CN111503067A - Acceleration pressurization system - Google Patents
Acceleration pressurization system Download PDFInfo
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- CN111503067A CN111503067A CN202010326703.9A CN202010326703A CN111503067A CN 111503067 A CN111503067 A CN 111503067A CN 202010326703 A CN202010326703 A CN 202010326703A CN 111503067 A CN111503067 A CN 111503067A
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- oil cylinder
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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
- F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
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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
- F15B11/08—Servomotor systems without provision for follow-up action; Circuits therefor with only one servomotor
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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
- F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
- F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B2211/00—Circuits for servomotor systems
- F15B2211/50—Pressure control
Abstract
The invention discloses an acceleration pressurization system, which comprises a second switching valve, a double-acting oil cylinder and a third switching valve, wherein the second switching valve, the double-acting oil cylinder and the third switching valve are arranged on an oil inlet and outlet way of an execution oil cylinder; the double-acting oil cylinder is internally provided with a piston with a large end and a small end, the large end and the small end corresponding to the piston are respectively a large cavity and a small cavity of the double-acting oil cylinder, the double-acting oil cylinder is connected with a branch through the large cavity and the small cavity and is arranged on a working oil inlet path of the execution oil cylinder in parallel, and the second switching valve is arranged on the branch path connected with the large cavity of the double-acting oil cylinder; the third switching valve is arranged on a working oil return path of the execution oil cylinder, and an oil return port of the execution oil cylinder is connected between the working oil return path and the working oil inlet path in a switching manner. On the premise of not changing the discharge capacity and pressure grade of a main pump, the acceleration pressurization system is added on a working oil way of the execution oil cylinder to accelerate the no-load running speed of the execution oil cylinder, increase the maximum output force of the oil cylinder load and realize the quick or large thrust extension of the execution oil cylinder.
Description
Technical Field
The invention belongs to a hydraulic control technology, and particularly relates to an accelerating and pressurizing system of a hydraulic oil cylinder.
Background
In engineering machinery, construction machinery and factory automation equipment which are driven by hydraulic pressure, a hydraulic oil cylinder is a main execution element, and due to the consideration of actual working requirements and design light weight, the hydraulic oil cylinder requires speed to move to contact with a load in a no-load process, flow needs to be improved, pressure needs to be improved after the load to do work on the load, the flow and the pressure needed by the hydraulic oil cylinder are often inconsistent, so that the condition that a single or a few groups of actions need to output larger thrust and a large-cylinder-diameter high-pressure oil cylinder is used exists.
The existing solution is to select the pressure grade and the main pump displacement of a corresponding hydraulic system according to the requirement of a large-bore high-pressure oil cylinder to meet the high-pressure large-flow output of the oil cylinder, and then to realize the low-pressure small-flow output of the oil cylinder by setting secondary overflow and speed regulation in the hydraulic system, so that the corresponding elements in the hydraulic system must be selected according to the large-flow high-pressure, and the cost remains high.
Disclosure of Invention
The technical problem solved by the invention is as follows: the accelerated pressurization system is provided, the accelerated extension and high-pressure driving of the hydraulic oil cylinder are realized on the premise of not changing the flow and pressure grade of the existing hydraulic system, and the cost of the hydraulic system of the equipment is effectively controlled.
The invention is realized by adopting the following technical scheme:
the acceleration pressurization system comprises a second switching valve 5, a double-acting oil cylinder 6 and a third switching valve 8 which are arranged on an oil inlet and outlet way of the execution oil cylinder;
the double-acting oil cylinder 6 is internally provided with a piston with a large end and a small end, the large end and the small end corresponding to the piston are respectively a large cavity and a small cavity of the double-acting oil cylinder, the double-acting oil cylinder 6 is connected with a branch through the large cavity and the small cavity and is arranged on a working oil inlet path of the execution oil cylinder in parallel, and the second switching valve 5 is arranged on the branch path connected with the large cavity of the double-acting oil cylinder 6;
the third switching valve 8 is arranged on a working oil return path of the execution oil cylinder, and an oil return port of the execution oil cylinder is connected between the working oil return path and a working oil inlet path in a switching manner.
