtain different embodiments.
Claims (10)
1. The utility model provides a loader combined action control hydraulic system which characterized in that:
the first hydraulic pump (2) sucks oil from the hydraulic oil tank (1), the first hydraulic pump (2) is connected with a first control valve (12), and the first control valve (12) is connected with a movable arm oil cylinder (13);
the second hydraulic pump (4) sucks oil from the hydraulic oil tank (1), the second hydraulic pump (4) is connected with a third control valve (5), and the third control valve (5) is respectively connected with a steering gear (6) and a fourth control valve (3); the steering gear (6) is connected with a right steering oil cylinder (7) and a left steering oil cylinder (8); the fourth control valve (3) is respectively connected with a second control valve (15) and the first control valve (12); the second control valve (15) is connected with a skip bucket oil cylinder (14);
the third control valve (5) preferentially supplies oil to the steering gear (6), and the redundant flow is supplied to the fourth control valve (3); the fourth control valve (3) preferentially supplies oil to the second control valve (15) and excess flow to the first control valve (12).
2. The compound motion control hydraulic system of a loader as claimed in claim 1, characterized in that: the second control valve (15) is a closed-center three-position seven-way valve, an oil inlet P5 of the second control valve (15) is connected with an oil outlet CF2 of the fourth control valve (3), a feedback oil port LS2 of the second control valve (15) is connected with a control port Y2 of the fourth control valve (3), and an oil outlet EF2 of the fourth control valve (3) is connected with the first control valve (12);
when the second control valve (15) is in a working position, hydraulic oil enters the second control valve (15) from the oil inlet P5 and then enters the skip bucket oil cylinder (14); at this time, a load signal is fed back from the feedback oil port LS2, and hydraulic oil flows to the control port Y2 of the fourth control valve (3) through the feedback oil port LS2, so that the spool of the fourth control valve (3) is controlled to move, and the hydraulic oil is preferentially supplied to the second control valve (15).
3. The compound motion control hydraulic system of a loader as claimed in claim 2, characterized in that: an oil inlet P2 of the third control valve (5) is connected with the second hydraulic pump (4), an oil outlet EF1 of the third control valve (5) is connected with an oil inlet P4 of the fourth control valve (3), an oil outlet CF1 of the third control valve (5) is connected with a steering gear (6), and a feedback oil port LS1 of the steering gear (6) is connected with a control port Y1 of the third control valve (5);
when the valve core of the third control valve (5) is in a left position, hydraulic oil enters the third control valve (5) from the oil inlet P2 and then enters the steering gear (6); at this time, a load signal is fed back from the feedback oil port LS1, and hydraulic oil flows to the control port Y1 of the third control valve (5) through the feedback oil port LS1, so that the spool of the third control valve (5) is controlled to move, and the hydraulic oil is preferentially supplied to the steering gear (6).
4. The compound motion control hydraulic system of a loader as claimed in claim 1, characterized in that: the valve core of the first control valve (12) is of an open center type, the first control valve (12) and the second control valve (15) adopt an integral valve group structure, and the first control valve (12) and the second control valve (15) are provided with independent oil inlets.
5. The compound motion control hydraulic system of a loader as claimed in claim 1, characterized in that: the first hydraulic pump (2) is a gear pump, a vane pump or a plunger pump; the second hydraulic pump (4) is a gear pump, a vane pump or a plunger pump.
6. The compound motion control hydraulic system of a loader as claimed in claim 1, characterized in that: an oil inlet of the first control valve (12) is connected with a first overflow valve (9); an oil inlet of the second control valve (15) is connected with a second overflow valve (16); and (3) adjusting the pressure of the first overflow valve (9) and the second overflow valve (16) according to the requirements of working conditions, thereby distributing the power of the hydraulic system.
7. The compound motion control hydraulic system of a loader according to any one of claims 1 to 6, characterized in that: the first control valve (12) and the second control valve (15) are correspondingly connected with the first operating lever (11) and the second operating lever (10) through mechanical flexible shafts respectively.
8. The compound motion control hydraulic system of a loader according to any one of claims 1 to 6, characterized in that: the first control valve (12) and the second control valve (15) are respectively and correspondingly connected with the first operating lever (11) and the second operating lever (10) through pilot valves.
