CN116557371B - Hydraulic servo adjusting device of large-load mechanism and control method thereof - Google Patents
Hydraulic servo adjusting device of large-load mechanism and control method thereof Download PDFInfo
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- CN116557371B CN116557371B CN202310836726.8A CN202310836726A CN116557371B CN 116557371 B CN116557371 B CN 116557371B CN 202310836726 A CN202310836726 A CN 202310836726A CN 116557371 B CN116557371 B CN 116557371B
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- 230000007246 mechanism Effects 0.000 title claims abstract description 40
- 238000000034 method Methods 0.000 title claims abstract description 23
- 230000001105 regulatory effect Effects 0.000 claims abstract description 7
- 230000001276 controlling effect Effects 0.000 claims abstract description 4
- 230000001502 supplementing effect Effects 0.000 claims description 22
- 230000006837 decompression Effects 0.000 claims description 19
- 238000012544 monitoring process Methods 0.000 claims description 5
- 230000009471 action Effects 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 1
- 230000005484 gravity Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000000630 rising 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
- 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
- F15B13/025—Pressure reducing valves
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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
-
- 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
- F15B19/00—Testing; Calibrating; Fault detection or monitoring; Simulation or modelling of fluid-pressure systems or apparatus not otherwise provided for
-
- 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
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/20—Hydro energy
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- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Fluid-Pressure Circuits (AREA)
Abstract
The application relates to the technical field of wind tunnel hydraulic control, and discloses a hydraulic servo adjusting device of a large negative load mechanism and a control method thereof, wherein the device comprises the following components: the control method comprises the following steps of: closing the two throttle valves; opening a servo proportional valve to drive the oil cylinder to move downwards; opening a throttle valve, and regulating the pressure of two cavities of the oil cylinder through a pressure reducing valve and an overflow valve; the servo proportional valve is used for controlling the motion of the oil cylinder in a closed loop manner. The application solves the problems that the upper cavity of the oil cylinder is sucked empty or the lower cavity of the oil cylinder exceeds the working pressure and the like in the hydraulic system of the large negative load mechanism due to mismatching of the area ratio of the opening of the servo proportional valve and the oil cylinder, and realizes the stable operation of the large negative load mechanism driven by the oil cylinder.
Description
Technical Field
The application relates to the technical field of wind tunnel hydraulic control, in particular to a hydraulic servo adjusting device of a large-load mechanism and a control method thereof.
Background
The technical field of wind tunnel hydraulic control is commonly used for driving a load mechanism by a hydraulic system, wherein the load mechanism is called positive load when an oil cylinder rod stretches out to provide thrust, and the load mechanism is called negative load (called negative load for short) when the oil cylinder rod stretches out to provide tension. The large load mechanism refers to a driving mechanism with a load of tens of tons or even hundreds of tons, when the driving mechanism moves up and down, the oil cylinder rod always provides a pulling force under the action of gravity, and the large load mechanism under the working condition is called as the large load mechanism.
In the prior art, a hydraulic servo system of a large-load mechanism generally adopts a servo proportional valve to directly control two cavities of an oil cylinder or only control the lower cavity of the oil cylinder to realize the displacement or speed control of the oil cylinder. The servo proportional valve is adopted to directly control the two cavities of the oil cylinder, and the problem that the upper cavity of the oil cylinder is empty or the lower cavity of the oil cylinder is overpressurized often exists because the area ratio of the opening of the servo proportional valve to the oil cylinder is not matched; the servo proportional valve is adopted to directly control the lower cavity of the oil cylinder, so that the response of the system is reduced, and the adjusting speed is slowed down.
Disclosure of Invention
Therefore, in order to solve the above-mentioned shortcomings, the present application provides a hydraulic servo-regulator of a large negative load mechanism and a control method thereof; according to the application, the pressure of the upper cavity of the oil cylinder is stabilized by adding the decompression oil supplementing loop and the overpressure overflow loop in the upper cavity of the oil cylinder, so that the stable operation and the rapid adjustment of the hydraulic servo system of the oil cylinder are controlled by the servo proportional valve.