Further, still include energy storage ware 1, energy storage ware 1 sets up on the work oil feed way of actuating cylinder through the branch road connection, be equipped with first switching valve 2 on the branch road of energy storage ware 1.
Further, the first switching valve 2 is a two-position two-way reversing valve and comprises a communication position and a stop position.
Furthermore, a hydraulic control one-way valve 7 connected with the double-acting oil cylinder 6 in parallel is further arranged on the working oil inlet path of the execution oil cylinder, and a pilot oil path of the hydraulic control one-way valve 7 is connected with a working oil return path of the execution oil cylinder.
Furthermore, the second switching valve 5 is a two-position three-way reversing valve, and comprises a communicating position and a stopping position, and the stopping position is provided with an intercommunicating oil path which communicates the large end of the double-acting oil cylinder 6 with the two ends of the large cavity.
Furthermore, the large cavity of the double-acting oil cylinder 6 is connected to the working oil return path through an oil drainage path at one side close to the small end.
Further, the third diverter valve 8 is two tee bend switching-over valves, including oil return work position and confluence work position, oil return work position will carry out the oil return opening and the work oil return way intercommunication of hydro-cylinder, confluence work position will carry out the oil return opening and the work oil inlet way intercommunication of hydro-cylinder.
Furthermore, a first check valve 3 and a second check valve 4 are respectively arranged on the working oil inlet path corresponding to the parallel sections of the hydraulic control check valve 7 and the double-acting oil cylinder 6.
As a preferable aspect of the acceleration/pressurization system of the present invention, the first switching valve 2, the second switching valve 5, and the third switching valve 8 are pilot-operated directional valves, the first switching valve 2 and the third switching valve 8 are all shifted by pilot pressure oil, and the second switching valve 5 is connected to a small chamber of the double-acting cylinder 6 through a pilot oil passage.
As still another preferable aspect of the acceleration/pressurization system of the present invention, the first switching valve 2, the second switching valve 5, and the third switching valve 8 are electrically controlled directional valves.
When the execution oil cylinder extends out in an idle load mode, pumped pressure oil enters a working oil inlet path of the execution oil cylinder, hydraulic oil stored in the energy accumulator enters the working oil inlet path through confluence of the first switching valve, return oil of the execution oil cylinder enters the working oil inlet path through confluence of the third switching valve, oil inlet amount entering the execution oil cylinder is increased, and the converged hydraulic oil enters a large cavity of the oil cylinder through the first one-way valve and the second one-way valve in the working oil inlet path to enable the execution oil cylinder to extend out quickly.
When the load of the execution oil cylinder extends out, the pumped pressure oil enters a working oil inlet path of the execution oil cylinder, as the back pressure in the working oil inlet pipe is increased, a part of the pressure oil enters the energy accumulator through the first switching valve for storage, and a part of the pressure oil enters the execution oil cylinder after being pressurized by the second switching valve through the double-acting oil cylinder, so that the pressurization of the execution oil cylinder is realized, and the return oil of the execution oil cylinder directly flows back to the oil tank through the third switching valve and the working oil return path.
When the execution oil cylinder retracts, the pumped pressure oil enters a working oil return path of the execution oil cylinder, enters the execution oil cylinder through the third switching valve to drive the oil cylinder to retract, meanwhile, the pressure oil on the working oil return path opens the hydraulic control one-way valve, and the return oil of the execution oil cylinder flows back to the oil tank through the hydraulic control one-way valve and the working oil inlet path.
The invention has the beneficial effects that: on the premise of not changing the discharge capacity and pressure grade of a main pump, the acceleration pressurization system is added on a working oil way of the execution oil cylinder to accelerate the no-load running speed of the execution oil cylinder and increase the maximum output force of the load of the oil cylinder, the whole process can automatically identify and switch according to the change of the system pressure caused by the load condition of the execution oil cylinder, the whole system is common hydraulic components, the installation is simple, and the cost is lower compared with that of large components such as a high-power main pump.
The invention is further described with reference to the following figures and detailed description.
