A parameter optimization method and device for a new energy engineering machinery hydraulic operation system

Abstract

This application discloses a parameter optimization method and device for a hydraulic operating system of new energy construction machinery, relating to the field of energy-saving technology for construction machinery. The method optimizes the dimensional parameters of the linkage mechanism. Steps S1 and S2 precisely select key dimensional parameters affecting the force transmission ratio, constructing a mechanical structure parameter space through grid scanning. Step S3 calculates the actual work done by the hydraulic cylinder based on each set of parameter samples, linking geometric dimensions with dynamic operation energy consumption. Step S4 introduces a full-link energy flow model to accurately calculate the difference between electrical energy consumption and actual work done, quantifying system energy loss. Step S5 uses traversal optimization to select the optimal parameter combination. This method overcomes the limitations of traditional "fragmented" design, actively guiding the working trajectories of the hydraulic pump and motor to concentrate in the high-efficiency zone through the coordinated optimization of mechanical structure parameters, hydraulic system operating points, and motor efficiency distribution, significantly reducing ineffective energy consumption during dynamic operation and significantly improving the overall machine energy efficiency.

Description

Technical Field

[0001] This application relates to the field of energy-saving technology for construction machinery, and in particular to a parameter optimization method and device for a hydraulic operating system of new energy construction machinery. Background Technology

[0002] With the deepening implementation of the "dual carbon" goals, developing low-emission new energy construction machinery has become an inevitable direction for the industry's transformation and upgrading. Electrification, as a core technological path to reduce carbon emissions from construction machinery, has already been applied in products such as electric loaders. However, limited by current battery energy density and cost, electric construction machinery generally faces bottlenecks such as short operating time and limited operational efficiency. Until a fundamental breakthrough is achieved in battery technology, systematically improving the overall energy efficiency of the machine is key to extending its operating range and enhancing its market competitiveness.

[0003] Improving energy efficiency is crucial for the development of new energy construction machinery. This directly impacts the duration and economic efficiency of a single charge, and is fundamental to promoting large-scale electrification and achieving carbon reduction goals in the industry. Currently, most research focuses on improving the efficiency of key components such as motors, hydraulic pumps, and valves, or on partial optimization of overall machine energy management strategies. This approach often suffers from the drawback of treating mechanical actuators, hydraulic transmission systems, and electric drive systems as independent subsystems in a "separate" design. This traditional "serialized" design method fails to comprehensively consider the coupling effect of the structural parameters and transmission characteristics of the linkage mechanism on the hydraulic system's operating point and the motor load. This results in the hydraulic system deviating from its high-efficiency zone for extended periods during actual dynamic operation, generating significant unnecessary energy losses and hindering further improvements in overall energy efficiency. Summary of the Invention

[0004] The purpose of this application is to provide a parameter optimization method and device for a hydraulic operating system of new energy engineering machinery, which can solve the above-mentioned problems.

[0005] The embodiments of this application are implemented as follows: Firstly, this application provides a parameter optimization method for a hydraulic operating system of new energy engineering machinery, used to optimize the dimensional parameters of the linkage mechanism of the hydraulic operating system. The hydraulic operating system includes a frame support, a bucket, a linkage mechanism connecting the frame support and the bucket, a hydraulic cylinder that drives the linkage mechanism, and an electric drive system that drives the hydraulic cylinder. The above parameter optimization method includes steps S1 to S5, wherein S1, S2, etc. are only step identifiers, and the execution order of the method does not necessarily follow the numerical order from smallest to largest. For example, step S2 can be executed first and then step S1, and this application does not impose any restrictions.

[0006] S1, Select the linkage mechanism size parameters that affect the force transmission ratio of the hydraulic operating system as the parameters to be optimized.

[0007] S2 defines the range of values ​​and the step size of the value change for the dimensional parameters of the linkage mechanism, and records each value within the defined range as a single parameter sample.

[0008] S3, calculate the actual work done by the boom hydraulic cylinder under the preset working conditions based on each set of parameter samples.

[0009] S4, calculate the difference between the power consumption of the electric drive system and the actual work done under the preset working condition, and use it as the energy loss of the hydraulic operation system.

[0010] S5. Among the various parameter samples, the target parameter sample corresponding to the lowest energy loss is selected as the optimal linkage mechanism size parameter.

[0011] It is understood that steps S1 to S5 of this application optimize the linkage mechanism dimensional parameters of the hydraulic operating system of new energy engineering machinery, which can fundamentally break through the limitations of the traditional "fragmented" design method, realize the deep synergistic matching of the three major subsystems of mechanical, hydraulic and electrical systems, and significantly improve the overall energy efficiency. Specifically, steps S1 and S2 construct a global mechanical structure parameter space by accurately selecting key dimensional parameters (such as the first and second spacing) that affect the system's force transmission ratio and performing grid scanning on their value range and step size; step S3 calculates the actual work done by the hydraulic cylinder under preset working conditions based on each set of parameter samples, thereby associating the abstract geometric dimensions with specific dynamic operating energy consumption; step S4 further introduces the full-link energy flow model of the electric drive system, accurately calculates the difference between electrical energy consumption and actual work done, and quantifies the system energy loss under the "mechanical-electrical-hydraulic" coupling effect; step S5 selects the optimal parameter combination that minimizes energy loss through traversal optimization. This series of steps optimizes the mechanical structure parameters in conjunction with the hydraulic system's operating point and the motor's efficiency distribution, actively guiding the hydraulic pump and motor's operating trajectory to concentrate in their high-efficiency zone. This significantly reduces ineffective energy consumption during dynamic operations, effectively extending the machine's range under current battery technology conditions, and improving the economy and environmental friendliness of construction machinery.

[0012] It is understandable that optimizing the linkage mechanism dimensional parameters of the hydraulic operating system of new energy engineering machinery according to steps S1 to S5 of this application can fundamentally break through the limitations of the traditional "fragmented and serial" design method, achieve deep synergistic matching of the three major subsystems of mechanical, hydraulic and electrical systems, and significantly improve the overall energy efficiency level of the machine. This optimization method changes the previous one-sided approach of only improving the efficiency of components or local control strategies by incorporating mechanical structural parameters into the global optimization scope. Its core lies in constructing a full-link energy flow analysis model from mechanical force transmission characteristics to the distribution of hydraulic system working points and then to motor load characteristics. By traversing and optimizing the key dimensional parameters of the linkage mechanism, it can actively guide the hydraulic pump to densely distribute its working point trajectory in its high-efficiency zone during actual dynamic operation, while making the motor's working point better coincide with its own high-efficiency zone, thereby greatly reducing the ineffective energy consumption and inefficient energy consumption caused by factor system mismatch. The optimal parameter combination finally selected can systematically improve the cumulative energy efficiency of the hydraulic operating system under typical working conditions. This not only directly reduces the energy consumption per unit of operation of the whole machine, but also effectively extends the driving time of new energy construction machinery under the conditions of limited battery energy density and cost. It also provides practical technical support for the large-scale electrification transformation of the industry, and has significant economic benefits and carbon reduction value.

