Digital valve group system with throttling and flow dual-mode control function and control method

Abstract

The invention discloses a digital valve group system with throttling and flow dual-mode control functions and a control method, and relates to the technical field of hydraulic control, the system comprises a control unit, a digital valve group, a flow stabilizing unit, a displacement sensor and a proportional electromagnet; the digital valve group is in pipeline connection with the flow stabilizing unit; the digital valve group, the displacement sensor and the proportional electromagnet are electrically connected with the control unit; the displacement sensor is used for detecting the displacement of a valve core in the flow stabilizing unit; the control unit is used for generating a control signal based on displacement of a valve element in the flow stabilizing unit. And the proportional electromagnet and the digital valve group are combined based on a control signal to realize control and switching of a throttling control mode and a flow control mode. The problems that an existing digital throttling valve is greatly influenced by pressure fluctuation, and a high-precision flow valve is high in cost and poor in anti-pollution capacity can be solved.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of hydraulic control, in particular to a digital valve group system with throttle and flow dual-mode control function and a control method. BACKGROUND

[0002] In the field of hydraulic transmission, flow control valve is the core element to realize speed control and power distribution. Traditional flow control mainly relies on proportional flow valve or servo valve. Proportional flow valve has simple structure and low cost, but its control precision is limited, and the output flow is easily affected by load pressure change; although servo valve has high precision and fast response, it has high manufacturing cost and strict requirements for oil cleanliness, and is difficult to maintain.

[0003] Digital throttle valve realizes multi-stage flow output through the combination of multiple on-off valves, and has the advantages of simple structure, strong anti-pollution ability and low cost, but its essence is open-loop control, and the output flow fluctuates with the pressure difference before and after the valve port, and cannot maintain stable flow under the condition of load change. SUMMARY

[0004] The purpose of the present application is to provide a digital valve group system with throttle and flow dual-mode control function and a control method, which can solve the problems of large influence of existing digital throttle valve on pressure fluctuation, high cost of high-precision flow valve and poor anti-pollution ability.

[0005] To achieve the above purpose, the present application provides the following solutions: In a first aspect, the present application provides a digital valve group system with throttle and flow dual-mode control function, comprising: a control unit, a digital valve group, a flow stabilizing unit, a displacement sensor and a proportional electromagnet; The digital valve group and the flow stabilizing unit are connected by pipelines; the digital valve group, the displacement sensor and the proportional electromagnet are electrically connected with the control unit; The displacement sensor is used to detect the displacement of the spool in the flow stabilizing unit; the control unit is used to generate a control signal based on the displacement of the spool in the flow stabilizing unit; the proportional electromagnet and the digital valve group jointly realize the control and switching of throttle control mode and flow control mode based on the control signal.

[0006] Optionally, the flow stabilizing unit is a flow sensor with a spool valve structure.

[0007] Optionally, the flow sensor with a spool valve structure comprises a cavity, a spring, an outlet and an inlet. One end of the valve core is connected to one end of the spring; the other end of the spring is disposed on the end wall of the cavity; a sliding valve is disposed on the valve core; the sliding valve divides the cavity into a first sub-cavity, a second sub-cavity, and a third sub-cavity; the outlet is disposed on the second sub-cavity; the inlets are all disposed on the third sub-cavity; the outlet is respectively connected to the inlet of the digital valve group and the pipeline of the first sub-cavity; the outlet of the digital valve group is connected to the pipeline of the actuator.

[0008] Optionally, the control unit includes: a controller, a first selector, a second selector, a flow-valve group mapping table, a displacement-flow converter, a displacement-electromagnetic force calculator, an adder, and a PID calculator; The first output terminal of the controller is electrically connected to the first input terminal of the first selector and the first input terminal of the adder, respectively; the flow-valve group mapping table is set on the connection path between the controller and the first selector; the second output terminal of the controller is electrically connected to the first input terminal of the second selector; the output terminal of the adder is electrically connected to the input terminal of the PID calculator; the output terminal of the PID calculator is electrically connected to the second input terminal of the first selector; the output terminal of the first selector is electrically connected to the digital valve group; the displacement sensor is electrically connected to the input terminal of the displacement-flow converter and the input terminal of the displacement-electromagnetic force calculator, respectively; the output terminal of the displacement-flow converter is electrically connected to the second input terminal of the adder; the output terminal of the displacement-electromagnetic force calculator is electrically connected to the second input terminal of the second selector; the output terminal of the second selector is electrically connected to the proportional electromagnet.

