CN113983035B - Hydraulic control system of multi-speed oil cylinder - Google Patents
Hydraulic control system of multi-speed oil cylinder Download PDFInfo
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- CN113983035B CN113983035B CN202111116638.8A CN202111116638A CN113983035B CN 113983035 B CN113983035 B CN 113983035B CN 202111116638 A CN202111116638 A CN 202111116638A CN 113983035 B CN113983035 B CN 113983035B
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- 238000006073 displacement reaction Methods 0.000 claims description 12
- 239000003921 oil Substances 0.000 description 300
- 239000010720 hydraulic oil Substances 0.000 description 76
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 239000013589 supplement Substances 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000001276 controlling effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 239000002828 fuel tank Substances 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Classifications
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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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/08—Servomotor systems incorporating electrically operated control means
- F15B21/087—Control strategy, e.g. with block diagram
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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
- F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
- F15B1/02—Installations or systems with accumulators
- F15B1/024—Installations or systems with accumulators used as a supplementary power source, e.g. to store energy in idle periods to balance pump load
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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
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
- F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
- F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
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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
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/0401—Valve members; Fluid interconnections therefor
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The disclosure provides a hydraulic control system of a multi-speed oil cylinder, and belongs to the field of hydraulic control. The hydraulic control system comprises a power output unit, a speed control unit and an execution oil cylinder. The speed control unit comprises a first hydraulic control reversing valve, a proportional reversing valve, a second hydraulic control reversing valve and an electromagnetic reversing valve, wherein an oil outlet of the first hydraulic control reversing valve is communicated with a rod cavity of the execution cylinder, an oil inlet of the proportional reversing valve is communicated with an oil outlet of the power output unit, a working oil port of the proportional reversing valve is communicated with a rodless cavity of the execution cylinder and a control oil port of the first hydraulic control reversing valve, and an oil outlet of the proportional reversing valve is communicated with an oil inlet of the power output unit. And an oil inlet of the second hydraulic control reversing valve is communicated with a rod cavity of the execution oil cylinder. The hydraulic control system can control the long-stroke oil cylinder to complete preset working conditions at various speeds.
Description
Technical Field
The disclosure belongs to the technical field of hydraulic control, and particularly relates to a hydraulic control system of a multi-speed oil cylinder.
Background
In the field of marine machinery, disc spring hydraulic brakes are often used to brake certain sports equipment. The disc spring type hydraulic brake comprises a brake pad, a brake disc, a plurality of disc springs and the like. When the brake is not needed, the disc spring is compressed through the oil cylinder, so that the disc spring drives the brake disc to move, and a gap exists between the brake disc and the brake pad. When the brake is needed, the oil cylinder is depressurized, and the brake disc is quickly connected with the brake block under the action of the disc spring.
In the related art, the motion of the oil cylinder is controlled by combining the proportional reversing valve with the power output unit, and when the oil cylinder is required to push the disc spring, hydraulic oil enters the proportional reversing valve through the power output unit and then enters the oil cylinder. The oil cylinder is driven to move at a constant speed through the proportional reversing valve, so that the compression movement of the disc spring is realized.
However, since the disc spring is an elastic element, when the disc spring is pushed and pressed, the stroke of the cylinder increases with an increase in the compression amount of the disc spring, and accordingly, the load increases with an increase in the compression amount of the disc spring. If the cylinder moves at a constant speed, the time for the cylinder to move to a predetermined position is relatively long, which seriously affects the response speed of the brake.
Disclosure of Invention
Embodiments of the present disclosure provide a hydraulic control system for a multi-speed cylinder that may control a long stroke cylinder to achieve a predetermined operating condition at multiple speeds. The technical scheme is as follows:
the embodiment of the disclosure provides a hydraulic control system of a multi-speed oil cylinder, which comprises a power output unit, a speed control unit and an execution oil cylinder;
the speed control unit comprises a first hydraulic control reversing valve, a proportional reversing valve and a second hydraulic control reversing valve, and the spring pressure value of the first hydraulic control reversing valve is smaller than that of the second hydraulic control reversing valve;
The first oil port of the first hydraulic control reversing valve is communicated with the oil outlet of the power output unit, the second oil port of the first hydraulic control reversing valve is communicated with the rod cavity of the execution oil cylinder, and the third oil port of the first hydraulic control reversing valve is communicated with the oil inlet of the power output unit;
An oil inlet of the proportional reversing valve is communicated with an oil outlet of the power output unit, a working oil port of the proportional reversing valve is communicated with a rodless cavity of the execution oil cylinder and a control oil port of the first hydraulic control reversing valve, and an oil outlet of the proportional reversing valve is communicated with an oil inlet of the power output unit;
The first oil port of the second hydraulic control reversing valve is communicated with the rod cavity of the execution oil cylinder, the second oil port of the second hydraulic control reversing valve is communicated with the oil inlet of the proportional reversing valve, the third oil port of the second hydraulic control reversing valve is communicated with the oil inlet of the power output unit, and the control oil port of the second hydraulic control reversing valve is communicated with the rod-free cavity of the execution oil cylinder.
In yet another implementation of the present disclosure, the speed control unit further includes an electromagnetic directional valve;
the first oil port of the electromagnetic directional valve is communicated with the oil outlet of the proportional directional valve, the second oil port of the electromagnetic directional valve is communicated with the oil inlet of the power output unit, and the third oil port of the electromagnetic directional valve is communicated with the oil inlet of the proportional directional valve.