[0013] In an optional embodiment of this application, the linkage mechanism includes a boom, which is hinged between the frame support and the bucket. The boom hydraulic cylinder is hinged between the frame support and the boom and is configured to push the boom to lift the bucket under the drive of the electric drive system.

[0014] In an optional embodiment of this application, the hinge point between the boom and the frame support is denoted as the fulcrum, the hinge point between the boom hydraulic cylinder and the frame support is denoted as the first hinge point, the hinge point between the boom hydraulic cylinder and the boom is denoted as the second hinge point, the distance between the first hinge point and the fulcrum is denoted as the first distance, and the distance between the second hinge point and the fulcrum is denoted as the second distance. Step S1 includes: selecting the first distance and the second distance, which affect the force transmission ratio of the hydraulic working system, as parameters to be optimized.

[0015] It is understandable that the first and second spacing directly determine the force transmission ratio curve of the linkage mechanism, that is, the relationship between the ratio of the boom hydraulic cylinder driving force and the bucket load force as the lifting height changes. The shape of the force transmission ratio curve has a decisive impact on the overall machine energy efficiency: if the force transmission ratio is not designed properly, the hydraulic cylinder will bear excessively high load peaks or drastically fluctuating loads at different lifting stages, causing the hydraulic pump to be forced to frequently operate in the inefficient zone, resulting in a large amount of energy loss; at the same time, this load fluctuation will also be transmitted to the drive motor, causing its operating point to deviate from the efficient zone. Therefore, by optimizing the first and second spacing, the force transmission ratio curve can be optimized, matching the hydraulic cylinder load characteristics with the efficiency distribution of the hydraulic pump and motor, actively guiding the working trajectory of the hydraulic pump and motor to their efficient zone, thereby reducing ineffective energy consumption from the source.

[0016] In an optional embodiment of this application, step S2 includes steps S21 to S24.

[0017] S21, define a first value range and a first value change step size for the first spacing, and define a second value range and a second value change step size for the second spacing.

[0018] S22, within the first value range, the first spacing value is selected sequentially in ascending order according to the step size of the first value change.

[0019] S23, after selecting the first spacing value each time, within the range of the second value, the second spacing value is selected sequentially in ascending order according to the step size of the second value change.

[0020] S24, record each selected first spacing value and second spacing value as a single set of parameter samples.

[0021] It is understandable that steps S21 to S24 construct a parameter sample set covering the global design space by setting the value range and variation step size for the first and second spacings respectively, and traversing the values ​​using a nested loop. The beneficial effects of this method are as follows: First, by limiting the value range, the optimization region can be focused on the geometrically feasible range in engineering, avoiding invalid searches; second, by setting a reasonable variation step size, a balance can be achieved between computational accuracy and optimization efficiency, capturing subtle changes near the optimal parameter without excessively increasing the computational burden due to an excessively small step size; finally, the use of a nested loop traversal method ensures that all possible combinations of the two parameters to be optimized are taken into consideration, forming a complete parameter sample space, laying a comprehensive and systematic data foundation for subsequent optimization, and avoiding the risk of missing the global optimal solution due to local searches.

[0022] In an optional embodiment of this application, step S3 includes steps S31 to S35.

[0023] S31, based on the first spacing value and the second spacing value in each set of parameter samples, calculate the force transmission ratio curve corresponding to the parameter sample. The horizontal axis of the force transmission ratio curve is the bucket height displacement, and the vertical axis of the force transmission ratio curve is the ratio of the boom driving force of the boom hydraulic cylinder to the bucket load force of the bucket.

[0024] S32, calculate the boom driving force curve under the preset working condition using the force ratio curve. The horizontal axis of the boom driving force curve is time, and the vertical axis of the boom driving force curve is the boom driving force. The preset working condition is to lift the preset bucket load weight according to the preset bucket height displacement curve. The horizontal axis of the bucket height displacement curve is time, and the vertical axis is the bucket height displacement.

[0025] S33, obtain the extension length of the boom hydraulic cylinder fed back by the displacement sensor, and obtain the hydraulic cylinder extension curve. The horizontal axis of the hydraulic cylinder extension curve is time, and the vertical axis of the hydraulic cylinder extension curve is the extension length of the boom hydraulic cylinder.

[0026] S34, multiply the corresponding points of the boom driving force curve and the hydraulic cylinder extension curve to obtain the actual work curve of the boom hydraulic cylinder under the preset working condition. The horizontal axis of the actual work curve is time, and the vertical axis of the actual work curve is the actual work value.

[0027] S35, determine the actual work value corresponding to the completion of the preset working condition based on the actual work curve.

[0028] It is understandable that steps S31 to S35 establish a complete calculation link from geometric parameters to actual work done, accurately linking abstract mechanical dimensions with specific energy consumption indicators. First, step S31 determines the force transmission ratio curve based on the first and second gaps, revealing the mechanical transmission characteristics of the mechanism under different geometric parameters. Step S32, combined with preset working conditions, transforms the static force transmission ratio into a dynamic driving force curve, making the calculation closely resemble the actual operation process. Step S33 introduces the hydraulic cylinder extension length fed back by a displacement sensor, ensuring the accuracy of the kinematic data. Step S34 accurately calculates the actual work done by the hydraulic cylinder at each moment by integrating the product of driving force and displacement. Step S35 finally summarizes the total work done to complete the entire working condition. This series of steps realizes the quantitative mapping of mechanical structural parameters to the load characteristics of the hydraulic system, providing an accurate mechanical work benchmark for subsequent energy loss calculations, and is a key foundation for evaluating the energy efficiency performance of different parameter schemes.

[0029] In an optional embodiment of this application, the electric drive system includes a battery, an inverter, a motor, a hydraulic pump, an oil tank, and a proportional directional valve. The battery supplies power to the motor through the inverter. The motor drives the hydraulic pump to draw oil from the oil tank and transmits it to the rodless chamber of the boom hydraulic cylinder through the proportional directional valve, pushing the piston rod of the boom hydraulic cylinder to extend, thereby pushing the boom to lift the bucket. The oil in the rod chamber of the boom hydraulic cylinder returns to the oil tank through the proportional directional valve.

[0030] As can be understood, the battery acts as an energy source, converting direct current (DC) to alternating current (AC) via an inverter to power the motor. The motor's rotation drives the hydraulic pump, which draws hydraulic fluid from the tank and builds pressure. This high-pressure fluid is then delivered via a proportional directional valve to the rodless chamber of the boom cylinder, pushing the piston rod out and thus lifting the bucket. Simultaneously, the low-pressure fluid in the rod chamber of the hydraulic cylinder flows back to the tank via the proportional directional valve, completing the hydraulic cycle. The proportional directional valve controls the flow and direction of the hydraulic fluid by adjusting its opening, achieving stepless adjustment of the boom's speed and direction. This process realizes the energy conversion and transfer from electrical energy to mechanical energy.

[0031] In an optional embodiment of this application, a safety valve is provided between the outlet of the hydraulic pump and the oil tank. This valve is configured to open when the hydraulic pressure at the pump outlet exceeds a safety threshold, allowing excess oil to flow back into the oil tank. This prevents excessive system pressure from damaging components, thus protecting the system, maintaining pressure stability, and ensuring safe and reliable operation.

