A multi-path hydraulic energy rapid release workstation with high and low pressure switching and a control method

Abstract

A multi-channel hydraulic energy rapid release workstation and control method with high / low pressure switching is disclosed, relating to the field of hydraulic control technology. It includes: an input valve block assembly, where pressurized oil, after being filtered by a filter within the input valve block assembly, enters the inlet accumulator assembly via a bypass to stabilize system pressure and absorb hydraulic shocks; another path serves as the main oil supply, entering the corresponding servo valve drive module; the inlet accumulator assembly is connected to the main oil circuit of the input valve block assembly via pipelines, and contains multiple inlet accumulators to absorb shocks during system pressure fluctuations, ensuring stable oil supply. This workstation solves the problems of large shocks, slow response, insufficient safety, and poor adaptability in traditional hydraulic systems through structural design and control logic, achieving integrated soft start, soft stop, rapid unloading, and multi-channel independent control, fully meeting the comprehensive requirements of high-precision hydraulic testing equipment for stability, safety, efficiency, and flexibility.

Description

Technical Field

[0001] This invention relates to the field of hydraulic control technology, and more particularly to a multi-channel hydraulic energy rapid release workstation with high and low pressure switching and a control method thereof. Background Technology

[0002] In servo valve-controlled hydraulic testing equipment, the hydraulic system serves as the power core, and its operational stability directly determines the testing accuracy, equipment lifespan, and sample safety. The core working logic of this type of testing equipment is as follows: by precisely controlling the flow and pressure of hydraulic oil through servo valves, the actuators such as cylinders are driven to complete preset test actions such as reciprocating motion, load simulation, and attitude adjustment. The precise displacement of the servo valve core and the stable output of hydraulic oil are the key prerequisites for ensuring the accuracy of the actuator's actions.

[0003] Currently, existing hydraulic workstations adapted to multiple actuators mostly adopt a single pressure circuit or a simple high-low pressure switching structure, which makes it difficult to simultaneously meet the dual requirements of "coordinated action of multiple actuators" and "high-precision and stable operation." In practical applications, this has revealed many technical defects, which can no longer meet the requirements of high-end testing equipment. Specifically, this is reflected in the following three aspects: Firstly, the problem of cascading precision failures and equipment damage caused by hydraulic shock is prominent.

[0004] Existing multi-channel hydraulic workstations typically achieve high-low pressure switching via conventional directional valves. During switching, sudden pressure changes in the hydraulic circuit cannot be effectively buffered, easily leading to hydraulic shocks. These shocks directly impact the servo valve, forcing the valve core to deviate from its preset position, resulting in decreased valve core positioning accuracy. This inaccurate valve core positioning further causes fluctuations in hydraulic oil flow output, causing cylinders and other actuators to operate erratically, resulting in jerky movements and additional mechanical shock forces. These shocks not only cause fatigue damage to the cylinder body and connecting parts of the testing equipment but also directly affect the test specimen, causing deformation and cracking, severely impacting the validity of test results and even rendering expensive specimens unusable, significantly increasing testing costs.

[0005] Secondly, the piston rod wear problem caused by hydrostatic support blockage is difficult to avoid.

[0006] Servo valve-controlled test equipment cylinders generally employ hydrostatic support structures, which achieve frictionless support for the piston rod through a high-pressure oil film. This is a core component ensuring the high-precision movement of the actuator. Existing hydraulic workstations lack dedicated protection and adaptation designs for hydrostatic supports. Impurities and contaminants in the hydraulic circuit can easily enter the micro-cavities and passages of the hydrostatic support along with the hydraulic oil, causing blockages in the support structure. Once the hydrostatic support is blocked, the oil film support function fails, and direct mechanical contact occurs between the piston rod and the cylinder body. This results in severe friction and wear during operation, leading not only to a sharp decrease in cylinder movement accuracy but also to piston rod scratches, cylinder body wear and leakage, ultimately causing downtime of the entire test equipment. Furthermore, the repair costs and time required for such wear failures are high, severely impacting the continuity of testing operations.

[0007] Third, the existing structure cannot adapt to the differentiated action requirements of multiple actuators.

[0008] High-end testing equipment often requires multiple actuators to complete complex actions synchronously, sequentially, or independently, with significant differences in the pressure and flow requirements of different actuators. Existing hydraulic workstations typically employ a simple parallel layout for multiple outputs, with low integration of high / low pressure switching and energy release structures. This results in an inability to achieve independent and precise control of pressure and flow for each actuator, and a lack of effective means to quickly release residual energy in the hydraulic circuit. When an actuator completes its action or undergoes an emergency shutdown, the residual pressure in the circuit cannot be released quickly. This not only hinders the response of other actuators but also exacerbates the risks of hydraulic shock and hydrostatic support blockage, leading to a significant reduction in the operational stability and collaborative working capability of the entire hydraulic system.

[0009] In summary, existing multi-channel hydraulic workstations used for servo valve control actuators fail to systematically address the core technical challenges of "hydraulic shock suppression, hydrostatic support protection, and differentiated adaptation to multiple actuators," resulting in poor operational stability, high equipment failure rates, and low testing safety. Therefore, developing a multi-channel hydraulic workstation capable of smooth high-low pressure switching, rapid hydraulic energy release, and adaptation to the coordinated operation requirements of multiple actuators, while resolving accuracy failures caused by hydraulic shocks and avoiding equipment wear due to hydrostatic support blockage, has become a pressing technical challenge in this field. Summary of the Invention

[0010] To address the above problems, this invention provides a multi-channel hydraulic workstation capable of smooth high-low pressure switching, rapid release of hydraulic energy, and adaptability to the collaborative operation requirements of multiple actuators. It also solves the accuracy failure problem caused by hydraulic shock and avoids equipment wear caused by hydrostatic support blockage. This invention is a multi-channel hydraulic energy rapid release workstation and control method with high-low pressure switching.

