Crank arrangement method for crankshaft, device, storage medium, and program product

Abstract

A crank arrangement method for a crankshaft, a device, a storage medium, and a program product. The method comprises: acquiring structural feature data of a target crankshaft having a plurality of crank structures (S101); on the basis of the structural feature data, determining a plurality of crank pin arrangement sequences of the target crankshaft (S102); on the basis of the structural feature data, establishing a motion model, wherein the motion model is used for describing a coordinated motion process of the crank structures, connecting rods corresponding to the crank structures, and piston structures in cylinders (S103); on the basis of the motion model, determining bearing block reaction force data, inertia moment data, and suction pipe flow rate data for the crank pin arrangement sequences, wherein the suction pipe flow rate data is used for describing a sectional flow rate of a main suction pipe corresponding to crank pins (S104); and on the basis of the bearing block reaction force data, the inertia moment data, and the suction pipe flow rate data, screening the crank pin arrangement sequences for a target crank arrangement sequence (S105). The method improves the product performance of a seven-cylinder reciprocating pump.

Description

Crankshaft crankpin arrangement methods, equipment, storage media and program products

[0001] This application claims priority to Chinese Patent Application No. 202411396013.5, filed on October 8, 2024, entitled “Method, apparatus, storage medium and program product for crankshaft crank arrangement”, the entire contents of which are incorporated herein by reference. Technical Field

[0002] This application relates to industrial control technology, and more particularly to a crankshaft crank arrangement method, device, storage medium, and program product. Background Technology

[0003] Reciprocating pumps are widely used in the petroleum industry, including products such as three-cylinder and five-cylinder reciprocating pumps. Currently, three-cylinder reciprocating pumps are the most commonly used in drilling and production equipment, while the number of five-cylinder reciprocating pumps is gradually increasing. In oil and gas well enhancement applications, five-cylinder fracturing pumps are primarily used. Both types of reciprocating pump technologies are maturing and operating stably. However, with the continued development of deep and ultra-deep wells and the increasing demand for oil and gas well enhancement, higher pressure and displacement conditions are emerging, which five-cylinder reciprocating pumps will find insufficient. Therefore, research into seven-cylinder reciprocating pump technology is imperative to meet these new demands.

[0004] Currently, in the research of seven-cylinder reciprocating pumps, how to reasonably achieve the crank arrangement is a key issue that needs to be analyzed. Summary of the Invention

[0005] This application provides a crankshaft crank arrangement method, equipment, storage medium, and program product, which achieves a reasonable crank arrangement and improves the product performance of a seven-cylinder reciprocating pump.

[0006] In a first aspect, this application provides a method for arranging crankshaft cranks, including:

[0007] Obtain structural feature data of a target crankshaft with multiple crank structures;

[0008] Based on structural feature data, a sequence of multiple crank pin arrangements for the target crankshaft is determined. The crank pin arrangement sequence is used to indicate the power-operating sequence of the hydraulic cylinders corresponding to the crank pins in the crankshaft structure.

[0009] Based on structural feature data, a motion model is established. The motion model is used to describe the coordinated motion process of the crank structure, the corresponding connecting rod, and the piston structure in the hydraulic cylinder.

[0010] Based on the motion model, the bearing seat support reaction force data, inertial moment data, and intake pipe flow data for the crank pin arrangement sequence are determined. The intake pipe flow data is used to describe the cross-sectional flow of the main intake pipe corresponding to the crank pin.

[0011] Based on the bearing seat reaction force data, inertial torque data, and suction pipe flow data, the target crank arrangement sequence is selected from the crank pin arrangement sequence.

[0012] In one possible implementation, based on structural feature data, a sequence of multiple crankpin arrangements for the target crankshaft is determined, including:

[0013] Based on structural feature data, the power interval angle of the hydraulic cylinder is determined. The structural feature data includes the type of reciprocating pump to which the target crankshaft belongs and the number of hydraulic cylinders corresponding to the target crankshaft. The power interval angle is used to indicate the angle between the phase angles of the crank pins.

[0014] Select the phase angle of any crank pin as the initial phase angle, and determine the range of values ​​for the initial phase angle;

[0015] Based on the initial phase angle range and the power interval angle, determine the phase angles of other crank pins, and establish the correspondence between the crank pins and the ranges of their phase angles.

[0016] Based on the correspondence, the crank pins are arranged and combined to remove duplicates, resulting in multiple crank pin arrangement sequences.

[0017] In one possible implementation, the bearing housing support reaction force data includes the bearing housing support reaction force of the bearing housing where the crank pin is located and the force characteristics of the pump frame; the inertial moment data includes the inertial moment and the excitation load characteristics; and the suction pipe flow rate data includes the cross-sectional flow rate of the main suction pipe corresponding to the crank pin and the flow balance characteristics.

[0018] Based on the motion model, the bearing seat reaction force data, inertial moment data, and suction pipe flow rate data for the crankpin arrangement sequence were determined, including:

[0019] Based on the motion model, the bearing housing support reaction force, inertial moment, and cross-sectional flow rate of the main suction pipe are determined. The inertial moment includes torsional moment and roll moment.

[0020] Based on the correspondence, the range of crank pin values ​​in the crank pin arrangement sequence is traversed to determine the pump frame stress characteristics, excitation load characteristics, and flow balance characteristics of each crank pin arrangement sequence.

[0021] The pump frame stress characteristics include the maximum value of the bearing seat reaction force and the resultant force of the bearing seat reaction force; the excitation load characteristics include the maximum value of the torsional moment, the fluctuation difference of the torsional moment, the maximum value of the roll moment, and the fluctuation difference of the roll moment. The fluctuation difference of the torsional moment is determined by the difference between the maximum and minimum values ​​of the torsional moment, and the fluctuation difference of the roll moment is determined by the difference between the maximum and minimum values ​​of the roll moment; the flow balance characteristics include the flow fluctuation value and the flow interruption angle. The flow fluctuation value is determined by the difference between the maximum and minimum values ​​of the cross-sectional flow rate, and the flow interruption angle is determined by the cross-sectional flow rate.

[0022] In one possible implementation, based on a motion model, the bearing housing support reaction force, inertial moment, and cross-sectional flow rate of the main suction pipe are determined, including:

[0023] Based on the motion model and the phase angle of the crank pin, the force exerted by the connecting rod on the corresponding crank pin and the inertial force of the crank pin are obtained.

[0024] Based on the applied forces and the inertial force of the crank pin, determine the total support reaction force of the crank pin.

[0025] Based on the total support reaction force of the crankpin, determine the bearing housing support reaction force.

[0026] In one possible implementation, based on a motion model, the bearing housing support reaction force, inertial moment, and cross-sectional flow rate of the main suction pipe are determined, including:

[0027] Based on the motion model and the phase angle of the crank pin, the inertial force characteristics during the coordinated motion process are obtained. The inertial force characteristics include a first inertial force about the rotating motion component and a second inertial force about the reciprocating motion component. The reciprocating motion component includes a piston structure, and the rotating motion component includes a crank structure.