[0032] It is understandable that the safety valve is connected in parallel between the hydraulic pump outlet and the oil tank. During normal operation, the valve is closed; when the system pressure exceeds the set safety threshold, the valve automatically opens, diverting excess oil back to the oil tank, thereby limiting the system pressure from continuing to rise, preventing overpressure damage to hydraulic components, and ensuring system safety.

[0033] In an optional embodiment of this application, step S4 includes steps S41 to S42.

[0034] S41, calculate the power consumption of the electric drive system under the preset operating condition according to the following formula: ; in, This represents the power consumption of the electric drive system. This represents the time required to complete the preset working condition; This represents the efficiency of the motor. This represents the battery efficiency of the battery. This represents the motor torque of the motor. ,in, The pump outlet pressure, representing the hydraulic pump, is fed back by a hydraulic sensor located at the pump outlet. This represents the pump displacement of the hydraulic pump. This represents the mechanical efficiency of the hydraulic pump. This represents the motor speed. , The outlet flow rate of the hydraulic pump is fed back by a flow sensor located at the outlet of the hydraulic pump. This represents the volumetric efficiency of the hydraulic pump.

[0035] S42, calculate the difference between the power consumption of the electric drive system and the actual work done under the preset working condition, and use it as the energy loss of the hydraulic working system.

[0036] It is understandable that steps S41 to S42, by constructing a complete power consumption calculation model, achieve precise quantification from hydraulic load to power consumption, providing a scientific basis for energy loss assessment. Step S41, based on real-time sensing parameters such as hydraulic pump outlet pressure, flow rate, and displacement, combined with the physical conversion relationship between motor torque and speed, and comprehensively considering the mechanical efficiency, volumetric efficiency, and battery efficiency of the hydraulic pump, accurately calculates the total power consumption required to complete the preset working conditions. This calculation process covers the entire chain of conversion from hydraulic energy to electrical energy, truly reflecting the energy consumption of the system in actual operation. Step S42 compares the power consumption with the actual work done by the hydraulic cylinder obtained in step S3; the difference between the two is the system energy loss, quantifying the various losses in the energy transfer and conversion process. This method provides a key indicator for evaluating the energy utilization efficiency of different mechanical parameter schemes, making the subsequent optimization process based on evidence.

[0037] In an optional embodiment of this application, step S5 includes steps S51 to S53.

[0038] S51, Organize the energy loss of the hydraulic operating system corresponding to each set of parameter samples.

[0039] S52, using the first spacing value in each group of parameter samples as the first dimension value, the second spacing value in each group of parameter samples as the second dimension value, and the energy loss corresponding to each group of parameter samples as the third dimension value, a three-dimensional surface diagram is constructed.

[0040] S53, find the target first spacing value and target second spacing value corresponding to the lowest energy loss in the three-dimensional surface diagram, and use them as the optimal linkage mechanism size parameters.

[0041] It is understood that this embodiment constructs an intuitive and scientific optimization method through steps S51 to S53. Step S51 systematically organizes the energy loss data corresponding to all parameter samples, laying a complete data foundation for subsequent analysis. Step S52 constructs a three-dimensional surface plot with the first spacing as the X-axis, the second spacing as the Y-axis, and energy loss as the Z-axis, transforming the abstract numerical relationship into an intuitive geometric surface. This allows designers to clearly observe the overall trend of energy loss changes with the two key dimensional parameters and identify the spatial distribution of low-efficiency and high-efficiency regions. Step S53 accurately determines the optimal parameter combination that minimizes system energy loss by locating the lowest point in the three-dimensional surface plot. This method not only ensures the reliable acquisition of the global optimal solution but also deepens the understanding of parameter coupling relationships through visualization, providing intuitive and effective decision support for engineering design.

[0042] Secondly, this application discloses a parameter optimization device for a hydraulic operating system of new energy engineering machinery, including a processor, an input device, an output device, and a memory, wherein the processor, input device, output device, and memory are interconnected, wherein the memory is used to store a computer program, the computer program includes program instructions, and the processor is configured to call the program instructions to execute the method as described in any of the first aspects.

[0043] To make the above-mentioned objectives, features and advantages of this application more apparent and understandable, optional embodiments are described below in detail with reference to the accompanying drawings. Attached Figure Description

[0044] To more clearly illustrate the technical solutions of the embodiments of this application, the accompanying drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of this application and should not be regarded as a limitation of the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0045] Figure 1 This is a structural schematic diagram of a hydraulic operating system for new energy engineering machinery provided in this application; Figure 2 yes Figure 1 The diagram shown illustrates the operation of the hydraulic operating system for new energy engineering machinery. Figure 3 This is a flowchart illustrating a parameter optimization method for a hydraulic operating system of new energy engineering machinery provided in this application; Figure 4 This is the transmission ratio curve provided in this application; Figure 5 This is a preset bucket height displacement curve under preset working conditions provided in this application. Detailed Implementation

[0046] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this application.

[0047] In a first aspect, this application provides a parameter optimization method for a hydraulic operating system of new energy engineering machinery, which is used to optimize the dimensional parameters of the linkage mechanism of the hydraulic operating system.

[0048] like Figure 1 As shown, the hydraulic operating system includes a frame support 1, a bucket 2, a linkage mechanism connecting the frame support 1 and the bucket 2, a hydraulic cylinder 3 that drives the linkage mechanism, and an electric drive system 4 that drives the hydraulic cylinder 3.

[0049] In an optional embodiment of this application, the linkage mechanism includes a boom 5, which is hinged between the frame support 1 and the bucket 2. A hydraulic cylinder 3 is hinged between the frame support 1 and the boom 5 and is configured to push the boom 5 to lift the bucket 2 under the drive of the electric drive system 4.

[0050] In an optional embodiment of this application, the hinge point between the boom 5 and the frame support 1 is denoted as fulcrum O, the hinge point between the hydraulic cylinder 3 and the frame support 1 is denoted as the first hinge point A, the hinge point between the hydraulic cylinder 3 and the boom 5 is denoted as the second hinge point B, the distance between the first hinge point A and the fulcrum O is denoted as the first distance L1, and the distance between the second hinge point B and the fulcrum O is denoted as the second distance L2.

[0051] This linkage mechanism uses the chassis support 1 as a fixed base and connects to the bucket 2 via the boom 5 to achieve lifting operations. Its core transmission principle is based on a three-point hinge layout: fulcrum O is the rotation center of the boom 5 and the chassis support 1, and the two ends of the hydraulic cylinder 3 are hinged to the first hinge point A and the second hinge point B, respectively. Figure 2 As shown, when hydraulic cylinder 3 extends, it drives boom 5 to rotate upwards around fulcrum O, thereby lifting bucket 2. During this process, the first distance L1 (distance from point A to point O) and the second distance L2 (distance from point B to point O) together form a lever arm combination, determining the lever relationship in which the hydraulic cylinder driving force is transmitted to the bucket lifting force. The values ​​of these two distances directly affect the force transmission ratio, that is, the ratio between the hydraulic cylinder output force and the bucket load force, which varies with the lifting height. This is a key geometric parameter determining the system's load characteristics and energy efficiency. Subsequently, the first distance L1 and the second distance L2 will be selected as the linkage mechanism dimensional parameters to be optimized.