In yet another implementation of the present disclosure, the speed control unit further includes an overflow valve;
The oil inlet of the overflow valve is communicated with the oil inlet of the proportional reversing valve, the oil outlet of the overflow valve is communicated with the oil outlet of the proportional reversing valve, and the control oil of the overflow valve is communicated with the oil inlet of the overflow valve.
In yet another implementation of the present disclosure, the speed control unit further comprises an accumulator;
And a working oil port of the energy accumulator is communicated with an oil inlet of the proportional reversing valve.
In yet another implementation of the present disclosure, the speed control unit further includes a first check valve;
The oil inlet of the first one-way valve is communicated with the oil outlet of the power output unit, and the oil outlet of the first one-way valve is communicated with the oil inlet of the proportional reversing valve.
In yet another implementation of the present disclosure, the power take-off unit includes a first flow pump, a second flow pump, and a fuel tank;
an oil outlet of the first flow pump is communicated with a first oil port of the first hydraulic control reversing valve, and an oil inlet of the first flow pump is communicated with the oil tank;
an oil outlet of the second flow pump is communicated with an oil inlet of the proportional reversing valve, and an oil inlet of the second flow pump is communicated with the oil tank.
In yet another implementation of the present disclosure, the output displacement of the first flow pump is less than the output displacement of the second flow pump.
In yet another implementation of the present disclosure, the power take-off unit further includes a second one-way valve;
the oil inlet of the second one-way valve is communicated with the oil outlet of the first flow pump, and the oil outlet of the second one-way valve is communicated with the first oil port of the first hydraulic control reversing valve.
In yet another implementation of the present disclosure, the power take-off unit further comprises an oil cooler;
The oil inlet of the oil cooler is communicated with the oil outlet of the first hydraulic control reversing valve, the oil outlet of the second hydraulic control reversing valve and the oil outlet of the electromagnetic reversing valve, and the oil outlet of the oil cooler is communicated with the oil tank.
In yet another implementation of the present disclosure, the power take-off unit further comprises a filter;
the oil inlet of the filter is communicated with the oil outlet of the oil cooler, and the oil outlet of the filter is communicated with the oil tank.
The technical scheme provided by the embodiment of the disclosure has the beneficial effects that:
When the hydraulic control system provided by the embodiment of the disclosure is used for driving the execution oil cylinder, firstly, the power output unit is started, so that hydraulic oil output by the power output unit enters the first hydraulic control reversing valve and the proportional reversing valve respectively.
When the brake of the disc spring type hydraulic brake is released through the hydraulic control system, a piston rod of the actuating cylinder needs to be driven to extend. For the proportional reversing valve, the valve core of the proportional reversing valve is in the right position after moving left, and an oil inlet in the proportional reversing valve is communicated with the working oil port. When hydraulic oil enters the proportional reversing valve, the hydraulic oil enters a rodless cavity of the execution oil cylinder from a working oil port of the proportional reversing valve, and a piston rod of the execution oil cylinder is pushed to extend out. At the same time, the valve core of the first hydraulic control reversing valve is in the lower position, and the first oil port and the second oil port of the first hydraulic control reversing valve are communicated. Hydraulic oil enters the first hydraulic control reversing valve through a first oil port of the first hydraulic control reversing valve. When the hydraulic oil enters the first hydraulic control reversing valve, the hydraulic oil is output from the second oil port of the first hydraulic control reversing valve, passes through the first oil port of the second hydraulic control reversing valve together with the hydraulic oil in the rod cavity of the execution oil cylinder, and enters the second hydraulic control reversing valve. Meanwhile, the valve core of the second hydraulic control reversing valve is positioned at the right position, and the first oil port and the second oil port of the second hydraulic control reversing valve are communicated. When hydraulic oil enters the second hydraulic control reversing valve, the hydraulic oil is output from a second oil port of the second hydraulic control reversing valve, enters the proportional reversing valve through an oil inlet of the proportional reversing valve, is output into a rodless cavity of the execution oil cylinder, forms a differential loop, and drives a piston rod of the execution oil cylinder to extend out at the fastest speed (high speed three gears) when the execution oil cylinder moves downwards at the high speed three gears.
When the load of the execution oil cylinder exceeds the spring pressure value of the first hydraulic control reversing valve, the valve core of the first hydraulic control reversing valve moves downwards and is in an upper position, and the third oil port and the first oil port of the first hydraulic control reversing valve are communicated. The hydraulic oil entering the first hydraulic control reversing valve through the first oil port of the first hydraulic control reversing valve does not enter the second hydraulic control reversing valve any more, but flows back to the power output unit through the third oil port of the first hydraulic control reversing valve. That is, in this condition, the rodless chamber of the actuator cylinder lacks the oil supply of the power take-off unit through the first pilot operated directional valve, as compared to the above descending high speed three-gear condition, so that the piston rod of the actuator cylinder is driven to extend at a normal speed (high speed two-gear).