9. A composite motion control method for a loader, which adopts the composite motion control hydraulic system for a loader according to claim 7, and is characterized by comprising the following steps:
when the steering and the movable arm lifting actions are carried out simultaneously;
pushing a first operating lever (11) to control a first control valve (12) to change a valve core of the first control valve (12), and directly supplying oil to a rodless cavity or a rod cavity of a movable arm oil cylinder (13) by a first hydraulic pump (2) at the moment to realize lifting or descending of a movable arm;
meanwhile, the steering wheel is controlled to operate the inner valve core of the steering gear (6) to rotate and reverse, when the inner valve core of the steering gear (6) rotates, a load signal is output from a feedback oil port LS1 of the steering gear (6) and enters a control port Y1 of the third control valve (5) to push the valve core of the third control valve (5) to move rightwards, so that the second hydraulic pump (4) directly supplies oil to the steering gear (6) through the third control valve (5), and then enters the left steering oil cylinder (8) or the right steering oil cylinder (7) through an L port or an R port of the steering gear (6) to realize the steering of the whole machine;
when the actions of lifting the movable arm and tipping the bucket are carried out simultaneously;
pushing a first operating lever (11) to control a first control valve (12) so as to enable a valve core of the first control valve (12) to move rightwards and change direction, and at the moment, directly supplying oil to a rodless cavity of a movable arm oil cylinder (13) by a first hydraulic pump (2) to realize the lifting action of a movable arm;
meanwhile, a second operating lever (10) is pushed to control the valve core of the second control valve (15) to move rightwards and change direction, so that the valve core of the second control valve (15) is in the left position, and hydraulic oil of the second hydraulic pump (4) enters a third control valve (5); at the moment, if the whole machine does not perform steering action, hydraulic oil cannot enter the steering gear (6) to further push the valve core of the third control valve (5) to move left, so that the valve core of the third control valve (5) is positioned at the right position, and hydraulic oil of the second hydraulic pump (4) enters the oil inlet P4 of the fourth control valve (3) through the oil outlet EF1 of the third control valve (5); a valve core of the second control valve (15) positioned at the left position outputs a load signal from a feedback oil port LS2 of the second control valve (15) to a control port Y2 of the fourth control valve (3) to push the valve core of the fourth control valve (3) to move upwards, so that the valve core of the fourth control valve (3) is positioned at the lower position, hydraulic oil entering from an oil inlet P4 of the fourth control valve (3) enters an oil inlet P5 of the second control valve (15) through an oil outlet CF2 of the fourth control valve (3) and then enters a rod cavity of a tipping bucket oil cylinder (14), and tipping bucket action is realized;
when the dump bucket oil cylinder (14) does not completely use the flow output by the second hydraulic pump (4), and the pressure of an oil outlet CF2 of the fourth control valve (3) is greater than the pressure of a control port Y2 and a return spring of the fourth control valve (3), a valve core of the fourth control valve (3) moves downwards; because the dump bucket oil cylinder (14) still acts, a valve core of the fourth control valve (3) is in a neutral position, hydraulic oil which is output by the second hydraulic pump (4) and enters from an oil inlet P4 of the fourth control valve (3) partially flows from an oil outlet CF2 to enter the second control valve (15) to realize dump bucket action, and the rest flows are output from an oil outlet EF2 and are merged with the hydraulic oil output by the first hydraulic pump (2) to enter the first control valve (12) to realize boom action.