[0052] like Figure 3 As shown, the above parameter optimization method includes steps S1 to S5. S1, S2, etc. are only step identifiers. The execution order of the method does not necessarily follow the order of numbers from smallest to largest. For example, step S2 can be executed first and then step S1 can be executed. This application does not impose any restrictions.

[0053] S1, Select the linkage mechanism size parameters that affect the force transmission ratio of the hydraulic operating system as the parameters to be optimized.

[0054] In an optional embodiment of this application, step S1 includes: selecting a first gap L1 and a second gap L2 that affect the force transmission ratio of the hydraulic operating system as parameters to be optimized.

[0055] It is understandable that the first spacing L1 and the second spacing L2 directly determine the force transmission ratio curve of the linkage mechanism, that is, the relationship between the driving force of the hydraulic cylinder 3 and the load force of the bucket as the lifting height changes. The shape of the force transmission ratio curve has a decisive impact on the overall energy efficiency of the machine: if the force transmission ratio is not designed reasonably, the hydraulic cylinder 3 will bear excessively high load peaks or drastically fluctuating loads at different lifting stages, causing the hydraulic pump 44 to be forced to frequently operate in the inefficient zone, resulting in a large amount of energy loss; at the same time, this load fluctuation will also be transmitted to the drive motor 43, causing its operating point to deviate from the efficient zone. Therefore, by optimizing the first spacing L1 and the second spacing L2, the force transmission ratio curve can be optimized, so that the load characteristics of the hydraulic cylinder 3 match the efficiency distribution of the hydraulic pump 44 and the motor 43, and the working trajectory of the hydraulic pump 44 and the motor 43 can be actively guided to their efficient zone, thereby reducing ineffective energy consumption from the source.

[0056] S2 defines the range and step size of the dimensional parameters of the linkage mechanism, and records each value within the defined range as a single parameter sample.

[0057] S3 calculates the actual work done by hydraulic cylinder 3 under preset working conditions based on each set of parameter samples.

[0058] S4 calculates the difference between the power consumption and the actual work done by the electric drive system 4 under the preset working conditions, which is used as the energy loss of the hydraulic working system.

[0059] S5. Among the various parameter samples, the target parameter sample corresponding to the lowest energy loss is selected as the optimal linkage mechanism size parameter.

[0060] It is understood that steps S1 to S5 of this application optimize the linkage mechanism dimensional parameters of the hydraulic operating system of new energy engineering machinery, which can fundamentally break through the limitations of the traditional "fragmented" design method, realize the deep synergistic matching of the three major subsystems of mechanical, hydraulic and electrical systems, and significantly improve the overall energy efficiency. Specifically, steps S1 and S2 construct a global mechanical structure parameter space by accurately selecting key dimensional parameters that affect the system's force transmission ratio (such as the first spacing L1 and the second spacing L2) and performing gridded scanning of their value range and step size; step S3 calculates the actual work done by the hydraulic cylinder 3 under the preset working conditions based on each set of parameter samples, thereby associating the abstract geometric dimensions with the specific dynamic operation energy consumption; step S4 further introduces the full-link energy flow model of the electric drive system 4, accurately calculates the difference between the electric energy consumption and the actual work done, and quantifies the system energy loss under the "mechanical-electrical-hydraulic" coupling effect; step S5 selects the optimal parameter combination that minimizes energy loss through traversal optimization. This series of steps optimizes the mechanical structure parameters in conjunction with the hydraulic system operating point and the efficiency distribution of the motor 43, actively guiding the working trajectories of the hydraulic pump 44 and the motor 43 to concentrate in their high-efficiency zones, thereby significantly reducing ineffective energy consumption during dynamic operations and effectively extending the overall machine's range under existing battery technology conditions, thus improving the economy and environmental friendliness of the construction machinery.

[0061] It is understandable that optimizing the linkage mechanism dimensional parameters of the hydraulic operating system of new energy engineering machinery according to steps S1 to S5 of this application can fundamentally break through the limitations of the traditional "fragmented and serial" design method, achieve deep synergistic matching of the three major subsystems of mechanical, hydraulic and electrical systems, and significantly improve the overall energy efficiency level of the machine. This optimization method changes the previous one-sided approach of only improving the efficiency of components or local control strategies by incorporating mechanical structural parameters into the global optimization scope. Its core lies in constructing a full-link energy flow analysis model from mechanical force transmission characteristics to the distribution of hydraulic system working points, and then to the load characteristics of motor 43. By traversing and optimizing the key dimensional parameters of the linkage mechanism, it can actively guide the working point trajectory of hydraulic pump 44 in actual dynamic operation to be densely distributed in its high-efficiency zone, while making the working point of motor 43 better coincide with its own high-efficiency zone, thereby greatly reducing the ineffective energy consumption and inefficient energy consumption caused by factor system mismatch. The optimal parameter combination finally selected can systematically improve the cumulative energy efficiency of the hydraulic operating system under typical working conditions. This not only directly reduces the energy consumption per unit of operation of the whole machine, but also effectively extends the driving time of new energy construction machinery under the conditions of limited energy density and cost of existing batteries. It also provides practical technical support for the large-scale electrification transformation of the industry, and has significant economic benefits and carbon reduction value.

[0062] In an optional embodiment of this application, step S2 includes steps S21 to S24.

[0063] S21 defines a first value range and a first value change step size for the first spacing L1, and defines a second value range and a second value change step size for the second spacing L2.

[0064] S22, within the first value range, select the first interval L1 value in ascending order with the first value change step size.

[0065] S23, after selecting the first spacing L1 value each time, within the second value range, select the second spacing L2 value in ascending order with the second value change step size.

[0066] S24. Each selected first spacing L1 value and second spacing L2 value is recorded as a single set of parameter samples.

[0067] It is understandable that steps S21 to S24 construct a parameter sample set covering the global design space by setting the value range and variation step size for the first spacing L1 and the second spacing L2, and traversing the values ​​using a nested loop. The beneficial effects of this method are: First, by limiting the value range, the optimization region can be focused on the practically feasible geometric size range in engineering, avoiding invalid searches; second, by setting a reasonable variation step size, a balance can be achieved between computational accuracy and optimization efficiency, capturing subtle changes near the optimal parameter without excessively increasing the computational burden due to an excessively small step size; finally, the nested loop traversal method ensures that all possible combinations of the two parameters to be optimized are taken into consideration, forming a complete parameter sample space, laying a comprehensive and systematic data foundation for subsequent optimization, and avoiding the risk of missing the global optimal solution due to local searches.