Specifically, the hydraulic servo adjusting device of the large negative load mechanism comprises an oil cylinder, wherein the oil cylinder is connected with a decompression oil supplementing loop and an overpressure overflow loop;
the oil cylinder is also connected with a servo proportional valve, an upper cavity and a lower cavity of the oil cylinder are respectively connected with the servo proportional valve through an upper cavity branch and a lower cavity branch, and the servo proportional valve is connected with an oil supply branch and an oil return branch; the upper cavity of the oil cylinder is provided with an upper cavity pressure sensor, and the lower cavity of the oil cylinder is provided with a lower cavity pressure sensor;
one end of the decompression oil supplementing loop is communicated with the upper cavity branch, and the other end of the decompression oil supplementing loop is communicated with the oil supplying branch;
and one end of the overpressure overflow loop is communicated with the upper cavity branch, and the other end of the overpressure overflow loop is communicated with the oil return branch.
Optionally, the pressure reducing and oil supplementing loop comprises a first throttle valve and a pressure reducing valve, wherein the pressure reducing valve is close to the upper cavity of the oil cylinder and is connected with the first throttle valve in series, and meanwhile, the pressure reducing valve is also connected with the overpressure overflow loop.
Optionally, the overpressure relief circuit comprises a second throttle valve and a relief valve, wherein the relief valve is close to an upper cavity of the oil cylinder and is connected in series with the relief valve.
The hydraulic servo system is characterized in that the pressure of the upper cavity of the oil cylinder is stabilized by adding the decompression oil supplementing loop and the overpressure overflow loop in the upper cavity of the oil cylinder, so that the stable operation and the rapid adjustment of the hydraulic servo system of the oil cylinder are controlled by the servo proportional valve.
On the other hand, the application also provides a control method of the hydraulic servo regulating device of the large negative load mechanism, which comprises the following steps:
s01, closing a decompression oil supplementing loop and an overpressure overflow loop;
s02, controlling a telescopic rod of a driving oil cylinder to move downwards, monitoring values of an upper cavity pressure sensor and a lower cavity pressure sensor of the oil cylinder, and if the values of the upper cavity pressure sensor of the oil cylinder are smaller than a first threshold value, entering a step S03; if the value of the lower cavity pressure sensor of the oil cylinder is larger than the rated working pressure of the oil cylinder, the step S04 is carried out, and optionally, the first threshold value is 1.0MPa.
S03, opening a decompression oil supplementing loop, adjusting the pressure of the upper cavity to a threshold range, and adjusting the pressure of the lower cavity to enable the pressure of the lower cavity to be 2.0 MPa-5.0 MPa, preferably 2.0MPa, lower than the rated working pressure of the oil cylinder. Preferably, the threshold value ranges from 1.0MPa to 5.0MPa.
S04, opening an overpressure overflow loop, regulating the pressure of the upper cavity to a threshold range, and regulating the pressure of the lower cavity to be lower than the rated working pressure of the cylinder so that the pressure of the lower cavity is 2.0-5.0 MPa, preferably 2.0MPa, lower than the rated working pressure of the cylinder.
S05, driving a telescopic rod of the oil cylinder to move upwards, and if the upper cavity pressure value is smaller than a first threshold value, entering a step S03; if the pressure value of the lower cavity of the oil cylinder is larger than the rated working pressure of the oil cylinder, entering step S04;
and S06, according to the steps S02 to S05, the pressure adjustment of the upper cavity and the lower cavity of the oil cylinder is completed.
S07, after the step S06 is completed, the hydraulic circuit formed by the servo proportional valve and the oil cylinder is put into closed-loop control, and the adjustment of hydraulic servo control parameters is completed.
The method can solve the problems of suction of the upper cavity of the oil cylinder and overpressure of the lower cavity of the oil cylinder in the hydraulic servo control system of the large-load mechanism.
The application has the following advantages:
according to the application, the pressure of the upper cavity of the oil cylinder is controlled by arranging the pressure reducing valve and the overflow valve in the hydraulic servo control system of the large negative load mechanism, so that the problems that the upper cavity of the oil cylinder is sucked or the lower cavity of the oil cylinder exceeds the working pressure and the like caused by mismatching of the area ratio of the opening of the servo proportional valve and the oil cylinder in the hydraulic system of the large negative load mechanism are solved, and the stable operation of the large negative load mechanism driven by the oil cylinder is realized.
Meanwhile, the application has good operability: the control purpose, the control object, the control method or the judgment basis is clear and easy to execute.
The application has wide application range: the hydraulic servo control system can simultaneously solve the problems of suction of the upper cavity of the oil cylinder and overpressure of the lower cavity of the oil cylinder in the hydraulic servo control system of the large-load mechanism.
