A control method and device of a two-plate die casting machine and a storage medium

Abstract

This application discloses a control method, equipment, and storage medium for a two-plate die-casting machine, including: setting a target speed and target pressure for the hammer's follow-out motion; after the injection action is completed, driving the hammer with the target speed and target pressure, while simultaneously limiting the return oil flow of the mold-opening cylinder, so that the hammer pushes the mold plate to perform a mold-opening action; during the process of the hammer pushing the mold plate, controlling the return oil pressure of the mold-opening cylinder by adjusting the opening degree of the pressure relief valve; when the mold plate is detected to have moved to a preset follow-out position, stopping the follow-out driving of the hammer, and completing the subsequent mold-opening action at a preset mold-opening speed until the mold opening is completed. This application achieves the technical effect of improving production safety and stability by simultaneously setting and controlling the target pressure and speed of the hammer's follow-out motion, so that the mold-opening speed is controlled by the hammer's push during the follow-out stage.

Description

Technical Field

[0001] This application relates to the field of die-casting machine control technology, and in particular to a control method, equipment and storage medium for a two-plate die-casting machine. Background Technology

[0002] In cold chamber die casting machines, a fixed valve opening is commonly used to control the hammer's follow-out motion during mold opening. This method drives the hammer by setting a fixed opening of a servo valve, causing it to move synchronously with the mold plate when mold opening begins. Its control objective is solely to match the hammer's follow-out speed as closely as possible to the mold opening speed, without independently managing or limiting the pressure parameters during the follow-out process.

[0003] However, this control method, which focuses solely on speed matching, has significant limitations. Because the follow-through force cannot be effectively controlled, excessive follow-through force can easily cause the die-casting cake to burst within the mold cavity when the adhesion between the die and the mold cavity is high. This not only damages the inner wall of the mold but also poses a safety hazard of flying metal and injury. Simultaneously, the enormous follow-through force is transmitted through the mold platen to the entire frame, causing severe vibrations during the mold opening stage. This vibration often triggers false alarms from auxiliary equipment such as sprayers mounted on the frame, affecting production continuity. Furthermore, if the actual follow-through speed of the hammer is lower than the mold opening speed, the movement of the mold platen can pull on the die-casting cake, posing a risk of breaking it off and leaving it inside the mold, leading to defects in the die-casting parts and production interruptions.

[0004] Therefore, how to design a control method that can accurately and coordinately control the ejection pressure and speed during the hammer ejection process in the mold opening stage of the die-casting machine, so as to eliminate the risk of material bursting and breaking, and effectively suppress mold opening vibration, has become a technical problem that needs to be solved in this field.

[0005] The above content is only used to help understand the technical solution of this application and does not represent an admission that the above content is prior art. Summary of the Invention

[0006] The main purpose of this application is to provide a control method, equipment and storage medium for a two-plate die casting machine, which aims to solve the technical problem of uncontrollable pressure when the hammer head follows out in existing die casting machines.

[0007] To achieve the above objectives, this application proposes a control method for a two-plate die-casting machine, the method comprising: Obtain the target speed and target pressure of the die-casting machine hammerhead following the ejection; After the injection action is completed, the hammer head is driven by the target speed and target pressure, and the return oil flow of the mold opening cylinder is controlled based on the target flow value, so that the hammer head pushes the template to perform the mold opening action; During the process of the hammer pushing the template, the return oil pressure of the mold opening cylinder is controlled by adjusting the opening degree of the pressure relief valve; When the template is detected to have moved to the preset follow-out position, the follow-out drive of the hammer head is stopped, and the subsequent mold opening action is completed at a preset mold opening speed until the mold opening is finished.

[0008] In one embodiment, the step of controlling the return oil flow of the mold-opening cylinder based on the target flow value, so that the hammer pushes the template to perform the mold-opening action, includes: Obtain the minimum opening speed value, and based on the minimum speed value, obtain the target flow rate value of the oil return path of the opening cylinder; The opening degree of the electrically controlled flow valve in the return oil circuit of the mold opening cylinder is adjusted by the target flow value to control the return oil flow of the mold opening cylinder.

[0009] In one embodiment, the step of controlling the return oil pressure of the mold-opening cylinder by adjusting the opening degree of the pressure relief valve during the process of the hammer pushing the template includes: Real-time acquisition of the actual mold opening speed and actual hammer ejection speed of the template; Calculate the speed difference between the actual hammer follow-out speed and the actual mold opening speed. Based on the comparison result of the speed difference with a preset speed difference threshold, adjust the opening degree of the pressure relief valve so that the mold opening speed is controlled by the push of the hammer.

[0010] In one embodiment, the step of adjusting the opening degree of the pressure relief valve based on a comparison between the speed difference and a preset speed difference threshold includes: Obtain the control current corresponding to the speed difference, and calculate the current control signal based on the control current and the speed difference; The opening degree of the pressure relief valve is controlled by the current control signal.

[0011] In one embodiment, the step of controlling the return oil pressure of the mold opening cylinder through the pressure relief valve includes: The actual pressure value of the rodless cavity of the mold opening cylinder is detected in real time by a pressure sensor, and the actual pressure value is compared with the target pressure to obtain the pressure deviation value. Based on the pressure deviation value, proportional-integral-differential calculations are performed to generate control commands for real-time control of the opening degree of the pressure relief valve. The control command controls the return oil pressure of the mold opening cylinder so that the actual pressure value follows the target pressure value.

[0012] In one embodiment, the step of stopping the hammer's follow-out drive when the template is detected to have moved to a preset follow-out position includes: The current position of the template is detected in real time by a position sensor located on the template's movement path; Calculate the position difference between the current position and the preset follow-out position coordinates. When the position difference is determined to be within the preset position error range, it is determined that the follow-out position has been reached.

[0013] In one embodiment, the step of completing subsequent mold-opening actions at a preset mold-opening speed until the mold-opening is completed includes: Output a stop command to the proportional valve or servo valve that drives the hammerhead; At the same time, according to the preset independent speed setting value, the corresponding control signal is output to the proportional directional valve that controls the mold opening cylinder to take over the speed control of the mold opening action.

[0014] In one embodiment, after the step of stopping the hammer's follow-up drive when the template is detected to have moved to a preset follow-up position, and completing the subsequent mold opening action at a preset mold opening speed until the mold opening is completed, the method further includes: Control the die-casting machine to switch to the preset empty cycle test mode; During the empty cycle test mode, real-time running data is acquired as the hammer pushes the template to the follow-out position. The real-time running data includes actual pressure change data, actual speed change data, and mold opening vibration intensity data.

[0015] In addition, to achieve the above objectives, this application also proposes a control device for a two-plate die-casting machine, the device comprising: a memory, a processor, and a computer program stored in the memory and executable on the processor, the computer program being configured to implement the steps of the control method for the two-plate die-casting machine as described above.

[0016] In addition, to achieve the above objectives, this application also proposes a storage medium, which is a computer-readable storage medium, on which a computer program is stored, and when the computer program is executed by a processor, it implements the steps of the control method for the two-plate die-casting machine as described above.

[0017] The one or more technical solutions proposed in this application have at least the following technical effects: The technical solution of this application obtains the target speed and target pressure of the die-casting machine hammer; after the injection action is completed, the hammer is driven by the target speed and target pressure, and the return oil flow of the mold opening cylinder is controlled based on the target flow value, so that the hammer pushes the template to perform the mold opening action; during the process of the hammer pushing the template, the return oil pressure of the mold opening cylinder is controlled by adjusting the opening degree of the pressure relief valve; when the template is detected to have moved to the preset follow-up position, the follow-up drive of the hammer is stopped, and the subsequent mold opening action is completed at the preset mold opening speed until the mold opening is completed.

[0018] This application achieves the technical effect of coordinated control of pressure and speed by simultaneously setting and controlling the target pressure and speed of the hammer head during the follow-out stage, so that the mold opening speed is controlled by the hammer head push during the follow-out stage, thereby improving production safety and stability. Attached Figure Description

[0019] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application.