Drawings
Fig. 1 is a hydraulic schematic diagram of an acceleration and pressurization system in a first embodiment.
Fig. 2 is a hydraulic schematic diagram of the acceleration pressurization system in the first embodiment when the actuating cylinder is in an unloaded extension state.
Fig. 3 is a hydraulic schematic diagram of the acceleration and pressurization system in the first embodiment when the actuating cylinder is in a load-extending state.
Fig. 4 is a hydraulic schematic diagram of the acceleration pressurizing system in the first embodiment when the actuating cylinder is in the retracted state.
Fig. 5 is a hydraulic schematic diagram of the acceleration and pressurization system in the second embodiment.
Reference numbers in the figures: 1-an energy accumulator, 2-a first switching valve, 3-a first one-way valve, 4-a second one-way valve, 5-a second switching valve, 6-a double-acting oil cylinder, 7-a hydraulic control one-way valve, 8-a third switching valve, 9-an execution oil cylinder, 100-a working oil inlet path and 200-a working oil return path.
Detailed Description
Example one
Referring to fig. 1, the acceleration and pressurization system shown in the figure is a specific embodiment of the present invention, and specifically includes an accumulator 1, a first switching valve 2, a first check valve 3, a second check valve 4, a second switching valve 5, a double-acting cylinder 6, a pilot-controlled check valve 7, and a third switching valve 8. With reference to fig. 2 and 3, the acceleration and pressurization system of the present embodiment achieves the purpose of idle acceleration and load pressurization during the work application process of the execution cylinder 9. The acceleration pressurization system of this embodiment is disposed on an oil inlet and outlet path of the execution oil cylinder 9, wherein a large cavity and a small cavity of the execution oil cylinder 9 are respectively connected to an a1 port and a B1 port of the acceleration pressurization system, the a port and the B port of the acceleration pressurization system are respectively connected to a hydraulic system reversing valve working oil port of the execution oil cylinder 9 in an abutting-joint manner, and a reversing control oil path related to the hydraulic oil cylinder belongs to the conventional technology, and is not described herein in detail.
In this embodiment, the piston of the execution cylinder 9 extends outward to be in a working state, the working oil inlet path 100 refers to a pressure oil path through which pumped hydraulic oil enters the large cavity of the execution cylinder 9 to push the piston to extend outward to work, and the working oil return path 200 refers to an oil return path through which return oil in the small cavity of the cylinder flows back to the oil tank when the execution cylinder extends outward to work. In practical application, the connection sequence of the working oil inlet path and the working oil return path and the large cavity and the small cavity of the execution oil cylinder can be adjusted and designed according to specific working conditions.
Specifically, in the acceleration and pressurization system of the embodiment, the flow rate of the hydraulic oil entering the execution oil cylinder is increased by using the return oil confluence of the energy accumulator 1 and the execution oil cylinder, the extension speed of the execution oil cylinder 9 is increased, the pressure of the hydraulic oil entering the execution oil cylinder is increased by using the pressurization effect of different sections of the piston of the double-acting working cylinder, and the extension pressure of the execution oil cylinder 9 is increased.
Wherein the interior of the double-acting oil cylinder 6 is a piston with a big end and a small end, namely the piston is provided with two piston heads with a big end with a large area and a small end with a small area, the big end and the small end corresponding to the piston are respectively a big cavity and a small cavity of the double-acting oil cylinder 6, the big cavity and the small cavity of the double-acting oil cylinder 6 are respectively connected with a working oil inlet 100 of the execution oil cylinder 9 through a branch, the double-acting oil cylinder 6 and the working oil inlet 100 of the execution oil cylinder 9 are arranged in parallel, the second switching valve 5 is arranged on a branch connected with the big cavity of the double-acting oil cylinder 6, the branch between the small cavity of the double-acting oil cylinder 6 and the working oil inlet 100 is normally open, the second switching valve 5 is a two-position three-way reversing valve and comprises a communication position and a cut-off position, wherein the communication position communicates the big cavity of the double-acting oil cylinder 6 with the working, an intercommunicating oil path for communicating the large end of the double-acting oil cylinder 6 with the two ends of the large cavity is arranged at the stop position of the second switching valve 5, and meanwhile, the large cavity of the double-acting oil cylinder 6 is connected to the working oil return path 200 through an oil drainage path at one side close to the small end, so that the large-end piston of the double-acting oil cylinder 6 can normally move in the large cavity no matter the second switching valve 5 is at the communication position or the stop position.