[0028] Based on the first inertial force and the second inertial force, determine the total inertial force of the crank pin;

[0029] Based on the total inertial force of the crankpins in the crankpin arrangement sequence and the spacing between adjacent crankpins in the structural feature data, the torsional moment and roll moment of the crankpin arrangement sequence are determined.

[0030] In one possible implementation, based on a motion model, the bearing housing support reaction force, inertial moment, and cross-sectional flow rate of the main suction pipe are determined, including:

[0031] Based on the phase angle of the crank pin, determine the instantaneous flow rate of the branch suction pipe corresponding to the crank pin;

[0032] Based on the instantaneous flow rate of the branch suction pipe, the cross-sectional flow rate of multiple flow sections on the main suction pipe is calculated. The flow sections are determined by the position of the branch suction pipe on the main suction pipe.

[0033] In one possible implementation, based on bearing seat reaction force data, inertial moment data, and suction pipe flow rate data, a target crankpin arrangement sequence is selected from the crankpin arrangement sequence, including:

[0034] The crank pin arrangement sequence corresponding to the pump frame stress characteristics, excitation load characteristics and flow balance characteristics that meet at least one preset screening condition is selected as the target crank arrangement sequence.

[0035] The screening conditions include: the maximum value of the bearing seat reaction force is less than the preset first force threshold; the resultant force of the bearing seat reaction force is less than the preset second force threshold; the maximum value of the torsional torque is less than the preset first torque threshold; the fluctuation difference of the torsional torque is less than the preset first torque fluctuation difference threshold; the maximum value of the roll torque is less than the preset second torque threshold; the fluctuation difference of the roll torque is less than the preset second torque fluctuation difference threshold; the flow fluctuation value is less than the preset flow fluctuation threshold; and the flow interruption angle is less than the preset angle threshold.

[0036] In a second aspect, this application provides an electronic device, including: a processor, and a memory communicatively connected to the processor;

[0037] The memory stores instructions that the computer executes;

[0038] The processor executes computer execution instructions stored in memory to implement the crankshaft crank arrangement method as described in the first aspect or any possible implementation of the first aspect.

[0039] Thirdly, this application provides a computer-readable storage medium storing computer-executable instructions, which, when executed by a processor, are used to implement a crankshaft crank arrangement method as described in the first aspect or any possible implementation of the first aspect.

[0040] Fourthly, this application provides a computer program product, including a computer program that, when executed by a processor, implements a crankshaft crank arrangement method as described in the first aspect or any possible implementation of the first aspect.

[0041] The crankshaft crank arrangement method, equipment, storage medium, and program product provided in this application analyze the motion of the crank structure, connecting rod, and piston structure in the hydraulic cylinder during the coordinated motion process. This determines the bearing seat support reaction force data, inertial torque data, and suction pipe flow data, taking into account the pump frame stress, vibration load, and flow balance. This data serves as the basis for selecting the target crank arrangement sequence, achieving a reasonable crank arrangement. This improves the comprehensiveness of the seven-cylinder reciprocating pump design, thereby enhancing the reliability and product performance of the seven-cylinder reciprocating pump. Attached Figure Description

[0042] The accompanying drawings, which are incorporated in and form part of this specification, illustrate embodiments consistent with this application and, together with the description, serve to explain the principles of this application.

[0043] Figure 1 is a flowchart illustrating the crankshaft crank arrangement method provided in an embodiment of this application;

[0044] Figure 2 is a schematic diagram of a crankshaft space coordinate system provided in an exemplary embodiment of this application;

[0045] Figure 3 is a schematic diagram of a crank pin arrangement sequence provided in an exemplary embodiment of this application;

[0046] Figure 4 is a schematic diagram of the motion model provided in an embodiment of this application;

[0047] Figure 5 is a flowchart illustrating the process of determining the crank pin arrangement sequence according to an embodiment of this application;

[0048] Figure 6 is a flowchart illustrating the process of determining bearing seat reaction force data, inertial moment data, and suction pipe flow rate data according to an embodiment of this application.

[0049] Figure 7 is a schematic diagram of the process for determining the bearing seat support reaction force according to an embodiment of this application;

[0050] Figure 8 is a schematic diagram of the forces acting on the crank provided in an embodiment of this application;

[0051] Figure 9 is a structural schematic diagram of the crankshaft provided in an embodiment of this application;

[0052] Figure 10 is a flowchart illustrating the determination of torsional moment and roll moment provided in an embodiment of this application;

[0053] Figure 11 is a schematic flowchart of the process for determining the cross-sectional flow rate provided in an embodiment of this application;

[0054] Figure 12 is a schematic diagram of the flow cross section on the main suction pipe provided in an embodiment of this application;

[0055] Figure 13 is a graph showing the flow interruption angle and flow rate fluctuation of the cross-section 1-1 provided in the embodiment of this application;

[0056] Figure 14 is a graph showing the flow interruption angle and flow rate fluctuation of the cross-section 2-2 provided in the embodiment of this application;

[0057] Figure 15 is a graph showing the flow interruption angle and flow rate fluctuation of the cross-section 3-3 provided in the embodiment of this application;

[0058] Figure 16 is a graph showing the flow interruption angle and flow rate fluctuation of the cross-section 4-4 provided in the embodiment of this application;

[0059] Figure 17 is a diagram showing the first fluctuation of the flow rate at the flow interruption angle of the flow cross section 5-5 provided in the embodiment of this application.

[0060] Figure 18 is a second fluctuation diagram of the flow interruption angle and cross-sectional flow rate of the flow section 5-5 provided in the embodiment of this application;

[0061] Figure 19 is a diagram showing the first fluctuation of the flow rate at the flow interruption angle of the cross-section 6-6 provided in the embodiment of this application.

[0062] Figure 20 is a second fluctuation diagram of the flow interruption angle and cross-sectional flow rate of the flow passage 6-6 provided in the embodiment of this application;

[0063] Figure 21 is a graph showing the flow interruption angle and flow rate fluctuation of the cross-section 7-7 provided in the embodiment of this application;

[0064] Figure 22 is a first distribution diagram of the maximum value of the bearing seat support reaction force of the crank pin arrangement sequence provided in the embodiment of this application;

[0065] Figure 23 is a second distribution diagram of the maximum value of the bearing seat support reaction force of the crank pin arrangement sequence provided in the embodiment of this application;

[0066] Figure 24 is a first distribution diagram of the resultant force of the bearing seat support reaction force of the crank pin arrangement sequence provided in the embodiment of this application;

[0067] Figure 25 is a second distribution diagram of the resultant force of the bearing seat support reaction force of the crank pin arrangement sequence provided in the embodiment of this application;

[0068] Figure 26 is a first distribution diagram of the maximum torsional torque of the crank pin arrangement sequence provided in the embodiment of this application;

[0069] Figure 27 is a second distribution diagram of the maximum torsional moment of the crank pin arrangement sequence provided in the embodiments of this application;

[0070] Figure 28 is a first distribution diagram of the fluctuation difference of torsional torque in the crank pin arrangement sequence provided in the embodiment of this application;

[0071] Figure 29 is a second distribution diagram of the fluctuation difference of torsional torque in the crank pin arrangement sequence provided in the embodiment of this application;

[0072] Figure 30 is a first distribution diagram of the maximum value of the rocking moment of the crank pin arrangement sequence provided in the embodiment of this application;

[0073] Figure 31 is a second distribution diagram of the maximum value of the rocking moment of the crank pin arrangement sequence provided in the embodiment of this application;

[0074] Figure 32 is a first distribution diagram of the fluctuation difference of the roll moment of the crank pin arrangement sequence provided in the embodiment of this application;

[0075] Figure 33 is a second distribution diagram of the fluctuation difference of the roll moment of the crank pin arrangement sequence provided in the embodiment of this application;

[0076] Figure 34 is a schematic diagram of the crankshaft crank arrangement device provided in an embodiment of this application;

[0077] Figure 35 is a schematic diagram of the structure of an electronic device provided in an embodiment of this application.