When the load of the execution oil cylinder is continuously increased and exceeds the spring pressure value of the second hydraulic control reversing valve, the valve core of the second hydraulic control reversing valve moves rightwards and is positioned at the left position, and the third oil port of the second hydraulic control reversing valve is communicated with the first oil port. After the hydraulic oil in the rod cavity of the execution oil cylinder enters the second hydraulic control reversing valve through the first oil port of the second hydraulic control reversing valve, the hydraulic oil does not flow back into the rodless cavity of the execution oil cylinder any more, but flows back into the power output unit through the third oil port of the second hydraulic control reversing valve. The actuator cylinder descends at a high speed in one gear. That is, under this condition, the rodless chamber of the actuator cylinder lacks the supply of hydraulic oil in the rod chamber of the actuator cylinder, as compared to the above descending high-speed second-gear condition, so the piston rod of the actuator cylinder is driven to extend at a normal speed (high-speed first-gear).
When braking of the disc spring type hydraulic brake is required to be driven by the hydraulic control system, the piston rod of the oil cylinder needs to be retracted. For the proportional reversing valve, the valve core of the proportional reversing valve is in the left position after being moved rightwards, and an oil outlet in the proportional reversing valve is communicated with the working oil port. Hydraulic oil in the rodless cavity of the execution oil cylinder flows to an oil outlet in the proportional reversing valve through a working oil port of the proportional reversing valve and flows back into the power output unit to execute pressure unloading of the oil cylinder. Meanwhile, hydraulic oil output by the power output unit enters the second hydraulic control reversing valve and the first hydraulic control reversing valve. When the hydraulic oil enters the second hydraulic control reversing valve, the valve core of the second hydraulic control reversing valve is positioned at the right position, and a second oil port of the second hydraulic control reversing valve is communicated with the first oil port. When the hydraulic oil enters the second hydraulic control reversing valve, the hydraulic oil is output from the first oil port of the second hydraulic control reversing valve, enters the rod cavity of the execution oil cylinder, and pushes the piston rod of the execution oil cylinder to retract rapidly. When hydraulic oil enters the first hydraulic control reversing valve, the valve core of the first hydraulic control reversing valve is in a lower position, the hydraulic oil is output from the second oil port of the first hydraulic control reversing valve, enters the rod cavity of the execution oil cylinder, and pushes the piston rod of the execution oil cylinder to retract rapidly.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present disclosure, the drawings required for the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present disclosure, and other drawings may be obtained according to these drawings without inventive effort for a person of ordinary skill in the art.
Fig. 1 is a schematic diagram of a hydraulic control system for a multi-speed ram provided by an embodiment of the present disclosure.
The symbols in the drawings are as follows:
1. A power output unit; 11. a first flow pump; 12. a second flow pump; 13. an oil tank; 14. a second one-way valve; 15. an oil cooler; 16. a filter; 17. a motor;
2. A speed control unit; 21. a first hydraulically controlled reversing valve; 22. a proportional reversing valve; 23. a second hydraulically controlled reversing valve; 24. an electromagnetic reversing valve; 25. an overflow valve; 26. an accumulator; 27. a first one-way valve;
3. And executing the oil cylinder.
Detailed Description
For the purposes of clarity, technical solutions and advantages of the present disclosure, the following further details the embodiments of the present disclosure with reference to the accompanying drawings.
The disclosed embodiment provides a hydraulic control system of a multi-speed oil cylinder, as shown in fig. 1, which comprises a power output unit 1, a speed control unit 2 and an execution oil cylinder 3.
The speed control unit 2 comprises a first hydraulic control reversing valve 21, a proportional reversing valve 22 and a second hydraulic control reversing valve 23, wherein the spring pressure value of the first hydraulic control reversing valve 21 is smaller than that of the second hydraulic control reversing valve 23.
The first oil port a of the first hydraulic control reversing valve 21 is communicated with an oil outlet of the power output unit 1, the second oil port b of the first hydraulic control reversing valve 21 is communicated with a rod cavity of the execution oil cylinder 3, and the third oil port c of the first hydraulic control reversing valve 21 is communicated with an oil inlet of the power output unit 1.
The oil inlet P of the proportional reversing valve 22 is communicated with the oil outlet of the power output unit 1, the working oil port A of the proportional reversing valve 22 is communicated with the rodless cavity of the execution oil cylinder and the control oil port of the first hydraulic control reversing valve 21, and the oil outlet T of the proportional reversing valve 22 is communicated with the oil inlet of the power output unit 1.
The first oil port a of the second hydraulic control reversing valve 23 is communicated with a rod cavity of the execution oil cylinder 3, the second oil port b of the second hydraulic control reversing valve 23 is communicated with an oil inlet P of the proportional reversing valve 22, the third oil port c of the second hydraulic control reversing valve 23 is communicated with an oil inlet of the power output unit 1, and the control oil port of the second hydraulic control reversing valve 23 is communicated with a rodless cavity of the execution oil cylinder 3.
When the hydraulic control system provided by the embodiment of the present disclosure is used to drive the execution cylinder 3, first, the power output unit 1 is started so that the hydraulic oil output by the power output unit 1 enters the first pilot operated directional valve 21 and the proportional directional valve 22, respectively.