[0011] The technical solution of this invention is: A multi-channel hydraulic energy rapid release workstation with high / low pressure switching includes: The pressure oil is filtered by the filter inside the input valve block assembly. One path goes through the bypass to the oil accumulator assembly to stabilize the system pressure and absorb hydraulic shocks; the other path serves as the main oil supply and enters the corresponding servo valve drive module. The oil inlet accumulator assembly is connected to the main oil circuit of the input valve block assembly through a pipeline. It contains multiple oil inlet accumulators to absorb shocks when the system pressure fluctuates, ensuring stable oil supply. The servo valve drive module has multiple components, including a control valve block assembly and an output valve block assembly. The control valve block assembly includes a third throttling damper, a two-position three-way valve, a slow accumulator, an adjustable flow valve, a two-position two-way valve, a third check valve, and a control valve block. The inlet of the third throttling damper is connected to the oil inlet P of the control valve block assembly, and the outlet is connected to the first working port of the two-position three-way valve; the second working port of the two-position three-way valve is connected to the oil inlet of the two-position two-way valve after being connected in series with the slow accumulator and the adjustable flow valve; the return port of the two-position three-way valve is connected to the return port of the control valve block assembly; the outlet of the two-position two-way valve is connected to the inlet of the third check valve, and the outlet of the third check valve is connected to the return port of the control valve block assembly; The output valve block assembly includes: The output valve block body is equipped with an oil inlet, a working oil inlet, an oil return inlet, and a control oil inlet; The output valve core is slidably installed in the valve hole of the valve block body; a feedback hole is axially opened in the middle, one end of which is connected to the working oil port and the other end is connected to the spring mounting hole, which is used to introduce the output pressure of the working oil port into the spring mounting hole at the top of the output valve core to form hydraulic pressure feedback. The output reset spring is fitted into the spring mounting hole of the output valve block body, and its two ends abut against the top of the output valve block body and the top of the output valve core, respectively. The output check valve connects the working port and the return port when the valve core is not working, and the flow direction is from the working port to the return port; it does not connect when the valve core rises. The oil pressure enters the workstation from the input valve block assembly. After being split, part of it enters the oil accumulator assembly for energy storage and pressure buffering, while the other part serves as the main oil circuit, entering multiple identical servo valve drive modules. Each servo valve drive module includes a control valve block group and an output valve block group, which ultimately delivers the pressure oil to the external servo valves and cylinders, realizing multi-channel independent hydraulic control.

[0012] Specifically, the input valve block assembly includes: The oil inlet buffer protection zone is located at the input port of the oil source pressure oil P and includes a first throttling damper and a first check valve. The first throttling damper is connected in series with the main oil inlet channel to buffer the pressure change when the oil source stops. The first check valve is connected in parallel with the first throttling damper.

[0013] The main high-pressure filtration zone includes the main filter, whose inlet is connected to the outlet of the throttling damper, and whose outlet is connected to the hydrostatic support dedicated oil supply zone and the system oil supply zone, respectively. The dedicated oil supply area for the hydrostatic support is branched off from the outlet side of the main filter and includes a hydrostatic oil circuit filter and a pilot port accumulator. The pilot port accumulator is connected to the outlet side of the hydrostatic oil circuit filter and is used to absorb oil circuit pressure fluctuations and stabilize the oil supply pressure and flow of the hydrostatic support.

[0014] The system's oil supply zone is used to provide power to the subsequent servo valves.

[0015] Specifically, the main filter is equipped with a differential pressure transmitter, which will indicate and alarm when the filter element becomes clogged.

[0016] Specifically, the main filter has a nominal filtration accuracy of 25µm, effectively intercepting solid contaminant particles with a diameter of not less than 25µm in the oil. Specifically, the static pressure oil filter has a nominal filtration accuracy of 3µm, effectively intercepting solid contaminant particles with a diameter of not less than 3 micrometers in the oil.

[0017] Specifically, the two-position three-way valve is a solenoid directional valve.

[0018] Specifically, the two-position two-way valve is a normally closed solenoid directional valve that works in conjunction with the two-position three-way valve to achieve gradual increase, gradual decrease, and emergency unloading control of the servo valve's oil supply pressure.

[0019] Specifically, this also includes oil return accumulator components; The return oil accumulator assembly is connected to the return oil interface of each output valve block group and is also connected to the oil tank to absorb hydraulic shock during the return oil process and stabilize the return oil pressure.

[0020] A control method for a multi-channel hydraulic energy rapid release workstation with high / low pressure switching includes the following steps: Step 1, Fuel Supply Phase Oil pressure oil enters the workstation through the input valve block assembly. After filtration, it is divided into two paths: the bypass oil enters the oil accumulator assembly for energy storage and pressure buffering; the main oil supply enters the corresponding control valve block assembly and is delivered to the output valve block assembly after being regulated by the pressure valve and flow valve. Step Two, Execution Phase The pressure oil from the output valve block assembly enters the P port of the external servo valve through the output port; the servo valve operates according to the control signal, adjusting the flow and direction of the oil entering the cylinder, and driving the cylinder to complete the corresponding action; Step 3, Oil Return Stage The return oil from the cylinder is discharged through the T port of the servo valve, returns to the return oil interface of the output valve block assembly through the pipeline, and then flows back to the oil tank after being buffered by the return oil accumulator assembly, completing one hydraulic cycle. The gradual pressure control process of the control valve block assembly includes a gradual pressure increase during the start-up phase and a gradual pressure decrease during the stop phase, specifically as follows: (1) Start-up phase: Pressure gradually increases When the system starts, the two-position three-way valve is energized, and the two-position two-way valve is de-energized; Pressure oil is input from the oil inlet P. After being buffered and slowed down by the third throttling damper, it enters the two-position three-way valve for reversal and diversion, forming two branches. One branch directly enters the control port of the control valve block as the main control pressure for the servo valve oil supply; the other branch is throttled by the adjustable flow valve and then returns to the oil tank through the two-position two-way valve, so that the control port of the control valve block is in a low-pressure output state. When the two-position three-way valve and the two-position two-way valve are energized at the same time, the two-position two-way valve closes, blocking the return oil path, so that the control port pressure of the control valve block tends to be consistent with the input pressure P; at the same time, the slow accumulator is connected to the control oil circuit, and through its buffering effect, the control port pressure slowly rises from low pressure to high pressure, realizing a gradual pressure increase. (2) Stopping phase: Pressure gradually decreases When the system stops, by controlling the on / off sequence of the two-position three-way valve 32 and the two-position two-way valve, the pressure at the control port of the control valve block gradually decreases from high pressure to low pressure, and then transitions from low pressure to complete closure. The control process of the output valve block assembly includes an initial state without control pressure, a normal operating pressure balance output state, and an emergency stop rapid unloading state, specifically: (1) Initial state without controlled pressure When the control port pressure delivered by the control valve block assembly is zero, the preload of the output reset spring keeps the output valve core in the initial lower position, the oil circuit between the oil inlet and the working oil port is blocked, the working oil port and the return oil port remain connected, and the residual pressure oil on the working oil port side is released to the oil tank through the output check valve to achieve pressureless standby. (2) Pressure balance and output during normal operation Once the control port pressure is established, the pressurized oil acts on the bottom of the output valve core, generating a hydraulic pressure F1 in the direction of the output reset spring, where F1 = P⋅A; where P is the pressure at the control port and A is the effective pressure-bearing area at the bottom of the output valve core. When F1 overcomes the preload force F2 of the output reset spring, the output valve core moves toward the output reset spring, the oil inlet is connected to the working oil port, the passage between the working oil port B and the return oil port is cut off, and the pressure oil flows from the oil inlet to the working oil port, forming the output pressure P1. As the output pressure P1 is established, the pressure oil flows into the spring chamber at the end of the output valve core through the feedback hole in the middle of the output valve core, generating a downward hydraulic pressure F3=P1⋅A1, where A1 is the effective pressure-bearing area at the top of the output valve core. When the system reaches dynamic equilibrium, F1=F2+F3 is satisfied. (3) Rapid unloading during emergency stop When the emergency stop button is pressed in an emergency, the control port pressure is quickly released to zero, the hydraulic pressure F1 at the bottom of the output valve core disappears, and the elastic force of the output reset spring pushes the output valve core to move down quickly; the oil circuit between the oil inlet and the working oil port is immediately blocked, cutting off the supply of pressurized oil; the working oil port and the return oil port are reconnected, and the residual pressurized oil on the working oil port side is quickly released to the oil tank through the output check valve, achieving safe unloading.