[0009] Optionally, the flow stabilization unit is a pressure compensator with a slide valve structure.

[0010] Optionally, the pressure compensator with the slide valve structure includes: a cavity, a spring, an outlet, and an inlet; One end of the valve core is connected to one end of the spring; the other end of the spring is disposed on the end wall of the cavity; a sliding valve is disposed on the valve core; the sliding valve divides the cavity into a first sub-cavity, a second sub-cavity, and a third sub-cavity; the outlet and the inlet are both disposed on the second sub-cavity; the outlet is respectively connected to the inlet of the digital valve group and the pipeline of the first sub-cavity; the third sub-cavity and the actuator are both connected to the outlet pipeline of the digital valve group.

[0011] Optionally, the control unit includes: a controller, a flow-valve group mapping table, a displacement-electromagnetic force calculator, and a second selector; The first output terminal of the controller is electrically connected to the digital valve group via the flow-valve group mapping table; the second output terminal of the controller is electrically connected to the first input terminal of the second selector; the displacement sensor is electrically connected to the input terminal of the displacement-electromagnetic force calculator; the output terminal of the displacement-electromagnetic force calculator is connected to the second input terminal of the second selector; and the output terminal of the second selector is electrically connected to the proportional electromagnet.

[0012] Optionally, the digital valve assembly includes: a proportional throttle valve and at least one on / off valve; The outlet and inlet of the digital valve assembly are both connected to the pipelines of the proportional throttle valve and the switching valve. Both the proportional throttle valve and the switching valve are electrically connected to the control unit.

[0013] Optionally, when there are multiple switching valves, the rated flow rates of the multiple switching valves are in a binary proportional relationship.

[0014] Secondly, this application provides a control method for a digital valve group system with dual-mode control of throttling and flow, including: Real-time displacement data of the valve core is acquired, and the differential pressure is determined based on the displacement data; A control signal is generated based on the pressure difference; The control signals are used to control and switch between throttling control mode and flow control mode.

[0015] According to the specific embodiments provided in this application, this application has the following technical effects: This application provides a digital valve group system and control method with dual-mode control of throttling and flow. By setting up a control unit, digital valve group, flow stabilization unit, displacement sensor, and proportional electromagnet, the system pressure difference can be adjusted in real time based on the displacement data of the valve core in the flow stabilization unit detected by the displacement sensor. This reduces the impact of load pressure fluctuations, increases anti-contamination capability, and enables control and switching between throttling and flow control modes. Furthermore, by replacing existing high-precision flow valves with digital valve groups, this application can reduce costs, thereby solving the problems of existing digital throttling valves being greatly affected by pressure fluctuations, and high-precision flow valves being expensive and having poor anti-contamination capability. Attached Figure Description

[0016] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0017] Figure 1 A schematic diagram of a digital valve group system with dual-mode control of throttling and flow provided in an embodiment of this application; Figure 2 A schematic diagram of the control strategy for a digital valve group system with dual-mode control of throttling and flow provided in an embodiment of this application; Figure 3 A schematic diagram of a digital valve group system with dual-mode control of throttling and flow provided in another embodiment of this application; Figure 4 A schematic diagram of the control strategy for a digital valve group system with dual-mode control of throttling and flow provided in another embodiment of this application; Figure 5 This is a schematic flowchart of a control method for a digital valve group system with dual-mode control of throttling and flow, provided in an embodiment of this application.

[0018] Figure label: 1 Digital valve manifold, 2 Flow stabilizing unit, 3 Two-position two-way proportional throttle valve, 4 First two-position two-way switching valve, 5 Second two-position two-way switching valve, 6 Third two-position two-way switching valve, 7 Valve core, 8 Chamber, 9 Spring, 10 Proportional electromagnet, 11 Displacement sensor, 12 Controller, 13 First selector, 14 Second selector, 15 Flow-valve manifold mapping table, 16 Displacement-flow converter, 17 Displacement-electromagnet force calculator, 18 Adder, 19 PID calculator, A Inlet of flow stabilizing unit, B Outlet of flow stabilizing unit, C Inlet of digital valve manifold, D Outlet of digital valve manifold. Detailed Implementation

[0019] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0020] To make the above-mentioned objectives, features and advantages of this application more apparent and understandable, the application will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0021] In one exemplary embodiment, this application provides a digital valve group 1 system with dual-mode control of throttling and flow, such as... Figure 1 and Figure 3 As shown, the system includes: a control unit, a digital valve group 1, a flow stabilization unit 2, a displacement sensor 11, and a proportional electromagnet 10.

[0022] Digital valve assembly 1 and flow stabilization unit 2 are connected by piping. Digital valve assembly 1, displacement sensor 11, and proportional electromagnet 10 are all electrically connected to the control unit.

[0023] Displacement sensor 11 is used to detect the displacement of valve core 7 in flow stabilization unit 2. Control unit is used to generate control signal based on the displacement of valve core 7 in flow stabilization unit 2. Proportional electromagnet 10 and digital valve group 1 jointly realize the control and switching between throttling control mode and flow control mode based on the control signal.

[0024] In actual operation, the oil passage is as follows: the hydraulic oil first flows into the inlet A of the flow stabilization unit 2, passes through its internal valve core 7, and then flows out from its outlet B. It then immediately enters the digital valve group 1, and after being regulated by the digital valve group 1, it flows out from the outlet D of the digital valve group 1 and finally to the actuator.

[0025] Furthermore, the proportional electromagnet 10 used in this application has dual functions: (1) When the system differential pressure is within the rated range (i.e., under rated operating conditions (throttling control mode)), it outputs a constant force to drive the valve core 7 to the fully open position, so that the flow stabilization unit 2 does not generate throttling effect and does not intervene in the system operation (i.e., it does not participate in the system control loop). (2) During the flow measurement process, according to the instructions of the control unit, it outputs a dynamic compensation force adapted to the operating conditions to offset the changes in hydraulic force and spring force (nonlinear deformation of spring 9) caused by the change in flow (flow velocity), ensuring a single-value, linear relationship between the displacement of valve core 7 and the flow value, significantly improving the accuracy of the flow feedback signal, thereby improving the measurement accuracy.

[0026] Furthermore, the digital valve assembly 1 used in this application may include a proportional throttle valve and at least one on / off valve. The outlet and inlet of the digital valve assembly 1 are both connected to the proportional throttle valve and the on / off valve via pipelines. Both the proportional throttle valve and the on / off valve are electrically connected to the control unit.

[0027] To achieve a wider range of flow output levels, the digital valve assembly 1 used in this application can be composed of a single two-position two-way proportional throttle valve 3 with a rated flow rate of q and multiple two-position two-way on / off valves with rated flow rates in a binary proportional relationship of q, 2q, 4q... connected in parallel. For example, to achieve continuous flow output from 0 to 8q through different combinations of opening states, such as... Figure 1 As shown, digital valve group 1 can be constructed by connecting in parallel one two-position two-way proportional throttle valve 3 with a rated flow rate of q and three two-position two-way switching valves (two-position two-way switching valve 4, two-position two-way switching valve 5, and three-position two-way switching valve 6) with rated flow rates in a binary ratio of q, 2q, and 4q. The inlets of the four valves are interconnected, forming the inlet C of digital valve group 1. The outlets of the four valves are interconnected, forming the outlet D of digital valve group 1.

[0028] In practical applications, the number of switching valves in digital valve group 1 is not limited to 3. It can also be 1, 2, 4, 5, 6 or more. As long as the rated flow capacity of each valve maintains a binary relationship, as many flow regulation levels as possible can be achieved with the minimum number of valves.

[0029] Based on the above description, different structures can be used to achieve differential pressure regulation in practical applications. Therefore, in one embodiment, the flow stabilization unit 2 used in this application is a slide valve type flow sensor. For example... Figure 1 As shown, the flow sensor with this slide valve structure includes: cavity 8, spring 9, outlet B and inlet A.

[0030] One end of the valve core 7 is connected to one end of the spring 9. The other end of the spring 9 is mounted on the end wall of the cavity 8. A sliding valve is mounted on the valve core 7. The sliding valve divides the cavity 8 into a first sub-cavity, a second sub-cavity, and a third sub-cavity. The outlet B is located in the second sub-cavity. The inlets A are all located in the third sub-cavity. The outlet B is connected to the inlet C of the digital valve group 1 and the pipeline of the first sub-cavity, respectively. The outlet D of the digital valve group 1 is connected to the actuator pipeline.

[0031] Based on the above-described structure of the flow sensor, its outlet B is connected to the cavity 8 at the left end of the valve core 7, and its inlet A is connected to the cavity 8 at the right end of the valve core 7. When the oil flows through the flow sensor, a hydraulic force related to the pressure difference between the inlet and outlet is formed on the left and right end faces of the valve core 7. The valve core 7 is displaced under the combined action of the spring force, the hydraulic force, and the electromagnetic force output by the proportional electromagnet 10. The amount of displacement is detected by the displacement sensor 11 and fed back to the control unit. This amount of displacement is a function of the flow rate passing through the flow sensor.

[0032] Furthermore, to further improve the accuracy of differential pressure control, in this embodiment, such as Figure 1 As shown, at least two pairs of symmetrical protrusions can be provided in the middle part of the cavity 8.

[0033] Based on the specific structure of the flow sensor provided in this embodiment, such as Figure 2 As shown, its corresponding control unit includes: controller 12, first selector 13, second selector 14, flow-valve group mapping table 15, displacement-flow converter 16, displacement-electromagnetic force calculator 17, adder 18 and PID calculator 19.

[0034] The first output terminal of controller 12 is electrically connected to the first input terminal of selector I 13 and the first input terminal of adder 18, respectively. A flow-valve group mapping table 15 is provided on the connection path between controller 12 and selector I 13. The second output terminal of controller 12 is electrically connected to the first input terminal of selector II 14. The output terminal of adder 18 is electrically connected to the input terminal of PID calculator 19. The output terminal of PID calculator 19 is electrically connected to the second input terminal of selector I 13. The output terminal of selector I 13 is electrically connected to digital valve group 1. Displacement sensor 11 is electrically connected to the input terminal of displacement-flow converter 16 and the input terminal of displacement-electromagnetic force calculator 17, respectively. The output terminal of displacement-flow converter 16 is electrically connected to the second input terminal of adder 18. The output terminal of displacement-electromagnetic force calculator 17 is electrically connected to the second input terminal of selector II 14. The output terminal of selector II 14 is electrically connected to proportional electromagnet 10.

[0035] Based on the structural description of this control unit in this embodiment, in practical applications, the core of the control strategy of the system provided in this application lies in intelligently switching between throttling control mode and flow control mode according to the system operating conditions, so as to achieve a balance between rapid response and high-precision control. Therefore, the control and switching process between throttling control mode and flow control mode can be described as follows: (1) Throttling control mode.

[0036] 1) The triggering condition is: when the system detects that the load pressure is stable and the pressure difference fluctuation before and after the valve port is within the preset rated range, the system will automatically adopt this mode.

[0037] 2) The control process is as follows: When the system differential pressure is within the rated range (or the target flow rate value set by the user is input), the controller 12 queries the preset flow-valve combination mapping table according to the target flow rate and directly outputs a control signal to drive the corresponding valve combination in the digital valve group 1 to open. At the same time, the controller 12 controls the proportional electromagnet 10 to output a constant current, so that it generates a constant electromagnetic force sufficient to overcome the preload force of the spring 9, pushing the valve core 7 to and maintaining it in the fully open position. At this time, the flow resistance of the flow sensor is minimal, and no significant throttling effect is produced. Its detection function does not intervene in the control loop (i.e., system control), and the system operates in an open-loop state.

[0038] The throttling control mode is an open-loop control, which eliminates the signal feedback and calculation links. It has the advantages of simple structure and fast response, and is suitable for steady-state or working conditions where dynamic accuracy requirements are not high.

[0039] (2) Flow control mode.

[0040] 1) Triggering conditions: When the system detects that the load change causes a significant fluctuation in the pressure difference across the valve orifice, or when the deviation between the actual flow rate and the target flow rate continues to exceed the set threshold, the system will automatically switch to this mode.

[0041] 2) Control Process: In this mode, the controller 12 adjusts the output of the proportional electromagnet 10 to output a dynamic compensation force based on the real-time flow rate, thereby offsetting the influence of changes in hydraulic force and spring force on the balance position of the valve core 7, thus activating the high-precision measurement function of the flow sensor. The flow sensor detects the displacement of the valve core 7 in real time through the displacement sensor 11 and converts it into an actual flow value, which is then fed back to the controller 12. The controller 12 compares the actual flow rate with the target flow rate, calculates the flow deviation, and generates a control signal based on the PID (proportional-integral-derivative) calculator 19, adder 18, and other components that incorporate closed-loop control algorithms such as PID. This dynamically adjusts the opening combination of each valve in the digital valve group 1 (such as switching on / off valves with different flow capacities or fine-tuning the opening of the proportional throttle valve) to maintain a stable flow rate.

[0042] The flow control mode is a closed-loop control. Through a continuous cycle of measurement, comparison and correction, it can effectively suppress flow changes caused by pressure fluctuations and ensure that the system output flow accurately and stably follows the target value. It is suitable for working conditions with variable loads or high control accuracy requirements.

[0043] (3) Mode switching.

[0044] The controller 12 monitors the system differential pressure in real time and automatically switches between throttling control mode and flow control mode based on whether it is within the rated range. The controller 12 continuously monitors the system differential pressure signal and / or flow deviation signal. When the signal is stable within the rated range, the faster-responding throttling control mode is prioritized. When the signal fluctuation exceeds the threshold, it seamlessly switches to the more accurate flow control mode. This intelligent switching strategy allows the system to leverage the speed advantage of open-loop control under stable operating conditions while possessing the high precision and strong anti-interference capability of closed-loop control under varying operating conditions, achieving an optimal performance balance that combines the speed of open-loop control with the accuracy of closed-loop control.

[0045] Based on the above description, such as Figure 2 As shown, the entire control process of the system can be described as follows: After system initialization, controller 12 monitors and determines the system differential pressure signal. When the system differential pressure is determined to be stable (i.e., fluctuations are within the rated range), the system enters throttling control mode. In this mode, selector I 13 switches to channel a, selector II 14 switches to channel d, and controller 12 outputs a flow control signal. q setBased on the user-defined target flow rate, the controller directly queries the pre-stored flow-valve group mapping table 15, driving the corresponding two-position two-way proportional throttle valve 3 and two-position two-way switching valve combination in digital valve group 1 to open. Simultaneously, the controller 12 outputs a constant drive current. F set This generates an electromagnetic force sufficient to push and hold valve core 7 to the fully open position. At this point, the flow sensor's channel is fully open, acting as a low-resistance channel that does not throttle the flow. The feedback signal from displacement sensor 11 also does not participate in the control. This mode offers rapid response and low system losses.

[0046] When controller 12 determines that the system differential pressure has fluctuated significantly (i.e., the fluctuation exceeds the preset threshold), the system immediately switches to flow control mode. In this mode, selector I 13 switches to channel b, selector II 14 switches to channel c, and displacement sensor 11 detects the displacement of valve core 7. x f The flow rate is then converted by the displacement-flow converter 16 to obtain the measured flow rate value. q f This value is the same as q set The instantaneous flow deviation is compared by adder 18, then calculated by PID calculator 19, and the calculated value is input to selector I 13 through channel b to form a new control signal for digital valve group 1. This signal controls the opening of different switching valves or fine-tuning proportional throttle valves, thereby changing the total flow area of ​​the system and accurately regulating and stabilizing the actual flow rate near the target value, thus controlling the system flow rate. Simultaneously, displacement sensor 11 detects the displacement of valve core 7. x f The displacement-electromagnet force calculator 17 calculates the changes in hydraulic force and spring force caused by the pressure difference, obtains the electromagnet compensation force, and inputs the calculated value to the second selector 14 through channel c, so that it outputs a dynamic compensation force that adapts to the real-time operating conditions, thereby ensuring that the displacement of valve core 7 has a precise linear relationship with the flow rate through the sensor, and activating the high-precision measurement function of the flow sensor.

[0047] therefore, Figure 1 The working principle of the system structure shown can be summarized as follows: Controller 12 receives flow setting commands from the user and flow feedback signals from the flow sensor. Controller 12 has a pre-stored flow-valve combination mapping table. When the system differential pressure is stable, controller 12 operates in throttling control mode, directly outputting the corresponding valve combination command according to the target flow rate to achieve rapid, open-loop flow regulation. When the system detects differential pressure fluctuations or a continuous deviation between the flow feedback value and the target value, controller 12 automatically switches to flow control mode, employing closed-loop control algorithms such as PID calculation to dynamically adjust the opening and closing combinations of digital valve group 1 to maintain a constant flow rate.

[0048] In another embodiment, the flow stabilizing unit 2 uses a pressure compensation method to achieve differential pressure regulation. Therefore, the flow stabilizing unit 2 in this embodiment is a pressure compensator with a slide valve structure. Figure 3 As shown, this slide valve type pressure compensator includes: cavity 8, spring 9, outlet B and inlet A.

[0049] One end of the valve core 7 is connected to one end of the spring 9. The other end of the spring 9 is mounted on the end wall of the cavity 8. A sliding valve is mounted on the valve core 7. The sliding valve divides the cavity 8 into a first sub-cavity, a second sub-cavity, and a third sub-cavity. Both the outlet B and the inlet A are located in the second sub-cavity. The outlet B is connected to the inlet C of the digital valve group 1 and the pipeline of the first sub-cavity, respectively. The third sub-cavity and the actuator are both connected to the outlet D pipeline of the digital valve group 1.

[0050] In this embodiment, the structure of the flow stabilizing unit 2, valve core 7, and cavity 8 (which may only have one protrusion), as well as the connection methods of the oil passages at the left and right ends of the cavity, are all the same as described above. Figure 1 and Figure 2 The illustrated embodiments differ, and the controller 12 also differs. Overall, the above... Figure 1 and Figure 2 The flow control method of the embodiment shown is that the flow sensor measures the displacement information of the valve core 7 and converts it into flow information. When the pressure difference between the two ends of the valve (the pressure difference between the inlet A and the outlet D) changes, the displacement of the flow sensor will change accordingly, and the detected flow information will also change accordingly. The detected flow information is given as feedback information to the controller 12, and the opening and closing combination of the digital valve group 1 is adjusted through closed-loop PID control to achieve flow regulation.

[0051] In this embodiment, when the pressure difference between the two ends of the valve (inlet A and outlet D) changes, the pressure at both ends of the pressure compensator will change accordingly. The valve core 7 will move left and right under the pressure change. After reaching a new equilibrium state, the throttling effect of the valve port will change accordingly, thereby regulating the pressure at (outlet B, which is also inlet C) so that the pressure difference between the two ends of the digital valve group 1 remains constant, thereby keeping the flow rate constant.

[0052] Based on the above description, this embodiment is similar to the one described above.Figure 1 and Figure 2 The difference between the embodiments shown is that: the above Figure 1 and Figure 2 The illustrated embodiment uses a flow sensor to measure flow rate, which is then fed back to the controller 12 to adjust the opening and closing combinations of the digital valve assembly 1, thereby achieving flow regulation. Another embodiment uses the displacement of the valve core 7 of a pressure compensator to adjust the pressure difference across the digital valve assembly 1, thus achieving flow regulation.

[0053] The two embodiments share the following characteristics: 1) Both can achieve throttling control and flow control. (The above...) Figure 1 and Figure 2 In the illustrated embodiment, the proportional electromagnet 10 actively outputs force to fully open the flow sensor, which is throttling control; the flow sensor then engages, resulting in flow control. In the same embodiment, the proportional electromagnet 10 outputs force to fully open the pressure compensator, which is also throttling control; the pressure compensator then engages, resulting in flow control. 2) The proportional electromagnet 10 can actively output force to compensate for changes in hydraulic and spring forces, making flow control more precise.

[0054] like Figure 4 As shown, and as Figure 3 The control unit corresponding to the pressure compensator shown includes: controller 12, flow-valve mapping table 15, displacement-electromagnetic force calculator 17, and second selector 14.

[0055] The first output of controller 12 is electrically connected to digital valve group 1 via flow-valve group mapping table 15. The second output of controller 12 is electrically connected to the first input of second selector 14. Displacement sensor 11 is electrically connected to the input of displacement-electromagnetic force calculator 17. The output of displacement-electromagnetic force calculator 17 is connected to the second input of second selector 14. The output of second selector 14 is electrically connected to proportional electromagnet 10.

[0056] Based on this control unit structure, in this embodiment, the system control process is as follows: After system initialization, controller 12 monitors the system differential pressure signal and makes a judgment. When the system differential pressure is determined to be in a stable state (i.e., the fluctuation is within the rated range), the system enters the throttling control mode. In this mode, selector II 14 switches to channel d, and controller 12 outputs a flow control signal. q set Based on the user-defined target flow rate, the controller directly queries the pre-stored flow-valve group mapping table 15, driving the corresponding two-position two-way proportional throttle valve 3 and two-position two-way switching valve combination in digital valve group 1 to open. Simultaneously, the controller 12 outputs a constant drive current. F setThis generates an electromagnetic force sufficient to pull the valve core 7 to and hold it in the fully open position. At this time, the flow channel of the pressure compensator is fully open, which is equivalent to a low-resistance flow channel. It does not produce a throttling effect. This mode has a rapid response and low system loss.

[0057] When controller 12 determines that the system differential pressure fluctuates significantly (i.e., the fluctuation exceeds the preset threshold), the system immediately switches to flow control mode. In this mode, the pressure compensator intervenes. Due to the pressure change in the left and right chambers of valve core 7, valve core 7 will autonomously reach a new equilibrium state, thereby adjusting the differential pressure across digital valve group 1 and controlling the flow rate. This function is achieved by the mechanical structure of the pressure compensator, and controller 12 does not participate in the control. At the same time, selector II 14 switches to channel C, and displacement sensor 11 detects the displacement of valve core 7. x f The displacement-electromagnet force calculator 17 calculates the changes in hydraulic force and spring force caused by the pressure difference, obtains the electromagnet compensation force, and inputs the calculated value to the second selector 14 through channel c, so that it outputs a dynamic compensation force that adapts to the real-time operating conditions, thereby eliminating the error caused by the change in hydraulic force and spring force on the force balance of valve core 7, and thus reducing the error of the pressure compensator in regulating the pressure difference of digital valve group 1, and improving the flow control accuracy.

[0058] Based on the same inventive concept, this application also provides a control method for a digital valve group system with dual-mode control of throttling and flow, such as... Figure 5 As shown, the method includes: Step 100: Acquire the displacement data of the valve core in real time, and determine the pressure difference based on the displacement data.

[0059] Step 101: Generate a control signal based on the pressure difference.

[0060] Step 102: Control and switch between throttling control mode and flow control mode based on control signals.

[0061] In summary, compared with the prior art, this application has at least the following advantages: 1. Features dual-mode control for intelligent switching. This application integrates both open-loop and closed-loop flow control modes, which can automatically switch according to system operating conditions, balancing fast response and high-precision control.

[0062] 2. The valve assembly is flexible in configuration and highly expandable. The digital valve assembly of this application can be constructed by connecting one two-position two-way proportional throttle valve with a rated flow of q and one or more two-position two-way switching valves with rated flow rates in a binary ratio of q, 2q, 4q... in parallel. The number of switching valves can be flexibly selected according to the required flow rate level and resolution (such as 1, 2, 3, 4, 5, 6, etc.), which has good versatility.

[0063] 3. Precise measurement and integrated functions. In this application, the flow stabilization unit is located before the valve assembly. Its proportional electromagnet has the dual functions of putting the flow stabilization unit into sleep mode and providing active power compensation, effectively improving the accuracy and reliability of flow measurement.

[0064] 4. Compact structure and cost-effectiveness. This application integrates a multi-stage two-position two-normally closed throttle valve and a flow sensor into one unit, reducing external piping and connections, and improving system rigidity and reliability; it utilizes a combination of on / off valves to achieve high-resolution flow regulation, which has significant cost advantages compared to traditional high-precision servo valves or proportional valves, and is also more resistant to contamination.

[0065] 5. Advanced control strategy. This application employs a clear closed-loop control mechanism to ensure stable flow even under harsh operating conditions, thereby enhancing the system's adaptability and robustness.

[0066] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0067] This document uses specific examples to illustrate the principles and implementation methods of this application. The descriptions of the above embodiments are only for the purpose of helping to understand the methods and core ideas of this application. Furthermore, those skilled in the art will recognize that, based on the ideas of this application, there will be changes in the specific implementation methods and application scope. Therefore, the content of this specification should not be construed as a limitation of this application.

Claims

1. A digital valve block system having a throttle and flow dual mode control function, characterized by, The control unit, the digital valve group, the flow stabilizing unit, the displacement sensor and the proportional electromagnet are connected in series. The digital valve group and the flow stabilizing unit are connected in series. The digital valve group, the displacement sensor and the proportional electromagnet are connected to the control unit. The displacement sensor is used to detect the displacement of the valve core in the flow stabilizing unit. The control unit is used to generate a control signal based on the displacement of the valve core in the flow stabilizing unit.

2. The digital valve block system with throttle and flow dual mode control function according to claim 1, characterized in that, The proportional electromagnet and the digital valve group jointly realize the control and switching of the throttle control mode and the flow control mode based on the control signal.

3. The digital valve block system with throttle and flow dual mode control function according to claim 2, characterized in that, The flow stabilizing unit is a flow sensor with a sliding valve structure. The flow sensor with a sliding valve structure includes a cavity, a spring, an outlet and an inlet.

4. The digital valve block system with throttle and flow dual mode control function according to claim 2, characterized in that, One end of the valve core is connected to one end of the spring, and the other end of the spring is arranged on the end wall of the cavity. A sliding valve is arranged on the valve core.

5. The digital valve block system with throttle and flow dual mode control function according to claim 1, wherein, The sliding valve divides the cavity into a first sub-cavity, a second sub-cavity and a third sub-cavity.

6. The digital valve block system with throttle and flow dual mode control function according to claim 5, wherein, The outlet is arranged on the second sub-cavity, and the inlet is arranged on the third sub-cavity. The outlet is connected to the inlet of the digital valve group and the first sub-cavity in series. The control unit includes a controller, a first selector, a second selector, a flow-valve group mapping table, a displacement-flow converter, a displacement-electromagnet force calculator, an adder and a PID calculator. The first output of the controller is connected to the first input of the first selector and the first input of the adder. The flow-valve group mapping table is arranged on the connection path between the controller and the first selector. The second output of the controller is connected to the first input of the second selector. The output of the adder is connected to the input of the PID calculator. The output of the PID calculator is connected to the second input of the first selector. The output of the first selector is connected to the digital valve group. The displacement sensor is connected to the input of the displacement-flow converter and the input of the displacement-electromagnet force calculator. The output of the displacement-flow converter is connected to the second input of the adder. The output of the displacement-electromagnet force calculator is connected to the second input of the second selector. The output of the second selector is connected to the proportional electromagnet. The flow stabilizing unit is a pressure compensator with a sliding valve structure. The pressure compensator with a sliding valve structure includes a cavity, a spring, an outlet and an inlet. One end of the valve core is connected to one end of the spring, and the other end of the spring is arranged on the end wall of the cavity. A sliding valve is arranged on the valve core. The sliding valve divides the cavity into a first sub-cavity, a second sub-cavity and a third sub-cavity. The outlet and the inlet are arranged on the second sub-cavity. The outlet is connected to the inlet of the digital valve group and the first sub-cavity in series. The third sub-cavity and the actuator are connected to the outlet of the digital valve group in series.

7. The digital valve block system with throttle and flow dual mode control function according to claim 5, wherein, The control unit comprises a controller, a flow-valve group mapping table, a displacement-magnet force calculator and a second selector; The first output of the controller is electrically connected with the digital valve group through the flow-valve group mapping table; the second output of the controller is electrically connected with the first input of the second selector; the displacement sensor is electrically connected with the input of the displacement-magnet force calculator; the output of the displacement-magnet force calculator is connected with the second input of the second selector; the output of the second selector is electrically connected with the proportional magnet.

8. The digital valve block system with throttle and flow dual mode control function according to claim 1, wherein, The digital valve group comprises a proportional throttle valve and at least one on-off valve; The outlet and inlet of the digital valve group are connected with the proportional throttle valve and the on-off valve; The proportional throttle valve and the on-off valve are electrically connected with the control unit.

9. The digital valve block system with throttle and flow dual mode control function according to claim 8, wherein, When the number of the on-off valves is more than one, the rated flow of the on-off valves is in a binary proportional relationship.

10. A control method of a digital valve group system having a throttle and flow dual mode control function, characterized by, The method comprises: acquiring displacement data of the valve core in real time, and determining a pressure difference based on the displacement data; generating a control signal based on the pressure difference; jointly implementing control and switching of the throttle control mode and the flow control mode based on the control signal.

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