When the brake of the disc spring type hydraulic brake is released by the hydraulic control system, the piston rod of the actuating cylinder 3 needs to be driven to extend. For the proportional reversing valve 22, the valve core of the proportional reversing valve 22 is left shifted and then is positioned at the right position, and an oil inlet P in the proportional reversing valve 22 is communicated with the working oil port A. When hydraulic oil enters the proportional reversing valve 22, the hydraulic oil enters the rodless cavity of the execution cylinder 3 from the working oil port A of the proportional reversing valve 22, and the piston rod of the execution cylinder 3 is pushed to extend. At the same time, the valve core of the first pilot operated directional valve 21 is in the lower position, and the first oil port a and the second oil port b of the first pilot operated directional valve 21 are communicated. Hydraulic oil enters the first pilot operated directional control valve 21 through the first oil port a of the first pilot operated directional control valve 21. After the hydraulic oil enters the first hydraulic control reversing valve 21, the hydraulic oil is output from the second oil port b of the first hydraulic control reversing valve 21, passes through the first oil port a of the second hydraulic control reversing valve 23 together with the hydraulic oil in the rod cavity of the execution cylinder 3, and enters the second hydraulic control reversing valve 23. At the same time, the valve core of the second hydraulic control reversing valve 23 is at the right position, and the first oil port a and the second oil port b of the second hydraulic control reversing valve 23 are communicated. When hydraulic oil enters the second hydraulic control reversing valve 23, the hydraulic oil is output from the second oil port b of the second hydraulic control reversing valve 23, enters the proportional reversing valve 22 through the oil inlet P of the proportional reversing valve 22, is output into the rodless cavity of the execution cylinder 3, forms a differential loop, and the execution cylinder 3 moves downwards at a high speed three-gear, and drives the piston rod of the execution cylinder 3 to extend at a fastest speed (the high speed three-gear).
When the load of the actuating cylinder 3 exceeds the spring pressure value of the first pilot operated directional valve 21, the valve core of the first pilot operated directional valve 21 moves downward and is in an upper position, and the third oil port c and the first oil port a of the first pilot operated directional valve 21 are communicated. The hydraulic oil that enters the first pilot operated directional valve 21 through the first oil port a of the first pilot operated directional valve 21 does not enter the second pilot operated directional valve 23 any more, but flows back into the power take-off unit 1 through the third oil port c of the first pilot operated directional valve 21. That is, in this condition, the rodless chamber of the actuator cylinder 3 lacks the oil supply of the power output unit 1 through the first pilot operated directional valve 21, as compared with the above descending high speed three-gear condition, so the piston rod of the actuator cylinder 3 is driven to extend at a normal speed (high speed two-gear).
When the load of the execution cylinder 3 continues to increase and exceeds the spring pressure value of the second hydraulic control reversing valve 23, the valve core of the second hydraulic control reversing valve 23 moves right and is positioned at the left, and the third oil port c of the second hydraulic control reversing valve 23 is communicated with the first oil port a. After the hydraulic oil in the rod cavity of the execution cylinder 3 enters the second hydraulic control reversing valve 23 through the first oil port a of the second hydraulic control reversing valve 23, the hydraulic oil does not flow back into the rodless cavity of the execution cylinder 3 any more, but flows back into the power output unit 1 through the third oil port c of the second hydraulic control reversing valve 23. The actuator cylinder 3 descends at a high speed in one gear. That is, in this condition, the rodless chamber of the execution cylinder 3 lacks the supply of the hydraulic oil in the rod chamber of the execution cylinder 3, as compared with the above descending high-speed second-gear condition, so the piston rod of the execution cylinder 3 is driven to extend at a normal speed (high-speed first gear).
When braking of the disc spring type hydraulic brake is required to be driven by the hydraulic control system, retraction of the piston rod of the cylinder 3 is required to be performed. For the proportional reversing valve 22, the valve core of the proportional reversing valve 22 is in the left position after being moved right, and an oil outlet T in the proportional reversing valve 22 is communicated with the working oil port A. Hydraulic oil in the rodless cavity of the execution cylinder 3 flows to an oil outlet T in the proportional reversing valve 22 through a working oil port A of the proportional reversing valve 22 and flows back into the power output unit 1 to execute pressure unloading of the cylinder 3. At the same time, the hydraulic oil output from the power output unit 1 enters the second pilot operated directional valve 23 and the first pilot operated directional valve 21. When the hydraulic oil enters the second hydraulic control reversing valve 23, the valve core of the second hydraulic control reversing valve 23 is positioned at the right position, and the second oil port b of the second hydraulic control reversing valve 23 is communicated with the first oil port a. When the hydraulic oil enters the second hydraulic control reversing valve 23, the hydraulic oil is output from the first oil port a of the second hydraulic control reversing valve 23, enters the rod cavity of the execution cylinder 3, and pushes the piston rod of the execution cylinder 3 to retract rapidly. When hydraulic oil enters the first hydraulic control reversing valve 21, the valve core of the first hydraulic control reversing valve 21 is in the lower position, the hydraulic oil is output from the second oil port b of the first hydraulic control reversing valve 21, enters the rod cavity of the execution oil cylinder 3, and pushes the piston rod of the execution oil cylinder 3 to retract rapidly.
Alternatively, the power output unit 1 includes a first flow pump 11, a second flow pump 12, and an oil tank 13. The oil outlet of the first flow pump 11 is communicated with a first oil port a of the first hydraulic control reversing valve 21, and the oil inlet of the first flow pump 11 is communicated with the oil tank 13. The oil outlet of the second flow pump 12 is communicated with the oil inlet P of the proportional reversing valve 22, and the oil inlet of the second flow pump 12 is communicated with the oil tank 13.