[0078] The accompanying drawings illustrate specific embodiments of this application, which will be described in more detail below. These drawings and descriptions are not intended to limit the scope of the concept in any way, but rather to illustrate the concept of this application to those skilled in the art through reference to particular embodiments. Detailed Implementation

[0079] Exemplary embodiments will now be described in detail, examples of which are illustrated in the accompanying drawings. When the following description relates to the drawings, unless otherwise indicated, the same numbers in different drawings denote the same or similar elements. The embodiments described in the following exemplary embodiments do not represent all embodiments consistent with this application. Rather, they are merely examples of apparatuses and methods consistent with some aspects of this application as detailed in the appended claims.

[0080] First, let me explain the terms used in this application:

[0081] Crankshaft: The crankshaft is one of the most important components in a reciprocating pump. It is powered by an electric motor to rotate, driving the connecting rod to reciprocate, and it bears complex alternating loads.

[0082] Crank: Consists of a crank pin on the crankshaft and its left and right adjacent crank arms; the crankshaft contains multiple cranks.

[0083] Crank pin: refers to the key part on the crankshaft used to connect the connecting rod. It is assembled with the connecting rod to form a rotating pair and transmits power to the connecting rod.

[0084] Connecting rod: It is a key component in reciprocating pumps. One end is connected to the crankshaft and the other end is connected to the crosshead, converting the rotational motion of the crankshaft into the reciprocating linear motion of the crosshead.

[0085] Piston: Connected to a crosshead via a piston rod, the piston moves in a reciprocating linear motion, thus changing the volume of the cylinder cavity.

[0086] Bearing housing reaction force: refers to the reaction force generated by the bearing housing on the bearing when it supports the bearing and bears the various forces generated by it (such as radial force and axial force).

[0087] Inertial torque: refers to the physical quantity of an object's rotational inertia about a certain axis.

[0088] Phase angle of crank pins: refers to the relative positional relationship between each crank pin (or crank) on the crankshaft, expressed as an angle. It is described in detail as follows: the projection point of the crank pin centerline on the end face of the crankshaft and the projection point of the crankshaft centerline on the end face form a straight line, and each crank pin forms an angle between the straight lines.

[0089] In existing technologies, analysis of field problems and applications of five-cylinder reciprocating pumps reveals that the crankshaft crank arrangement is a crucial factor affecting the overall pump vibration, stress, and flow fluctuations. Different crank arrangements result in variations in pump performance and reliability. Therefore, in the research of seven-cylinder reciprocating pumps, the performance differences caused by different crank arrangements necessitate a focused analysis of how to achieve a reasonable crank arrangement.

[0090] Based on the above problems, this application analyzes the data of the crank structure, connecting rod and piston structure during the coordinated motion process to determine the bearing seat reaction force data, inertial torque data and suction pipe flow data corresponding to the crank structure. This data is used as the basis for screening the target crank arrangement sequence, so as to achieve a reasonable crank arrangement and improve the reliability and product performance of the seven-cylinder reciprocating pump.

[0091] The execution subject of the method in this application embodiment can be any electronic device with data processing capabilities, such as a terminal or server. It is understood that this application can be applied to independent electronic devices, as well as to electronic device clusters or distributed systems composed of multiple electronic devices.

[0092] For example, the method of this application embodiment is applied to a terminal device. The terminal device acquires the structural feature data of the crankshaft, determines the crank pin arrangement sequence of the crankshaft based on the structural feature data, and then combines the motion data of the crankshaft, connecting rod and piston structure in the coordinated motion process to determine the bearing seat support reaction force data, inertial torque data and suction pipe flow data of each crank pin arrangement sequence, thereby filtering out the target crank arrangement sequence.

[0093] It should be noted that the embodiments of this application can be applied to any crankshaft with multiple crankshaft structures, and the embodiments of this application do not limit the specific application scenario. For example, the crankshaft can be a seven-crankshaft.

[0094] The crankshaft crankpin arrangement method provided in this application aims to solve the above-mentioned technical problems of the prior art.

[0095] The technical solution of this application and how the technical solution of this application solves the above-mentioned technical problems are described in detail below with specific embodiments. These specific embodiments can be combined with each other, and the same or similar concepts or processes may not be described again in some embodiments. The embodiments of this application will now be described with reference to the accompanying drawings.

[0096] Figure 1 is a flowchart illustrating the crankshaft crankpin arrangement method provided in an embodiment of this application. The crankshaft crankpin arrangement method includes steps S101 to S105, wherein:

[0097] S101. Obtain the structural feature data of the target crankshaft with multiple crank structures.

[0098] In this application, a crankshaft with multiple crankshafts may be a seven-crankshaft, and this application does not limit this. The structural feature data may include crankshaft structure, support method, and connection structure, and may be feature data related to the structure of the crankshaft.

[0099] For example, a seven-turn crankshaft is used as an example for illustration. Figure 2 is a schematic diagram of the crankshaft spatial coordinate system provided in an exemplary embodiment of this application. Based on the structural feature data of the seven-turn crankshaft, a spatial rectangular coordinate system is established. As shown in Figure 2, point O is the center point of the crankshaft axis, the horizontal direction of the crankshaft (from the power end to the hydraulic end) is the X-axis, the vertical upward direction is the Y-axis, and the axial direction is the Z-axis, so as to intuitively display the structural features of the crankshaft.

[0100] S102. Based on structural feature data, determine the arrangement sequence of multiple crank pins of the target crankshaft. The arrangement sequence of crank pins is used to indicate the working order of the hydraulic cylinders corresponding to the crank pins in the crankshaft structure.

[0101] In this application, the hydraulic cylinder can correspond to the crankshaft structure, and the crank pin arrangement sequence includes the phase angle of the crank pins corresponding to the power sequence, so that the hydraulic cylinder performs work according to the crank pin arrangement sequence. For example, for a seven-crankshaft, the crank pin arrangement sequence is 1523467, then the hydraulic cylinders (corresponding to crank pins) performing work in each power interval angle are 1523467.