The third switching valve 8 is arranged on a working oil return path 200 of the execution oil cylinder 9, an oil return port of the execution oil cylinder 9 is connected between the working oil return path 200 and the working oil inlet path 100 in a switching manner, the third switching valve 8 is a two-position three-way reversing valve and comprises an oil return working position and a confluence working position, the oil return working position communicates the oil return port of the execution oil cylinder 9 with the working oil return path 200, direct oil return of the execution oil cylinder 9 is achieved, the confluence working position communicates the oil return port of the execution oil cylinder 9 with the working oil inlet path 100, and the oil return and oil inlet confluence of the execution oil cylinder 9 is achieved, so that the working speed of the execution oil cylinder is.
The energy accumulator 1 is connected and arranged on a working oil inlet path 100 of the execution oil cylinder 9 through a branch path, the first switching valve 2 is arranged on a connecting branch path of the working oil inlet path 100 and the energy accumulator 1, the first switching valve 2 is a two-position two-way reversing valve and comprises a communicating position and a stopping position, the communicating position communicates the energy accumulator 1 with the working oil inlet path 100, and the stopping position stops the energy accumulator 1 from the working oil inlet path 100.
In addition, a hydraulic control one-way valve 7 connected with the double-acting oil cylinder 6 in parallel is further arranged on the working oil inlet path of the execution oil cylinder 9, and a pilot oil path of the hydraulic control one-way valve 7 is connected with a working oil return path of the execution oil cylinder and used for serving as an oil return path of the working oil inlet path 100 when the execution oil cylinder 9 is in a retraction state. The parallel section corresponding to the hydraulic control one-way valve 7 and the double-acting oil cylinder 6 on the working oil inlet path is respectively provided with a first one-way valve 3 and a second one-way valve 4, and the normal work of each parallel hydraulic component is ensured through the one-way valves.
In this embodiment, the first switching valve 2, the second switching valve 5, and the third switching valve 8 are pilot-operated directional control valves, the first switching valve 2 and the third switching valve 8 are both shifted by pilot pressure oil, that is, the pressure oil passing through the first switching valve 2 and the third switching valve 8 is partially communicated to pilot holes of the corresponding directional control valves to push valve cores to perform directional switching, the second switching valve 5 is connected to a small cavity of the double-acting cylinder 6 through a pilot oil path, and the pressure created after a piston in the double-acting cylinder is in place is used to push the second directional control valve 5 to perform directional switching.
The operation of the supercharging system according to the present embodiment will be described in detail below.
When the oil cylinder does not act, the valve cores of the first switching valve 2, the second switching valve 5 and the third switching valve 8 stop at the initial positions under the action of spring force, and partial pressure oil is stored in the energy accumulator 1.
As shown in fig. 2, when the actuating cylinder 9 extends in no-load, the pumped pressure oil enters the working oil inlet path 100 from the port a, the first switching valve 2 is switched to the upper position under the action of pressure, and the pressure oil stored in the accumulator 1 is released through the upper position of the first switching valve 2 to merge with the entered oil in the working oil inlet path 100; at the same time, the pressure is not enough to push the third switching valve 8, and the third switching valve 8 is maintained at the right position; when the pressure oil of the working oil inlet path 100 enters the large cavity of the execution oil cylinder 9, the oil returned from the small cavity of the execution oil cylinder 9 is merged with the oil inlet of the working oil inlet path 100 through the right position of the third switching valve 8. The second switching valve 5 is pressure balanced and is maintained at the lower position, and the double-acting cylinder 6 does not act. In the working state of fig. 2, the pumped pressure oil, the pressure oil released by the accumulator 1 and the small-cavity return oil of the execution oil cylinder 9 are converged in the working oil inlet path 100 and enter the large cavity of the execution oil cylinder 9 through the first check valve 3, the second check valve 4 and the hydraulic control check valve 7, so that the piston rod of the execution oil cylinder 9 is accelerated to extend out.