Drawings
FIG. 1 is a schematic diagram of the system configuration of the hydraulic servo-regulator of the heavy load mechanism according to the present application.
In the figure: 1. a first throttle valve; 2. a pressure reducing valve; 3. a second throttle valve; 4. an overflow valve; 5. an upper cavity pressure sensor; 6. a lower cavity pressure sensor; 7. an oil cylinder; 71. an upper chamber; 72. a lower cavity; 73. a telescopic rod; 8. a servo proportional valve; 100. an upper cavity branch; 200. a lower chamber branch; 300. an oil return branch; 400. an oil supply branch; 500. an overpressure overflow loop; 600. and a decompression oil supplementing loop.
Detailed Description
Embodiments of the present application are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative and intended to explain the present application and should not be construed as limiting the application.
In this document, relational terms such as first and second, and the like may be used solely to distinguish one entity or action from another entity or action without necessarily requiring or implying any actual such relationship or order between such entities or actions. Moreover, the terms "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus.
As described above in the background, in the prior art, a hydraulic servo system of a large negative load mechanism generally adopts a servo proportional valve to directly control two cavities of an oil cylinder or only control a lower cavity of the oil cylinder to realize displacement or speed control of the oil cylinder. The servo proportional valve is adopted to directly control the two cavities of the oil cylinder, and the problem that the upper cavity of the oil cylinder is empty or the lower cavity of the oil cylinder is overpressurized often exists because the area ratio of the opening of the servo proportional valve to the oil cylinder is not matched; the servo proportional valve is adopted to directly control the lower cavity of the oil cylinder, so that the response of the system is reduced, and the adjusting speed is slowed down.
Based on the problems, the application provides a hydraulic servo regulating device of a large negative load mechanism and a control method thereof; according to the application, the pressure of the upper cavity of the oil cylinder is stabilized by adding the decompression oil supplementing loop and the overpressure overflow loop in the upper cavity of the oil cylinder, so that the stable operation and the rapid adjustment of the hydraulic servo system of the oil cylinder are controlled by the servo proportional valve.
In one embodiment, the application provides a hydraulic servo adjusting device of a large negative load mechanism, as shown in fig. 1, wherein the large negative load mechanism comprises an oil cylinder 7, and the oil cylinder is connected with a decompression oil supplementing circuit 600 and an overpressure overflow circuit 500;
the oil cylinder 7 is also connected with a servo proportional valve 8, an upper cavity 71 and a lower cavity 72 of the oil cylinder 7 are respectively connected with the servo proportional valve 8 through an upper cavity branch 100 and a lower cavity branch 200, and the servo proportional valve 8 is connected with an oil supply branch 400 and an oil return branch 300; wherein an upper cavity 71 of the oil cylinder 7 is provided with an upper cavity pressure sensor 5, and a lower cavity 72 of the oil cylinder 7 is provided with a lower cavity pressure sensor 6;
one end of the pressure-reducing and oil-supplementing circuit 600 is communicated with the upper cavity branch 100, and the other end is communicated with the oil supply branch 400;
the overpressure overflow circuit 500 has one end communicated with the upper chamber branch 100 and the other end communicated with the oil return branch 300.
Further, the pressure reducing and oil supplementing circuit 600 includes a first throttle valve 1 and a pressure reducing valve 2, wherein the pressure reducing valve 2 is close to the upper chamber 71 of the cylinder, and is connected in series with the first throttle valve 1, and the pressure reducing valve 2 is also connected with the overpressure and overflow circuit 500.
Further, the overpressure relief circuit 500 includes a second throttle valve 3 and a relief valve 4, and the relief valve 4 is adjacent to the upper chamber 71 side of the cylinder and is connected in series with the relief valve 4.
The key of the technical scheme is that the pressure of the upper cavity of the oil cylinder is stabilized by adding a decompression oil supplementing loop and an overpressure overflow loop in the upper cavity of the oil cylinder, so that the stable operation and the rapid adjustment of a hydraulic servo system of the oil cylinder are controlled by a servo proportional valve.
In one embodiment, the present application provides a control method of a hydraulic servo adjusting device of a large negative load mechanism, comprising:
s01, closing a decompression oil supplementing loop and an overpressure overflow loop;
illustratively, the first throttle valve and the second throttle valve are closed.
S02, controlling a telescopic rod 73 of the driving oil cylinder to move downwards, monitoring values of an upper cavity pressure sensor and a lower cavity pressure sensor of the oil cylinder, and if the values of the upper cavity pressure sensor of the oil cylinder are smaller than a first threshold value, entering a step S03; if the value of the lower cavity pressure sensor of the oil cylinder is larger than the rated working pressure of the oil cylinder, entering step S04;
illustratively, a servo proportional valve is opened, and a telescopic rod of the oil cylinder is driven to move downwards; monitoring values of an upper cavity pressure sensor and a lower cavity pressure sensor of the oil cylinder, and if the values of the upper cavity pressure sensor of the oil cylinder are smaller than 1.0MPa (namely the first threshold value), entering step S03; if the value of the lower cavity pressure sensor of the oil cylinder is larger than the rated working pressure (generally 21 MPa) of the oil cylinder, the step S04 is carried out.
S03, opening a decompression oil supplementing loop, adjusting the pressure of the upper cavity to a threshold range, and adjusting the pressure of the lower cavity to be lower than the rated working pressure of the oil cylinder, so that the pressure of the lower cavity is 2.0-5.0 MPa, preferably 2.0MPa, lower than the rated working pressure of the oil cylinder.
The first throttle valve is opened, the pressure reducing valve is slowly adjusted to enable the value of the upper cavity pressure sensor of the oil cylinder to rise, and meanwhile the value rising condition of the lower cavity pressure sensor of the oil cylinder is observed, wherein the upper cavity pressure adjusting range (namely the threshold range) of the oil cylinder is 1.0-5.0 MPa.
S04, opening an overpressure overflow loop, reducing the pressure of the upper cavity to a threshold range, and adjusting the pressure of the lower cavity to be lower than the rated working pressure of the oil cylinder, so that the pressure of the lower cavity is 2.0-5.0 MPa, preferably 2.0MPa, lower than the rated working pressure of the oil cylinder;
the second throttle valve is opened, the pressure reducing valve is slowly adjusted to enable the value of the upper cavity pressure sensor of the oil cylinder to be reduced, and meanwhile the condition of the reduction of the value of the lower cavity pressure sensor of the oil cylinder is observed, wherein the upper cavity pressure adjusting range (namely the threshold range) of the oil cylinder is 1.0-5.0 MPa.
S05, driving a telescopic rod of the oil cylinder to move upwards, and if the upper cavity pressure value is smaller than a first threshold value, entering a step S03; if the pressure value of the lower cavity of the oil cylinder is larger than the rated working pressure of the oil cylinder, entering step S04;
illustratively, opening a servo proportional valve to drive a telescopic rod of an oil cylinder to move upwards; monitoring the values of an upper cavity pressure sensor and a lower cavity pressure sensor of the oil cylinder, and if the values of the upper cavity pressure sensor are smaller than 1.0MPa, entering a step S03; if the value of the pressure sensor of the lower cavity of the oil cylinder is larger than the rated working pressure (generally 21 MPa) of the oil cylinder, the step S04 is carried out.
And S06, according to the steps S02 to S05, the pressure adjustment of the upper cavity and the lower cavity of the oil cylinder is completed.
And S07, putting the hydraulic circuit formed by the servo proportional valve and the oil cylinder into closed-loop control (such as PID control) after the step S06 is completed, and completing the adjustment of hydraulic servo control parameters.
According to the application, the pressure of the upper cavity of the oil cylinder is controlled by the pressure reducing valve and the overflow valve, so that the problems that the upper cavity of the oil cylinder is sucked up or the lower cavity of the oil cylinder exceeds the working pressure and the like caused by mismatching of the area ratio of the opening of the servo proportional valve and the oil cylinder are solved, the oil cylinder drives the large negative load mechanism to stably operate, the problems that the upper cavity of the oil cylinder is sucked up or the lower cavity of the oil cylinder exceeds the working pressure caused by mismatching of the area ratio of the opening of the servo proportional valve and the oil cylinder in the hydraulic system of the large negative load mechanism are solved, and the stable operation of the oil cylinder drives the large negative load mechanism is realized.
Meanwhile, the application has good operability, definite control purpose, control object, control method or judgment basis and easy execution; the application has wide application range and can simultaneously solve the problems of suction of the upper cavity of the oil cylinder and overpressure of the lower cavity of the oil cylinder in the hydraulic servo control system of the large-load mechanism.