[0068] For example, suppose the first spacing L1 (distance from the first hinge point A to the fulcrum O) ranges from 400 mm to 600 mm, with a first value variation step of 50 mm; the second spacing L2 (distance from the second hinge point B to the fulcrum O) ranges from 600 mm to 900 mm, with a second value variation step of 50 mm. Then, a single set of parameter samples generated using a nested loop method would be: First sample group: L1 = 400mm, L2 = 600mm; Second sample group: L1 = 400mm, L2 = 650mm; The third sample group: L1 = 400mm, L2 = 700mm; Fourth sample group: L1 = 400mm, L2 = 750mm; Fifth sample group: L1 = 400mm, L2 = 800mm; Sixth sample group: L1 = 400mm, L2 = 850mm; Seventh sample group: L1 = 400mm, L2 = 900mm; Eighth sample group: L1 = 450mm, L2 = 600mm; Ninth sample group: L1 = 450mm, L2 = 650mm; Tenth sample group: L1 = 450mm, L2 = 700mm; Eleventh sample group: L1 = 450mm, L2 = 750mm; Twelfth sample group: L1 = 450mm, L2 = 800mm ...and so on, a total of 4×6=24 sets of complete parameter samples are generated.

[0069] In an optional embodiment of this application, S3 includes steps S31 to S35.

[0070] S31. Based on the first spacing L1 value and the second spacing L2 value in each set of parameter samples, calculate the force transmission ratio curve corresponding to the parameter sample. The horizontal axis of the force transmission ratio curve is the bucket height displacement, and the vertical axis of the force transmission ratio curve is the ratio of the boom driving force of the hydraulic cylinder 3 to the bucket load force of the bucket 2.

[0071] like Figure 4 As shown, the electric loader transmits the pressure and speed of the hydraulic cylinder 3 to the bucket 2 through a multi-stage linkage. During the lifting process, the lever arm of both the bucket load force and the driving force changes continuously with the height above the ground. The bucket load force requires the driving force to adjust in response to the changing lever arm. The ratio of the boom driving force of the hydraulic cylinder 3 to the bucket load force is called the "transmission ratio." The transmission ratios at different positions form the "transmission ratio curve" of the lifting process. Based on the L1 and L2 values ​​in each set of parameter samples, a geometric model and kinematic equations of the linkage mechanism are established. According to the principle of force balance, the ratio between the hydraulic cylinder driving force and the bucket load force at different bucket heights is calculated, thus plotting the transmission ratio curve as a function of height.

[0072] S32, calculate the boom driving force curve under the preset working condition using the force ratio curve. The horizontal axis of the boom driving force curve represents time, and the vertical axis represents the boom driving force. The preset working condition is to perform a lifting operation by carrying a preset bucket load weight according to a preset bucket height displacement curve, such as... Figure 5 As shown, the horizontal axis of the bucket height displacement curve represents time, and the vertical axis represents the bucket height displacement.

[0073] In step S32, firstly, the input conditions for the preset working condition are determined: given the bucket load weight (i.e., the total weight of the bucket and material), the bucket load force at any given time can be calculated. This force is equal to the gravity corresponding to the bucket load weight and is a constant value. Simultaneously, a bucket height displacement curve is provided, which describes the change in bucket lifting height over time. Secondly, the correspondence between the force ratio and height is established. The force ratio curve, i.e., the functional relationship between the force ratio and bucket height, has already been obtained in step S31. For any given time, the bucket height at the current moment is determined based on the bucket height displacement curve, and then the corresponding force ratio value at that height is found through the force ratio curve. Finally, the boom driving force is calculated. According to the definition of the force ratio, the boom driving force is equal to the bucket load force multiplied by the force ratio. Therefore, for each moment, multiplying the constant bucket load force by the current force ratio value yields the boom driving force at that moment. Plotting the calculated driving force results for all moments in chronological order yields the boom driving force curve under the preset working condition.

[0074] S33, obtain the extension length of hydraulic cylinder 3 as fed back by displacement sensor, and obtain the hydraulic cylinder extension curve. The horizontal axis of the hydraulic cylinder extension curve is time, and the vertical axis of the hydraulic cylinder extension curve is the extension length of hydraulic cylinder 3.

[0075] It is understandable that in step S33, the extension length of the hydraulic cylinder piston rod is fed back in real time through a displacement sensor, recording the change in the hydraulic cylinder length over time from the start to the end of the lifting process, thus forming a hydraulic cylinder extension curve. This curve reflects the movement trajectory of the hydraulic cylinder during the boom lifting process and is the basis for calculating the work done by the displacement.

[0076] S34, multiply the corresponding points of the boom driving force curve and the hydraulic cylinder extension curve to obtain the actual work curve of hydraulic cylinder 3 under the preset working conditions. The horizontal axis of the actual work curve is time, and the vertical axis of the actual work curve is the actual work value.

[0077] In step S34, the actual work curve of the boom hydraulic cylinder is obtained by multiplying the boom driving force by the extension length of the hydraulic cylinder point by point, reflecting the total mechanical energy output by the hydraulic cylinder during the lifting process. This work value includes two parts: one part is used to overcome the gravity of the bucket material to complete the effective lifting operation, which is called useful work; the other part is used to overcome the gravitational potential energy increased by the weight of the mechanical linkage structure. It is worth noting that this optimization method mainly adjusts the dimensional parameters of the linkage mechanism. During the optimization process, the change in the weight of the mechanical components is minimal and can be ignored. Therefore, although the actual work includes the energy corresponding to the increase in gravitational potential energy, it remains basically constant under parameter changes and does not affect the relative comparison between different parameter schemes. Based on this, the actual work is used as a benchmark to measure the mechanical output energy, which is then used to calculate energy loss by comparing it with electrical energy consumption. This can scientifically reflect the loss level of the system in the energy conversion process and ensure the rationality and accuracy of the optimization results.

[0078] It can be understood that step S34 performs a dot product operation between the boom driving force curve obtained in step S32 and the hydraulic cylinder extension curve obtained in step S33 at corresponding time points. For each sampling time point, the driving force is multiplied by the small displacement increment at that time point to obtain the instantaneous work element at that time point. Connecting the instantaneous work elements at all time points in chronological order constitutes the actual work curve. This curve reflects the cumulative change trend of the hydraulic cylinder work over time during the lifting process.

[0079] S35 determines the actual work value corresponding to the completion of the preset working condition based on the actual work curve.

[0080] Step S35 integrates or sums the actual work curve to calculate the total mechanical work consumed by the hydraulic cylinder in completing the lifting operation during the entire preset working condition from the start to the end of the lifting process; this is the actual work value. This value serves as the benchmark for subsequent energy loss calculations and is used for comparison with electrical energy consumption.