[0020] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, for those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0021] Figure 1 This is a flowchart illustrating the first embodiment of the control method for a two-plate die-casting machine according to this application; Figure 2 This is a detailed schematic diagram of step S20 in the first embodiment; Figure 3 This is a detailed schematic diagram of step S30 in the first embodiment; Figure 4 This is a detailed schematic diagram of step S40 in the first embodiment; Figure 5 This is a schematic diagram of another detailed process of step S40 in the first embodiment; Figure 6 This is a flowchart illustrating the second embodiment of the control method for a two-plate die-casting machine according to this application; Figure 7 This is a schematic diagram of the equipment structure of the hardware operating environment involved in the control method of the two-plate die-casting machine in this embodiment of the application.

[0022] The purpose, features, and advantages of this application will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0023] It should be understood that the specific embodiments described herein are merely illustrative of the technical solutions of this application and are not intended to limit this application.

[0024] In related technologies, two-plate die casting machines typically use a fixed-opening hammer follow-out control method. This method cannot effectively manage the pressure applied during the follow-out process, which poses risks such as material bursting, severe mold opening vibration, and material breakage due to asynchronous speeds.

[0025] Based on the aforementioned deficiencies in related technologies, this application proposes a control method for a two-plate die-casting machine. In this method, by setting and coordinating the target speed and target pressure of the hammer follow-out, the mold opening action is completed by the controlled push of the hammer at a specific stage, thereby achieving effective limitation of the follow-out force and precise matching of speed.

[0026] To better understand the technical solution of this application, a detailed description will be provided below in conjunction with the accompanying drawings and specific implementation methods.

[0027] Based on this, the embodiments of this application provide a control method for a two-plate die-casting machine, referring to... Figure 1 , Figure 1 This is a flowchart illustrating the first embodiment of the control method for a two-plate die-casting machine according to this application. In this embodiment, the control method for the two-plate die-casting machine includes steps S10 to S40: Step S10: Obtain the target speed and target pressure of the die-casting machine hammer. In this embodiment, the target speed and target pressure of the die-casting machine's hammer ejection are obtained by accessing the human-machine interface integrated into the die-casting machine's control system. This interface is typically a high-resolution touchscreen, embedded in the control cabinet or a separate operating console, providing a dedicated menu for setting process parameters. Within the menu, there are clearly marked "Ejection Speed" and "Ejection Pressure" input fields, each displaying its engineering unit (such as mm / s, Bar, or MPa) and the upper and lower limits of the system's allowed values. These limits are determined by the die-casting machine's mechanical structural strength, the rated working capacity of the hydraulic system, and safety regulations, aiming to prevent equipment overload caused by misoperation from the outset.

[0028] Operators input specific values ​​in the corresponding fields based on the workpiece material characteristics, mold structure complexity, and expected production cycle time corresponding to the current production task. For example, for large, thin-walled parts or mold cavities that are relatively fragile, a lower target pressure and a moderate target speed may be set to balance mold opening requirements with mold protection. Input triggers a background verification process in the interface program. This verification algorithm immediately compares the input value with a parameter safety range database pre-stored in the system's non-volatile memory. If the input value exceeds the permissible range, the system will immediately display a visual alarm window on the interface accompanied by an audible prompt, and simultaneously lock the "Confirm" button until the operator corrects the input value to within the valid range.

[0029] The verified parameters are then received by the main controller of the control system. This controller, typically a programmable logic controller (PLC) or an industrial PC, writes these two key parameters into its internal temporary data storage area allocated for the current production cycle. This storage area shares access permissions with sub-modules such as injection process control and mold opening control, ensuring smooth data flow. The writing process is accompanied by data format standardization processing, such as converting manually entered decimal values ​​into fixed-point or floating-point numbers required for the controller's internal calculations, and standardizing the pressure units to the system's internal standard pressure units.

[0030] This involves not only the static reception and storage of parameters but also the system's process formula management function. For mature and stable production processes, the aforementioned target speed and target pressure values ​​can be used as components of a "parameter set," along with dozens of other parameters such as injection speed, injection pressure, and holding time, and saved as a complete process formula. Operators can directly call existing formula names from the formula library, and the system will automatically load all parameter values ​​contained in that formula, including the target speed and target pressure involved in this claim, thereby significantly improving changeover efficiency and eliminating batch-to-batch differences that may result from manual input. Whether through manual input or formula retrieval, successfully acquiring and storing compliant target speed and target pressure parameters signifies the completion of the control system's initial configuration, providing a precise command reference for subsequent execution of pressure- and speed-based composite control.

[0031] Step S20: After the injection action is completed, the hammer head is driven by the target speed and target pressure, and the return oil flow of the mold opening cylinder is controlled based on the target flow value, so that the hammer head pushes the template to perform the mold opening action. In this embodiment, after the injection action is completed, the hammer head is driven by the target speed and target pressure, and the return oil flow of the mold opening cylinder is controlled based on the target flow rate value, so that the hammer head pushes the template to perform the mold opening action.

[0032] The termination of the injection action is determined deterministically by the control system through multi-sensor information fusion. This is primarily based on the high-precision displacement sensor signal mounted on the injection cylinder reaching the preset injection endpoint position, and the injection process timer reaching the set injection time. Additionally, the system may monitor the pressure curve of the injection chamber to confirm whether it has entered the pressure holding plateau stage or begun to decay. When all these conditions are met, the controller generates a Boolean truth value signal indicating "injection complete," which directly triggers the initiation of the follow-up and mold opening coordinated control sequence.

[0033] The controller then reads the preset target hammer follow-up speed V_target and target pressure P_target from the temporary data storage area. These parameters are sent to the core of the control algorithm of the hammer servo drive unit. This control algorithm typically includes a speed closed loop and a pressure closed loop, which work together in a cross-limiting or master-slave manner. The speed loop uses V_target as the setpoint and the real-time speed V_actual obtained by differentiating the hammer displacement sensor as the feedback value. Its output initially determines the theoretical current command I_speed of the servo valve or proportional valve that drives the hammer forward. The pressure loop uses P_target as the upper limit setpoint and the pressure sensor reading P_actual installed on the hammer propulsion oil circuit as the feedback value. Its output generates a pressure limit command I_pressure_limit. The final actual current command I_valve acting on the valve core is obtained by comparing I_speed and I_pressure_limit by selecting the lower value, ensuring that the pushing pressure will not exceed the set safety upper limit at any time, thereby achieving controlled drive with the required speed but limited by the pressure boundary.

[0034] Simultaneously, to facilitate the hammer's role as the primary force driving the template movement, the system initiates coordinated calculation and control of the return oil flow rate of the mold opening cylinder. Based on the target speed V_target, the mechanical transmission ratio between the hammer and the moving template (typically a 1:1 direct connection), and the effective working area A_rod of the rod chamber of the mold opening cylinder, the system calculates in real-time the hydraulic oil flow rate Q_target = V_target * A_rod required to match the hammer's driving speed. This Q_target value is set as the target flow rate for the flow control valve on the mold opening cylinder's return oil path.

[0035] The control module then sends a command to the flow control valve, adjusting its opening to a position where the Q_target flow can pass. This flow control valve can be an independent proportional flow valve or a simulated on / off valve controlled by a precise pulse width modulation signal. By limiting the return oil flow, it is essentially equivalent to applying controllable damping to the retraction motion of the piston rod of the mold opening cylinder. At this time, the oil inlet valve controlling the active extension of the mold opening cylinder is usually closed or in a minimally pre-opened state. Therefore, when the hammer begins to move forward and push against the mold plate under controlled pressure and speed, the piston rod of the mold opening cylinder cannot retract freely and quickly due to the limited return oil; its movement speed is clamped near the value determined by Q_target, thus passively and forcibly following the hammer's advancing speed to the initial opening speed of the entire moving mold plate assembly. This series of parallel actions constitutes the primary stage of the hammer driving the mold plate to perform the mold opening motion.

[0036] Step S30: During the process of the hammer pushing the template, the return oil pressure of the mold opening cylinder is controlled by adjusting the opening degree of the pressure relief valve; During the process of the hammer pushing the template, the return oil pressure of the mold opening cylinder is controlled by the pressure relief valve so that the mold opening speed is controlled by the pushing of the hammer.

[0037] During the dynamic phase where the hammer continuously pushes the mold plate, a real-time closed-loop adjustment of the return oil pressure of the mold opening cylinder is introduced to achieve precise tracking between the mold opening speed and the hammer's advancing speed and to absorb system disturbances. The core of this process is establishing a pressure fine-tuning loop aimed at "maintaining speed synchronization." The system continuously samples two key real-time signals: one is the instantaneous advancing speed V_punch calculated by the hammer displacement sensor, and the other is the return oil back pressure P_return measured by a pressure sensor installed on the return oil line of the rod chamber of the mold opening cylinder.

[0038] The controller's synchronous logic unit directly uses V_punch as the current desired mold opening speed V_mold_desired. Simultaneously, the actual mold opening speed V_mold_actual is obtained by differentiating the signal from the displacement sensor on the moving mold plate. The speed deviation ΔV = V_mold_desired - V_mold_actual is calculated. This deviation signal is processed by a proportional-integral controller, which outputs a command ΔP_set to correct the return oil back pressure setpoint. This command is added to a preset base back pressure value P_base based on system characteristics to form the instantaneous return oil back pressure target value P_return_target.

[0039] The actual measured return oil pressure P_return is compared with the target value P_return_target, and the pressure deviation signal is sent to the dedicated control subroutine of the pressure relief valve. This pressure relief valve is usually a proportional relief valve with a fast response, and its pilot control pressure is proportional to the input current. The controller outputs a corresponding analog current signal to drive the proportional relief valve according to the magnitude and direction of the pressure deviation. If the actual mold opening speed lags behind the hammer speed (ΔV>0), it indicates that the return oil resistance is too large. The controller will instruct the proportional relief valve to reduce its pilot set pressure, increase the flow tendency of its main valve port, or open a bypass unloading channel, thereby reducing the pressure P_return in the return oil line, reducing the back pressure damping of the mold opening cylinder piston rod retraction, and enabling it to move faster to keep up with the hammer.

[0040] Conversely, if the actual mold opening speed tends to exceed the hammer speed due to inertia or other reasons (ΔV<0), the controller will instruct the proportional relief valve to increase the set pressure, enhancing its overflow resistance and thus increasing the return oil back pressure P_return. This generates additional hydraulic braking on the retraction of the mold opening cylinder, causing its speed to drop back to synchronize with the hammer speed. Through this continuous, millisecond-level dynamic pressure adjustment, the movement of the mold opening cylinder is firmly "attached" to the forward movement of the hammer. This speed synchronization method based on pressure regulation can effectively mitigate speed inconsistencies caused by changes in friction between the template and guide rail, fluctuations in hydraulic oil temperature, or slight load unevenness, ensuring a smooth and stable follow-up process. It fundamentally avoids the risk of shearing of the material cake or impact load on the mold due to speed differences, while significantly reducing equipment operating noise and vibration.

[0041] Step S40: When the template is detected to have moved to the preset follow-out position, the follow-out drive of the hammer head is stopped, and the subsequent mold opening action is completed at a preset mold opening speed until the mold opening is completed.

[0042] When the template is detected to have moved to the preset follow-out position, the follow-out drive of the hammer head is stopped, and the subsequent mold opening action is completed at the preset mold opening speed until the mold opening is finished.

[0043] The real-time position of the moving template is continuously monitored using a high-precision linear displacement sensor, such as an optical or magnetic ruler. This sensor is directly mounted on the frame, and its reading head is mechanically coupled to the moving template, providing absolute or incremental position signals with micron-level resolution. The preset follow-out position L_follow_out, as one of the key process parameters, is determined and stored in the initial setup along with the target speed and target pressure. This position represents the endpoint of the stroke required for the hammer-assisted pushing of the template, typically set to a distance that allows the material cake to smoothly exit the pressure chamber and complete the initial mold opening.

[0044] The position comparison logic unit within the controller continuously compares the current position L_current of the template fed back by the sensor with L_follow_out. When the system determines that the condition L_current ≥ L_follow_out is met, it immediately generates a "follow-out in position" status flag signal. This signal triggers a state switch in the control sequence. First, for the hammer drive, the controller sends a closing command processed by a ramp function generator to its servo valve. This command does not instantly reduce the valve current to zero, but rather smoothly reduces the current to the value required to keep the hammer stationary or slightly backward within tens to hundreds of milliseconds according to an adjustable decreasing slope. This ramp deceleration method effectively avoids pressure shocks and pipeline vibrations caused by sudden changes in flow in the hydraulic system, achieving a gentle removal of the hammer's driving force.

[0045] As the hammer drive begins to decelerate, the control system seamlessly transfers control of the mold-opening cylinder. The flow control valve, previously used to limit the return oil flow to achieve speed tracking, has its setpoint significantly increased or directly switched to its maximum opening state, removing the manual restriction on the return oil. Simultaneously, the proportional relief valve, which was used to finely adjust the return oil back pressure for synchronization, has its control signal reset to a higher safety pressure value or directly switched to normally open mode, preventing it from actively interfering with the main circuit pressure. At this point, the return oil passage of the mold-opening cylinder returns to a low-resistance state.

[0046] Next, the control system retrieves the "normal mold opening speed" V_mold_normal, independently set for the subsequent mold opening stage, from the process parameter library. This speed is typically higher than the speed of the follow-up stage, aiming to improve mold opening efficiency. Based on V_mold_normal and the dimensional parameters of the mold opening cylinder, the controller recalculates and generates control signals for the main directional valve and speed regulating valve that control the active retraction of the mold opening cylinder. Driven by its own hydraulic pump station, the mold opening cylinder then actively and forcefully continues to pull the moving platen backward according to the new speed setting value V_mold_normal. The system continues to monitor the platen position until it reaches the final set "mold opening termination position." At this point, the controller cuts off the power supply to the mold opening cylinder and may trigger subsequent auxiliary actions such as ejection and spraying, marking the successful completion of the entire mold opening process, including the hammer follow-up auxiliary stage and the independent mold opening stage. This implementation ensures a clear division and smooth transition between functional stages, fully utilizing the equipment's efficiency for rapid mold opening after completing the necessary protective synchronous follow-up.

[0047] Furthermore, you can also view Figure 2 , Figure 2 This is a detailed schematic diagram of step S20 in the first embodiment, based on the shown... Figure 2 The step of controlling the return oil flow of the mold opening cylinder based on the target flow value, so that the hammer pushes the template to perform the mold opening action, includes S21~22: Step S21: Obtain the minimum speed value of the mold opening, and obtain the target flow rate value of the oil return path of the mold opening cylinder based on the minimum speed value; Step S22: Adjust the opening degree of the electrically controlled flow valve of the mold opening cylinder return oil circuit according to the target flow value to control the return oil flow of the mold opening cylinder.

[0048] In this embodiment, the minimum speed value for the mold opening action is determined. This minimum speed value is not a fixed constant, but exists as a configurable process parameter in the control system. Its value comes from two main sources: one is a default safety value preset by the equipment manufacturer based on the machine model and basic performance, which is usually set to ensure smooth start-up of the mold opening action and avoid crawling; the other is a specific value manually input and stored by the process engineer in the upper-level human-machine interface during the process debugging phase, based on the characteristics of the specific product being produced. This value may take into account the mold weight, guide rail friction, and special requirements for the smoothness of the initial mold opening stage. During execution, the minimum speed value, denoted as V_min, is first retrieved from the parameter memory. This value represents the minimum mold opening speed baseline achieved to ensure continuous motion in the initial stage of the hammer pushing the template.

[0049] After successfully acquiring V_min, the target flow rate is calculated. This calculation is based on the fundamental principle of hydraulic transmission, namely, the cylinder's movement speed is proportional to the flow rate of hydraulic oil flowing into or out of its chamber. Specifically, for the return oil path of the mold-opening cylinder, the relationship between its flow rate and the cylinder's retraction speed is determined by the effective working area of ​​the cylinder's rod chamber. The control system internally stores the precise geometric parameters of the mold-opening cylinder, especially its piston rod diameter and cylinder inner diameter. Through calculation, the effective pressure-bearing area A_rod of the rod chamber can be obtained. The target flow rate Q_target is determined by the product of the minimum speed value V_min and this effective area A_rod, i.e., Q_target = V_min × A_rod. This calculation process is completed in real time by the controller's arithmetic logic unit, ensuring that the obtained Q_target directly corresponds in a physical sense to the theoretical oil flow rate required to achieve V_min. The calculation result is temporarily stored in a fast access register for later retrieval.

[0050] The focus is on the physical realization of the calculated target flow rate value through an electrically controlled flow valve. The electrically controlled flow valve, installed on the return oil line of the rod chamber of the mold-opening cylinder, is typically a proportional flow valve or a high-frequency response servo valve. This valve receives analog voltage or current command signals from the controller, and its valve spool opening is proportional to the magnitude of the input signal, thereby achieving continuous and precise regulation of the flow rate. The flow control module integrated within the controller uses Q_target, calculated in step S21, as the setpoint.

[0051] The execution of the flow control module consists of two stages: initialization and closed-loop fine-tuning. During initialization, the controller calculates an initial, estimated control signal value (such as current I_initial) based on the parameters Q_target and the current system oil temperature (temperature affects oil viscosity and thus the flow coefficient) by consulting a pre-calibrated valve flow-opening-pressure drop characteristic curve or data table, and outputs it to the electrically controlled flow valve. The valve core then moves to the corresponding opening position, establishing a preliminary oil return path.

[0052] Due to factors such as load pressure fluctuations and oil temperature changes, it is difficult to maintain a precise constant flow rate over a long period relying solely on the initial opening setting. Therefore, the system typically enters a closed-loop regulation phase. This phase relies on a flow sensor installed downstream of the electronically controlled flow valve or integrated within the valve. This sensor monitors the instantaneous flow rate Q_actual through the return oil path in real time and feeds it back to the controller. The flow control module compares Q_actual with the target value Q_target to obtain the flow deviation ΔQ. By performing a proportional-integral operation on ΔQ, the controller generates a correction amount ΔI for the initial control signal. The final control signal applied to the electronically controlled flow valve is I_control = I_initial + ΔI. Through this closed-loop negative feedback mechanism, the system can dynamically adjust the valve opening to compensate for flow fluctuations caused by factors such as changes in return oil back pressure, thereby stably controlling the actual return oil flow rate Q_actual within a very small error range near the target flow rate value Q_target.

[0053] By precisely implementing the above process, the system constructs a constrained oil return path for the mold opening cylinder. This path allows the oil to be discharged at a flow rate strictly corresponding to the preset minimum mold opening speed. This ensures that the mold plate can start and move at a speed of no less than V_min under the push of the hammer, while effectively preventing the mold opening cylinder from "stalling" or "rushing" due to excessively fast oil return by limiting the maximum possible flow rate. This creates the necessary hydraulic boundary conditions for the hammer to drive the mold plate in a controllable initial mold opening action as the sole active power source, and is a key guarantee for realizing the core coordinated action of "pushing the mold plate with the hammer".

[0054] Furthermore, you can also view Figure 3 , Figure 3 This is a detailed process diagram of step S30 in the first embodiment, based on the shown... Figure 3 The step of controlling the return oil pressure of the mold opening cylinder by adjusting the opening degree of the pressure relief valve during the process of the hammer pushing the template includes S31~32: Step S31: Real-time acquisition of the actual mold opening speed and actual hammer head ejection speed of the template; Step S32: Calculate the speed difference between the actual hammer follow-out speed and the actual mold opening speed. Based on the comparison result of the speed difference and the preset speed difference threshold, adjust the opening degree of the pressure relief valve so that the mold opening speed is controlled by the push of the hammer.

[0055] Real-time speed acquisition and pressure relief valve regulation control based on speed differences rely on a high-precision sensing system deployed on the die-casting machine's motion mechanism. For acquiring the actual mold opening speed, incremental or absolute linear displacement sensors are typically installed on the moving mold platen or components rigidly connected to it. These sensors sample the real-time position coordinates of the mold platen at a constant high frequency (e.g., 1000 Hz). Upon receiving these discrete position signals, the controller calculates the instantaneous movement speed of the mold platen in each sampling period—the actual mold opening speed V_mold_actual—by performing a numerical differentiation algorithm, such as using a first-order backward differential or a more precise digital filter. This differentiation calculation process considers the accuracy of the sampling time interval and may introduce low-pass filtering to suppress high-frequency interference caused by mechanical vibration or signal noise, thereby obtaining a smooth and reliable speed estimate.

[0056] The actual follow-through speed of the hammerhead is acquired from the injection hammerhead itself. Another set of displacement sensors, mounted on the hammerhead guide rail or hydraulic cylinder, monitors the hammerhead's position in real time. Using the same numerical differentiation processing method, the controller calculates the instantaneous propulsion speed of the hammerhead, i.e., the actual follow-through speed V_punch_actual. To ensure strict synchronization of the two speed values ​​on the time axis, the displacement sampling signals used to calculate V_mold_actual and V_punch_actual must be read and processed by the same timed interrupt service routine of the controller, or a synchronous acquisition module with precise timestamps must be used to eliminate comparison errors caused by asynchronous sampling times. These two processed actual speed values ​​are continuously updated to the controller's shared data area.

[0057] The controller dynamically calculates the speed deviation and makes control decisions accordingly. Within each control cycle (e.g., 1 millisecond), the controller reads the latest V_punch_actual and V_mold_actual from the shared data area. Then, it calculates the instantaneous speed difference ΔV = V_punch_actual - V_mold_actual. This ΔV value has a clear physical meaning: a positive value indicates that the hammer's advancing speed is faster than the mold opening speed, with the mold movement lagging; a negative value indicates that the mold opening speed tends to exceed the hammer's advancing speed.

[0058] The calculated ΔV is not directly used for control, but needs to be compared with a preset speed difference threshold ΔV_threshold. This threshold is a small non-negative quantity set based on the system's mechanical characteristics, control stability requirements, and process experience. The comparison logic is as follows: If |ΔV| ≤ ΔV_threshold, the current mold opening speed and hammer speed are considered to be in good synchronization, and no adjustment to the pressure relief valve is needed; the current control signal can be maintained. If ΔV > ΔV_threshold, it indicates that the hammer speed is significantly faster than the mold plate speed, and the mold plate movement has failed to keep up with the hammer's push. In this case, the return oil back pressure of the mold opening cylinder needs to be reduced to lower its motion damping. The controller will generate an adjustment command to increase the opening of the pressure relief valve. Conversely, if ΔV < -ΔV_threshold, it indicates that the mold plate speed tends to lead, and the return oil back pressure needs to be increased to apply damping. The controller will generate an adjustment command to decrease the opening of the pressure relief valve.

[0059] The generation of adjustment commands is typically based on a proportional or proportional-integral control law. For example, when |ΔV| exceeds a threshold, the change in control output U, ΔU, is proportional to (|ΔV| - ΔV_threshold), and its direction (increase or decrease) is determined by the sign of ΔV. This threshold-based control strategy avoids frequent system actions under small, insignificant speed fluctuations, enhances the system's anti-interference capability, and can quickly and forcefully intervene to correct when the speed exceeds the allowable range, thereby ensuring that the mold opening speed is effectively "locked" to the hammer pushing speed, achieving controlled synchronous motion.

[0060] In addition, based on the above Figure 3 The content of step S32 shown, which involves adjusting the opening degree of the pressure relief valve based on the comparison result between the speed difference and the preset speed difference threshold, includes S32-1 to S32-2: Step S32-1: Obtain the control current corresponding to the speed difference, and calculate the current control signal based on the control current and the speed difference; Step S32-2: Control the opening degree of the pressure relief valve through the current control signal.

[0061] When generating and executing the pressure relief valve current control signal based on the speed difference, the focus is on converting the speed difference information into a current control signal that can directly drive the actuator (pressure relief valve). After confirming that adjustment is needed, the controller first calculates a basic control current demand value I_base based on the current speed difference ΔV (or the portion exceeding the threshold). This calculation process is implemented through a predefined or online self-tuning control function. The most common approach is to use a proportional relationship: I_base = Kp * (ΔV - sign(ΔV) * ΔV_threshold), where Kp is the proportional gain coefficient and sign is the sign function. This means that only the portion of the speed difference exceeding the threshold will produce a control effect, and the strength of the effect is proportional to the size of this portion. For higher precision control, a proportional-integral algorithm may also be used to incorporate the accumulated amount of historical deviations into the calculation to eliminate steady-state errors.

[0062] After obtaining the basic control current I_base, necessary signal processing and compensation are required to generate the final output. First, the system may apply an output limit to I_base to ensure its value is within the safe current range allowed by the pressure relief valve drive amplifier, preventing overload. Second, the static characteristics of the pressure relief valve itself need to be considered, such as its dead zone and saturation characteristics. The controller may internally store calibration data tables or fitting curves for the valve, used for nonlinear compensation of I_base, so that the final output current change corresponds more linearly to the change in valve spool opening. Furthermore, in some implementations, the calculation of the current control signal also needs to incorporate the feedback value of the current return oil pressure, forming an inner loop of a pressure-speed cascade control, so that the output current can more accurately achieve the expected pressure adjustment target. After the above calculations, limiting, and compensation, the final current control signal I_control used to control the current cycle is obtained.

[0063] The calculated digital current control signal I_control is physically applied to the pressure relief valve. The controller converts the digital value I_control into a corresponding analog voltage or current signal through its built-in digital-to-analog converter module or a dedicated analog output module. This analog signal is transmitted to the pressure relief valve's drive amplifier. The pressure relief valve here is typically a proportional relief valve, whose internal pilot-stage electromagnet coil or a force motor that directly drives the main valve core receives this analog current signal.

[0064] The magnitude of the current signal I_control directly determines the electromagnetic force acting on the proportional electromagnet. This electromagnetic force balances with the spring force and hydraulic pressure within the valve, thereby precisely setting the valve's overflow pressure or directly controlling the opening degree of the main valve core. When I_control increases, the electromagnetic force strengthens, pushing the valve core to open more easily or directly increasing the opening degree, resulting in a decrease in the set pressure of the pressure relief valve or an increase in its flow capacity, thus reducing the actual back pressure in the return oil circuit of the mold opening cylinder. Conversely, when I_control decreases, the set pressure of the pressure relief valve increases or the opening degree decreases, and the return oil back pressure rises accordingly. Through the closed-loop link constructed above, the difference signal ΔV reflecting the speed synchronization state can be quickly and accurately converted into real-time adjustment of the damping characteristics of the hydraulic circuit. That is, by continuously adjusting the opening degree of the pressure relief valve to change the return oil pressure, the fine-grained tracking control of the mold opening speed can be achieved, ensuring that it is always controlled by the push of the hammer.

[0065] Furthermore, based on the content described in the first or second embodiment above, the step of controlling the return oil pressure of the mold opening cylinder through the pressure relief valve includes: The actual pressure value of the rodless cavity of the mold opening cylinder is detected in real time by a pressure sensor, and the actual pressure value is compared with the target pressure to obtain the pressure deviation value. Based on the pressure deviation value, proportional-integral-differential calculations are performed to generate control commands for real-time control of the opening degree of the pressure relief valve. The control command controls the return oil pressure of the mold opening cylinder so that the actual pressure value follows the target pressure value.

[0066] In pressure relief valve control based on pressure closed loop to achieve return oil pressure tracking, accurate measurement of the pressure in the rodless chamber of the mold opening cylinder is crucial. In the hydraulic circuit, a high-dynamic-response pressure sensor is installed near the oil port of the rodless chamber of the mold opening cylinder or directly on its pressure line. This sensor typically employs piezoresistive or piezoelectric principles, enabling real-time detection of the hydraulic oil pressure within the chamber and converting it into a standard analog voltage or current signal. The controller continuously acquires this signal at a fixed high sampling frequency (e.g., 1kHz) through its analog input module, and after analog-to-digital conversion and digital filtering, obtains a stable and reliable actual pressure value P_actual in the rodless chamber of the mold opening cylinder. This pressure value directly reflects the magnitude of the back pressure generated by the mold opening cylinder to resist the retraction motion during the hammer's push of the mold plate.

[0067] After acquiring the actual pressure value, the control system compares it with the preset target pressure value P_target. This target pressure value P_target is the hammer follow-out target pressure acquired and stored in one embodiment of the claim, and its physical meaning is the maximum back pressure limit allowed to be applied to the rodless cavity of the mold-opening cylinder. Within each control cycle, the controller calculates the instantaneous pressure deviation value e(t) = P_target - P_actual. The sign and magnitude of this deviation value e(t) have clear meanings: when e(t) is positive, it indicates that the actual pressure has not reached the target upper limit and there is still a pressure margin; when e(t) is negative, it indicates that the actual pressure has exceeded the target limit and needs to be reduced immediately.

[0068] The core step in generating the real-time control of the pressure relief valve opening is to perform proportional-integral-derivative (PID) calculations based on the aforementioned pressure deviation value e(t). The controller's PID control algorithm module receives a continuous sequence of e(t). The proportional calculation part directly multiplies the current e(t) by the proportional gain coefficient Kp, generating a control action proportional to the instantaneous deviation, aiming to respond quickly to pressure fluctuations. The integral calculation part accumulates and sums e(t) over time, then multiplies it by the integral gain coefficient Ki to eliminate steady-state pressure deviations, ensuring the accuracy of long-term pressure control and preventing the actual pressure value from deviating from the target value for a long time. The derivative calculation part calculates the rate of change of e(t), multiplies it by the derivative gain coefficient Kd, and uses it to predict the pressure change trend, achieving the effect of proactive adjustment and suppression of pressure oscillations. After the results of the three calculations are linearly superimposed and processed by output limiting, a preliminary control output u_pid(t) is generated. This u_pid(t) is a dimensionless or intermediate variable with specific physical units, and its magnitude and sign directly correspond to the degree of control effort required to correct the current pressure deviation.

[0069] The aforementioned control quantity u_pid(t) needs to be further converted into a physical control command that can directly drive the pressure relief valve. Based on the electrical characteristics of the pressure relief valve (usually a proportional relief valve), the controller maps u_pid(t) to a corresponding analog current command I_command. This mapping process may include linear scaling, dead-zone compensation, and nonlinear correction based on the valve characteristic curve. The final generated current control command I_command is applied to the proportional electromagnet of the pressure relief valve through the controller's analog output channel. The magnitude of the current I_command determines the electromagnetic force acting on the valve core, thereby dynamically setting the opening pressure of the pressure relief valve or directly adjusting its valve opening.

[0070] By executing the aforementioned current control commands, the pressure relief valve adjusts its state in real time. When the actual pressure P_actual approaches or exceeds the target pressure P_target (i.e., e(t) is zero or negative), the controller output I_command will increase the opening degree of the pressure relief valve or decrease the opening pressure setpoint, thereby providing an additional release path for the hydraulic oil in the rodless chamber of the mold opening cylinder, allowing the pressure P_actual in that chamber to be released and decrease. Conversely, when P_actual is much lower than P_target, the controller output I_command will cause the pressure relief valve to tend to close or increase its opening pressure setpoint, reducing release and allowing the back pressure P_actual to rise. Through this closed negative feedback loop composed of a pressure sensor, a controller PID algorithm, and an electro-hydraulic proportional pressure relief valve, the system can achieve dynamic and precise closed-loop regulation of the pressure in the rodless chamber of the mold opening cylinder. Its ultimate control objective is to ensure that the actual pressure value P_actual closely follows the change of the target pressure value P_target, suppressing pressure fluctuations within the allowable range. This ensures that the hammer pushes the template in a controlled back pressure environment at the hydraulic level, which is one of the key guarantee mechanisms for achieving smooth and controlled synchronous mold opening.

[0071] Furthermore, you can also view Figure 4 , Figure 4 This is a detailed schematic diagram of step S40 in the first embodiment, based on the shown... Figure 4 The step of stopping the hammer's follow-out drive when the template is detected to have moved to a preset follow-out position includes S41~42: Step S41: The current position of the template is detected in real time by a position sensor located on the template movement path; Step S42: Calculate the position difference between the current position and the preset follow-out position coordinates. When the position difference is determined to be within the preset position error range, it is determined that the follow-out position has been reached.

[0072] In position-sensor-based positioning and comparison-based positioning determination, a high-precision linear displacement measurement system installed along the template's movement path is relied upon. This system typically employs a non-contact measurement principle, such as a magnetic scale or optical scale. The magnetic scale band of the magnetic scale is fixed parallel to the template's movement direction to the fixed template or body of the die-casting machine, while its reading head is rigidly mounted on the moving template, moving synchronously with it. The optical scale system consists of an optical scale and a reading head, installed in a similar manner. Regardless of the type used, the sensor possesses a measurement range matching the machine's mold-opening stroke, and a resolution far exceeding control accuracy requirements (typically reaching the micrometer level). After system power-on initialization or mold replacement, a reference point calibration may be necessary to establish the correspondence between the sensor's mechanical zero point and the control system's logical coordinate zero point.

[0073] Position sensors output raw signals representing the current position at extremely high frequencies (typically kilohertz to megahertz, depending on the sensor type and interface), such as phase difference square waves or serial data. The controller's dedicated high-speed counting module or position interface card receives and decodes these signals in real time. The decoding process converts the sensor's raw pulses or codes into corresponding linear position data L_current_raw. Due to potential electrical noise or mechanical vibration in the field environment, this raw data may contain glitches. Therefore, the controller typically performs digital filtering on L_current_raw, such as using a moving average filter or a first-order low-pass digital filter, to smooth the data, suppress high-frequency interference, and ultimately obtain a stable and reliable template current position value L_current, which is stored in the process image area for control logic to access. This data acquisition and processing chain ensures the real-time performance and accuracy of the position feedback.

[0074] The precise determination of position arrival is achieved through software logic. The controller reads the pre-set follow-up position coordinate value L_follow_out from the parameter storage area. This value is input by the operator during the process setting stage and represents the expected endpoint position to be reached during the hammer-assisted pushing stage. In each control cycle (e.g., 1ms), the control program calculates the algebraic difference ΔL = L_follow_out - L_current between the current position L_current and the target position L_follow_out.

[0075] The determination of whether "arrival" has been achieved is not triggered at the exact moment ΔL equals zero, but rather by introducing a preset position error range ±ε. This error range ε ​​is a positive number, and its setting must comprehensively consider the sensor resolution, system tracking error, mechanical backlash, and control response delay. The purpose of setting this range is to avoid the system frequently triggering and exiting the "in position" state near the target point due to minor overshoot or measurement fluctuations, thereby ensuring the stability and reliability of state switching.

[0076] The decision logic is as follows: The system continuously monitors the value of ΔL. When the conditions ΔL ≤ +ε and ΔL ≥ -ε are met, i.e., when the current position L_current falls within the interval centered at L_follow_out and with a width of ε, the logic unit inside the controller immediately sets a flag bit (Flag_Arrival) indicating "follow-out position reached". The transition edge of this flag bit (e.g., from 0 to 1) serves as a deterministic condition signal for triggering the hammer stop and mold opening control mode switching in subsequent steps. This comparison method based on the error band is more practical in engineering than absolute equality judgment, effectively absorbing the inherent small uncertainties and disturbances of the system, and achieving robust position endpoint detection.

[0077] Furthermore, you can also view Figure 5 , Figure 5 This is a schematic diagram of another detailed process of step S40 in the first embodiment, based on the shown... Figure 5 The step of completing the subsequent mold opening actions at a preset mold opening speed until the mold opening is completed includes S43~44: Step S43: Output a stop command to the proportional valve or servo valve that drives the hammer head; In step S44, simultaneously, according to the preset independent speed setting value, a corresponding control signal is output to the proportional directional valve controlling the mold opening cylinder to control the speed of the mold opening action.

[0078] In the independent speed control of hammer head drive stop and mold opening, the "follow-out position reached" flag must be confirmed valid before execution. The goal of this step is to safely and smoothly terminate the hammer head's advancing motion. The controller outputs a specific stop command to the electro-hydraulic proportional valve or servo valve driving the hammer head. This command is not simply a cut-off of the control signal, but typically a command decay process processed by a ramp function.

[0079] The controller has a preset stop ramp time T_decay or ramp slope. When a stop command is received, the controller reads the current control signal value (e.g., current I_current) output to the hammer drive valve and, starting from this value, linearly or exponentially decays the signal to a predetermined safety holding value I_hold within the T_decay time according to the set ramp rule. This safety holding value may be zero (corresponding to valve closure) or a small positive value used to maintain a slight contact force between the hammer and the material cake or to maintain its position during the mold opening stage, depending on the process requirements. This ramp decay process is implemented in real time through the controller's analog output module. This ensures a smooth decrease in the hydraulic cylinder pressure driving the hammer and a smooth drop in hammer speed to zero, thereby avoiding hydraulic shock, pipeline vibration, and potential rigid impact on mechanical connecting parts caused by sudden valve closure.

[0080] It starts synchronously but executes independent control logic, aiming to achieve a seamless transfer of control over the mold opening action. The controller calls the speed value V_mold_independent, which is pre-set for the "independent mold opening stage," from the process parameter library. This speed value is typically independent of the target speed of the follow-up stage, aiming to achieve rapid and efficient completion of the remaining mold opening stroke.

[0081] Simultaneously, the control system will reconfigure the control circuit of the mold opening cylinder. Previously, the control signals of valves (such as electrically controlled flow valves and proportional relief valves) used to limit return oil flow and regulate back pressure during the follow-up phase are reset to an invalid state or set to a safe mode allowing full flow, thus releasing their constraint on the movement of the mold opening cylinder. At the same time, the main proportional directional valve controlling the retraction of the mold opening cylinder piston rod is activated to speed control mode.

[0082] The controller, based on the independent mold opening speed setpoint V_mold_independent, the size parameters of the mold opening cylinder, and the current system pressure, uses its internal speed control algorithm to calculate and generate a control signal for the main proportional directional valve in real time. This signal determines the opening degree and direction of the proportional directional valve, thereby precisely controlling the flow rate into the rodless chamber and out of the rod chamber of the mold opening cylinder, driving the cylinder to retract at a uniform speed of V_mold_independent. This control process is an independent closed-loop or open-loop speed control, no longer affected by the coupling effect of the hammer speed. Through the coordinated execution of steps S43 and S44, the system achieves a smooth switch between the power source and the control mode: the hammer power is smoothly removed, and the mold opening cylinder quickly and accurately takes over the subsequent mold opening action, opening the mold to its final position at the set independent speed, thus completing the entire mold opening sequence.

[0083] Reference Figure 6 , Figure 6 This is a flowchart illustrating a second embodiment of the control method for a two-plate die-casting machine according to this application. In this embodiment, after the step of stopping the hammer's follow-up drive when the mold plate is detected to have moved to a preset follow-up position, and completing the subsequent mold opening action at a preset mold opening speed until the mold opening is completed, the method further includes steps S50-70: Step S50: Control the die-casting machine to switch to the preset empty cycle test mode; Step S60: During the empty cycle test mode, real-time running data is acquired during the process of the hammer pushing the template to the follow-out position. The real-time running data includes actual pressure change data, actual speed change data, and mold opening vibration intensity data.

[0084] Upon entering the empty cycle test mode, the control system will temporarily disable interlock signals with peripheral equipment such as the furnace, pouring machine, and spraying machine, and ensure that there is no material cake in front of the injection punch. The system executes the mold closing and injection empty strokes sequentially according to the currently loaded production process parameters. When the process reaches the stage of hammer ejection and mold opening synchronization, the controller calls the same control logic as in normal production. Based on the previously set target pressure, target speed, and control parameters of each valve, it drives the hammer and controls the mold opening cylinder to return oil, simulating the actual ejection process. This test cycle can be set to be executed continuously multiple times to obtain statistically more stable data.

[0085] The system focuses on synchronously acquiring multi-dimensional real-time operational data during the hammer follow-out phase of the test cycle. The data acquisition system consists of a cluster of sensors deployed at key locations and a high-speed data recording module. Actual pressure change data is primarily acquired through dynamic pressure sensors installed in the hammer propulsion oil circuit and the return oil circuit of the rodless chamber of the mold opening cylinder. These sensors record transient pressure changes at a high sampling rate (e.g., 10kHz). Actual velocity change data originates from high-resolution displacement sensors installed on the hammer and moving mold platen; instantaneous velocity values ​​are obtained by real-time differentiation of the displacement signals. Mold opening vibration intensity data is measured using vibration acceleration sensors (e.g., triaxial accelerometers) installed on the moving mold platen or key parts of the frame to quantify the level of mechanical impact.

[0086] The analog signals from all the aforementioned sensors are connected to a synchronous data acquisition card to ensure strict synchronization of the sampling clocks of all channels, thus avoiding analysis errors caused by time differences. The acquisition card digitizes the analog signals and transmits them in real-time via a high-speed bus (such as EtherCAT or PCIe) to a dedicated data buffer in the host industrial computer or controller. In one test cycle, all data from the start of the hammer's movement to the template reaching the follow-up position is completely recorded, forming a multi-dimensional real-time running data sequence with timestamps. This data sequence is temporarily stored in non-volatile memory for subsequent analysis.

[0087] In the core process of achieving intelligent self-optimization of the system, after completing a preset number of empty loop tests and accumulating sufficient data, the built-in optimization algorithm automatically starts. This algorithm first analyzes the collected real-time operating data, extracting key features such as: whether the pressure peak exceeds a safety threshold, the steady-state error and overshoot of velocity tracking, the time to reach the target position, and the root mean square value or peak value of vibration acceleration. Based on these features, the algorithm constructs one or more objective functions, such as minimizing the difference between the pressure peak and the target pressure, minimizing the velocity tracking error, and minimizing the vibration intensity as optimization objectives.

[0088] Subsequently, the optimization algorithm operates within a safe parameter optimization space. This space is initialized with the currently set target pressure value P_target, target velocity value V_target, PID control parameters (Kp_f, Ki_f, Kd_f) of the electrically controlled flow valve, and PID control parameters (Kp_r, Ki_r, Kd_r) of the pressure relief valve. The optimization algorithm can employ strategies such as gradient descent, simplex method, or genetic algorithm, iteratively adjusting the aforementioned set of parameters by establishing a relationship model between parameter perturbations and the objective function response. In each iteration, the system may predict performance changes through software simulation models, or rapidly execute one or several empty loop tests under safe, minor parameter modifications to obtain actual response data.

[0089] When the optimization algorithm finds a new set of parameters that significantly improves the objective function (e.g., under satisfied constraints, the overall performance index improves by more than a set percentage compared to the initial parameters), this set of parameters will be automatically locked by the system. The controller will update these optimized parameter values ​​to the corresponding control loop, replacing the original set values. The system may prompt the operator for confirmation or automatically enter a new round of verification empty loop testing to confirm the optimization effect. Through the closed loop formed by steps S50 to S70, the goal of learning from production or testing and automatically optimizing key control parameters is achieved, enabling the die-casting machine to adaptively adjust to better follow-up synchronization performance, reducing reliance on manual experience-based adjustments, and continuously maintaining low vibration levels and high operational stability.

[0090] It should be noted that the above examples are only for understanding this application and do not constitute a limitation on the control method of the two-plate die-casting machine of this application. Any simple modifications based on this technical concept are within the protection scope of this application.

[0091] This application provides a control device for a two-plate die-casting machine. The control device for the two-plate die-casting machine includes: at least one processor; and a memory communicatively connected to the at least one processor; wherein the memory stores instructions executable by the at least one processor, and the instructions are executed by the at least one processor to enable the at least one processor to perform the control method for the two-plate die-casting machine in the above embodiment 1.

[0092] The following is for reference. Figure 7 The diagram illustrates a structural schematic of a control device suitable for implementing the embodiments of this application for a two-plate die-casting machine. The control device for the two-plate die-casting machine in the embodiments of this application may include, but is not limited to, mobile terminals such as mobile phones, laptops, digital radio receivers, PDAs (Personal Digital Assistants), PADs (Portable Application Description), etc., and fixed terminals such as digital TVs, desktop computers, etc. Figure 7 The control equipment of the two-plate die-casting machine shown is merely an example and should not impose any limitations on the functionality and scope of use of the embodiments of this application.

[0093] like Figure 7As shown, the control device of the two-plate die-casting machine may include a processing unit 1001 (e.g., a central processing unit, a graphics processing unit, etc.), which can perform various appropriate actions and processes according to the program stored in the read-only memory (ROM) 1002 or the program loaded from the storage device 1003 into the random access memory (RAM) 1004. The RAM 1004 also stores various programs and data required for the operation of the control device of the two-plate die-casting machine. The processing unit 1001, ROM 1002, and RAM 1004 are interconnected via a bus 1005. An input / output (I / O) interface 1006 is also connected to the bus. Typically, the following systems can be connected to I / O interface 1006: input devices 1007 including, for example, touchscreens, touchpads, keyboards, mice, image sensors, microphones, accelerometers, gyroscopes, etc.; output devices 1008 including, for example, liquid crystal displays (LCDs), speakers, vibrators, etc.; storage devices 1003 including, for example, magnetic tapes, hard disks, etc.; and communication devices 1009. Communication device 1009 allows the control equipment of the two-plate die-casting machine to communicate wirelessly or wiredly with other devices to exchange data. Although the control equipment of the two-plate die-casting machine with various systems is shown in the figure, it should be understood that it is not required to implement or possess all the systems shown. More or fewer systems can be implemented or possessed alternatively.

[0094] Specifically, according to the embodiments disclosed in this application, the processes described above with reference to the flowcharts can be implemented as computer software programs. For example, embodiments disclosed in this application include a computer program product comprising a computer program carried on a computer-readable medium, the computer program containing program code for performing the methods shown in the flowcharts. In such embodiments, the computer program can be downloaded and installed from a network via a communication device, or installed from storage device 1003, or installed from ROM 1002. When the computer program is executed by processing device 1001, it performs the functions defined in the methods of the embodiments disclosed in this application.

[0095] The control device for the two-plate die-casting machine provided in this application adopts the control method for the two-plate die-casting machine in the above embodiments, which can solve the technical problem of uncontrollable pressure when the hammer head follows out in existing die-casting machines. Compared with the prior art, the beneficial effects of the control device for the two-plate die-casting machine provided in this application are the same as the beneficial effects of the control method for the two-plate die-casting machine provided in the above embodiments, and other technical features in the control device for the two-plate die-casting machine are the same as the features disclosed in the method of the previous embodiment, and will not be repeated here.

[0096] It should be understood that the various parts disclosed in this application can be implemented using hardware, software, firmware, or a combination thereof. In the description of the above embodiments, specific features, structures, materials, or characteristics can be combined in any suitable manner in one or more embodiments or examples.

[0097] The above description is merely a specific embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.

[0098] This application provides a storage medium, which is a computer-readable storage medium having computer-readable program instructions (i.e., a computer program) stored thereon, which are used to execute the control method of the two-plate die-casting machine in the above embodiments.

[0099] The computer-readable storage medium provided in this application may be, for example, a USB flash drive, but is not limited to, electrical, magnetic, optical, electromagnetic, infrared, or semiconductor systems, devices, or any combination thereof. More specific examples of computer-readable storage media may include, but are not limited to: electrical connections with one or more wires, portable computer disks, hard disks, random access memory (RAM), read-only memory (ROM), erasable programmable read-only memory (EPROM or flash memory), optical fiber, portable compact disk read-only memory (CD-ROM), optical storage devices, magnetic storage devices, or any suitable combination thereof. In this embodiment, the computer-readable storage medium may be any tangible medium containing or storing a program that can be used by or in conjunction with an instruction execution system, system, or device. The program code contained on the computer-readable storage medium may be transmitted using any suitable medium, including but not limited to: wires, optical cables, RF (Radio Frequency), etc., or any suitable combination thereof.

[0100] The aforementioned computer-readable storage medium may be included in the control equipment of the two-plate die-casting machine; or it may exist independently and not be assembled into the control equipment of the two-plate die-casting machine.

[0101] The aforementioned computer-readable storage medium carries one or more programs. When the aforementioned one or more programs are executed by the control device of the two-plate die-casting machine, the control device of the two-plate die-casting machine implements the technical content of the control method embodiment of the two-plate die-casting machine as shown above.

[0102] Computer program code for performing the operations of this application can be written in one or more programming languages ​​or a combination thereof, including object-oriented programming languages ​​such as Java, Smalltalk, and C++, and conventional procedural programming languages ​​such as the "C" language or similar programming languages. The program code can be executed entirely on the user's computer, partially on the user's computer, as a standalone software package, partially on the user's computer and partially on a remote computer, or entirely on a remote computer or server. In cases involving remote computers, the remote computer can be connected to the user's computer via any type of network—including a Local Area Network (LAN) or a Wide Area Network (WAN)—or can be connected to an external computer (e.g., via the Internet using an Internet service provider).

[0103] The flowcharts and block diagrams in the accompanying drawings illustrate the architecture, functionality, and operation of possible implementations of systems, methods, and computer program products according to various embodiments of this application. In this regard, each block in a flowchart or block diagram may represent a module, segment, or portion of code containing one or more executable instructions for implementing a specified logical function. It should also be noted that in some alternative implementations, the functions indicated in the blocks may occur in a different order than those indicated in the drawings. For example, two consecutively indicated blocks may actually be executed substantially in parallel, and they may sometimes be executed in reverse order, depending on the functions involved. It should also be noted that each block in the block diagrams and / or flowcharts, and combinations of blocks in the block diagrams and / or flowcharts, can be implemented using a dedicated hardware-based system that performs the specified function or operation, or using a combination of dedicated hardware and computer instructions.

[0104] The modules described in the embodiments of this application can be implemented in software or hardware. The names of the modules do not necessarily limit the functionality of the unit itself.

[0105] The readable storage medium provided in this application is a computer-readable storage medium that stores computer-readable program instructions (i.e., a computer program) for executing the control method of the above-described two-plate die-casting machine, which can solve the technical problem of uncontrollable pressure when the hammer head follows through in existing die-casting machines. Compared with the prior art, the beneficial effects of the computer-readable storage medium provided in this application are the same as the beneficial effects of the control method of the two-plate die-casting machine provided in the above embodiments, and will not be repeated here.

Claims

1. A control method of a two-plate die casting machine, characterized by, Includes the following steps: Obtain the target speed and target pressure of the die-casting machine hammerhead following the ejection; After the injection action is completed, the hammer head is driven by the target speed and target pressure, and the return oil flow of the mold opening cylinder is controlled based on the target flow value, so that the hammer head pushes the template to perform the mold opening action; During the process of the hammer pushing the template, the return oil pressure of the mold opening cylinder is controlled by adjusting the opening degree of the pressure relief valve; When the template is detected to have moved to the preset follow-out position, the follow-out drive of the hammer head is stopped, and the subsequent mold opening action is completed at a preset mold opening speed until the mold opening is finished.

2. The control method of a two-plate die casting machine according to claim 1, characterized in that, The step of controlling the return oil flow of the mold-opening cylinder based on the target flow value, so that the hammer pushes the template to perform the mold-opening action, includes: Obtain the minimum opening speed value, and based on the minimum speed value, obtain the target flow rate value of the oil return path of the opening cylinder; The opening degree of the electrically controlled flow valve in the return oil circuit of the mold opening cylinder is adjusted by the target flow value to control the return oil flow of the mold opening cylinder.

3. The control method of a two-plate die casting machine according to claim 1, characterized in that, The step of controlling the return oil pressure of the mold opening cylinder by adjusting the opening degree of the pressure relief valve during the process of the hammer pushing the template includes: Real-time acquisition of the actual mold opening speed and actual hammer ejection speed of the template; Calculate the speed difference between the actual hammer follow-out speed and the actual mold opening speed. Based on the comparison result of the speed difference with a preset speed difference threshold, adjust the opening degree of the pressure relief valve so that the mold opening speed is controlled by the push of the hammer.

4. The control method of a two-plate die casting machine according to claim 3, characterized in that, The step of adjusting the opening of the pressure relief valve based on the comparison result between the speed difference and the preset speed difference threshold includes: Obtain the control current corresponding to the speed difference, and calculate the current control signal based on the control current and the speed difference; The opening degree of the pressure relief valve is controlled by the current control signal.

5. The control method of a two-plate die-casting machine according to any one of claims 1 or 3, characterized in that, The step of controlling the return oil pressure of the mold opening cylinder through the pressure relief valve includes: The actual pressure value of the rodless cavity of the mold opening cylinder is detected in real time by a pressure sensor, and the actual pressure value is compared with the target pressure to obtain the pressure deviation value. Based on the pressure deviation value, proportional-integral-differential calculations are performed to generate control commands for real-time control of the opening degree of the pressure relief valve. The control command controls the return oil pressure of the mold opening cylinder so that the actual pressure value follows the target pressure value.

6. The control method of a two-plate die casting machine according to Claim 1, characterized in that, The step of stopping the hammer's follow-out drive when the template is detected to have moved to a preset follow-out position includes: The current position of the template is detected in real time by a position sensor located on the template's movement path; Calculate the position difference between the current position and the preset follow-out position coordinates. When the position difference is determined to be within the preset position error range, it is determined that the follow-out position has been reached.

7. The control method of a two-plate die casting machine according to Claim 1, characterized in that, The step of completing subsequent mold-opening actions at a preset mold-opening speed until the mold-opening is completed includes: Output a stop command to the proportional valve or servo valve that drives the hammerhead; At the same time, according to the preset independent speed setting value, the corresponding control signal is output to the proportional directional valve that controls the mold opening cylinder to take over the speed control of the mold opening action.

8. The control method of a two-plate die casting machine according to Claim 1, characterized in that, After the step of stopping the hammer's follow-up drive when the template is detected to have moved to a preset follow-up position, and completing the subsequent mold opening action at a preset mold opening speed until the mold opening is completed, the method further includes: Control the die-casting machine to switch to the preset empty cycle test mode; During the empty cycle test mode, real-time running data is acquired as the hammer pushes the template to the follow-out position. The real-time running data includes actual pressure change data, actual speed change data, and mold opening vibration intensity data.

9. A control device for a two-plate die-casting machine, characterized in that, The control device of the two-plate die-casting machine stores a computer program, which, when executed by a processor, implements the control method of the two-plate die-casting machine according to any one of claims 1-8.

10. A storage medium, characterized in that, The storage medium stores a computer program, which, when executed by a processor, implements the control method for the two-plate die-casting machine according to any one of claims 1-8.

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