[0102] For example, taking a seven-crankshaft as an example, the crankpin arrangement sequence is the order in which the seven crankpins are arranged in a certain direction, and the phase angle of each crankpin is different in each phase sequence. Figure 3 is a schematic diagram of the crankpin arrangement sequence provided in an exemplary embodiment of this application. As shown in Figure 3, the angle between the crankpins (the straight line from the center of the crankpin to the center of the crankshaft projected onto the end face) is γ = 360° / 7. The phase angle is the angle between the center of the crankpin and the XZ plane in one direction of the circumference; the crankpin arrangement sequence (phase sequence) is the order in which the seven crankpins are arranged in that direction, and the phase angle of each crankpin is different in each phase sequence; the initial phase is a calibration state in which the phase angle of one crankpin is selected as the initial phase angle, and then the phase angles of other crankpins are determined according to the phase sequence for subsequent analysis and calculation. All crankpin arrangement sequences can be obtained by using the idea of ​​permutation and combination. For example, the crankpin arrangement sequence can be A 7 7 = 5040 kinds.

[0103] S103. Based on structural feature data, establish a motion model. The motion model is used to describe the coordinated motion process of the crank structure, the corresponding connecting rod, and the piston structure in the hydraulic cylinder.

[0104] In this application, the crankshaft structure can drive the piston structure in the hydraulic cylinder to move through the corresponding connecting rod, and the motion model can be used to describe the motion force analysis of the motion process.

[0105] For example, Figure 4 is a schematic diagram of the motion model provided in an embodiment of this application. As shown in Figure 4, the motion model can be a model of the motion force of a crank-connecting rod mechanism. In Figure 4, the subscript F indicates the force, such as F... 3x This can represent the force acting on the crank pin in the x-direction, with the arrow indicating the direction of the force. In practical applications, F 1x F 1y F is the force exerted by the connecting rod on the crosshead. 2x F represents the frictional force between the crosshead and the guide plate. 2y F represents the normal force exerted by the crosshead on the guide plate. 3x F 3y ω is the force exerted by the connecting rod on the crankpin; F is the combined piston force; m2 is the sum of the masses of the reciprocating moving parts such as the crosshead, plunger, intermediate connecting rod, and crosshead bearing; θ is the crankshaft phase angle; ω is the crankshaft rotational angular velocity; β is the connecting rod swing angle; L is the connecting rod length; l is the distance from the connecting rod center of mass C to the crankpin center.

[0106] As shown in Figure 4, a motion model can be established based on the crankshaft's corresponding crankshaft structure, support method, and connection structure.

[0107] S104. Based on the motion model, determine the bearing seat support reaction force data, inertial moment data, and intake pipe flow rate data for the crank pin arrangement sequence. The intake pipe flow rate data is used to describe the cross-sectional flow rate of the main intake pipe corresponding to the crank pin.

[0108] In this application, the motion model can be used to analyze the reaction force F of the connecting rod on the crankshaft during crank motion. L and crank pin inertial force F h Furthermore, this can be determined based on the reaction force F of the connecting rod on the crankshaft. L and the crank pin inertial force F h It can determine the bearing housing support reaction force data; and it can also determine the inertial torque data and suction pipe flow data for the crank pin arrangement sequence based on the motion model.

[0109] For example, the reaction force F of the connecting rod on the crankshaft can be determined according to the following expressions (1) and (2). L The force acts on the center of the crank pin. Using the formula directly, the forces acting in the X and Y axes are calculated as follows: FLx (θ)=F 3x =-m3a cx -m2a(θ)+F+f2F 2y J(θ) (1) F Ly (θ)=F 3y =(m2-m3)g-m3a cy +F 2y (2)

[0110] Where: m3 is the mass of the connecting rod; a cx Let a be the x-axis acceleration of the connecting rod's center of mass; cy θ is the y-axis acceleration of the connecting rod's center of mass; a(θ) is the acceleration of the reciprocating component, in m / s². 2 f2 is the friction coefficient between the crosshead and the guide plate, which is calculated based on actual conditions; J(θ) is the friction factor between the crosshead and the guide plate.

[0111] The crankpin inertial force F can be determined according to expression (3). h The crankshaft rotates, and the inertial force of the crankpin itself is: F h =Rω 2 m1(3)

[0112] Where: m1 is the sum of the masses of rotating components such as the crank pin and connecting rod big end bearing; R is the crank length.

[0113] Furthermore, this can be based on the reaction force F of the connecting rod on the crankshaft. L Crank pin inertial force F h Determine the bearing seat support reaction force data for the crank pin arrangement sequence.

[0114] S105. Based on the bearing seat reaction force data, inertial torque data, and suction pipe flow data, the target crank arrangement sequence is selected from the crank pin arrangement sequence.

[0115] In this application, the target crank pin arrangement sequence can be determined from multiple crank pin arrangement sequences. The target crank pin arrangement sequence can be selected based on bearing seat support reaction force data, inertial torque data, and suction pipe flow rate data.

[0116] For example, the optimal order of multiple crankpin arrangement sequences can be analyzed by comprehensively considering bearing support reaction force data, inertial moment data, and suction pipe flow rate data. For instance, the crankpin arrangement sequence with the minimum force among the bearing support reaction force data can be identified. Based on the comprehensive analysis and screening of bearing support reaction force data, inertial moment data, and suction pipe flow rate data, a target crankpin arrangement sequence can be selected from multiple crankpin arrangement sequences.

[0117] In this embodiment, the crankshaft crank arrangement method, device, electronic device, and storage medium provided in this application analyze the motion of the crank structure, connecting rod, and piston structure in the hydraulic cylinder during the coordinated motion process to determine the bearing seat support reaction force data, inertial torque data, and suction pipe flow data. These data are then used as the basis for determining the optimal sequence of crank pin arrangement. This achieves a reasonable crank arrangement considering the pump frame stress, vibration load, and flow balance, thus improving the comprehensiveness of the seven-cylinder reciprocating pump design and consequently enhancing the reliability and performance of the seven-cylinder reciprocating pump.

[0118] Figure 5 is a flowchart illustrating the process of determining the crankpin arrangement sequence according to an embodiment of this application. In step S102, determining the multiple crankpin arrangement sequences of the target crankshaft based on structural feature data includes steps S501 to S504, wherein:

[0119] S501. Based on structural feature data, determine the power interval angle of the hydraulic cylinder. The structural feature data includes the type of reciprocating pump to which the target crankshaft belongs and the number of hydraulic cylinders corresponding to the target crankshaft. The power interval angle is used to indicate the angle between the phase angles of the crank pins.

[0120] S502. Select the phase angle of any crank pin as the initial phase angle, and determine the range of values ​​for the initial phase angle.

[0121] S503. Based on the value range of the initial phase angle and the power interval angle, determine the phase angle of other crank pins, and establish the correspondence between the value range of the phase angle of the crank pins.

[0122] S504. Based on the correspondence, the crank pins are arranged and combined to remove duplicates, resulting in multiple crank pin arrangement sequences.

[0123] For example, the included angle between the crankpins (the straight line from the center of the crankpin to the center of the crankshaft projected onto the end face) can be determined based on structural feature data. For instance, taking a seven-crankshaft as an example, as shown in Figure 3, the included angle between the crankpins (the straight line from the center of the crankpin to the center of the crankshaft projected onto the end face) is γ = 360° / 7. According to the crankshaft operating conditions, the crankshaft rotation process is a closed-loop rotation. Therefore, when the phase angles of crankpins 1, 2, ..., 7 are taken as the initial phases, they can be considered as a phase sequence, such as the seven phase sequences 1234567, 2345671, ..., 7654321. For the phase sequences in the clockwise and counterclockwise directions of the crankshaft circumference, given the interchangeability of the left and right ends of the crankshaft (i.e., the crankshaft rotates 180° along the Y-axis), they are considered repeating phase sequences. For example, phase sequences 1234567 and 1765432 are repeating phase sequences, and duplicates can be removed from these repeating phase sequences. Taking a seven-crankshaft as an example, after weight removal, the number of phase sequences of the seven-cylinder reciprocating pump crankshaft is 5040 / (7×2)=360. This application utilizes the phase sequence repetition characteristic to take the phase angle of crankpin No. 1 as the initial phase angle of all phase sequences and assign numbers as shown in Table 1 below.

[0124] Table 1. Correspondence between the phase sequence numbers of the seven-cylinder pump crankshaft

[0125] In practical applications, a spatial rectangular coordinate system is established based on the seven-crankshaft structure, and the included angles between the crankpins are obtained. Using the spatial rectangular coordinate system, the definitions of phase angle, phase sequence, and initial phase are given, and the number of all phase sequences is calculated. The arrangement pattern of all phase sequences is analyzed, and duplicate phase sequences are removed to obtain the total number of phase sequences for the seven-crankshaft. Utilizing the characteristic of repeated phase sequences, all phase sequences are adjusted using the phase angle of crankpin number 1 as the initial phase to obtain the final phase sequence of the seven-crankshaft and assign it a number.

[0126] In this embodiment, through the steps S501 to S504 described above, multiple crank pin arrangement sequences can be effectively determined, and duplicates can be removed, reducing the workload of subsequent crank pin arrangement sequence analysis.

[0127] In an exemplary embodiment, the bearing housing support reaction force data includes the bearing housing support reaction force of the bearing housing where the crank pin is located and the force characteristics of the pump frame; the inertial moment data includes the inertial moment and the excitation load characteristics; and the suction pipe flow rate data includes the cross-sectional flow rate of the main suction pipe corresponding to the crank pin and the flow balance characteristics.

[0128] Figure 6 is a flowchart illustrating the process of determining bearing seat reaction force data, inertial moment data, and suction pipe flow rate data according to an embodiment of this application. In step S104, determining the bearing seat reaction force data, inertial moment data, and suction pipe flow rate data for the crank pin arrangement sequence based on the motion model includes steps S601 to S602, wherein:

[0129] S601. Based on the motion model, determine the bearing seat support reaction force, inertial moment, and cross-sectional flow rate of the main suction pipe. The inertial moment includes torsional moment and roll moment.

[0130] S602. Based on the correspondence, traverse the value range of the crank pins in the crank pin arrangement sequence to determine the pump frame force characteristics, excitation load characteristics and flow balance characteristics of each crank pin arrangement sequence.

[0131] The pump frame stress characteristics include the maximum value of the bearing seat reaction force and the resultant force of the bearing seat reaction force; the excitation load characteristics include the maximum value of the torsional moment, the fluctuation difference of the torsional moment, the maximum value of the roll moment, and the fluctuation difference of the roll moment. The fluctuation difference of the torsional moment is determined by the difference between the maximum and minimum values ​​of the torsional moment, and the fluctuation difference of the roll moment is determined by the difference between the maximum and minimum values ​​of the roll moment; the flow balance characteristics include the flow fluctuation value and the flow interruption angle. The flow fluctuation value is determined by the difference between the maximum and minimum values ​​of the cross-sectional flow rate, and the flow interruption angle is determined by the cross-sectional flow rate.

[0132] For example, based on the motion model shown in Figure 4, the bearing housing support reaction force, inertial moment, and cross-sectional flow rate of the main suction pipe can be determined. The inertial moment includes torsional moment and roll moment. As shown in Table 2 below, the correspondence between crank pin and phase angle values ​​can be used to traverse the value range of the crank pins in the crank pin arrangement sequence to determine the pump frame force characteristics, excitation load characteristics, and flow balance characteristics of each crank pin arrangement sequence.

[0133] Table 2 Correspondence between crank pin and phase angle values

[0134] Where θ is the phase angle of the crank pin.

[0135] In this embodiment, by traversing the value range of the crank pins in the crank pin arrangement sequence through the correspondence, the pump frame stress characteristics, excitation load characteristics, and flow balance characteristics of each crank pin arrangement sequence can be determined. Furthermore, based on the above characteristics, a method for comprehensive phase sequence optimization can be determined, thereby enabling reasonable crank arrangement, improving the comprehensiveness of the seven-cylinder reciprocating pump design, and thus improving the reliability and product performance of the seven-cylinder reciprocating pump.

[0136] Figure 7 is a schematic flowchart of the process for determining the bearing housing support reaction force according to an embodiment of this application. In step S601, determining the bearing housing support reaction force, inertial torque, and cross-sectional flow rate of the main suction pipe based on the motion model includes steps S701 to S703, wherein:

[0137] S701. Based on the motion model and the phase angle of the crank pin, obtain the force applied by the connecting rod to the corresponding crank pin and the inertial force of the crank pin.

[0138] S702. Based on the applied force and the inertial force of the crank pin, determine the total support reaction force of the crank pin.

[0139] S703. Based on the total support reaction force of the crankpin, determine the bearing housing support reaction force.

[0140] In this application, a motion force model of a single crank-connecting rod mechanism is used to analyze the force situation. Corresponding numbers for the crank pins and phase angles of the seven-crankshaft are assigned, and the total support reaction force of the crank pins and the support reaction force of each bearing seat in each phase sequence are calculated. Specific values ​​for the phase angles are set, and the maximum value and resultant force of the bearing seat support reaction force are calculated. The bearing seat support reaction force in each phase sequence is then analyzed.

[0141] For example, Figure 8 is a force diagram of the crank provided in the embodiment of this application, and Figure 9 is a structural diagram of the crankshaft provided in the embodiment of this application, wherein each crank is supported by a corresponding bearing seat. Taking a seven-crankshaft as an example, as shown in Figure 9, the bearing seats corresponding to each crank of the seven-crankshaft are numbered as I, II, III, IV, V, VI, VII, VIII, and the crank pins of the seven-crankshaft are numbered as 1, 2, 3, 4, 5, 6, 7. As shown in Figure 8, from the force analysis model of the crank, the support reaction force of the bearing seat on the crankshaft can be derived, which mainly consists of two parts: one is the reaction force of the connecting rod on the crankshaft, and the other is the inertial force of the crank pin itself during the rotation of the crankshaft. The total support reaction force of the crank pin can be calculated. The component of the total support reaction force on the X-axis is expressed as (4): R xi =(F Lx (θ)+F h cosθ) / 2(4); The component of the total support reaction force on the Y-axis is given by expression (5): R yi =(F Ly (θ)+F h sinθ) / 2(5); where: F Lx (θ) is the reaction force F of the connecting rod on the crankshaft. L Component of force along the X-axis; F Ly (θ) is the reaction force F of the connecting rod on the crankshaft. L Component of force along the Y-axis; F h θ represents the inertial force of the crank pin; θ is the phase angle.

[0142] Further analyzing the crankshaft structure, each crankpin is primarily supported by the cranks on either side. Force transmission can be considered to be limited to the bearing housings on the two cranks, without affecting the remaining bearing housings. Therefore, the support reactions of each bearing housing can be obtained using the following expression:

[0143] Bearing housing I:

[0144] Bearing housing II-VII:

[0145] Bearing housing VIII:

[0146] Where: i takes values ​​from 2 to 7.

[0147] Based on the range of α from 0 to 360° as shown in Table 2, in order to ensure the accuracy of the calculation while simplifying the calculation, this application takes an initial phase angle every 5°, that is, α takes values ​​of 0, 5°, 10°, ..., 355°. The maximum value of the bearing support reaction force and the resultant force value of each phase sequence are calculated through expressions (6) to (8). Based on this, the bearing support reaction force of each phase sequence is analyzed, and the maximum value of the bearing support reaction force of each phase sequence is calculated as follows: R max =MAX(R1,R i ,R8)(9); Calculate the resultant force of the bearing support reaction force for each phase sequence: R 合 =R1+∑2 7 R i +R8(10).

[0148] In this embodiment, the bearing seat support reaction force can be effectively determined through the above steps S701 to S703. This is beneficial for selecting the target crank arrangement sequence based on the bearing seat support reaction force, thereby improving the comprehensiveness of the seven-cylinder reciprocating pump design and thus improving the reliability and product performance of the seven-cylinder reciprocating pump.

[0149] Figure 10 is a flowchart illustrating the determination of torsional torque and roll torque according to an embodiment of this application. In step S601, determining the bearing seat support reaction force, inertial torque, and cross-sectional flow rate of the main suction pipe based on the motion model includes steps S1001 to S1003, wherein:

[0150] S1001. Based on the motion model and the phase angle of the crank pin, obtain the inertial force characteristics during the coordinated motion process. The inertial force characteristics include a first inertial force about the rotating motion component and a second inertial force about the reciprocating motion component. The reciprocating motion component includes a piston structure, and the rotating motion component includes a crank structure.

[0151] S1002. Based on the first inertial force and the second inertial force, determine the total inertial force of the crank pin;

[0152] S1003. Based on the total inertial force of the crank pins in the crank pin arrangement sequence and the spacing between adjacent crank pins in the structural feature data, determine the torsional moment and roll moment of the crank pin arrangement sequence.

[0153] In this application, the inertial torque of each phase sequence, including torsional torque and roll torque, is analyzed using the inertial force calculation theory of single crank connecting rod mechanism. The maximum value and fluctuation difference of the torsional torque and roll torque of each phase sequence are calculated by setting the phase angle value.

[0154] For example, to determine the inertial force, the unbalanced mass of the crank-connecting rod mechanism can be divided into two parts: the mass of the reciprocating part and the mass of the rotating part. Here, for simplified calculation, the reciprocating mass is concentrated entirely at the center of the crosshead, and the unbalanced rotating mass is transferred entirely to the center of the crank pin.

[0155] During operation, the connecting rod undergoes a complex motion combining rotation and reciprocating motion. Simplifying the calculation of the connecting rod's mass, one part of the mass is concentrated at the center of the crank pin due to rotational motion, while the other part is concentrated at the center of the crosshead due to reciprocating motion.

[0156] The inertial force of the rotating component is calculated as shown in expressions (11) and (12): F H =Rω 2 (m1+km3) (11) k=l / L (12)

[0157] The inertial force of the reciprocating motion component is calculated as shown in expression (13): F W =-(m1+(1-k)m2)a(θ) (13)

[0158] The total inertial force of each phase sequence is calculated as shown in expressions (14) and (15): I xi =(F H cos(θ)+F w )=(Rω 2 (m1+km3)cos(θ)-(m1+(1- k)m2)a(θ)) (14); I yi =Rω 2 (m1+km3)sin(θ) (15);

[0159] The values ​​of i and θ are consistent with those in Table 2.

[0160] Optionally, taking a seven-crankshaft as an example, referring to the flow diagram shown in Figure 1 and the structural diagram of the crankshaft shown in Figure 9, the resultant force of the inertial forces of the seven reciprocating motions and the rotational inertial forces in the X, Y, and Z directions is equal to zero, but their resultant torque on the X and Y axes is not zero, which will cause the entire pump to twist and roll. This application assumes that the crankshaft's center of mass is at point O, so the No. 4 crank pin does not generate a torque.

[0161] The torsional moment can be obtained as shown in expression (16): M x =(3I x1+2I x2 +I x3 -I x5 -2I x6 -3I x7 )×S(16);

[0162] The roll moment can be obtained as shown in expression (17): M y =(3I y1 +2I y2 +I y3 -I y5 -2I y6 -3I y7 )×S(17);

[0163] Among them: I xi I is the inertial force in the X-axis direction during single-crutch motion; yi is the inertial force in the Y-axis direction during single-crank motion; S is the distance between adjacent crank pins.

[0164] When calculating the inertial torque of each phase sequence, the values ​​of α shown in Table 2 are 0, 5°, 10°, ..., 355°. The maximum value and fluctuation difference of the overall pump rolling torque and torsional torque under each phase sequence are calculated using expressions (16) and (17). In this way, the inertial torque data in step S104 can be determined.

[0165] The maximum torsional torque and fluctuation difference of the entire pump in each phase sequence are calculated as shown in expressions (18) and (19): M xmax =MAX(M x(α＝0°) M x(α＝5°) M x(α＝10°) ,…,M x(α＝355°) (18) M x波动差值 =MAX(M x(α＝0°) M x(α＝5°) M x(α＝10°) ,…,M x(α＝355°) )- MIN(M x(α＝0°) M x(α＝5°) M x(α＝10°) ,…,M x(α＝355°) (19)

[0166] The maximum value of the yaw moment and the fluctuation difference of the whole pump in each phase sequence are calculated as shown in expressions (20) and (21): M ymax =MAX(M y(α＝0°) M x(α＝5°) M y(α＝10°) ,…,M y(α＝355°) (20) M y波动差值 =MAX(M y(α＝0°) M y(α＝5°) M y(α＝10°) ,…,My(α＝355°) )- MIN(M y(α＝0°) M y(α＝5°) M y(α＝10°) ,…,M y(α＝355°) )(twenty one)

[0167] In this embodiment, the inertial torque data in step S1001 to S1003 can be effectively determined through the above steps. This is beneficial for screening the target crank arrangement sequence based on the inertial torque data, and for improving the comprehensiveness of the seven-cylinder reciprocating pump design, thereby improving the reliability and product performance of the seven-cylinder reciprocating pump.

[0168] Figure 11 is a schematic flowchart of the process for determining the cross-sectional flow rate provided in an embodiment of this application. In step S601, determining the bearing seat support reaction force, inertial moment, and cross-sectional flow rate of the main suction pipe based on the motion model includes steps S1101 to S1102, wherein:

[0169] S1101. Based on the phase angle of the crank pin, determine the instantaneous flow rate of the branch suction pipe corresponding to the crank pin;

[0170] S1102. Based on the instantaneous flow rate of the branch suction pipe, calculate the cross-sectional flow rate of multiple flow sections on the main suction pipe. The flow sections are determined by the position of the branch suction pipe on the main suction pipe.

[0171] In this application, the uniformity of the suction tube flow rate is mainly reflected by two parameters: the flow interruption angle and the flow rate fluctuation value. The flow interruption angle affects the continuity of suction, while the flow rate fluctuation affects the stability of suction. Each section of the main suction tube is numbered, and the flow rate at each section is calculated using dimensionless instantaneous flow rate. The uniformity of the suction tube flow rate is analyzed using the flow interruption angle and fluctuation value at each section.

[0172] For example, the uniformity of the suction pipe flow rate is mainly reflected by two parameters: the flow interruption angle and the flow fluctuation value. The flow interruption angle affects the continuity of suction, while the flow fluctuation affects the stability of suction. Figure 12 is a schematic diagram of the flow cross-section on the main suction pipe provided in an embodiment of this application. As shown in Figure 12, the main suction pipe is divided into 7 cross-sections, namely cross-section 1-1, cross-section 2-2, cross-section 3-3, cross-section 4-4, cross-section 5-5, cross-section 6-6, and cross-section 7-7. The numbers of each branch suction pipe correspond one-to-one with the crank pin numbers. The flow rate of each cross-section can be obtained in the following way:

[0173] 1-1 Sectional Flow Rate: 2-2 Section Flow Rate:

[0174] 3-3 Sectional Flow Rate: 4-4 Section Flow Rate:

[0175] 5-5 Section Flow Rate: 6-6 Section Flow Rate:

[0176] 7-7 Sectional Flow Rate:

[0177] in: This refers to the dimensionless instantaneous flow rate of a single cylinder intake.

[0178] The dimensionless instantaneous flow rate of each inhalation tube can be obtained by expression (11):

[0179] The values ​​of i and θ correspond to those in Table 2 above.

[0180] The α value is set to 0, 5°, 10°, ..., 355°, resulting in 72 possible values. The flow interruption angle and flow fluctuation value at each cross-section are then calculated. The flow interruption angle is determined by whether there is flow at that cross-section. If the flow is 0, a flow interruption occurs, and the flow interruption angle is equal to the number of angles with 0 flow multiplied by 5.

[0181] Calculate the flow fluctuation values ​​at section 1-1 for each phase sequence:

[0182] Calculate the flow fluctuation values ​​at section 2-2 for each phase sequence:

[0183] Calculate the flow fluctuation values ​​at section 3-3 for each phase sequence:

[0184] Calculate the flow fluctuation values ​​at section 4-4 for each phase sequence:

[0185] Calculate the flow fluctuation values ​​at section 5-5 for each phase sequence:

[0186] Calculate the flow fluctuation values ​​at section 6-6 for each phase sequence:

[0187] Calculate the flow fluctuation values ​​at section 7-7 for each phase sequence:

[0188] Optionally, Figure 13 is a graph showing the fluctuation of flow interruption angle and cross-sectional flow rate of flow section 1-1 provided in an embodiment of this application; Figure 14 is a graph showing the fluctuation of flow interruption angle and cross-sectional flow rate of flow section 2-2 provided in an embodiment of this application; Figure 15 is a graph showing the fluctuation of flow interruption angle and cross-sectional flow rate of flow section 3-3 provided in an embodiment of this application; Figure 16 is a graph showing the fluctuation of flow interruption angle and cross-sectional flow rate of flow section 4-4 provided in an embodiment of this application; Figure 17 is a first graph showing the fluctuation of flow interruption angle and cross-sectional flow rate of flow section 5-5 provided in an embodiment of this application; Figure 18 is a second graph showing the fluctuation of flow interruption angle and cross-sectional flow rate of flow section 5-5 provided in an embodiment of this application; Figure 19 is a first graph showing the fluctuation of flow interruption angle and cross-sectional flow rate of flow section 6-6 provided in an embodiment of this application; Figure 20 is a second graph showing the fluctuation of flow interruption angle and cross-sectional flow rate of flow section 6-6 provided in an embodiment of this application; and Figure 21 is a graph showing the fluctuation of flow interruption angle and cross-sectional flow rate of flow section 7-7 provided in an embodiment of this application.

[0189] In this embodiment, the above calculation of cross-sectional flow rate is beneficial for screening the target crank arrangement sequence based on cross-sectional flow rate, which is beneficial for improving the comprehensiveness of the seven-cylinder reciprocating pump design, thereby improving the reliability and product performance of the seven-cylinder reciprocating pump.

[0190] In an exemplary embodiment, step S105, based on bearing seat reaction force data, inertial moment data, and suction pipe flow rate data, filters out a target crank pin arrangement sequence from the crank pin arrangement sequence, including:

[0191] The crank pin arrangement sequence corresponding to the pump frame stress characteristics, excitation load characteristics and flow balance characteristics that meet at least one preset screening condition is selected as the target crank arrangement sequence.

[0192] The screening conditions include: the maximum value of the bearing seat reaction force is less than the preset first force threshold; the resultant force of the bearing seat reaction force is less than the preset second force threshold; the maximum value of the torsional torque is less than the preset first torque threshold; the fluctuation difference of the torsional torque is less than the preset first torque fluctuation difference threshold; the maximum value of the roll torque is less than the preset second torque threshold; the fluctuation difference of the roll torque is less than the preset second torque fluctuation difference threshold; the flow fluctuation value is less than the preset flow fluctuation threshold; and the flow interruption angle is less than the preset angle threshold.

[0193] For example, Figure 22 is a first distribution diagram of the maximum value of the bearing seat support reaction force of the crank pin arrangement sequence provided in the embodiment of this application; Figure 23 is a second distribution diagram of the maximum value of the bearing seat support reaction force of the crank pin arrangement sequence provided in the embodiment of this application; Figure 24 is a first distribution diagram of the resultant force of the bearing seat support reaction force of the crank pin arrangement sequence provided in the embodiment of this application; Figure 25 is a second distribution diagram of the resultant force of the bearing seat support reaction force of the crank pin arrangement sequence provided in the embodiment of this application.