In the above described implementation, the tank 13 is used to provide the power hydraulic oil for the entire hydraulic control system. The first flow pump 11 is used for pumping power hydraulic oil for a first pilot operated directional valve 21 in the hydraulic control system. The second flow pump 12 is used to pump the power hydraulic oil to the proportional directional valve 22 in the hydraulic control system so that the hydraulic oil can be filled into the execution cylinder 3, and finally the execution cylinder 3 can be moved.
In this embodiment, in order to enable the hydraulic oil in the oil tank 13 to meet the actual temperature demand, a thermometer is generally arranged on the side wall of the oil tank 13 so that it is possible to observe in real time whether the temperature in the oil tank 13 meets the actual demand.
In order to ensure that the quantity of oil in the tank 13 can meet the requirements of actual use, it is also usual to arrange a level gauge on the side wall of the tank 13, so that the depth of the hydraulic oil in the tank 13 can be observed in real time by means of the level gauge, in order to determine the volume of hydraulic oil in the tank 13.
Optionally, the power output unit 1 further comprises an electric motor 17, the electric motor 17 being for driving the first flow pump 11 and the second flow pump 12.
The motor 17 is used to drive the first flow pump 11 and the second flow pump 12 to rotate.
Illustratively, the first flow pump 11 and the second flow pump 12 are fixed displacement pumps.
By setting the first flow pump 11 and the second flow pump 12 as fixed displacement pumps, the output flow of the first flow pump 11 and the second flow pump 12 can be a constant value under the condition of constant rotation speed, that is, after the rotation speeds of the first flow pump 11 and the second flow pump 12 are selected, the corresponding output flow cannot be changed, so that the output flow of the first flow pump 11 and the second flow pump 12 cannot be changed under the condition of constant rotation speed, and further the movement stability of the execution cylinder 3 is ensured.
Alternatively, the output displacement of the first flow pump 11 is smaller than the output displacement of the second flow pump 12.
In the above implementation manner, the output displacement of the first flow pump 11 is smaller than the output displacement of the second flow pump 12, so that when the piston rod of the execution cylinder 3 extends, hydraulic oil can be input to the proportional reversing valve 22 through the large displacement of the second flow pump 12, and the piston rod of the execution cylinder 3 can be ensured to move quickly. The first flow pump 11 outputs slightly small-displacement hydraulic oil as the extension speed of the regulating piston rod, so that the safety and reliability of the execution cylinder 3 are improved.
In the present embodiment, the first flow pump 11 is a low-pressure large-flow pump, and the second flow pump 12 is a high-pressure small-flow pump.
Optionally, the power take-off unit 1 further comprises a second non-return valve 14. The oil inlet a of the second one-way valve 14 is communicated with the oil outlet of the first flow pump 11, and the oil outlet b of the second one-way valve 14 is communicated with the first oil port a of the first hydraulic control reversing valve 21.
In the above implementation manner, the second check valve 14 is used to limit the flow direction of the oil path between the oil outlet of the first flow pump 11 and the first oil port a of the first pilot operated directional valve 21, that is, by setting the second check valve 14, the hydraulic oil flowing out from the oil outlet of the first flow pump 11 can only be input to the first oil port a of the first pilot operated directional valve 21 in one direction, but cannot flow in the opposite direction, so as to improve the safety of the hydraulic control system.
Optionally, the power take-off unit 1 further comprises an oil cooler 15. The oil inlet of the oil cooler 15 is communicated with the oil outlet b of the first hydraulic control reversing valve 21, the oil outlet b of the second hydraulic control reversing valve 23 and the oil outlet b of the electromagnetic reversing valve 24, and the oil outlet of the oil cooler 15 is communicated with the oil tank 13.
In the above implementation manner, the oil cooler 15 is configured to reduce the hydraulic oil recovered into the oil tank 13, so that the hydraulic oil flowing out from the rodless cavity in the execution cylinder 3 can be quickly cooled, thereby improving the safety of the hydraulic control system.
Optionally, the power output unit 1 further comprises a filter 16, an oil inlet of the filter 16 is communicated with an oil outlet of the oil cooler 15, and an oil outlet of the filter 16 is communicated with the oil tank 13.
In the above implementation manner, the addition of the filter 16 can improve the use safety of the hydraulic control system, avoid impurities from entering the oil tank 13, and further enter the whole oil path again under the driving of the first flow pump 11 and the second flow pump 12, without affecting the use of each valve element, and avoid affecting the normal use of the execution oil cylinder 3.
With continued reference to fig. 1, the speed control unit 2 optionally further comprises an electromagnetic directional valve 24. The first oil port a of the electromagnetic directional valve 24 is communicated with the oil outlet P of the proportional directional valve 22, the second oil port b of the electromagnetic directional valve 24 is communicated with the oil inlet of the power output unit 1, and the third oil port c of the electromagnetic directional valve 24 is communicated with the oil inlet A of the proportional directional valve 22.