[0081] It is understandable that steps S31 to S35 establish a complete calculation link from geometric parameters to actual work done, accurately linking abstract mechanical dimensions with specific energy consumption indicators. First, step S31 determines the force transmission ratio curve based on the first gap L1 and the second gap L2, revealing the mechanical transmission characteristics of the mechanism under different geometric parameters. Step S32, combined with preset working conditions, transforms the static force transmission ratio into a dynamic driving force curve, making the calculation closely resemble the actual operation process. Step S33 introduces the extension length of the hydraulic cylinder 3 fed back by a displacement sensor, ensuring the accuracy of the kinematic data. Step S34 accurately calculates the actual work done by the hydraulic cylinder 3 at each moment by integrating the product of the driving force and displacement. Step S35 finally summarizes the total work done to complete the entire working condition. This series of steps realizes the quantitative mapping of mechanical structural parameters to the load characteristics of the hydraulic system, providing an accurate mechanical work benchmark for subsequent energy loss calculations, and is a key foundation for evaluating the energy efficiency performance of different parameter schemes.

[0082] In optional embodiments of this application, reference continues to be made to... Figure 1 The electric drive system 4 includes a battery 41, an inverter 42, a motor 43, a hydraulic pump 44, an oil tank 45, and a proportional directional valve 46. The battery 41 supplies power to the motor 43 through the inverter 42. The motor 43 drives the hydraulic pump 44 to draw oil from the oil tank 45 and transmits it to the rodless chamber of the hydraulic cylinder 3 through the proportional directional valve 46, pushing the piston rod of the hydraulic cylinder 3 to extend, thereby pushing the boom 5 to lift the bucket 2. The oil in the rod chamber of the hydraulic cylinder 3 returns to the oil tank 45 through the proportional directional valve 46.

[0083] In an optional embodiment of this application, the outlet of the hydraulic pump 44 is connected to the first port of the proportional directional valve 46, the second port of the proportional directional valve 46 is connected to the rodless chamber of the hydraulic cylinder 3, the rod chamber of the hydraulic cylinder 3 is connected to the third port of the proportional directional valve 46, and the fourth port of the proportional directional valve 46 is connected to the oil tank 45. When the proportional directional valve 46 is in the first state, the first port is connected to the second port, and the oil in the oil tank 45 is drawn by the hydraulic pump 44 into the rodless chamber of the hydraulic cylinder 3; when the proportional directional valve 46 is in the second state, the third port is connected to the fourth port, and the oil in the rod chamber of the hydraulic cylinder 3 flows back to the oil tank 45 through the proportional directional valve 46.

[0084] It can be understood that battery 41, acting as an energy source, outputs DC power, which is converted into AC power by inverter 42 to drive motor 43 to rotate. Motor 43 drives hydraulic pump 44 to work, drawing oil from oil tank 45 and building up pressure. High-pressure oil enters the rodless chamber of hydraulic cylinder 3 through the first and second ports of proportional directional valve 46, pushing the piston rod to extend, thereby driving boom 5 to lift bucket 2. At the same time, low-pressure oil in the rod chamber of hydraulic cylinder 3 flows back to oil tank 45 through the third and fourth ports of proportional directional valve 46, completing the hydraulic cycle. Proportional directional valve 46 switches the oil circuit by controlling the valve core position: in the first state, the pumped oil enters the rodless chamber to achieve lifting; in the second state, the rod chamber returns oil to achieve lowering. By adjusting the valve opening, the boom movement speed can also be steplessly controlled. This process realizes the energy conversion and transfer from electrical energy to mechanical energy to hydraulic energy and back to mechanical energy.

[0085] In optional embodiments of this application, such as Figure 1 As shown, a safety valve 47 is installed between the outlet of the hydraulic pump 44 and the oil tank 45. This valve is configured to open when the hydraulic pressure at the outlet of the hydraulic pump 44 exceeds a safety threshold, allowing excess oil to flow back into the oil tank 45. This prevents excessive system pressure from damaging components, protecting the system, maintaining pressure stability, and ensuring safe and reliable operation.

[0086] It is understood that the safety valve 47 is connected in parallel between the outlet of the hydraulic pump 44 and the oil tank 45. During normal operation, the valve is closed; when the system pressure exceeds the set safety threshold, the valve automatically opens, diverting excess oil back to the oil tank 45, thereby limiting the system pressure from continuing to rise, preventing overpressure damage to hydraulic components, and ensuring system safety.

[0087] In an optional embodiment of this application, step S4 includes steps S41 to S42.

[0088] S41, calculate the power consumption of the electric drive system 4 under the preset operating conditions according to the following formula: ; in, This represents the power consumption of the electric drive system 4. This represents the time required to complete the preset working conditions; This represents the efficiency of the motor. This represents the battery efficiency of battery 41. This represents the motor torque of motor 43. ,in, The pump outlet pressure of hydraulic pump 44 is fed back by a hydraulic sensor located at the outlet of hydraulic pump 44. This represents the pump displacement of hydraulic pump 44. This represents the mechanical efficiency of hydraulic pump 44; This represents the motor speed of motor 43. , The outlet flow rate of hydraulic pump 44 is fed back by a flow sensor located at the outlet of hydraulic pump 44. This represents the volumetric efficiency of hydraulic pump 44.

[0089] S42, calculate the difference between the power consumption and the actual work done by the electric drive system 4 under the preset working conditions, and use it as the energy loss of the hydraulic working system.

[0090] It is understandable that steps S41 to S42, by constructing a complete power consumption calculation model, achieve precise quantification from hydraulic load to power consumption, providing a scientific basis for energy loss assessment. Step S41, based on real-time sensing parameters such as outlet pressure, flow rate, and displacement of hydraulic pump 44, combined with the physical conversion relationship between motor torque and speed, and comprehensively considering the mechanical efficiency, volumetric efficiency, and battery efficiency of hydraulic pump 44, accurately calculates the total power consumption required to complete the preset working conditions. This calculation process covers the entire chain of conversion from hydraulic energy to electrical energy, truly reflecting the energy consumption of the system in actual operation. Step S42 compares the power consumption with the actual work done by hydraulic cylinder 3 obtained in step S3; the difference between the two is the system energy loss, quantifying various losses in the energy transfer and conversion process. This method provides a key indicator for evaluating the energy utilization efficiency of different mechanical parameter schemes, making the subsequent optimization process based on evidence.

[0091] In an optional embodiment of this application, step S5 includes steps S51 to S53.

[0092] S51, compile the energy loss of the hydraulic operating system corresponding to each set of parameter samples.

[0093] S52, using the first spacing L1 value in each set of parameter samples as the first dimension value, the second spacing L2 value in each set of parameter samples as the second dimension value, and the energy loss corresponding to each set of parameter samples as the third dimension value, a three-dimensional surface plot is constructed.

[0094] S53. Find the target first spacing L1 and target second spacing L2 values ​​corresponding to the lowest energy loss in the three-dimensional surface plot, and use them as the optimal linkage mechanism size parameters.

[0095] It is understood that this embodiment constructs an intuitive and scientific optimization method through steps S51 to S53. Step S51 systematically organizes the energy loss data corresponding to all parameter samples, laying a complete data foundation for subsequent analysis. Step S52 constructs a three-dimensional surface plot with the first spacing L1 as the X-axis, the second spacing L2 as the Y-axis, and energy loss as the Z-axis, transforming abstract numerical relationships into intuitive geometric surfaces. This allows designers to clearly observe the overall trend of energy loss changes with the two key dimensional parameters and identify the spatial distribution of low-efficiency and high-efficiency regions. Step S53 accurately determines the optimal parameter combination that minimizes system energy loss by locating the lowest point in the three-dimensional surface plot. This method not only ensures the reliable acquisition of the global optimal solution but also deepens the understanding of parameter coupling relationships through visualization, providing intuitive and effective decision support for engineering design.

[0096] Secondly, this application provides a parameter optimization device for a hydraulic operating system of new energy construction machinery. The parameter optimization device for the hydraulic operating system of new energy construction machinery includes one or more processors; one or more input devices; one or more output devices; and a memory. The processors, input devices, output devices, and memory are connected via a bus. The memory stores a computer program, which includes program instructions, and the processor executes the program instructions stored in the memory. The processor is configured to invoke the program instructions to perform the operation of any method of the first aspect.

[0097] It should be understood that, in the embodiments of the present invention, the processor may be a central processing unit (CPU), or it may be other general-purpose processors, digital signal processors (DSPs), application-specific integrated circuits (ASICs), field-programmable gate arrays (FPGAs), or other programmable logic devices, discrete gate or transistor logic devices, discrete hardware components, etc. A general-purpose processor may be a microprocessor or any conventional processor.

[0098] Input devices may include touchpads, fingerprint sensors (used to collect the user's fingerprint information and fingerprint orientation information), microphones, etc., while output devices may include displays (LCDs, etc.), speakers, etc.

[0099] The memory may include read-only memory and random access memory, and provides instructions and data to the processor. A portion of the memory may also include non-volatile random access memory. For example, the memory may also store information about the device type.

[0100] In specific implementations, the processor, input device, and output device described in the embodiments of the present invention can execute the implementation method described in any of the methods in the first aspect, or can execute the implementation method of the terminal device described in the embodiments of the present invention, which will not be repeated here.

[0101] Thirdly, the present invention provides a computer-readable storage medium storing a computer program, the computer program including program instructions that, when executed by a processor, implement the steps of any of the methods of the first aspect.

[0102] The aforementioned computer-readable storage medium can be an internal storage unit of the terminal device in any of the foregoing embodiments, such as a hard disk or memory of the terminal device. The aforementioned computer-readable storage medium can also be an external storage device of the terminal device, such as a plug-in hard disk, smart media card (SMC), secure digital (SD) card, flash card, etc., provided on the terminal device. Furthermore, the aforementioned computer-readable storage medium may include both internal storage units and external storage devices of the terminal device. The aforementioned computer-readable storage medium is used to store the aforementioned computer program and other programs and data required by the terminal device. The aforementioned computer-readable storage medium can also be used to temporarily store data that has been output or will be output.

[0103] Those skilled in the art will recognize that the units and algorithm steps of the various examples described in conjunction with the embodiments disclosed herein can be implemented in electronic hardware, computer software, or a combination of both. To clearly illustrate the interchangeability of hardware and software, the components and steps of the various examples have been generally described in terms of functionality in the foregoing description. Whether these functions are implemented in hardware or software depends on the specific application and design constraints of the technical solution. Those skilled in the art can use different methods to implement the described functions for each specific application, but such implementations should not be considered beyond the scope of this invention.

[0104] In the several embodiments provided in this application, it should be understood that the disclosed terminal devices and methods can be implemented in other ways. For example, the device embodiments described above are merely illustrative. For instance, the division of the units described above is only a logical functional division, and in actual implementation, there may be other division methods. For example, multiple units or components may be combined or integrated into another system, or some features may be ignored or not executed. In addition, the mutual coupling or direct coupling or communication connection shown or discussed may be indirect coupling or communication connection through some interfaces, devices or units, or it may be an electrical, mechanical or other form of connection.

[0105] The units described above as separate components may or may not be physically separate. The components shown as units may or may not be physical units; that is, they may be located in one place or distributed across multiple network units. Some or all of the units can be selected to achieve the purpose of the embodiments of the present invention, depending on actual needs.

[0106] Furthermore, the functional units in the various embodiments of the present invention can be integrated into one processing unit, or each unit can exist physically separately, or two or more units can be integrated into one unit. The integrated unit can be implemented in hardware or as a software functional unit.

[0107] If the aforementioned integrated units are implemented as software functional units and sold or used as independent products, they can be stored in a computer-readable storage medium. Based on this understanding, the technical solution of this invention, in essence, or the part that contributes to the prior art, or all or part of the technical solution, can be embodied in the form of a software product. This computer software product is stored in a storage medium and includes several instructions to cause a computer device (which may be a personal computer, server, or network device, etc.) to execute all or part of the steps of the methods in the various embodiments of this invention. The aforementioned storage medium includes various media capable of storing program code, such as USB flash drives, portable hard drives, read-only memory (ROM), random access memory (RAM), magnetic disks, or optical disks.

[0108] The terms "first," "second," "first," or "second" used in the various embodiments of this disclosure may modify various components regardless of their order and / or importance, but these terms do not limit the corresponding components. The above terms are configured only for the purpose of distinguishing an element from other elements. For example, "first user equipment" and "second user equipment" refer to different user equipments, although both are user equipment. For example, without departing from the scope of this disclosure, a first element may be referred to as a second element, and similarly, a second element may be referred to as a first element.

[0109] When an element (e.g., a first element) is referred to as being "operably or communicatively coupled" or "operably or communicatively coupled to" or "connected to" another element (e.g., a second element), it should be understood that the first element is directly connected to the second element or that the first element is indirectly connected to the second element via yet another element (e.g., a third element). Conversely, it can be understood that when an element (e.g., a first element) is referred to as being "directly connected" or "directly coupled" to another element (the second element), no element (e.g., a third element) is inserted between the two.

[0110] It should be noted that, in this document, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes that element. Furthermore, components, features, and elements with the same names in different embodiments of this application may have the same meaning or different meanings, the specific meaning of which must be determined by its interpretation in that specific embodiment or further in conjunction with the context of that specific embodiment.

[0111] The above description is merely an optional embodiment of this application and an explanation of the technical principles employed. Those skilled in the art should understand that the scope of the invention involved in this application is not limited to technical solutions formed by specific combinations of the above-described technical features, but should also cover other technical solutions formed by arbitrary combinations of the above-described technical features or their equivalents without departing from the above-described inventive concept. For example, technical solutions formed by substituting the above-described features with (but not limited to) technical features with similar functions disclosed in this application.

[0112] Depending on the context, the words “if” or “when” as used here can be interpreted as “when…” or “in response to determination” or “in response to detection.” Similarly, depending on the context, the phrases “if determination” or “if detection (of the stated condition or event)” can be interpreted as “when determination” or “in response to determination” or “when detection (of the stated condition or event)” or “in response to detection (of the stated condition or event).”

[0113] The above description is merely an optional embodiment of this application and an explanation of the technical principles employed. Those skilled in the art should understand that the scope of the invention involved in this application is not limited to technical solutions formed by specific combinations of the above-described technical features, but should also cover other technical solutions formed by arbitrary combinations of the above-described technical features or their equivalents without departing from the above-described inventive concept. For example, technical solutions formed by substituting the above-described features with (but not limited to) technical features with similar functions disclosed in this application.

[0114] The above description is merely an optional embodiment of this application and is not intended to limit this application. Various modifications and variations can be made to this application by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this application should be included within the protection scope of this application.

Claims

1. A parameter optimization method for a hydraulic operating system of new energy engineering machinery, used to optimize the dimensional parameters of the linkage mechanism of the hydraulic operating system, the hydraulic operating system including a frame support, a bucket, a linkage mechanism connecting the frame support and the bucket, a hydraulic cylinder driving the linkage mechanism, and an electric drive system driving the hydraulic cylinder, characterized in that, The parameter optimization method includes the following steps: S1, Select the linkage mechanism size parameters that affect the force transmission ratio of the hydraulic working system as the parameters to be optimized; S2, define the range of values ​​and the step size of value change for the dimensional parameters of the linkage mechanism, and record each value within the defined range as a single parameter sample; S3, calculate the actual work done by the boom hydraulic cylinder under the preset working conditions based on each set of parameter samples; S4, calculate the difference between the power consumption of the electric drive system and the actual work done under the preset working condition, and use it as the energy loss of the hydraulic operation system; S5. Among the various parameter samples, the target parameter sample corresponding to the lowest energy loss is selected as the optimal linkage mechanism size parameter.

2. The parameter optimization method for the hydraulic operation system of new energy engineering machinery according to claim 1, characterized in that, The linkage mechanism includes a boom, which is hinged between the frame support and the bucket. The boom hydraulic cylinder is hinged between the frame support and the boom and is configured to push the boom to lift the bucket under the drive of the electric drive system.

3. The parameter optimization method for the hydraulic operation system of new energy engineering machinery according to claim 2, characterized in that, The hinge point between the boom and the frame support is denoted as the fulcrum, the hinge point between the boom hydraulic cylinder and the frame support is denoted as the first hinge point, the hinge point between the boom hydraulic cylinder and the boom is denoted as the second hinge point, the distance between the first hinge point and the fulcrum is denoted as the first distance, and the distance between the second hinge point and the fulcrum is denoted as the second distance. Step S1 includes: selecting the first spacing and the second spacing, which affect the force transmission ratio of the hydraulic operating system, as parameters to be optimized.

4. The parameter optimization method for the hydraulic operation system of new energy engineering machinery according to claim 3, characterized in that, Step S2 includes: S21, define a first value range and a first value change step size for the first spacing, and define a second value range and a second value change step size for the second spacing; S22, within the first value range, the first interval value is selected sequentially in ascending order according to the step size of the first value change; S23, after selecting the first spacing value each time, within the range of the second value, the second spacing value is selected sequentially in ascending order with the second value change step size; S24, record each selected first spacing value and second spacing value as a single set of parameter samples.

5. The parameter optimization method for the hydraulic operation system of new energy engineering machinery according to claim 4, characterized in that, S3 includes: S31, based on the first spacing value and the second spacing value in each set of parameter samples, calculate the force transmission ratio curve corresponding to the parameter sample. The horizontal axis of the force transmission ratio curve is the bucket height displacement, and the vertical axis of the force transmission ratio curve is the ratio of the boom driving force of the boom hydraulic cylinder to the bucket load force of the bucket. S32, calculate the boom driving force curve under the preset working condition using the transmission ratio curve. The horizontal axis of the boom driving force curve is time, and the vertical axis of the boom driving force curve is the boom driving force. The preset working condition is to lift the preset bucket load weight according to the preset bucket height displacement curve. The horizontal axis of the bucket height displacement curve is time, and the vertical axis is the bucket height displacement. S33, obtain the extension length of the boom hydraulic cylinder fed back by the displacement sensor, and obtain the hydraulic cylinder extension curve. The horizontal axis of the hydraulic cylinder extension curve is time, and the vertical axis of the hydraulic cylinder extension curve is the extension length of the boom hydraulic cylinder. S34, Multiply the corresponding points of the boom driving force curve and the hydraulic cylinder extension curve to obtain the actual work curve of the boom hydraulic cylinder under the preset working condition. The horizontal axis of the actual work curve is time, and the vertical axis of the actual work curve is the actual work value. S35, determine the actual work value corresponding to the completion of the preset working condition based on the actual work curve.

6. The parameter optimization method for the hydraulic operation system of new energy engineering machinery according to claim 5, characterized in that, The electric drive system includes a battery, an inverter, a motor, a hydraulic pump, an oil tank, and a proportional directional valve. The battery supplies power to the motor via the inverter. The motor drives the hydraulic pump to draw oil from the oil tank and transmits it to the rodless chamber of the boom hydraulic cylinder through the proportional directional valve. This pushes the piston rod of the boom hydraulic cylinder to extend, thereby pushing the boom to lift the bucket. The oil in the rod chamber of the boom hydraulic cylinder returns to the oil tank through the proportional directional valve.

7. The parameter optimization method for the hydraulic operation system of new energy engineering machinery according to claim 6, characterized in that, A safety valve is provided between the outlet of the hydraulic pump and the oil tank. It is configured to open when the hydraulic pressure at the outlet of the hydraulic pump is greater than a safety threshold, so that excess oil flows back into the oil tank.

8. The parameter optimization method for the hydraulic operation system of new energy engineering machinery according to claim 6, characterized in that, Step S4 includes: S41, calculate the power consumption of the electric drive system under the preset operating conditions according to the following formula: in, This represents the power consumption of the electric drive system. This represents the time required to complete the preset working condition; This represents the efficiency of the motor. This represents the battery efficiency of the battery. This represents the motor torque of the motor. ,in, The pump outlet pressure, representing the hydraulic pump, is fed back by a hydraulic sensor located at the pump outlet. This represents the pump displacement of the hydraulic pump. This represents the mechanical efficiency of the hydraulic pump. This represents the motor speed. , The outlet flow rate of the hydraulic pump is fed back by a flow sensor located at the outlet of the hydraulic pump. This represents the volumetric efficiency of the hydraulic pump. S42, calculate the difference between the power consumption of the electric drive system and the actual work done under the preset working condition, and use it as the energy loss of the hydraulic working system.

9. The parameter optimization method for the hydraulic operation system of new energy engineering machinery according to claim 8, characterized in that, Step S5 includes: S51, Organize the energy loss of the hydraulic operating system corresponding to each set of parameter samples; S52, using the first spacing value in each group of parameter samples as the first dimension value, the second spacing value in each group of parameter samples as the second dimension value, and the energy loss corresponding to each group of parameter samples as the third dimension value, a three-dimensional surface diagram is constructed. S53, find the target first spacing value and target second spacing value corresponding to the lowest energy loss in the three-dimensional surface diagram, and use them as the optimal linkage mechanism size parameters.

10. A parameter optimization device for a hydraulic operating system of new energy engineering machinery, characterized in that, The system includes a processor, an input device, an output device, and a memory, which are interconnected. The memory is used to store a computer program, which includes program instructions. The processor is configured to invoke the program instructions to perform the method as described in any one of claims 1 to 9.

Images