10. The composite-motion control method for the loader according to claim 9, characterized in that:
when the turning direction and the tipping bucket do not move;
the pressure of an oil outlet CF2 port of the fourth control valve (3) is greater than the sum of the pressure of a control port Y2 and the pressure of a return spring of the fourth control valve (3), and a valve core of the fourth control valve (3) moves downwards to enable the valve core of the fourth control valve (3) to be positioned at an upper position; the hydraulic oil which is output by the second hydraulic pump (4) and enters from the oil inlet P4 of the fourth control valve (3) is output from the oil outlet EF2, and is converged with the hydraulic oil output by the first hydraulic pump (2) to enter the oil inlet P1 of the first control valve (12), so that the efficiency maximization of the movable arm oil cylinder (13) is realized, and the movable arm can be quickly lifted.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210620505.2A CN114688115B (en) | 2022-06-02 | 2022-06-02 | Compound action control hydraulic system and method for loader |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210620505.2A CN114688115B (en) | 2022-06-02 | 2022-06-02 | Compound action control hydraulic system and method for loader |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114688115A true CN114688115A (en) | 2022-07-01 |
| CN114688115B CN114688115B (en) | 2022-08-30 |
Family
ID=82130966
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210620505.2A Active CN114688115B (en) | 2022-06-02 | 2022-06-02 | Compound action control hydraulic system and method for loader |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114688115B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115030259A (en) * | 2022-07-26 | 2022-09-09 | 徐工集团工程机械股份有限公司科技分公司 | Multi-way valve for loader, loader hydraulic system and loader |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102094441A (en) * | 2010-12-23 | 2011-06-15 | 山东临工工程机械有限公司 | Hydraulic system of loader |
| CN203924195U (en) * | 2014-05-07 | 2014-11-05 | 山东临工工程机械有限公司 | Loader hydraulic control system |
| CN104265702A (en) * | 2014-09-10 | 2015-01-07 | 徐工集团工程机械股份有限公司 | Natural gas loader starting system |
| CN205742332U (en) * | 2016-05-06 | 2016-11-30 | 厦门厦工机械股份有限公司 | The hydraulic system of wheel loader |
| CN107268703A (en) * | 2017-07-06 | 2017-10-20 | 山东临工工程机械有限公司 | Loader hydraulic system |
-
2022
- 2022-06-02 CN CN202210620505.2A patent/CN114688115B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102094441A (en) * | 2010-12-23 | 2011-06-15 | 山东临工工程机械有限公司 | Hydraulic system of loader |
| CN203924195U (en) * | 2014-05-07 | 2014-11-05 | 山东临工工程机械有限公司 | Loader hydraulic control system |
| CN104265702A (en) * | 2014-09-10 | 2015-01-07 | 徐工集团工程机械股份有限公司 | Natural gas loader starting system |
| CN205742332U (en) * | 2016-05-06 | 2016-11-30 | 厦门厦工机械股份有限公司 | The hydraulic system of wheel loader |
| CN107268703A (en) * | 2017-07-06 | 2017-10-20 | 山东临工工程机械有限公司 | Loader hydraulic system |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115030259A (en) * | 2022-07-26 | 2022-09-09 | 徐工集团工程机械股份有限公司科技分公司 | Multi-way valve for loader, loader hydraulic system and loader |
| CN115030259B (en) * | 2022-07-26 | 2024-04-09 | 徐工集团工程机械股份有限公司科技分公司 | Multi-way valve for loader, loader hydraulic system and loader |
Also Published As
| Publication number | Publication date |
|---|---|
| CN114688115B (en) | 2022-08-30 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US10184225B2 (en) | Working machine | |
| EP3505688B1 (en) | System for controlling construction machinery and method for controlling construction machinery | |
| CN108316389B (en) | Multi-way valve for wheel excavator | |
| CN109311648A (en) | Fluid power system | |
| CN114688115B (en) | Compound action control hydraulic system and method for loader | |
| WO2021093300A1 (en) | Energy-saving control system and control method for excavator boom | |
| CN111733921A (en) | Loader hydraulic system and engineering machinery | |
| JPH0640406U (en) | Split / merge switching device for multiple pumps in load sensing system | |
| CN110159609B (en) | Master control valve and hydraulic system | |
| CN203188273U (en) | Excavator hydraulic control system and hydraulic excavator | |
| JP2002206256A (en) | Hydraulic device for backhoe | |
| CN214366949U (en) | Hydraulic system of excavator | |
| CN115038844B (en) | Hydraulic system | |
| CN217759049U (en) | Pilot signal valve group, full-variable hydraulic system and loader | |
| CN212742675U (en) | Excavator hydraulic system and excavator | |
| CN211778291U (en) | Multi-way valve of excavator | |
| CN107504000A (en) | A kind of lorry-mounted crane multi-way reversing device | |
| CN113251017A (en) | Flow regulation type oil pumping system, hydraulic crushing system and excavator | |
| CN217557055U (en) | Electrically-controlled full-variable hydraulic system and loader | |
| CN217537150U (en) | All-variable hydraulic system and loader | |
| CN215759296U (en) | Hydraulic system of small excavator | |
| CN111501893A (en) | Negative flow hydraulic system and excavator | |
| CN205591274U (en) | Small -size excavator combination flow control system | |
| CN217974568U (en) | Constant-variable flow-converging control hydraulic system of loader | |
| CN114909351B (en) | Quantitative closed-center hydraulic system and working method and control method thereof |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |