A novel Y-axis servo hydraulic counterweight method and system for boring machines

Abstract

The present invention discloses a novel Y-axis servo hydraulic counterweight method and system for a boring machine, which belongs to the field of boring processing technology, and includes real-time monitoring of the movement speed of the Y-axis to obtain a speed value; generating a pressure analog quantity according to the speed value; and adjusting the required output pressure value according to the pressure analog quantity. The present invention adjusts the pressure of the hydraulic oil in real time according to the actual movement speed of the Y-axis, thereby dynamically adjusting the counterweight effect, ensuring that the load of the Y-axis remains balanced during the movement process, improving the stability of the Y-axis movement and the processing accuracy, and effectively improving the overall processing efficiency.

Description

Technical Field

[0001] The invention relates to the technical field of boring processing, and in particular to a novel Y-axis servo hydraulic counterweight method and system for a boring machine. Background Art

[0002] During boring, the motion accuracy and efficiency of the Y-axis (lateral moving axis) are critical to machining quality. In order to ensure the stability and accuracy of the Y-axis during movement, a hydraulic counterweight system is usually required to offset the effect of gravity on the Y-axis movement. The hydraulic counterweight system can effectively reduce the load fluctuation of the Y-axis during movement by providing a certain balance force, thereby improving machining accuracy.

[0003] However, traditional hydraulic counterweight systems usually use constant pressure for counterweighting. This method cannot adjust the counterweight effect in real time when the Y-axis movement speed changes. When the motor speed increases, the motor torque will decrease. If the hydraulic counterweight still maintains a constant pressure, it will cause the Y-axis load to be unbalanced, which will affect the processing accuracy. Therefore, the limitations of traditional hydraulic counterweight systems in dealing with rapid movement of the Y-axis are becoming increasingly prominent. With the continuous improvement of processing accuracy and efficiency requirements in the field of boring processing, traditional hydraulic counterweight systems can no longer meet current production needs. Summary of the invention

[0004] To solve the above problems, the present invention provides a new servo hydraulic counterweight method and system for the Y-axis of a boring machine, which dynamically adjusts the counterweight effect by adjusting the pressure of the hydraulic oil in real time according to the actual movement speed of the Y-axis, ensuring that the load of the Y-axis remains balanced during the movement, thereby improving the stability and processing accuracy of the Y-axis movement and effectively improving the overall processing efficiency.

[0005] The above objectives can be achieved through the following solutions:

[0006] A novel Y-axis servo hydraulic counterweight method for a boring machine includes real-time monitoring of the movement speed of the Y-axis to obtain a speed value; generating a pressure simulation value according to the speed value; and adjusting a required output pressure value according to the pressure simulation value.

[0007] Furthermore, generating the pressure analog quantity according to the speed value includes: calculating a hydraulic pressure value according to the speed value; and generating the pressure analog quantity according to the hydraulic pressure value.

[0008] Furthermore, the calculation of the hydraulic pressure value according to the speed value includes: establishing a control equation for characterizing the relationship between the hydraulic pressure value and the speed value, and for the hydraulic pressure value ,have:

[0009] ;

[0010] In the formula, represents the speed value, Indicates the density of the liquid required for hydraulic pressure, Represents the effective working area of ​​the required hydraulic cylinder piston; the speed value is input into the control equation to obtain the hydraulic pressure value.

[0011] Furthermore, the step of adjusting the required output pressure value according to the pressure analog value further includes: collecting a hydraulic flow value; and switching a control gear of the output pressure value according to the hydraulic flow value.

[0012] Further, the control gear for switching the output pressure value according to the hydraulic flow value includes: determining whether the absolute value of the hydraulic flow value is less than a preset first threshold value; if so, switching to a high gear for hydraulic control; if not, determining whether the absolute value of the hydraulic flow value is less than a preset second threshold value; if so, switching to a middle gear for hydraulic control; if not, switching to a low gear for hydraulic control.

[0013] Furthermore, the switching to a high gear for hydraulic control includes: decoding the pressure analog quantity to obtain a current required pressure value; adding the current required pressure value to a preset adjustment value to obtain a required pressure value for the high gear; generating a high gear pulse signal of a corresponding number and frequency according to the required pressure value for the high gear; and adjusting the pulse signal for the high gear to obtain an output pressure value for the high gear.

[0014] Furthermore, the switching to the mid-range position for hydraulic control includes: decoding the pressure analog quantity to obtain the current required pressure value; generating a mid-range position pulse signal of corresponding quantity and frequency according to the current required pressure value; and adjusting the output pressure value of the mid-range position according to the mid-range position pulse signal.

[0015] Furthermore, the switching to a low gear for hydraulic control includes: decoding the pressure analog quantity to obtain a current required pressure value; subtracting the current required pressure value from the adjustment value to obtain a low gear required pressure value; generating a low gear pulse signal of corresponding quantity and frequency according to the low gear required pressure value; and adjusting the low gear pulse signal to obtain an output pressure value of the low gear.

[0016] Furthermore, the method further includes: calculating the difference between the required pressure value corresponding to the first threshold and the actual required pressure value to obtain a first difference; calculating the difference between the required pressure value corresponding to the second threshold and the actual required pressure value to obtain a second difference; calculating the difference between the first threshold and the second threshold to obtain a third difference; calculating the average value of the first threshold and the second threshold to obtain a flow mean; using the first difference, the second difference, the third difference, the flow mean and the current hydraulic flow value to calculate an adjustment value, for the adjustment value ,have:

[0017] ;

[0018] In the formula, is a constant coefficient, is the first difference, is the second difference, is the third difference, is the current hydraulic flow value, is the flow mean.

[0019] Based on the same inventive concept, the present invention also provides a new type of boring machine Y-axis servo hydraulic counterweight system, the system comprising: a speed monitoring module, used to monitor the movement speed of the Y-axis in real time to obtain a speed value; a servo control module, connected to the speed monitoring module, used to generate a pressure analog value according to the speed value; a servo, connected to the servo control module, used to adjust the required output pressure value according to the pressure analog value.

[0020] Compared with the prior art, the present invention has the following advantages:

[0021] 1. The present invention realizes dynamic counterweighting by real-time monitoring of the movement speed of the Y-axis and adjusting the pressure of the hydraulic oil in real time according to the speed value; this dynamic adjustment can ensure that the load of the Y-axis remains balanced during the movement process, avoiding the problem of load imbalance caused by speed changes;

[0022] 2. Since the pressure of the hydraulic oil can be adjusted in real time, the present invention effectively reduces the load fluctuation of the Y-axis during movement, thereby improving the processing accuracy; at the same time, the dynamic counterweight also enhances the stability of the Y-axis movement, making the processing process more stable and reliable;

[0023] 3. By optimizing the hydraulic counterweight system, the vibration and error during movement are reduced, so that the Y-axis can work more efficiently during movement, reducing the extended processing time and increased energy consumption caused by load imbalance, and the overall processing efficiency has been significantly improved;

[0024] 4. The present invention optimizes the stress state of the counterweight cylinder by further adjusting the output pressure value, which helps to reduce the loss of the counterweight cylinder and extend its service life.

[0025] Other features and advantages of the present invention will be described in the following description, and partly become apparent from the description, or understood by practicing the present invention. The purpose and other advantages of the present invention can be realized and obtained by the structures pointed out in the description, claims and drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0026] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0027] Figure 1 The present invention is a flowchart of a novel Y-axis servo hydraulic counterweight method for a boring machine according to an embodiment of the present invention.

[0028] Figure 2 The present invention is a flowchart of a novel Y-axis servo hydraulic counterweight method for a boring machine according to an embodiment of the present invention.

[0029] Figure 3 It is a structural diagram of a new type of boring machine Y-axis servo hydraulic counterweight system. DETAILED DESCRIPTION

[0030] In order to make the purpose, technical solution and advantages of the embodiments of the present invention clearer, the technical solution in the embodiments of the present invention will be clearly and completely described below in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0031] Reference Figure 1 An embodiment of the present invention proposes a novel servo hydraulic counterweighting method for the Y-axis of a boring machine, which realizes dynamic counterweighting by real-time monitoring and adjusting the movement speed of the Y-axis and the pressure of the hydraulic oil, thereby improving the processing accuracy, stability and efficiency, and has strong adaptability and intelligent control characteristics.

[0032] The novel boring machine Y-axis servo hydraulic counterweight method of this embodiment specifically includes:

[0033] Monitor the movement speed of the Y-axis in real time and obtain the speed value;

[0034] Specifically, this step is the basis of the entire process. It uses specific sensors or monitoring devices to capture the movement speed of the Y-axis (i.e., the lateral movement axis of the boring machine) in real time, and converts this speed into a numerical value that can be processed by subsequent steps; it can also calculate the movement speed of the Y-axis by monitoring the rotation speed of the motor output shaft.

[0035] For example, suppose the Y axis is performing a complex boring task, and its speed is constantly changing. At this time, the monitoring device will continuously monitor the movement of the Y axis. For example, within one second, the Y axis may accelerate from 0 to 10m / s, and then decelerate to 5m / s; these speed changes will be captured in real time and converted into corresponding values, such as 0, 10, 5, etc., for use in subsequent steps.

[0036] generating a pressure analog value according to the velocity value;

[0037] Specifically, after obtaining the Y-axis movement speed value, this value will be used to calculate the required hydraulic pressure value, and then this pressure value will be converted into a pressure analog value, which can be understood and executed.

[0038] For example, when the speed of the Y-axis accelerates from 0 to 10m / s, the required hydraulic pressure value at this time will be calculated according to the preset control equation (which takes into account factors such as speed, liquid density and force area); assuming that this pressure value is 100pa, then this pressure value will be converted into an analog quantity, such as a specific voltage or current value, which can be received and processed.

[0039] The required output pressure value is adjusted according to the pressure analog quantity.

[0040] Specifically, after the pressure analog value is obtained, the required output pressure value will be adjusted according to the analog value to ensure that the Y-axis always maintains the counterweight balance during the movement.

[0041] For example, when an analog quantity representing a pressure value of 100 Pa is received, it will immediately adjust the required output pressure to 100 Pa; in this way, no matter how the speed of the Y-axis changes, the load balance of the Y-axis can be maintained by adjusting the hydraulic pressure in real time, thereby improving the processing accuracy and efficiency; these three steps together constitute a closed-loop control, which can adjust the required output pressure value in real time according to the movement speed of the Y-axis, thereby ensuring the stability and accuracy of the processing process.

[0042] Further, generating a pressure analog value according to the velocity value includes:

[0043] Calculate the hydraulic pressure value according to the speed value;

[0044] Specifically, the required hydraulic pressure value is calculated based on the real-time monitored Y-axis movement speed value using a preset control equation; this control equation usually takes into account multiple factors such as speed, liquid density, and force area to ensure that the calculated hydraulic pressure value can accurately reflect the load requirements during the Y-axis movement process.

[0045] The hydraulic pressure value is converted into a pressure analog quantity.

[0046] Specifically, after the hydraulic pressure value is calculated, it is necessary to convert this pressure value into an analog quantity that can be understood and executed; this analog quantity is usually a voltage or current signal, and its magnitude is proportional to the hydraulic pressure value.

[0047] For example, assuming that the calculated hydraulic pressure value is 100 Pa, there will be a conversion rule or converter inside to convert this pressure value into a specific voltage or current signal; for example, it can be stipulated that a pressure of 1 Pa corresponds to a voltage of 1 mV, so a pressure of 100 Pa corresponds to a voltage of 100 mV; in this way, this voltage signal can be sent to adjust the required output pressure value to reach 100 Pa; the process of generating a pressure analog value based on a speed value includes two sub-steps of calculating the hydraulic pressure value and converting the pressure analog value. These two sub-steps together ensure that the required output pressure value can be adjusted in real time according to the movement speed of the Y-axis, thereby maintaining the counterweight balance of the Y-axis and improving processing accuracy and efficiency.

[0048] Further, the calculating the hydraulic pressure value according to the speed value includes:

[0049] Establish a control equation for characterizing the relationship between the hydraulic pressure value and the speed value. ,have:

[0050] ;

[0051] In the formula, represents the speed value, Indicates the density of the liquid required for hydraulic pressure, Indicates the effective working area of ​​the required hydraulic cylinder piston;

[0052] The speed value is input into the control equation to obtain the hydraulic pressure value.

[0053] For example, assume that the Y-axis movement speed value is 5m / s, the liquid density is 1000kg / m³, and the force area is 0.1m²; substitute these values ​​into the control equation for calculation, and get the hydraulic pressure value of 1250N. In this way, the hydraulic pressure value at the given speed, liquid density and force area is 1250N; this value will then be converted into a pressure analog value and used to adjust the required output pressure value; ensure that the required hydraulic pressure value can be accurately calculated according to the Y-axis movement speed, thereby providing a basis for the subsequent adjustment of the required output pressure value.

[0054] Furthermore, if Figure 2 As shown, the output pressure value required for adjusting the pressure analog quantity further includes:

[0055] Collect hydraulic flow value;

[0056] Specifically, it is necessary to collect the hydraulic flow value of the hydraulic counterweight system in real time; the hydraulic flow value refers to the volume of fluid passing through the hydraulic system per unit time, which is one of the important indicators for measuring the working efficiency and performance of the hydraulic system; collecting the hydraulic flow value usually requires the use of special flow sensors or flow meters, which can monitor the fluid flow in the hydraulic system in real time and transmit the collected data.

[0057] The control gear of the output pressure value is switched according to the hydraulic flow value.

[0058] Specifically, after obtaining the hydraulic flow value, the gear of the hydraulic control will be switched according to this value; the gear of the hydraulic control is usually related to parameters such as the opening degree of the hydraulic valve and the speed of the hydraulic pump, and different gears correspond to different hydraulic output pressures and flows; by switching the gear of the hydraulic control, the output pressure value and flow of the hydraulic counterweight system can be accurately controlled, thereby meeting the load requirements under different working conditions.

[0059] Furthermore, if Figure 2 As shown, the control gear position of switching the output pressure value according to the hydraulic flow value includes:

[0060] Determining whether the absolute value of the hydraulic flow value is less than a preset first threshold;

[0061] If so, switch to high gear for hydraulic control;

[0062] Specifically, the hydraulic flow value of the current hydraulic counterweight system is obtained and its absolute value is calculated; then this absolute value is compared with a preset first threshold; the first threshold is a lower flow value. When the absolute value of the hydraulic flow value is less than this threshold, it usually means that the load demand is very small, and it is possible to switch to a high gear for hydraulic control to reduce energy consumption and improve response speed.

[0063] Exemplarily, assuming that the first threshold is set to 5 L / min, if the system detects that the absolute value of the hydraulic flow value is 3 L / min, which is less than the first threshold, then it will switch to a high gear for hydraulic control.

[0064] If not, determining whether the absolute value of the hydraulic flow value is less than a preset second threshold;

[0065] Specifically, if the absolute value of the hydraulic flow value is greater than or equal to the first threshold, the next step of judgment will be entered; in this step, the absolute value of the hydraulic flow value will be compared with the preset second threshold; the second threshold is an intermediate value between the first threshold and the high flow value. When the absolute value of the hydraulic flow value is less than the second threshold, it means that the load demand is moderate and the hydraulic control can be switched to the mid-range position to balance energy consumption and performance.

[0066] For example, assuming that the second threshold is set to 20 L / min, if the system detects that the absolute value of the hydraulic flow value is 15 L / min, which is less than the second threshold but greater than the first threshold, then it will switch to the mid-range position for hydraulic control.

[0067] If so, switch to the middle position for hydraulic control;

[0068] If not, switch to low gear for hydraulic control.

[0069] Specifically, if the absolute value of the hydraulic flow value is not less than the second threshold, it will switch to a low gear for hydraulic control; this usually means that the load demand is very large and more hydraulic pressure and flow are needed to meet the demand, and the low gear can provide a larger output pressure and flow range.

[0070] For example, if the absolute value of the monitored hydraulic flow value is 30L / min, which is greater than the second threshold value, the hydraulic control will be switched to a low gear to ensure that sufficient hydraulic pressure and flow can be provided to meet the load requirements; the process of switching the hydraulic control gear according to the hydraulic flow value is a logical judgment process based on threshold comparison; by setting different thresholds, it can automatically switch to the appropriate hydraulic control gear according to the size of the hydraulic flow value, thereby achieving precise control of the output pressure value and flow of the hydraulic counterweight system to meet the load requirements under different working conditions.

[0071] Further, the switching to a high gear for hydraulic control includes:

[0072] Decoding the pressure analog quantity to obtain the current required pressure value;

[0073] Specifically, the movement speed of the Y-axis is monitored in real time, and the current required pressure value is calculated based on the speed value; this required pressure value changes dynamically and is adjusted as the movement speed of the Y-axis changes.

[0074] Add the current demand pressure value to the preset adjustment value to obtain the high-speed demand pressure value;

[0075] Specifically, when the current hydraulic flow value is less than the first threshold value in the high gear, it means that the current hydraulic flow value is low and a faster response speed is required to maintain stability; at this time, the adjustment range of the pressure simulation quantity can be increased, that is, based on the current demand pressure value calculated according to the speed value, an additional adjustment amount is added to improve the response speed of the system.

[0076] Generate high-speed gear pulse signals of corresponding quantity and frequency according to the required pressure value of the high-speed gear;

[0077] Specifically, the received pressure analog quantity is decoded. Since the pressure analog quantity is usually a voltage or current signal, and its size is proportional to the hydraulic pressure value, the decoding process is to convert this signal back to the corresponding hydraulic pressure value, that is, the demand pressure value; this demand pressure value represents the output pressure that the hydraulic counterweight system is expected to achieve; after receiving the high-speed demand pressure value, a pulse signal of the corresponding number and frequency will be generated according to the preset algorithm; these pulse signals are the key to controlling the hydraulic system actuators (such as hydraulic pumps, proportional valves, etc.), and their number and frequency determine the output state of the actuators and the output pressure of the hydraulic system.

[0078] The output pressure value of the high-speed position is obtained by adjusting the pulse signal of the high-speed position.

[0079] Specifically, after receiving the pulse signal of the high gear, the actuator will adjust its output state according to the requirements of the signal, thereby changing the output pressure value of the hydraulic system to reach the required pressure value of the high gear; this process is real-time and accurate, ensuring the load balance and processing accuracy of the Y-axis during movement.

[0080] Exemplarily, in order to meet the working pressure requirement in the high gear, the preset adjustment value is 5MPa; assuming that at a certain moment, the movement speed of the Y-axis accelerates, through real-time monitoring and calculation, the current required pressure value is obtained to be 10MPa; 10MPa is added to 5MPa, and the required pressure value for the high gear is 15MPa; after receiving the required pressure value of 15MPa, a pulse signal with a frequency of 50Hz and a duty cycle of 60% is generated, and these signals are sent to the control unit of the hydraulic pump; after receiving the pulse signal, the hydraulic pump adjusts the output state according to the requirements of the signal, so that the output pressure value of the hydraulic system quickly rises to 15MPa; in this way, it successfully switches to the high gear for hydraulic control, ensuring the load balance and processing accuracy of the Y-axis during rapid movement.

[0081] Further, the switching to the middle gear position for hydraulic control includes:

[0082] Decoding the pressure analog quantity to obtain the current required pressure value;

[0083] Specifically, the received pressure analog quantity is decoded. Since the pressure analog quantity is usually a voltage or current signal, and its size is proportional to the hydraulic pressure value, the decoding process is to convert this signal back to the corresponding hydraulic pressure value, that is, the required pressure value; this required pressure value represents the output pressure that the hydraulic counterweight system is expected to achieve.

[0084] Generate a mid-range pulse signal of corresponding quantity and frequency according to the current demand pressure value;

[0085] Specifically, after the required pressure value is obtained, a pulse signal of corresponding quantity and frequency will be generated according to this value; the pulse signal is a discrete signal, and its quantity and frequency can accurately control the opening and closing of the hydraulic valve, thereby achieving precise adjustment of the required output pressure; in this process, a pulse width modulation (PWM) or pulse frequency modulation (PFM) algorithm is usually used to convert the required pressure value into a corresponding pulse signal.

[0086] Adjust the output pressure value of the mid-range position according to the pulse signal of the mid-range position.

[0087] Specifically, the required output pressure value is adjusted according to the generated pulse signal; this process is usually achieved by controlling the opening and closing of the hydraulic valve. When the number and frequency of the pulse signals increase, the opening time of the hydraulic valve will become longer, thereby increasing the required output pressure value; conversely, when the number and frequency of the pulse signals decrease, the opening time of the hydraulic valve will become shorter, and the output pressure value will also decrease accordingly; in this way, the required output pressure value can be accurately controlled to meet the load requirements during the Y-axis movement.

[0088] For example, assuming that the voltage signal corresponding to the received pressure analog quantity is 5 volts, the required pressure value obtained after decoding is 200 Pa; a PWM algorithm is set internally to convert the required pressure value of 200 Pa into a pulse signal with a frequency of 1000 Hz and a duty cycle of 50%; then, this pulse signal is sent to the control valve of the hydraulic counterweight system; the control valve adjusts its opening and closing time according to the frequency and duty cycle of the pulse signal, thereby achieving precise control of the required output pressure value; finally, the required output pressure value stabilizes at around 200 Pa, meeting the load requirements during the Y-axis movement; ensuring that the required output pressure value can be accurately adjusted according to the movement speed and load requirements of the Y-axis, thereby improving processing accuracy and efficiency.

[0089] Further, the switching to a low gear position for hydraulic control includes:

[0090] Decoding the pressure analog quantity to obtain the current required pressure value;

[0091] Specifically, the speed monitoring module monitors the movement speed of the Y-axis in real time, and calculates the current required hydraulic pressure value according to the preset control equations and parameters (such as liquid density, force area, etc.), that is, the current demand pressure value

[0092] Subtract the current required pressure value from the adjustment value to obtain the required pressure value for the low gear;

[0093] Specifically, when the current hydraulic flow value is greater than or equal to the second threshold value in the low gear, it means that the current hydraulic flow value is high and may face a large load pressure; at this time, the adjustment range of the pressure simulation value can be appropriately reduced, that is, based on the preliminary calculation of the current demand pressure value, an adjustment amount is reduced to protect the equipment from excessive pressure shocks.

[0094] Generate low-gear pulse signals of corresponding quantity and frequency according to the required pressure value of the low-gear;

[0095] Specifically, the received pressure analog quantity is decoded. Since the pressure analog quantity is usually a voltage or current signal, and its size is proportional to the hydraulic pressure value, the decoding process is to convert this signal back to the corresponding hydraulic pressure value, that is, the required pressure value; this required pressure value represents the output pressure that the hydraulic counterweight system is expected to achieve; after receiving the required pressure value of the low gear, a pulse signal of the corresponding number and frequency will be generated according to the preset algorithm; since the output pressure required at the low gear is smaller, the number and frequency of the generated pulse signals will also be reduced accordingly.

[0096] The output pressure value of the low gear is obtained by adjusting the pulse signal of the low gear.

[0097] Specifically, after receiving the low-gear pulse signal, the actuator (such as a hydraulic valve, a proportional valve, etc.) will adjust its output state according to the signal requirements, thereby reducing the output pressure value of the hydraulic system to meet the low-gear working requirements.

[0098] For example, assume that during a certain processing process, the movement speed of the Y-axis suddenly increases, causing the detected hydraulic flow value to rise rapidly and exceed the second threshold, so it switches to low-gear control; through real-time monitoring and calculation, the current required pressure value is 20MPa; the preset adjustment value is 5MPa, therefore, the current required pressure value 20MPa is subtracted from the adjustment value 5MPa, and the low-gear required pressure value is 15MPa; according to the low-gear required pressure value of 15MPa, a pulse signal with a frequency of 30Hz and a duty cycle of 40% is generated; after receiving these pulse signals, the actuator gradually reduces the output pressure value of the hydraulic system, and finally stabilizes at about 15MPa; in this way, it successfully switches to low gear for hydraulic control, which not only meets the current work needs, but also effectively protects the equipment from the risk of excessive pressure shock; the hydraulic output pressure is flexibly adjusted according to the actual load conditions to ensure the stability and processing accuracy of the Y-axis during movement, while extending the service life of the equipment.

[0099] Furthermore, the method further comprises:

[0100] Calculate the difference between the required pressure value corresponding to the first threshold and the actual required pressure value to obtain a first difference;

[0101] Calculate the difference between the required pressure value corresponding to the second threshold and the actual required pressure value to obtain a second difference;

[0102] Calculating a difference between the first threshold and the second threshold to obtain a third difference;

[0103] Calculate the average of the first threshold and the second threshold to obtain a flow mean;

[0104] The adjustment value is calculated by using the first difference, the second difference, the third difference, the flow mean and the current hydraulic flow value. ,have:

[0105] ;

[0106] In the formula, is a constant coefficient, is the first difference, is the second difference, is the third difference, is the pressure calibration value of the current hydraulic flow value, is the pressure calibration value of the flow mean.

[0107] Specifically, in order to control the output pressure more accurately, it is often necessary to dynamically adjust the gear of the hydraulic control according to the current hydraulic flow value; and in order to achieve more detailed adjustment, a method for calculating the adjustment value can be introduced. The method is based on a comprehensive consideration of multiple parameters, including the difference between the demand pressure value corresponding to the preset first threshold and the actual required pressure value (first difference), the difference between the demand pressure value corresponding to the second threshold and the actual required pressure value (second difference), the difference between the first threshold and the second threshold (third difference), the average value of the first threshold and the second threshold (flow mean) and the current hydraulic flow value; the pressure calibration value of the current hydraulic flow is compared with the pressure calibration value of the flow mean, and the difference is adjusted according to the first difference, the second difference and the third difference to obtain a dynamic adjustment value; this adjustment value is used to fine-tune the initially calculated demand pressure value in high or low gear to more accurately meet the actual load requirements.

[0108] Based on the same inventive concept, Figure 3 As shown, the present invention also provides a novel Y-axis servo hydraulic counterweight system for a boring machine, the system comprising:

[0109] The speed monitoring module is used to monitor the movement speed of the Y-axis in real time and obtain the speed value;

[0110] A servo control module, connected to the speed monitoring module, for generating a pressure analog value according to the speed value;

[0111] A servo is connected to the servo control module and is used to adjust a required output pressure value according to the pressure analog quantity.

[0112] Furthermore, the servo control module includes: a pressure calculation unit and an analog quantity conversion unit; wherein:

[0113] The pressure calculation unit is connected to the speed monitoring module and is used to calculate the hydraulic pressure value according to the speed value;

[0114] The analog quantity conversion unit is connected to the pressure calculation unit and is used to convert the hydraulic pressure value into a pressure analog quantity.

[0115] Furthermore, the server comprises: a pressure requirement decoding unit, a pulse signal generating unit and a pressure adjustment execution unit; wherein:

[0116] The pressure demand decoding unit is connected to the analog quantity conversion unit and is used to decode the pressure analog quantity to obtain the required pressure value;

[0117] The pulse signal generating unit is connected to the pressure requirement decoding unit and is used to generate a pulse signal of corresponding quantity and frequency according to the required pressure value;

[0118] The pressure adjustment execution unit is connected to the pulse signal generation unit and is used to adjust the required output pressure value according to the pulse signal.

[0119] Furthermore, the system further comprises:

[0120] A hydraulic flow value collection module is used to collect hydraulic flow values;

[0121] The gear switching control module is connected to the hydraulic flow value acquisition module and the pressure adjustment execution unit respectively, and is used to switch the control gear of the output pressure value according to the hydraulic flow value; wherein the gear switching control module selects to switch to a high gear, a middle gear or a low gear for hydraulic control according to the comparison result of the absolute value of the hydraulic flow value with a preset first threshold value and a second threshold value.

[0122] It should be noted that the electrical connection between the above-mentioned units does not necessarily mean the connection between the lines, and the indirect connection mode can be applied to the embodiments of the present invention as long as the purpose of the present invention is achieved. The above is only an exemplary embodiment of the present invention and cannot be used to limit the scope of the present invention.

[0123] That is, any equivalent changes and modifications made according to the teachings of the present invention are still within the scope of the present invention. After considering the disclosure of the specification and the truth of practice, those skilled in the art will easily think of other embodiments of the present invention. This application is intended to cover any variation, use or adaptive change of the present invention, which follows the general principles of the present invention and includes common knowledge or customary technical means in the art that are not described in the present invention.

Claims

1. A novel boring machine Y-axis servo hydraulic counterweight method, characterized in that: The method comprises: Monitor the movement speed of the Y-axis in real time and obtain the speed value; Establish a control equation for characterizing the relationship between the hydraulic pressure value and the speed value. ,have: ； In the formula, represents the speed value, Indicates the density of the liquid required for hydraulic pressure, Indicates the effective working area of ​​the required hydraulic cylinder piston; Inputting the speed value into the control equation to obtain the hydraulic pressure value; generating a pressure analog value according to the hydraulic pressure value; Collecting a hydraulic flow value, and determining whether an absolute value of the hydraulic flow value is less than a preset first threshold; If yes, switch to a high gear and use the pressure analog value to perform hydraulic control; If not, determining whether the absolute value of the hydraulic flow value is less than a preset second threshold; If the absolute value of the hydraulic flow value is less than a preset second threshold value, switching to the middle gear position and using the pressure analog value for hydraulic control; If the absolute value of the hydraulic flow value is greater than or equal to a preset second threshold, the gear is switched to a low gear and hydraulic control is performed using the pressure analog value.

2. According to the novel boring machine Y-axis servo hydraulic counterweight method of claim 1, it is characterized in that: The switching to a high gear for hydraulic control comprises: Decoding the pressure analog quantity to obtain the current required pressure value; Add the current demand pressure value to the preset adjustment value to obtain the high-speed demand pressure value; Generate high-speed gear pulse signals of corresponding quantity and frequency according to the required pressure value of the high-speed gear; The output pressure value of the high-speed position is obtained by adjusting the pulse signal of the high-speed position.

3. The novel Y-axis servo hydraulic counterweight method of a boring machine according to claim 2 is characterized in that: The switching to the middle gear position for hydraulic control includes: Decoding the pressure analog quantity to obtain the current required pressure value; Generate a mid-range pulse signal of corresponding quantity and frequency according to the current demand pressure value; Adjust the output pressure value of the mid-range position according to the pulse signal of the mid-range position.

4. The novel Y-axis servo hydraulic counterweight method of a boring machine according to claim 3 is characterized in that: The switching to the low gear position for hydraulic control includes: Decoding the pressure analog quantity to obtain the current required pressure value; Subtract the current required pressure value from the adjustment value to obtain the required pressure value for the low gear; Generate low-gear pulse signals of corresponding quantity and frequency according to the required pressure value of the low-gear; The output pressure value of the low gear is obtained by adjusting the pulse signal of the low gear.

5. The novel Y-axis servo hydraulic counterweight method of a boring machine according to claim 4 is characterized in that: The method further comprises: Calculate the difference between the required pressure value corresponding to the first threshold and the actual required pressure value to obtain a first difference; Calculate the difference between the required pressure value corresponding to the second threshold and the actual required pressure value to obtain a second difference; Calculating a difference between the first threshold and the second threshold to obtain a third difference; Calculate the average of the first threshold and the second threshold to obtain a flow mean; The adjustment value is calculated by using the first difference, the second difference, the third difference, the flow mean and the current hydraulic flow value. ,have: ; In the formula, is a constant coefficient, is the first difference, is the second difference, is the third difference, is the pressure calibration value of the current hydraulic flow value, is the pressure calibration value of the flow mean.

6. A novel Y-axis servo hydraulic counterweight system for a boring machine, applied to a novel Y-axis servo hydraulic counterweight method for a boring machine as claimed in any one of claims 1 to 5, characterized in that: The system comprises: The speed monitoring module is used to monitor the movement speed of the Y-axis in real time and obtain the speed value; A servo control module, connected to the speed monitoring module, for generating a pressure analog value according to the speed value; A servo is connected to the servo control module and is used to adjust a required output pressure value according to the pressure analog quantity.

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