[0021] Specifically, the input valve block assembly control method includes: S1.1 Oil Inlet and Backflow Buffer Protection Stage The pressurized oil output from the oil source first enters the first check valve and then the filter with an inner outer diameter. When the oil source stops, the reverse oil can slowly flow back through the parallel throttle valve to avoid impact damage to the filter.

[0022] S1.2 Main Road Primary High-Pressure Filtration Stage The pressurized oil enters the high-pressure main filter to complete the primary high-precision filtration of the system's oil supply, raising the oil cleanliness to the basic standard suitable for servo valves and hydrostatic support cylinders, laying the foundation for subsequent secondary filtration. S1.3 Static pressure support for dedicated secondary filtration and pressure stabilization stage A portion of the oil diverted from the outlet side of the high-pressure main filter enters the dedicated oil supply unit for the hydrostatic support: S1.31, the oil passes through the external inlet and internal outlet hydrostatic oil circuit filter to complete secondary fine filtration, completely intercepting micron-sized tiny impurities, preventing impurities from entering the tiny oil chambers and oil passages of the hydrostatic support, and avoiding blockage of the hydrostatic support from the root cause. S1.32, the finely filtered oil flows through the pilot port accumulator. The pilot port accumulator absorbs the pressure fluctuations of the main oil circuit and the flow fluctuations caused by the actions of multiple actuators in real time, so that the oil pressure and flow rate output to the hydrostatic support part remain constant, and a high-pressure oil film is stably formed, which effectively avoids abnormal wear between the piston rod and the hydrostatic support part due to unstable pressure. S1.4 System Voltage Stabilization and Multiplexing Stage Most of the oil filtered by the high-pressure main filter is delivered to the corresponding servo valve drive modules through independent oil distribution lines, providing stable and clean hydraulic power to each servo valve and cylinder actuator, and meeting the needs of multiple actuators of the test equipment to coordinate their actions.

[0023] This invention constructs a multi-channel hydraulic energy rapid release workstation with high and low pressure switching, consisting of an input valve block assembly, an oil inlet accumulator assembly, and a multi-channel independent servo valve drive module. The integrated structure and rational oil circuit layout simultaneously meet the high precision, high safety, and high stability requirements of multi-channel hydraulic testing. During system operation, pressurized oil is cleaned and filtered through a filter within the input valve block assembly. One path enters the oil inlet accumulator assembly for energy storage and pressure buffering, effectively absorbing system pressure fluctuations and reducing hydraulic shocks, providing a continuous and stable oil supply environment for the main oil circuit. The other path serves as the main oil supply, entering the multi-channel servo valve drive module. Pressure regulation and output control are achieved by the control valve block assembly and output valve block assembly, ultimately precisely delivering the pressurized oil to external servo valves and actuator cylinders, realizing multi-channel independent and non-interfering hydraulic drive and testing control.

[0024] In terms of pressure control, this workstation achieves progressive pressure regulation through a control valve block assembly. During startup, the pressure gradually increases from the closed state to a low pressure, then smoothly transitions to a high pressure. During shutdown, the pressure gradually decreases from high pressure to low pressure before completely shutting off, avoiding hydraulic shocks caused by sudden pressure increases and decreases, and effectively protecting precision components such as servo valves and sample workpieces from damage. The output valve block assembly adopts a valve core pressure feedback structure. The output pressure acts on the spring chamber through a feedback orifice in the middle of the valve core, creating a dynamic balance between the control pressure at the bottom of the valve core, the feedback pressure at the top, and the return spring force. This allows the output pressure to change smoothly and linearly with the input pressure, significantly improving pressure output accuracy and operational stability. Simultaneously, the system is equipped with an emergency rapid unloading function. In case of emergencies, the control port pressure can be quickly released, the valve core quickly resets under spring action, immediately cutting off the main oil supply circuit, and the residual pressure at the working port is quickly guided back to the oil tank through a check valve, achieving rapid energy release and significantly improving equipment operational safety.

[0025] Meanwhile, this design employs a parallel design of multi-channel servo valve drive modules, each of which can be independently controlled and supplied with oil. This supports simultaneous testing of multiple workpieces as well as sequential multi-step testing of a single workpiece, significantly improving testing efficiency and equipment utilization. The output valve block can be equipped with a high-flow valve core according to the operating conditions, adapting to the testing requirements of high-frequency response and rapid action of the hydraulic cylinder. It also reserves multiple interface types, compatible with different types of components such as servo valves and hydrostatic supports, possessing strong versatility and expandability. Furthermore, the system adopts a multi-stage high-precision filtration structure to effectively intercept oil impurities, preventing scratches or jamming of precision mating surfaces such as valve cores and valve holes, thus extending the equipment's service life.

[0026] In summary, this workstation solves the problems of large impact, slow response, insufficient safety, and poor adaptability of traditional hydraulic systems from the perspectives of structural design and control logic. It achieves integrated soft start, soft stop, rapid unloading, and multi-channel independent control, which can fully meet the comprehensive requirements of high-precision hydraulic testing equipment for stability, safety, efficiency, and flexibility. Attached Figure Description

[0027] Figure 1 This is a schematic diagram of the hydraulic workstation's internal structure; Figure 2 This is a top view of the hydraulic workstation. Figure 3 This is the hydraulic schematic diagram of the workstation; Figure 4 yes Figure 3 A magnified schematic diagram of one of the servo valve drive modules; Figure 5 This is the hydraulic schematic diagram of the input valve block assembly; Figure 6 This is a schematic diagram of the three-dimensional structure of the input valve block assembly; Figure 7 This is the main view of the control valve block assembly; Figure 8 yes Figure 7 Schematic diagram of the cross section in direction A; Figure 9 This is a side view of the control valve block assembly; Figure 10 This is a top view of the control valve block assembly; Figure 11 yes Figure 10 Schematic diagram of the section along the B-direction; Figure 12 This is the hydraulic schematic diagram of the control valve block assembly; Figure 13 This is a schematic diagram of the internal cross-sectional structure of the output valve block assembly; Figure 14 This is the schematic diagram of the output valve block assembly; In the diagram, 1 is the input valve block assembly, 11 is the first check valve, 12 is the differential pressure transmitter, 13 is the main line filter, 14 is the static pressure oil circuit filter, and 15 is the pilot port accumulator. 2 is the oil accumulator assembly. 3 is the control valve block assembly; 31 is the third throttling damper; 32 is a two-position three-way valve; 33 is a slow accumulator; 34 is an adjustable flow valve; 35 is a two-position two-way valve; 36 is the third check valve; 37 is the output pressure gauge; and 38 is the control valve block. 4 is the output valve block assembly, 41 is the output valve core, 42 is the output return spring, 43 is the output check valve, and 44 is the output valve block body. 5 is the oil return accumulator assembly, and 6 is the hydraulic cylinder. Detailed Implementation

[0028] Embodiments of the present invention are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and should not be construed as limiting the present invention.

[0029] In the description of this invention, it should be understood that the terms "upper," "lower," "left," "right," "vertical," "horizontal," etc., indicating orientation or positional relationships are based on the orientation or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the invention. In the description of this invention, unless otherwise stated, "a plurality of" means two or more.

[0030] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal communication between two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances.

[0031] The following is for reference. Figure 1-14 Description of embodiments according to the present invention; A multi-channel hydraulic energy rapid release workstation with high / low pressure switching includes: Input valve block assembly 1 serves as the main inlet of the workstation, used for filtering, stabilizing and diverting the oil source; after being filtered by the filter in the input valve block assembly 1, the pressurized oil enters the oil accumulator assembly 2 via a bypass to stabilize the system pressure and absorb hydraulic shock; the other path serves as the main oil supply and enters the corresponding servo valve drive module. The specific structure and working principle of the input valve block assembly 1 of the present invention will be described in detail below with reference to the accompanying drawings: This embodiment addresses the technical challenge of the hydrostatic support cylinder in the testing equipment having extremely high requirements for oil cleanliness and pressure stability. It integrates multi-stage filtration, a dedicated hydrostatic branch, and a pressure-stabilizing buffer structure into the input valve block assembly 1. The specific implementation method is as follows: Composition of the input valve block assembly: As shown in Figure 5-6, the input valve block assembly 1 is an integrated valve block structure, serving as the central hub for hydraulic oil processing and distribution in the entire multi-channel hydraulic workstation. Internally, it integrates various functional components through precision-machined oil circuits, specifically including an inlet buffer protection zone, a main high-pressure filtration zone, a dedicated oil supply zone for static pressure support, and a system overflow stabilization zone. The specific composition and connection relationships of each zone are as follows: Oil inlet and return buffer protection zone The pressurized oil output from the oil source first enters the first check valve 11 and then the filter with an inner outer diameter. When the oil source stops, the reverse oil can slowly flow back through the first damper connected in parallel to avoid impact damage to the filter.

[0032] Main road high-pressure filtration area This area is the core purification unit for the system's oil supply. The core component is a 25μm high-pressure main line filter 13. Its inlet is connected to the outlet of the throttling damper, and its outlet is connected to both the hydrostatic support dedicated oil supply area and the system overflow pressure stabilization area. The 25μm high-pressure main line filter 13 uses a replaceable filter element structure to intercept large particulate impurities in the hydraulic oil, completing the primary high-precision filtration of the oil. A differential pressure transmitter 12 is integrated on the main line filter. When the filter element becomes clogged, the differential pressure transmitter 12 provides an indication and alarm, facilitating timely maintenance and replacement of the filter element, ensuring stable and clean system oil supply.

[0033] Dedicated oil supply area for hydrostatic support This area is a dedicated branch designed to adapt to the hydrostatic support cylinder of the test equipment. It is branched off from the oil outlet side of the 25μm high-pressure main filter and includes a 3μm hydrostatic oil filter 14 and a pilot port accumulator 15 in sequence. Among them, the 3μm static pressure oil circuit filter 14 adopts an external inlet and internal outlet high pressure replaceable filter element structure to further intercept micron-level tiny impurities and ensure the cleanliness of the oil entering the static pressure support part; the pilot port accumulator 15 is connected to the oil outlet side of the 3μm static pressure oil circuit filter 14 to absorb oil circuit pressure fluctuations and stabilize the oil supply pressure and flow of the static pressure support.

[0034] The working principle of the input valve block assembly is as follows: Based on the above structure, the working process of the input valve block assembly 1 revolves around the core logic of "buffer protection, graded filtration, and static pressure-specific stabilization," precisely adapting to the usage requirements of the static pressure support cylinder. The specific working principle is as follows: Oil inlet buffer and backflow protection stage The pressurized oil P output from the oil source first enters the check valve. When the oil source stops, the reverse oil can slowly return through the first damper connected in parallel, avoiding hydraulic shock caused by sudden changes in flow rate and damage to subsequent filter elements; The system's oil supply zone is used to provide power to the subsequent servo valves.

[0035] Primary high-pressure filtration stage of the main road After being buffered and protected, the pressurized oil enters the 25μm high-pressure main filter 13 to complete the primary high-precision filtration of the system oil supply. This effectively intercepts large particulate contaminants such as metal shavings and rubber impurities in the hydraulic oil, raising the oil cleanliness to the basic standard suitable for servo valves and hydrostatic support cylinders, thus laying the foundation for subsequent secondary filtration.

[0036] Static pressure supports dedicated secondary filtration and pressure stabilization stages A portion of the oil diverted from the outlet side of the 25μm high-pressure main filter enters the dedicated oil supply unit for the hydrostatic support: The first step is that the oil passes through the 3μm external inlet and internal outlet hydrostatic oil circuit filter 14 to complete secondary fine filtration, completely intercepting micron-sized tiny impurities and preventing impurities from entering the tiny oil chambers and oil passages of the hydrostatic support, thus avoiding blockage of the hydrostatic support from the source. The second step involves the finely filtered oil flowing through the pilot accumulator 15. The pilot accumulator 15 absorbs pressure fluctuations in the main oil circuit and flow fluctuations caused by the actions of multiple actuators in real time, keeping the oil pressure and flow rate output to the hydrostatic support constant and forming a stable high-pressure oil film. This effectively prevents abnormal wear between the piston rod and the hydrostatic support due to unstable pressure, ensuring the motion accuracy and service life of the hydrostatic support cylinder.

[0037] System voltage regulation and multiplexing stage Most of the oil filtered by the 25μm high-pressure main filter 13 is delivered to the four servo valve drive modules through four independent oil distribution lines, providing stable and clean hydraulic power to each servo valve and cylinder actuator, and meeting the needs of the test equipment for coordinated operation of multiple actuators.

[0038] In summary, the input valve block assembly 1 of the present invention, through its integrated hierarchical filtration structure, dedicated static pressure stabilization design, and backflow protection mechanism, not only solves the problems of insufficient oil cleanliness and large pressure fluctuations in traditional hydraulic workstations, leading to static pressure support blockage and wear, but also achieves stable oil supply to multiple actuators, perfectly meeting the usage requirements of high-precision testing equipment.

[0039] The oil inlet accumulator assembly 2 is connected to the main oil circuit of the input valve block assembly 1 through a pipeline, and integrates multiple oil inlet accumulators inside. Its main functions are: to absorb shocks when the system pressure fluctuates, to supplement instantaneous flow when multiple working groups operate simultaneously, to ensure stable oil supply, and to avoid insufficient oil supply and sudden pressure drop caused by simultaneous operation of multiple working groups, thereby improving the control accuracy of the servo valve.

[0040] To ensure the safety, stability, and control accuracy of servo valve operation, and to prevent impact damage to the servo valve core and seals caused by sudden pressure rises and falls, while also enabling rapid and safe shutdown in case of emergencies, hydraulic testing equipment must meet the following two core technical requirements: For servo valve oil supply control, the pressure needs to be gradually increased during the start-up phase, that is, the oil supply gradually switches from the closed state to the low-pressure supply state, and then steadily rises to the set high-pressure state; during the shutdown phase, the pressure needs to be gradually decreased, that is, the oil pressure steadily drops from the set high-pressure state to the low-pressure state, and then the oil supply is shut off, so as to avoid damage to the servo valve caused by sudden pressure changes throughout the process.

[0041] If an emergency occurs during automatic operation of the equipment, the system must respond quickly after the operator presses the emergency stop button. It must immediately cut off the pressure oil supply to the servo valve and simultaneously connect the residual pressure oil that has been output to the servo valve to the return oil line to achieve rapid pressure relief and ensure the safety of the equipment, servo valve and operator.

[0042] To meet the above two core technical requirements, this case specifically designed a control valve block assembly 3 (corresponding to the attached...) Figure 7-11 Control valve block assembly, accessories Figure 12 Hydraulic schematic diagram of control valve block assembly and output valve block assembly 4 (corresponding attached) Figure 13-14 Output valve block assembly (hydraulic schematic diagram of output valve block assembly). Through the coordinated operation of the two components, the gradual pressure regulation of the servo valve oil supply and the rapid unloading and oil cut-off control in case of emergencies are accurately realized, which is fully adapted to the safe operation of hydraulic testing equipment and the high-precision use requirements of servo valve.

[0043] The servo valve drive module has multiple components, including control valve block assembly 3 and output valve block assembly 4; The control valve block assembly 3 is an integrated valve block structure, including a third throttling damper, a two-position three-way valve 32, a slow accumulator 33, an adjustable flow valve 34, a two-position two-way valve 35, a third check valve 36, an output pressure gauge 37, and a control valve block 38. Each component forms a pressure progressive regulation and unloading circuit through the internal oil passages of the valve block. The specific connection relationship is as follows: The inlet of the third throttling damper is connected to the oil inlet P of the control valve block assembly 3, and the outlet is connected to the first working port (port 3) of the two-position three-way valve 32. The second working port (port 2) of the two-position three-way valve 32 is connected to the oil inlet (port 2) of the two-position two-way valve 35 after being connected in series with the slow accumulator 33 and the adjustable flow valve 34. The return port (port 1) of the two-position three-way valve 32 is directly connected to the return port T of the control valve block assembly 3. The oil outlet (port 1) of the two-position two-way valve 35 is connected to the inlet end of the third check valve 36, and the outlet end of the third check valve is connected to the return port T of the control valve block assembly 3. The oil return port (port 3) of the two-position three-way valve 35 and the outlet end of the third one-way valve 36 are connected to the oil return port T through the internal oil circuit of the valve block.

[0044] The third throttling damper is a throttling orifice with a fixed flow area, used to buffer pressure changes at the oil inlet P; The adjustable flow valve 34 is a throttling structure with an adjustable flow area, used to provide a suitable opening state for the valve in the control valve block, and the output is a low pressure state.

[0045] The two-position three-way valve 32 is a solenoid directional valve; The two-position two-way valve 35 is a normally closed solenoid directional valve. The two work together to achieve gradual increase, gradual decrease and emergency unloading control of the servo valve's oil supply pressure.

[0046] like Figure 12 As shown, the pressure progressive control process of the control valve block assembly 3 in this case is as follows: I. Start-up Phase: Gradual Increase in Pressure When the system starts, the two-position three-way valve 32 is energized, and the two-position two-way valve 35 is de-energized.

[0047] Pressurized oil is input from inlet P, and first passes through a throttling orifice (third throttling damper 31) to buffer the flow, causing the oil velocity to decrease slowly. Then, the pressurized oil enters the two-position three-way valve 32 for reversal and diversion, forming two branches: One branch goes directly into the control port of the control valve block 38, serving as the main control pressure for the servo valve's oil supply; the other branch, after being throttled by the adjustable flow valve 34, returns to the oil tank through the two-position two-way valve 35.

[0048] With the above-mentioned reversing and throttling combined, the control port of the control valve block 38 presents a low-pressure output state.

[0049] When the two-position three-way valve 32 and the two-position two-way valve 35 are energized at the same time, the two-position two-way valve 35 closes, the oil circuit blocks the return oil path, and at this time the control port pressure of the control valve block 38 tends to be consistent with the input pressure P. At the same time, the slow accumulator 33 is connected to the control oil circuit. Its buffering effect allows the control port pressure to rise slowly from low pressure to high pressure, achieving a gradual increase in pressure and preventing the servo valve from being impacted or malfunctioning due to a sudden increase in pressure.

[0050] II. Ceasefire Phase: Gradual Decrease in Pressure When the system stops, by controlling the on / off sequence of the two-position three-way valve 32 and the two-position two-way valve 35, the pressure at the control port of the control valve block 38 gradually decreases from high pressure to low pressure, and then transitions from low pressure to complete closure. By combining the pressure relief buffer of the slow accumulator 33, the pressure at the control port is gradually reduced and safely shut off, effectively preventing component damage and system shock caused by the sudden release of residual pressure on the servo valve side.

[0051] The output valve block assembly 4 is connected to the corresponding control valve block assembly 3, serving as the output interface for the hydraulic oil in that circuit, and also integrates a return oil interface. The pressure oil regulated by the control valve block assembly 3 enters the output valve block assembly 4 and is connected to the P port of the external servo valve through the output port. The return oil port (T port) of the external servo valve is connected to the return oil interface of the output valve block assembly 4 through a pipeline. This return oil interface is connected to the return oil accumulator assembly 5 and the oil tank of the workstation to realize the circulation of the oil.

[0052] The structure of output valve block assembly 4 is as follows: The output valve block assembly 4 in this case is an integrated cartridge valve structure, including an output valve core 41, an output return spring 42, an output check valve 43, and a valve block body 44. A gap seal is used between the output valve core 41 and the output valve block 44 to achieve reliable on / off control. The specific structure is as follows: Output valve block assembly 4 includes: The output valve block body 44 is provided with an oil inlet A, a working oil inlet B, an oil return port and a control oil inlet X; Output valve core 41 is slidably installed in the valve hole of valve block body 44, and the two are sealed by gap; a feedback hole is axially opened in the middle, one end of the feedback hole is connected to working oil port B, and the other end is connected to spring mounting hole, which is used to introduce the output pressure P1 of working oil port B into the spring mounting hole at the top of output valve core 41 to form hydraulic pressure feedback. The output reset spring 42 is fitted into the spring mounting hole of the output valve block body 44, and its two ends abut against the top of the output valve block body 44 and the top of the output valve core 41, respectively. The output check valve 43 connects the working oil port B and the return oil port when the machine is stopped, and its conduction direction is from the working oil port B to the return oil port C.

[0053] The working principle of output valve block assembly 4 is as follows: 1. Initial state without controlled pressure When the control port pressure from the control valve block assembly is zero, the preload of the output reset spring 42 holds the output valve core 41 in its initial lower position; at this time: The oil passage between oil inlet A and working oil inlet B is blocked; Working oil port B is kept connected to return oil port C (oil tank); residual pressure oil on the working oil port B side is quickly released to the oil tank through output check valve 43 to achieve pressureless standby. 2. Pressure balance and output during normal operation Once the control port pressure is established, the pressurized oil acts on the control port x at the bottom of the output valve core 41 through the output control pressure port of the input valve block, generating a hydraulic pressure F1 in the direction of the output return spring 42, where F1 = P⋅A. Where P is the pressure at the oil control port, and A is the effective pressure-bearing area at the bottom of the output valve core 41; When F1 overcomes the preload force F2 of the output reset spring 42, the output valve core 41 moves toward the output reset spring 42, the oil inlet A is connected to the working oil port B, the pressure oil flows from the oil inlet A to the working oil port B, and the output pressure P1 is output; the passage between the working oil port B and the return oil port is cut off. As P1 is established, the pressure oil flows into the spring cavity at the end of the output valve core 41 through the feedback hole in the middle of the output valve core 41, generating a downward hydraulic pressure F3=P1⋅A1, where A1 is the effective pressure-bearing area of ​​the top of the output valve core (the end connected to the output reset spring 42). When the system reaches dynamic equilibrium, F1=F2+F3 is satisfied.

[0054] By dynamically balancing the pressure difference across the output valve core 41 with the spring force of the output reset spring 42, the large displacement of the valve core is effectively limited, allowing the output pressure P1 to change smoothly and linearly with the input pressure P, thus avoiding the impact of sudden pressure changes on the servo valve.

[0055] 3. Rapid unloading during emergency stop When the emergency stop button is pressed in an emergency, the control port pressure is rapidly released to zero, the hydraulic pressure F1 at the bottom of the output valve core 41 disappears, and the elastic force of the output reset spring 42 pushes the output valve core 41 to move downwards rapidly. Figure 13 The direction is for reference only; The oil circuit between inlet A and working port B is immediately blocked, cutting off the supply of pressurized oil; working port B and return port are reconnected, and the residual pressurized oil on the working port B side is quickly released to the oil tank through output check valve 43, achieving safe unloading.

[0056] Oil return accumulator assembly 5 The return oil accumulator assembly 5 is connected to the return oil interface of each output valve block group 4, and is also connected to the oil tank. Its main function is to absorb hydraulic shock during the return oil process, stabilize the return oil pressure, prevent return oil fluctuations from interfering with the position of the servo valve core, and provide a certain return oil back pressure to the system, thereby improving the smoothness of the actuator operation. In this case, the return oil accumulator assembly 5 consists of two conventional accumulators.

[0057] A control method for a multi-channel hydraulic energy rapid release workstation with high / low pressure switching, taking a single channel as an example, and the same applies to four channels, includes: fuel supply phase Oil pressure oil enters the workstation via input valve block assembly 1, and after filtration, it is divided into two paths: Bypass oil enters the inlet accumulator assembly 2 for energy storage and pressure buffering; The main oil supply enters the corresponding control valve block assembly 3, and after being regulated by the pressure valve and flow valve, it enters the output valve block assembly 4; Execution phase The pressure oil from the output valve block assembly 4 enters the P port of the external servo valve through the output port; the servo valve operates according to the control signal, adjusting the flow and direction of the oil entering the cylinder 6, and driving the cylinder 6 to complete the corresponding action; oil return phase The return oil from cylinder 6 is discharged through the T port of the servo valve, returns to the return oil interface of output valve block assembly 4 through the pipeline, and then flows back to the oil tank after being buffered by return oil accumulator assembly 5, completing one hydraulic cycle.

[0058] The four working groups operate independently, and can operate simultaneously or separately without interfering with each other, thus meeting the operational needs of multiple actuators in the testing equipment.

[0059] This hydraulic workstation features a specially designed structure and oil circuit to meet the high-precision testing requirements of hydraulic components such as servo valves. Its overall safety, stability, adaptability, and efficiency are outstanding, as detailed below: 1. Achieve gradual pressure control. During the start-up phase, the pressure smoothly transitions from the off state to low pressure and then slowly rises to high pressure. During the shutdown phase, the pressure gradually decreases from high pressure to low pressure and then completes the shutdown. There are no sudden pressure changes throughout the process, which effectively avoids damage to the sample workpiece caused by hydraulic shock and ensures the safe and stable operation of the workstation.

[0060] 2. Equipped with an emergency unloading protection mechanism, if an emergency occurs during automatic operation of the equipment, the pressure oil supply to the servo valve can be quickly cut off, and the output pressure oil can be quickly connected to the return oil pipeline to release energy, which greatly improves the safety protection level of the workstation operation.

[0061] 3. The output valve block's valve core supports customized design, and a high-flow valve core can be selected according to testing requirements, fully meeting the testing conditions of high-frequency, high-speed operation of the hydraulic cylinder in the testing equipment. Meanwhile, the multi-input, multi-output hydraulic circuit layout allows for simultaneous testing of multiple samples, as well as multi-step sequential testing of a single sample, significantly improving testing efficiency.

[0062] 4. Multiple functional interfaces are reserved to adapt to the pilot port connection requirements of different components such as servo valves and hydrostatic supports, ensuring functional adaptability for various hydraulic tests and providing strong expandability. Pressure accumulators are configured at the inlet, outlet, and hydrostatic support pilot ports as needed, effectively suppressing pressure and flow fluctuations caused by changes in system demand. When the workstation and actuator are far apart, it reduces the impact of inertia and pipeline resistance during hydraulic oil delivery, compensating for insufficient flow and pressure at specific frequencies. When the servo valve opens, causing a drop in pipeline pressure, the accumulator can immediately release fluid to maintain pressure; when the servo valve closes, it automatically refills, maintaining a stable pipeline fluid operation. The accumulator in the return pipeline can also reduce discharge pulsations caused by actuator movement, effectively mitigating problems such as hose swaying and hard pipe impact, further improving system operational stability.

[0063] In summary, this hydraulic workstation, through its integrated structure and oil circuit design, fully meets the core technical requirements of testing equipment for soft start, soft stop, emergency rapid unloading, and multi-channel synchronous operation, and is suitable for various high-precision, multi-condition hydraulic component testing scenarios.

[0064] Regarding the information disclosed in this case, the following points need to be clarified: (1) The accompanying drawings of the embodiments disclosed in this case only involve the structures involved in the embodiments disclosed in this case. Other structures can refer to the general design. (2) Where there is no conflict, the embodiments and features disclosed in this case can be combined with each other to obtain new embodiments; The above are merely specific embodiments disclosed in this case, but the scope of protection of this disclosure is not limited thereto. The scope of protection disclosed in this case shall be determined by the scope of protection of the claims.

Claims

1. A multi-channel hydraulic energy rapid release workstation with high and low pressure switching, characterized in that, include: The pressure oil is filtered by the filter in the input valve block assembly (1). One path goes through the bypass to the oil accumulator assembly (2) to stabilize the system pressure and absorb hydraulic shock; the other path serves as the main oil supply and enters the corresponding servo valve drive module. The oil inlet accumulator assembly (2) is connected to the main oil circuit of the input valve block assembly (1) through a pipeline. It is equipped with multiple oil inlet accumulators to absorb shocks when the system pressure fluctuates, thus ensuring stable oil supply. The servo valve drive module is provided in multiple parts, including a control valve block assembly (3) and an output valve block assembly (4). Among them, the control valve block assembly (3) includes a third throttling damper (31), a two-position three-way valve (32), a slow accumulator (33), an adjustable flow valve (34), a two-position two-way valve (35), a third check valve (36), and a control valve block (38). The inlet end of the third throttling damper (31) is connected to the oil inlet P of the control valve block assembly (3), and the outlet end is connected to the first working port of the two-position three-way valve (32); the second working port of the two-position three-way valve (32) is connected to the oil inlet of the two-position two-way valve (35) after being connected in series with the slow accumulator (33) and the adjustable flow valve (34); the return port of the two-position three-way valve (35) is connected to the return port of the control valve block assembly (3); the outlet port of the two-position two-way valve (35) is connected to the inlet end of the third check valve (36), and the outlet end of the third check valve (36) is connected to the return port of the control valve block assembly (3); The output valve block assembly (4) includes: The output valve block body (44) is provided with an oil inlet, a working oil inlet, an oil return inlet and a control oil inlet; Output valve core (41) is slidably installed in the valve hole of valve block body (44); a feedback hole is axially opened in the middle, one end of the feedback hole is connected to the working oil port, and the other end is connected to the spring mounting hole, which is used to introduce the output pressure of the working oil port into the spring mounting hole at the top of the output valve core (41) to form hydraulic pressure feedback. The output reset spring (42) is fitted into the spring mounting hole of the output valve block body (44), and its two ends abut against the top of the output valve block body (44) and the output valve core (41) respectively. Output check valve (43): When the valve core is not working, the working oil port and the return oil port are connected, and the direction of conduction is from the working oil port to the return oil port; when the valve core rises, it is not connected. The oil source pressure oil enters the workstation from the input valve block assembly (1). After being diverted, part of it enters the oil accumulator assembly (2) for energy storage and pressure buffering, while the other part serves as the main oil circuit and enters multiple identical servo valve drive modules. Each servo valve drive module includes a control valve block group (3) and an output valve block group (4), which ultimately delivers the pressure oil to the external servo valve and cylinder to achieve multi-channel independent hydraulic control.

2. The multi-channel hydraulic energy rapid release workstation with high and low pressure switching according to claim 1, characterized in that, The input valve block assembly (1) includes: The oil inlet buffer protection zone is set at the input port of the oil source pressure oil P, including a first throttling damper and a first check valve (11); the first throttling damper is connected in series with the main oil inlet channel to buffer the pressure change when the oil source stops; the first check valve (11) is connected in parallel with the first throttling damper. The main high-pressure filtration zone includes the main filter (13), whose inlet is connected to the outlet of the throttling damper, and whose outlet is connected to the hydrostatic support dedicated oil supply zone and the system oil supply zone respectively. The dedicated oil supply area for the hydrostatic support is branched off from the oil outlet side of the main filter and includes a hydrostatic oil circuit filter (14) and a pilot port accumulator (15). The pilot port accumulator (15) is connected to the oil outlet side of the hydrostatic oil circuit filter (14) and is used to absorb oil circuit pressure fluctuations and stabilize the oil supply pressure and flow rate of the hydrostatic support. The system's oil supply zone is used to provide power to the subsequent servo valves.

3. A multi-channel hydraulic energy rapid release workstation with high and low pressure switching according to claim 2, characterized in that, The main filter (13) is equipped with a differential pressure transmitter. When the filter element is clogged, the differential pressure transmitter will provide an indication and alarm.

4. A multi-channel hydraulic energy rapid release workstation with high and low pressure switching according to claim 2, characterized in that, The main filter (13) has a nominal filtration accuracy of 25 μm, which effectively intercepts solid pollutant particles with a particle size of not less than 25 μm in the oil.

5. A multi-channel hydraulic energy rapid release workstation with high and low pressure switching according to claim 2, characterized in that, The static pressure oil filter (14) has a nominal filtration accuracy of 3µm, which effectively intercepts solid pollutant particles with a particle size of not less than 3µm in the oil.

6. A multi-channel hydraulic energy rapid release workstation with high and low pressure switching according to claim 1, characterized in that, The two-position three-way valve (32) is an electromagnetic directional valve.

7. A multi-channel hydraulic energy rapid release workstation with high and low pressure switching according to claim 6, characterized in that, The two-position two-way valve (35) is a normally closed electromagnetic directional valve that works in conjunction with the two-position three-way valve (32) to achieve gradual increase, gradual decrease and emergency unloading control of the servo valve oil supply pressure.