In the above implementation, when the electromagnet on the left side of the proportional directional valve 22 is powered, the spool of the proportional directional valve 22 moves to the right, and the spool is in the left position. The working oil port A of the proportional reversing valve 22 is communicated with the oil outlet T. The rodless cavity of the execution cylinder 3 is communicated with the oil tank 13 through the proportional reversing valve 22, and the pressure in the rodless cavity of the execution cylinder 3 is unloaded. At this time, the hydraulic oil output by the second flow pump 12 enters the rod cavity of the execution cylinder 3 through the second hydraulic control reversing valve 23, and the hydraulic oil output by the first flow pump 11 enters the rod cavity of the execution cylinder through the first hydraulic control reversing valve 21 to push the piston rod of the execution cylinder 3 to move upwards for retraction. The actuator cylinder 3 moves up with an up-shift.
When the electromagnet at the upper position of the electromagnetic directional valve 24 is powered on, the valve core of the electromagnetic directional valve 24 moves downwards and is at the upper position, and the third oil port c of the electromagnetic directional valve 24 is communicated with the first oil port a. Hydraulic oil output from the rodless cavity of the execution cylinder 3 enters the electromagnetic directional valve 24 through the oil outlet T of the proportional directional valve 22. After entering the electromagnetic directional valve 24, the hydraulic oil enters the second hydraulic directional valve 23 through the third oil port c of the electromagnetic directional valve 24, and flows into the first oil port a together with the hydraulic oil output by the second flow pump 12 through the second oil port b of the second hydraulic directional valve 23, and finally enters the rod cavity of the execution cylinder 3, and the execution cylinder 3 moves upwards in the second up gear.
That is, the upward movement speed of the actuating cylinder 3 can be controlled by controlling the electromagnetic directional valve 24 to satisfy different working conditions.
Optionally, the speed control unit 2 further includes an overflow valve 25, an oil inlet a of the overflow valve 25 is communicated with an oil inlet P of the proportional directional valve 22, an oil outlet b of the overflow valve 25 is communicated with an oil outlet T of the proportional directional valve 22, and a control oil c of the overflow valve 25 is communicated with an oil inlet a of the overflow valve.
In the above implementation manner, since the oil inlet a of the relief valve 25 is communicated with the oil inlet P of the proportional directional valve 22, the control oil port c of the relief valve 25 is communicated with the own oil inlet a, so that the pressure at the oil inlet in the relief valve 25 is lower than the pressure in the spring cavity of the relief valve 25, and the relief valve 25 is not opened. When the pressure at the oil inlet in the relief valve 25 is higher than the pressure in the spring cavity of the relief valve 25, the relief valve 25 is opened, so that the pressure in the rodless cavity of the execution cylinder 3 is not excessively high, and the relief valve overflows when the execution cylinder 3 is overloaded, thereby protecting the execution cylinder 3.
Optionally, the speed control unit 2 further includes an accumulator 26, and an operating oil port of the accumulator 26 is communicated with the oil inlet P of the proportional directional valve 22.
In the above-described implementation, the accumulator 26 serves as an auxiliary power source, and may supplement the flow rate that the implement cylinder 3 needs to supplement when descending at a high speed.
Illustratively, the number of the accumulators 26 is two, the two accumulators 26 are respectively located at two sides of the oil inlet P of the proportional directional valve 22, and the oil outlets of the two accumulators 26 are communicated with the oil inlet of the proportional directional valve 22.
Optionally, the speed control unit 2 further includes a first check valve 27, an oil inlet a of the first check valve 27 is communicated with an oil outlet of the power output unit 1, and an oil outlet b of the first check valve 27 is communicated with an oil inlet P of the proportional reversing valve 22.
In the above implementation manner, the first check valve 27 is used to limit the flow direction of the oil path between the oil outlet of the second flow pump 12 of the power output unit 1 and the oil inlet P of the proportional reversing valve 22, that is, by setting the first check valve 27, the hydraulic oil flowing out from the oil outlet of the second flow pump 12 can only be input to the oil inlet P of the proportional reversing valve 22 in one direction, but cannot flow in the opposite direction, so as to improve the safety of the hydraulic control system.
In this embodiment, the proportional reversing valve 22 is a three-position four-way proportional reversing valve. The relief valve 25 is an electromagnetic proportional relief valve, so that the pressure in the spring chamber of the relief valve 25 can be automatically adjusted by adjusting the size of the inlet of the relief valve 25, thereby adjusting the pressure entering the actuating cylinder 3.
Optionally, the hydraulic control system further comprises a controller electrically connected to the proportional reversing valve 22, the electromagnetic reversing valve 24, and the relief valve 25.
In the above-described embodiment, the controller can automatically control the operating states of the proportional directional valve 22, the electromagnetic directional valve 24, the relief valve 25, and the like, thereby improving the operating efficiency.
The working manner of the hydraulic control system provided by the embodiment of the present disclosure is briefly described below:
When the hydraulic control system provided by the embodiment of the present disclosure is used to drive the execution cylinder 3, first, the power output unit 1 is started so that the hydraulic oil output by the power output unit 1 enters the first pilot operated directional valve 21 and the proportional directional valve 22, respectively.
When the piston rod of the actuating cylinder 3 needs to be driven to extend, hydraulic oil output by the second flow pump 12 enters the proportional reversing valve 22, at this time, the valve core of the proportional reversing valve 22 is positioned at the right position, and an oil inlet P in the proportional reversing valve 22 is communicated with the working oil port A. When hydraulic oil enters the proportional reversing valve 22, the hydraulic oil enters the rodless cavity of the execution cylinder 3 from the working oil port A of the proportional reversing valve 22, and the piston rod of the execution cylinder 3 is pushed to extend out rapidly.