As shown in fig. 3, when the actuating cylinder 9 is loaded when extending, the oil inlet pressure at the port a rises, the first switching valve 2 is switched to the upper position under the action of pressure, and part of the pressure oil enters the energy accumulator through the lower position of the first switching valve 2 to store energy; meanwhile, the third switching valve 8 is switched to the left position under the action of pressure oil, and the small cavity of the execution oil cylinder 9 is directly communicated with the oil tank through the left position of the third switching valve 8. In the working oil inlet path 100, pressure oil enters a small cavity of the double-acting oil cylinder 6 through the first one-way valve 3, a piston rod in the double-acting oil cylinder 6 runs to the large cavity until the small cavity is filled with the pressure oil, return oil in the double-acting oil cylinder 6 passes through a left return oil tank of the third switching valve 8 through an oil discharge path, a valve core of the second switching valve 5 is pushed to be switched to an upper position along with the pressure rise of the small cavity of the double-acting oil cylinder 6, the working oil inlet path 100 is communicated with the large cavity of the double-acting oil cylinder 6, the pressure oil in the working oil inlet path 100 enters the large cavity of the double-acting oil cylinder 6 through the upper position of the second switching valve 5 to push a piston rod of the double-acting oil cylinder 6 to move to the small cavity, return oil in the double-acting oil cylinder 6 passes through the left return oil tank of the third switching valve 8 through the oil discharge path, after being pressurized, the hydraulic oil in the small cavity of the double-acting oil cylinder 6 enters the large cavity of the execution oil cylinder 9 through the second one-way valve 4, so that the piston rod of the execution oil cylinder 9 is pressurized and extends out. When the piston rod of the double-acting oil cylinder 6 runs to the top of the small cavity until the large cavity is filled, the small cavity of the double-acting oil cylinder 6 cuts off the pilot pressure oil of the second switching valve 5, the second switching valve 5 is reset and switched to the lower position, the pressure oil of the working oil inlet 100 fills the small cavity of the double-acting oil cylinder 6 again, and the pressurization action of the execution oil cylinder 9 in the continuous extension process is realized through the repeated switching of the second switching valve 5 and the reciprocating motion of the double-acting oil cylinder 6.
As shown in fig. 4, when the execution cylinder 9 retracts after completing the extending action, the reversing valve of the hydraulic system switches the working oil inlet path and the working oil return path, at this time, the working oil inlet path 100 is returned, the working oil return path 200 is fed, the pumped pressure oil is fed from the port B, the third switching valve 8 is switched to the left position under the pressure action, meanwhile, the pilot-operated check valve 7 is opened under the pressure action of the fed oil, the pressure oil enters the small cavity of the execution cylinder 9 from the working oil return path 200 through the left position of the third switching valve 8, the piston rod of the execution cylinder 9 is pushed to retract, the large cavity returned oil of the execution cylinder 9 is returned from the port a through the bypass oil path where the pilot-operated check valve 7 is located, and the first check valve 3 and the second check valve 4 arranged on the working oil inlet path 100 prevent the returned oil from entering the.
Example two
Referring to fig. 5, the present embodiment is another specific embodiment of the boost system of the present invention, which is different from the first embodiment in that: in this embodiment, the first switching valve 2, the second switching valve 5, and the third switching valve 8 all adopt electrically controlled directional valves, and the electrically controlled directional valves can be triggered and switched by pressure sensors or position sensors arranged on the oil paths.
If the first switching valve 2 and the third switching valve 8 are feedback-controlled by a pressure sensor provided on the working oil feed line 100, the operation of the second switching valve 5 is feedback-controlled by a position sensor that detects the movement of the piston of the double-acting cylinder 6.