The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the application. Thus, the present application is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (6)
1. The control method of the hydraulic servo regulating device of the large negative load mechanism is characterized in that the large negative load mechanism comprises an oil cylinder, the hydraulic servo regulating device comprises a decompression oil supplementing loop and an overpressure overflow loop, and the oil cylinder is connected with the decompression oil supplementing loop and the overpressure overflow loop; the oil cylinder is connected with a servo proportional valve, an upper cavity and a lower cavity of the oil cylinder are respectively connected with the servo proportional valve through an upper cavity branch and a lower cavity branch, and the servo proportional valve is connected with an oil supply branch and an oil return branch; the upper cavity of the oil cylinder is provided with an upper cavity pressure sensor, and the lower cavity of the oil cylinder is provided with a lower cavity pressure sensor; one end of the decompression oil supplementing loop is communicated with the upper cavity branch, and the other end of the decompression oil supplementing loop is communicated with the oil supplying branch; one end of the overpressure overflow loop is communicated with the upper cavity branch, and the other end of the overpressure overflow loop is communicated with the oil return branch;
the control method comprises the following steps:
s01, closing a decompression oil supplementing loop and an overpressure overflow loop;
s02, controlling a telescopic rod of a driving oil cylinder to move downwards, monitoring values of an upper cavity pressure sensor and a lower cavity pressure sensor of the oil cylinder, and if the values of the upper cavity pressure sensor of the oil cylinder are smaller than a first threshold value, entering a step S03; if the value of the lower cavity pressure sensor of the oil cylinder is larger than the rated working pressure of the oil cylinder, entering step S04;
s03, opening a decompression oil supplementing loop, adjusting the pressure of the upper cavity to a threshold range, and adjusting the pressure of the lower cavity to enable the pressure of the lower cavity to be lower than the rated working pressure of the oil cylinder;
s04, opening an overpressure overflow loop, reducing the pressure of the upper cavity to a threshold range, and adjusting the pressure of the lower cavity to enable the pressure of the lower cavity to be lower than the rated working pressure of the oil cylinder;
s05, driving a telescopic rod of the oil cylinder to move upwards, and if the upper cavity pressure value is smaller than a first threshold value, entering a step S03; if the pressure value of the lower cavity of the oil cylinder is larger than the rated working pressure of the oil cylinder, entering step S04;
s06, installing the steps S02 to S05 to finish the pressure adjustment of the upper cavity and the lower cavity of the oil cylinder;
s07, after the step S06 is completed, the hydraulic circuit formed by the servo proportional valve and the oil cylinder is put into closed-loop control, and the adjustment of hydraulic servo control parameters is completed.
2. The control method of the hydraulic servo-regulator of the large negative load mechanism according to claim 1, characterized in that: the pressure reducing and oil supplementing loop comprises a first throttle valve and a pressure reducing valve, wherein the pressure reducing valve is close to an upper cavity of the oil cylinder and is connected with the first throttle valve in series, and meanwhile, the pressure reducing valve is also connected with the overpressure overflow loop.
3. The control method of the hydraulic servo-regulator of the large negative load mechanism according to claim 1, characterized in that: the overpressure overflow loop comprises a second throttle valve and an overflow valve, wherein the overflow valve is close to an upper cavity of the oil cylinder and is connected with the second throttle valve in series.
4. The control method of a large negative load mechanism hydraulic servo-regulator according to claim 1, wherein the first threshold value is 1.0MPa.
5. The control method of a hydraulic servo-regulator of a large negative load mechanism according to claim 1, wherein the threshold value range is 1.0MPa to 5.0MPa.
6. The control method of a hydraulic servo adjusting device of a large negative load mechanism according to claim 1, wherein the lower cavity pressure of the cylinder in step S03 and step S04 is 2.0MPa to 5.0MPa lower than the rated operating pressure of the cylinder.
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| CN202310836726.8A CN116557371B (en) | 2023-07-10 | 2023-07-10 | Hydraulic servo adjusting device of large-load mechanism and control method thereof |
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| CN202310836726.8A CN116557371B (en) | 2023-07-10 | 2023-07-10 | Hydraulic servo adjusting device of large-load mechanism and control method thereof |
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| CN116557371B true CN116557371B (en) | 2023-09-01 |
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