Meanwhile, the hydraulic oil output by the first flow pump 11 enters the first hydraulic control reversing valve 21, the valve core of the first hydraulic control reversing valve 21 is in the lower position, the hydraulic oil passes through the first oil port a and the second oil port b of the first hydraulic control reversing valve 21 and then passes through the first oil port a of the second hydraulic control reversing valve 23 together with the hydraulic oil in the rod cavity of the execution cylinder 3, the valve core of the second hydraulic control reversing valve 23 is in the right position, and the first oil port a and the second oil port b of the second hydraulic control reversing valve 23 are communicated. The hydraulic oil enters the proportional reversing valve 22 through the oil inlet P of the proportional reversing valve 22 after passing through the second oil port b of the second hydraulic control reversing valve 23, is further output into the rodless cavity of the execution oil cylinder 3, forms a differential loop, and drives the piston rod of the execution oil cylinder 3 to extend out at the fastest speed when the execution oil cylinder 3 moves downwards at a high speed of three steps.
When the load of the execution cylinder 3 exceeds the spring pressure value of the first pilot operated directional valve 21, the valve core of the first pilot operated directional valve 21 moves to the upper position for operation, and the first oil port a and the third oil port c of the first pilot operated directional valve 21 are communicated. The hydraulic oil output by the first flow pump 11 flows back to the oil tank 13 after being output by the third oil port c of the first hydraulic control reversing valve 21. The actuator cylinder 3 descends in the second gear at high speed. When the spring pressure value of the actuating cylinder 3 exceeds the spring pressure value of the second hydraulic control reversing valve 23, the valve core of the second hydraulic control reversing valve 23 moves to the left, the third oil port c of the second hydraulic control reversing valve 23 is communicated with the first oil port a, and hydraulic oil flowing out of the rodless cavity in the actuating cylinder 3 flows back into the oil tank 13 again after passing through the third oil port c of the second hydraulic control reversing valve 23, so that the actuating cylinder 3 descends at a high speed in a first gear.
When the piston rod of the actuation cylinder 3 needs to be driven to retract. At this time, the valve core of the proportional reversing valve 22 is at the left position, and the oil outlet T in the proportional reversing valve 22 is communicated with the working oil port a. The rodless cavity of the execution cylinder 3 is communicated with the proportional reversing valve 22 through a working oil port A of the proportional reversing valve 22, and is communicated with the power output unit 1 through an oil outlet T of the proportional reversing valve 22, so that the pressure unloading of the rodless cavity of the execution cylinder 3 is executed. The hydraulic oil output by the first flow pump 11 enters the first hydraulic control reversing valve 21, the valve core of the first hydraulic control reversing valve 21 is in a lower position, the first oil port a and the second oil port b of the first hydraulic control reversing valve 21 are communicated, the hydraulic oil is input into the rod cavity of the execution oil cylinder 3 through the second oil port b of the first hydraulic control reversing valve 21, and the piston rod of the execution oil cylinder 3 is pushed to move upwards to retract. The hydraulic oil output by the second flow pump 12 enters the second hydraulic control reversing valve 23, a first oil port a of the second hydraulic control reversing valve 23 is communicated with a second oil port b, and the hydraulic oil is input into a rod cavity of the execution cylinder 3 through the second oil port b of the second hydraulic control reversing valve 23 to push a piston rod of the execution cylinder 3 to move upwards to retract. The actuator cylinder 3 moves up with an up-shift.
When the electromagnet at the upper position of the electromagnetic directional valve 24 is powered on, the valve core of the electromagnetic directional valve 24 moves downwards and is at the upper position, and the third oil port c of the electromagnetic directional valve 24 is communicated with the first oil port a. Hydraulic oil output from the rodless cavity of the execution cylinder 3 enters the electromagnetic directional valve 24 through the oil outlet T of the proportional directional valve 22. After entering the electromagnetic directional valve 24, the hydraulic oil enters the second hydraulic directional valve 23 through the third oil port c of the electromagnetic directional valve 24, and flows into the first oil port a together with the hydraulic oil output by the second flow pump 12 through the second oil port b of the second hydraulic directional valve 23, and finally enters the rod cavity of the execution cylinder 3, and the execution cylinder 3 moves upwards in the second up gear.
The foregoing description of the preferred embodiments of the present disclosure is provided for the purpose of illustration only, and is not intended to limit the disclosure to the particular embodiments disclosed, but on the contrary, the intention is to cover all modifications, equivalents, alternatives, and alternatives falling within the spirit and principles of the disclosure.