When the execution oil cylinder 9 extends out in a no-load mode, pumped pressure oil enters the working oil inlet path 100 from the port A, the first switching valve 2 can be controlled to be switched to the upper position as long as the pressure built in the working oil inlet path 100 is detected, and the pressure oil stored in the energy accumulator 1 is released through the upper position of the first switching valve 2 and is converged with the oil entering the working oil inlet path 100; because the oil is unloaded, at this time, the oil inlet pressure in the working oil inlet path 100 does not reach the pressure threshold value switched by the third switching valve 8, and the third switching valve 8 is maintained at the right position; the second switching valve 5 maintains the lower position according to the detected position of the piston of the double-acting oil cylinder 6, the double-acting oil cylinder 6 does not act, the pumped pressure oil, the pressure oil released by the energy accumulator 1 and the small cavity return oil of the execution oil cylinder 9 are converged in the working oil inlet path 100 and enter the large cavity of the execution oil cylinder 9 through the first check valve 3, the second check valve 4 and the hydraulic control check valve 7, and the piston rod of the execution oil cylinder 9 is accelerated to extend.
When the execution oil cylinder 9 extends out and is loaded, the oil inlet pressure at the port A is increased, the first switching valve 2 is still switched to the upper position, and part of pressure oil enters the energy accumulator through the lower position of the first switching valve 2 to store energy; at this time, the back pressure inside the working oil inlet path 100 is increased due to the load, the pressure signal reaches the switching threshold of the third switching valve 8 and is switched to the left position, and the small cavity of the actuating cylinder 9 is directly communicated with the oil tank through the left position of the third switching valve 8. In the working oil inlet path 100, pressure oil enters a small cavity of the double-acting oil cylinder 6 through the first one-way valve 3, a piston rod in the double-acting oil cylinder 6 runs to the large cavity until the small cavity is filled with the pressure oil, return oil in the double-acting oil cylinder 6 passes through a left position oil return tank of the third switching valve 8 through an oil discharge path, after a piston of the double-acting oil cylinder 6 moves to a limit position of the large cavity, a detected piston position signal triggers and controls a valve core of the second switching valve 5 to be switched to an upper position, the working oil inlet path 100 is communicated with the large cavity of the double-acting oil cylinder 6, the pressure oil in the working oil inlet path 100 enters the large cavity of the double-acting oil cylinder 6 through the upper position of the second switching valve 5 to push a piston rod of the double-acting oil cylinder 6 to move to the small cavity, the return oil of the double-acting oil cylinder 6 passes through the left position oil return tank of the third switching valve 8 through the oil, after being pressurized, the hydraulic oil in the small cavity of the double-acting oil cylinder 6 enters the large cavity of the execution oil cylinder 9 through the second one-way valve 4, so that the piston rod of the execution oil cylinder 9 is pressurized and extends out. When the piston rod of the double-acting oil cylinder 6 runs to the top extreme position of the small cavity, the detected position signal controls the second switching valve 5 to reset and switch to the lower position again, the pressure oil of the working oil inlet path 100 fills the small cavity of the double-acting oil cylinder 6 again, and the pressurization action of the execution oil cylinder 9 in the continuous extending process is realized through the repeated switching of the second switching valve 5 and the reciprocating motion of the double-acting oil cylinder 6.
When the execution oil cylinder 9 retracts after the extension action is finished, pumped pressure oil enters from the port B, the third switching valve 8 is switched to the left position in a feedback mode through a detected pressure signal, meanwhile, the hydraulic control one-way valve 7 is opened under the action of oil inlet pressure, the pressure oil enters the small cavity of the execution oil cylinder 9 from the working oil return path 200 through the left position of the third switching valve 8, the piston rod of the execution oil cylinder 9 is pushed to retract, oil returning from the port A is conducted from the large cavity of the execution oil cylinder 9 through a bypass oil path where the hydraulic control one-way valve 7 is located, and the first one-way valve 3 and the second one-way valve 4 arranged on the working oil inlet path 100 prevent the oil returning from entering the double-acting oil.
The above description is only one embodiment of the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, replacement, or improvement made within the scope of the claims of the present invention should be included in the scope of the present invention.