8. A multi-channel hydraulic energy rapid release workstation with high and low pressure switching according to claim 1, characterized in that, It also includes an oil return accumulator assembly (5); The return oil accumulator assembly (5) is connected to the return oil interface of each output valve block group (4) and is also connected to the oil tank to absorb the hydraulic shock during the return oil process and stabilize the return oil pressure.

9. A control method for a multi-channel hydraulic energy rapid release workstation with high / low pressure switching, applied to the multi-channel hydraulic energy rapid release workstation with high / low pressure switching as described in claim 1, characterized in that... Includes the following steps: Step 1, Fuel Supply Phase Oil source pressure oil enters the workstation through the input valve block assembly (1), and after filtration, it is divided into two paths. The bypass oil enters the oil accumulator assembly (2) for energy storage and pressure buffering; the main oil supply enters the corresponding control valve block assembly (3), and after being regulated by the pressure valve and flow valve, it is delivered to the output valve block assembly (4). Step Two, Execution Phase The pressure oil of the output valve block assembly (4) enters the P port of the external servo valve through the output port; the servo valve acts according to the control signal, adjusts the flow and direction of the oil entering the cylinder, and drives the oil cylinder to complete the corresponding action; Step 3, Oil Return Stage The oil return from the cylinder is discharged through the T port of the servo valve, returns to the oil return interface of the output valve block assembly (4) through the pipeline, and then flows back to the oil tank after being buffered by the oil return accumulator assembly (5), completing one hydraulic cycle. The gradual pressure control process of the control valve block assembly (3) includes a gradual pressure increase during the start-up phase and a gradual pressure decrease during the stop phase, specifically: (1) Start-up phase: Pressure gradually increases When the system starts, the two-position three-way valve (32) is energized and the two-position two-way valve (35) is de-energized; Pressure oil is input from the inlet P. After being buffered and decelerated by the third throttling damper (31), it enters the two-position three-way valve (32) for reversal and diversion, forming two branches. One branch directly enters the control port of the control valve block (38) as the main control pressure for the servo valve oil supply; the other branch is throttled by the adjustable flow valve (34) and then returns to the oil tank through the two-position two-way valve (35); so that the control port of the control valve block (38) presents a low-pressure output state. When the two-position three-way valve (32) and the two-position two-way valve (35) are energized at the same time, the two-position two-way valve (35) closes, blocking the return oil path, so that the control port pressure of the control valve block (38) tends to be consistent with the input pressure P; at the same time, the slow accumulator (33) is connected to the control oil circuit, and through its buffering effect, the control port pressure slowly rises from low pressure to high pressure, realizing a gradual increase in pressure; (2) Stopping phase: Pressure gradually decreases When the system stops, by controlling the on / off sequence of the two-position three-way valve (32) and the two-position two-way valve (35), the pressure at the control port of the control valve block 38 gradually decreases from high pressure to low pressure, and then transitions from low pressure to complete closure. The control process of the output valve block assembly (4) includes an initial state without control pressure, a normal working pressure balance output state, and an emergency stop rapid unloading state, specifically: (1) Initial state without controlled pressure When the control port pressure delivered by the control valve block assembly is zero, the preload of the output reset spring (42) keeps the output valve core (41) in the initial lower position, the oil circuit between the oil inlet and the working oil port is blocked, the working oil port and the return oil port are kept connected, and the residual pressure oil on the working oil port side is discharged to the oil tank through the output check valve (43) to achieve pressureless standby. (2) Pressure balance and output during normal operation Once the control port pressure is established, the pressure oil acts on the bottom of the output valve core (41) to generate a hydraulic pressure F1 in the direction of the output reset spring (42), F1=P⋅A; where P is the pressure of the control port and A is the effective pressure bearing area at the bottom of the output valve core (41); When F1 overcomes the preload force F2 of the output reset spring (42), the output valve core (41) moves toward the output reset spring (42), the oil inlet is connected to the working oil port, the passage between the working oil port B and the return oil port is cut off, and the pressure oil flows from the oil inlet to the working oil port to form the output pressure P1. As the output pressure P1 is established, the pressure oil flows into the spring cavity at the end of the output valve core (41) through the feedback hole in the middle of the output valve core (41), generating a downward hydraulic pressure F3=P1⋅A1, where A1 is the effective pressure-bearing area at the top of the output valve core. When the system reaches dynamic equilibrium, it satisfies F1=F2+F3. (3) Rapid unloading during emergency stop When the emergency stop button is pressed in an emergency, the pressure at the control port is quickly released to zero, the hydraulic pressure F1 at the bottom of the output valve core (41) disappears, and the elastic force of the output reset spring (42) pushes the output valve core (41) to move down quickly; the oil circuit between the inlet and the working port is immediately blocked, cutting off the supply of pressure oil; the working port and the return port are reconnected, and the residual pressure oil on the working port side is quickly released to the oil tank through the output check valve (43) to achieve safe unloading.

10. The control method for a multi-channel hydraulic energy rapid release workstation with high and low pressure switching according to claim 9, characterized in that, The control method for the input valve block assembly (1) includes: S1.1 Oil Inlet Buffer and Backflow Protection Stage The pressurized oil output from the oil source first enters the first check valve and then enters the high-pressure main filter (13) with the outer diameter inside. When the oil source stops, the reverse oil can slowly flow back through the first damper in parallel to avoid impact damage to the filter. S1.2 Main Road Primary High-Pressure Filtration Stage The pressurized oil enters the high-pressure main filter (13) to complete the primary high-precision filtration of the system oil supply, raising the oil cleanliness to the basic standard for adapting to servo valves and hydrostatic support cylinders, laying the foundation for subsequent secondary filtration. S1.3 Static pressure support for dedicated secondary filtration and pressure stabilization stage A portion of the oil diverted from the outlet side of the high-pressure main filter enters the dedicated oil supply unit for the hydrostatic support: S1.31, the oil passes through the external inlet and internal outlet hydrostatic oil circuit filter (14) to complete secondary fine filtration, completely intercepting micron-level tiny impurities, preventing impurities from entering the tiny oil chambers and oil passages of the hydrostatic support, and avoiding blockage of the hydrostatic support from the root cause. S1.32, the oil after fine filtration flows through the pilot port accumulator (15). The pilot port accumulator (15) absorbs the pressure fluctuation of the main oil circuit and the flow fluctuation caused by the action of the multi-path actuator in real time, so that the oil pressure and flow rate output to the static pressure support part remain constant, and a high pressure oil film is formed stably, which effectively avoids abnormal wear of the piston rod and the static pressure support part due to unstable pressure. S1.4 System Voltage Stabilization and Multiplexing Stage Most of the oil filtered by the high-pressure main filter (13) is delivered to the corresponding servo valve drive module through an independent oil distribution circuit, providing stable and clean hydraulic power for each servo valve and cylinder actuator, and meeting the needs of multiple actuators of the test equipment to work together.

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