Claims (10)
1. A hydraulic control system of a multi-speed oil cylinder, characterized in that the hydraulic control system comprises a power output unit (1), a speed control unit (2) and an execution oil cylinder (3);
the speed control unit (2) comprises a first hydraulic control reversing valve (21), a proportional reversing valve (22) and a second hydraulic control reversing valve (23), wherein the spring pressure value of the first hydraulic control reversing valve (21) is smaller than that of the second hydraulic control reversing valve (23);
The first oil port of the first hydraulic control reversing valve (21) is communicated with the oil outlet of the power output unit (1), the second oil port of the first hydraulic control reversing valve (21) is communicated with the rod cavity of the execution oil cylinder (3), and the third oil port of the first hydraulic control reversing valve (21) is communicated with the oil inlet of the power output unit (1);
An oil inlet of the proportional reversing valve (22) is communicated with an oil outlet of the power output unit (1), a working oil port of the proportional reversing valve (22) is communicated with a rodless cavity of the execution oil cylinder (3) and a control oil port of the first hydraulic control reversing valve (21), and an oil outlet of the proportional reversing valve (22) is communicated with an oil inlet of the power output unit (1);
the first oil port of the second hydraulic control reversing valve (23) is communicated with a rod cavity of the execution oil cylinder (3), the second oil port of the second hydraulic control reversing valve (23) is communicated with an oil inlet of the proportional reversing valve (22), the third oil port of the second hydraulic control reversing valve (23) is communicated with an oil inlet of the power output unit (1), and a control oil port of the second hydraulic control reversing valve (23) is communicated with a rodless cavity of the execution oil cylinder (3).
2. The hydraulic control system according to claim 1, characterized in that the speed control unit (2) further comprises an electromagnetic directional valve (24);
The first oil port of the electromagnetic directional valve (24) is communicated with the oil outlet of the proportional directional valve (22), the second oil port of the electromagnetic directional valve (24) is communicated with the oil inlet of the power output unit (1), and the third oil port of the electromagnetic directional valve (24) is communicated with the oil inlet of the proportional directional valve (22).
3. The hydraulic control system according to claim 1, characterized in that the speed control unit (2) further comprises a relief valve (25);
An oil inlet of the overflow valve (25) is communicated with an oil inlet of the proportional reversing valve (22), an oil outlet of the overflow valve (25) is communicated with an oil outlet of the proportional reversing valve (22), and control oil of the overflow valve (25) is communicated with an oil inlet of the overflow valve.
4. The hydraulic control system according to claim 1, characterized in that the speed control unit (2) further comprises an accumulator (26);
an operating oil port of the energy accumulator (26) is communicated with an oil inlet of the proportional reversing valve (22).
5. The hydraulic control system according to claim 1, characterized in that the speed control unit (2) further comprises a first non-return valve (27);
an oil inlet of the first one-way valve (27) is communicated with an oil outlet of the power output unit (1), and an oil outlet of the first one-way valve (27) is communicated with an oil inlet of the proportional reversing valve (22).
6. The hydraulic control system according to claim 2, characterized in that the power take-off unit (1) comprises a first flow pump (11), a second flow pump (12) and a tank (13);
an oil outlet of the first flow pump (11) is communicated with a first oil port of the first hydraulic control reversing valve (21), and an oil inlet of the first flow pump (11) is communicated with the oil tank (13);
an oil outlet of the second flow pump (12) is communicated with an oil inlet of the proportional reversing valve (22), and an oil inlet of the second flow pump (12) is communicated with the oil tank (13).
7. The hydraulic control system according to claim 6, characterized in that the output displacement of the first flow pump (11) is smaller than the output displacement of the second flow pump (12).
8. The hydraulic control system according to claim 6, characterized in that the power take-off unit (1) further comprises a second non-return valve (14);
An oil inlet of the second one-way valve (14) is communicated with an oil outlet of the first flow pump (11), and an oil outlet of the second one-way valve (14) is communicated with a first oil port of the first hydraulic control reversing valve (21).
9. The hydraulic control system according to claim 6, characterized in that the power take-off unit (1) further comprises an oil cooler (15);
an oil inlet of the oil cooler (15) is communicated with an oil outlet of the first hydraulic control reversing valve (21), an oil outlet of the second hydraulic control reversing valve (23) and an oil outlet of the electromagnetic reversing valve (24), and an oil outlet of the oil cooler (15) is communicated with the oil tank (13).
10. The hydraulic control system according to claim 9, characterized in that the power take-off unit (1) further comprises a filter (16);
an oil inlet of the filter (16) is communicated with an oil outlet of the oil cooler (15), and an oil outlet of the filter (16) is communicated with the oil tank (13).
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| CN202111116638.8A CN113983035B (en) | 2021-09-23 | 2021-09-23 | Hydraulic control system of multi-speed oil cylinder |
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Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105221506A (en) * | 2015-09-18 | 2016-01-06 | 徐州工业职业技术学院 | A kind of load-sensitive valve and load-sensitive hydraulic system |
| CN111692141A (en) * | 2020-04-30 | 2020-09-22 | 武汉船用机械有限责任公司 | Hydraulic system for controlling oil cylinder |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH06288402A (en) * | 1993-03-31 | 1994-10-11 | Komatsu Ltd | Oil pressure passage for swirl |
| JP3900949B2 (en) * | 2002-02-04 | 2007-04-04 | コベルコ建機株式会社 | Control device and control method for hydraulic work machine |
| JP2011106591A (en) * | 2009-11-18 | 2011-06-02 | Hitachi Constr Mach Co Ltd | Hydraulic driving device of construction machine |
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2021
- 2021-09-23 CN CN202111116638.8A patent/CN113983035B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105221506A (en) * | 2015-09-18 | 2016-01-06 | 徐州工业职业技术学院 | A kind of load-sensitive valve and load-sensitive hydraulic system |
| CN111692141A (en) * | 2020-04-30 | 2020-09-22 | 武汉船用机械有限责任公司 | Hydraulic system for controlling oil cylinder |
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