Claims (10)
1. The acceleration pressure boost system, its characterized in that: the hydraulic control system comprises a second switching valve (5), a double-acting oil cylinder (6) and a third switching valve (8), wherein the second switching valve (5), the double-acting oil cylinder and the third switching valve are arranged on an oil inlet and outlet way of an execution oil cylinder;
the double-acting oil cylinder (6) is internally provided with a piston with a large end and a small end, the large end and the small end corresponding to the piston are respectively a large cavity and a small cavity of the double-acting oil cylinder, the double-acting oil cylinder (6) is connected with a branch through the large cavity and the small cavity and is arranged on a working oil inlet path of the execution oil cylinder in parallel, and the second switching valve (5) is arranged on the branch connected with the large cavity of the double-acting oil cylinder (6);
and the third switching valve (8) is arranged on a working oil return path of the execution oil cylinder, and an oil return port of the execution oil cylinder is switched and connected between the working oil return path and a working oil inlet path.
2. The accelerating and supercharging system of claim 1, further comprising an energy accumulator (1), wherein the energy accumulator (1) is connected and arranged on a working oil inlet path of the execution oil cylinder through a branch path, and a first switching valve (2) is arranged on the branch path of the energy accumulator (1).
3. An accelerated boost system according to claim 2, said first switching valve (2) being a two-position two-way reversing valve comprising a communication position and a shut-off position.
4. The accelerating and supercharging system of claim 1, wherein a pilot-operated check valve (7) connected in parallel with the double-acting cylinder (6) is further arranged on the working oil inlet path of the execution cylinder, and a pilot oil path of the pilot-operated check valve (7) is connected with the working oil return path of the execution cylinder.
5. The accelerated pressure system according to claim 1, wherein the second switching valve (5) is a two-position three-way reversing valve, and comprises a communication position and a stop position, and an oil communication path for communicating the large end of the double-acting oil cylinder (6) with the two ends of the large cavity is arranged at the stop position.
6. An accelerated boost system according to claim 5, the large chamber of the double acting cylinder (6) being connected to the working return by a drain on the side close to the small end.
7. The boost system according to claim 1, wherein the third switching valve (8) is a two-position three-way directional valve, and comprises an oil return working position and a confluence working position, the oil return working position communicates the oil return port of the execution cylinder with the working oil return path, and the confluence working position communicates the oil return port of the execution cylinder with the working oil inlet path.
8. The accelerating and supercharging system of claim 4, wherein a first check valve (3) and a second check valve (4) are respectively arranged on the working oil inlet path corresponding to the hydraulic control check valve (7) and the parallel section of the double-acting oil cylinder (6).
9. An acceleration and pressure boost system according to any of claims 2-8, the first (2), second (5) and third (8) switching valves being pilot operated directional valves, the first (2) and third (8) switching valves being all directional by pilot pressure oil, the second switching valve (5) being connected to the small chamber of the double acting cylinder (6) by a pilot oil line.
10. The boost system according to any of claims 2-8, the first switching valve (2), the second switching valve (5) and the third switching valve (8) being electronically controlled directional valves.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010326703.9A CN111503067A (en) | 2020-04-23 | 2020-04-23 | Acceleration pressurization system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202010326703.9A CN111503067A (en) | 2020-04-23 | 2020-04-23 | Acceleration pressurization system |
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| CN111503067A true CN111503067A (en) | 2020-08-07 |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113339335A (en) * | 2021-06-16 | 2021-09-03 | 海南浙江大学研究院 | Servo actuating system that pressure boost was launched |
| CN117366035A (en) * | 2023-12-07 | 2024-01-09 | 吉林大学 | Large-cavity bag type rapid supercharging device |
-
2020
- 2020-04-23 CN CN202010326703.9A patent/CN111503067A/en active Pending
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113339335A (en) * | 2021-06-16 | 2021-09-03 | 海南浙江大学研究院 | Servo actuating system that pressure boost was launched |
| CN113339335B (en) * | 2021-06-16 | 2022-11-22 | 海南浙江大学研究院 | Servo actuating system for pressurization ejection |
| CN117366035A (en) * | 2023-12-07 | 2024-01-09 | 吉林大学 | Large-cavity bag type rapid supercharging device |
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