[0194] The crankshaft support reactions can be analyzed based on Figures 22 to 25. Referring to Figures 22 to 25, the phase sequence numbers with the smallest force among the maximum support reactions are: 165; 167; 177–179; 182; 184; 187–188; 190; 208–210; 226–228; 233; 267–268; 271–272; 277–280; 315; 318; 333–334; 337–338; 349–350. The phase sequence numbers with the smallest resultant support reaction force are: 184; 208; 226; 228; 255; 267; 272; 277; 280; 333–334; 337–338; 350–351. The optimal phase sequence numbers for comprehensive stress are: 184; 208; 226; 228; 267; 272; 277; 280; 333~334; 337~338; 350.

[0195] Optionally, Figure 26 is a first distribution diagram of the maximum value of the torsional torque of the crank pin arrangement sequence provided in the embodiment of this application; Figure 27 is a second distribution diagram of the maximum value of the torsional torque of the crank pin arrangement sequence provided in the embodiment of this application; Figure 28 is a first distribution diagram of the fluctuation difference of the torsional torque of the crank pin arrangement sequence provided in the embodiment of this application; and Figure 29 is a second distribution diagram of the fluctuation difference of the torsional torque of the crank pin arrangement sequence provided in the embodiment of this application.

[0196] The unbalanced torsional moment can be analyzed based on Figures 26 to 29. Referring to Figures 26 to 29, the analysis results of the unbalanced torsional moment are shown in Table 3 below.

[0197] Table 3. Analysis results of unbalanced torsional moments

[0198] Optionally, Figure 30 is a first distribution diagram of the maximum value of the rocker torque of the crank pin arrangement sequence provided in the embodiment of this application; Figure 31 is a second distribution diagram of the maximum value of the rocker torque of the crank pin arrangement sequence provided in the embodiment of this application; Figure 32 is a first distribution diagram of the fluctuation difference of the rocker torque of the crank pin arrangement sequence provided in the embodiment of this application; and Figure 33 is a second distribution diagram of the fluctuation difference of the rocker torque of the crank pin arrangement sequence provided in the embodiment of this application.

[0199] Based on Figures 30 to 33, the unbalanced roll moment is analyzed. Referring to Figures 30 to 33, the roll moment analysis results are shown in Table 4 below.

[0200] Table 4. Results of Rolling Moment Analysis

[0201] Optionally, the uniformity of each cross section of the suction tube can be analyzed based on Figures 13 to 21.

[0202] In practical applications, analysis of the instantaneous flow curves at various cross-sections of the suction pipe reveals that the wider the flow interruption area, the longer the duration of zero instantaneous flow, making it more prone to pipe sedimentation, which is the main cause of sand settling in the pipe. Large fluctuations in instantaneous flow indicate a large inertial head in the pipeline, which can easily lead to vibration of the entire pump and affect its performance.

[0203] Referring to the flow analysis results in section 1-1 of Figure 13, there is no difference in the phase sequence. Referring to the flow analysis results in section 2-2 of Figure 14, there is no difference in the phase sequence. Referring to the flow analysis results in section 3-3 of Figure 15, the flow interruption angle is 0° for all phases. The phase sequence numbers with the smallest flow fluctuation are 217-336, with fluctuation values ​​between 1.0415 and 1.0435. The phase sequence numbers with the next smallest flow fluctuation are 121-216 and 337-360, with fluctuation values ​​between 1.3099. Referring to the flow analysis results in section 4-4 of Figure 16, the phase sequence numbers with the smallest flow interruption angle and the smallest flow fluctuation are: 163-198; 265-276; 301-312; 343-354, with fluctuation values ​​between 0.8788 and 0.8801. Referring to the flow analysis results of section 5-5 in Figures 17 and 18, the phase sequence numbers with the smallest flow interruption angle and flow fluctuation are 37–42; 79–84; 155–158; 173–180; 187–194; 209–212; 227–230; 245–248; 265–272; 309–312; 327–328; 333–334; 339–340; 345–352; and 357–358, with fluctuation values ​​between 0.881 and 0.8782. Referring to Figures 19 and 20, the flow analysis results for section 6-6 show that the phase sequence numbers with the smallest flow interruption angle and flow fluctuation are 9–10; 15–16; 33–36; 39–40; 45–46; 51–52; 57–64; 69–70; 75–76; 81–82; 85–88; 105–106; 111–112; 129–130; 135–136; 154; 158; 161–162; 165–166; 172–174; 179; 183; 184; 190–192; 197; 207–208; 211; 215; 225–2 The values ​​for phases 26, 229, 233, 244, 248, 251, 252, 255–256, 260–261, 263–264, 267, 272–273, 276, 279, 283–286, 288, 291, 295–298, 300, 303, 308–309, 312, 315–316, 320–321, 323–327, 329, 332, 334–336, 338, 340–342, 344, 347, 350, 353, 355–357, and 359 show fluctuations between 1.0198 and 1.0204. Referring to Figure 21, the flow analysis results for section 7-7 show no difference in phase sequence.

[0204] Considering the minimum flow interruption angle and flow fluctuation of cross sections 3-3, 4-4, 5-5, and 6-6, the optimal phase sequence numbers for the intake main flow are: 173-174; 179; 190-192; 267; 309; 312; 347; 350.

[0205] Optionally, based on the above analysis and the judgment criteria, the preferred phase sequence is shown in Table 5 below, which means the preferred phase sequence can be used as the target crank arrangement sequence. The phase sequence numbers and corresponding phase sequences in Table 5 can be obtained from Table 1.

[0206] Table 5 Preferred Phase Sequence

[0207] In this embodiment, 360 unique phase sequence arrangements were obtained through phase sequence analysis of a seven-cylinder crankshaft, laying the foundation for subsequent research. A set of optimal phase sequence determination criteria was provided for researchers' reference. Through the calculation and analysis of the 360 ​​phase sequences, a comprehensive phase sequence optimization method based on four indicators—optimal pump frame stress, minimum excitation load (minimum torsional and lateral torques at the power end), and good flow balance—was derived for different application scenarios. An optimal phase sequence that can be referenced for the seven-cylinder reciprocating pump was obtained, providing a theoretical basis and multiple solutions for crankshaft phase sequence design. This can have a positive impact on the overall pump design, improving the product performance of the seven-cylinder reciprocating pump.

[0208] In an exemplary embodiment, FIG34 is a schematic diagram of a crankshaft crank arrangement device 340 provided in an embodiment of the present application, the crankshaft crank arrangement device 340 including:

[0209] Data acquisition module 3401 is used to acquire structural feature data of a target crankshaft with multiple crank structures;

[0210] The sequence generation module 3402 is used to determine the arrangement sequence of multiple crank pins of the target crankshaft based on structural feature data. The arrangement sequence of crank pins is used to indicate the working order of the hydraulic cylinders corresponding to the crank pins in the crankshaft structure.

[0211] The motion model construction module 3403 is used to build a motion model based on structural feature data. The motion model is used to describe the coordinated motion process of the crank structure, the corresponding connecting rod, and the piston structure in the hydraulic cylinder.

[0212] The calculation module 3404 is used to determine the bearing seat support reaction force data, inertial moment data and intake pipe flow data for the crank pin arrangement sequence based on the motion model. The intake pipe flow data is used to describe the cross-sectional flow of the main intake pipe corresponding to the crank pin.

[0213] The sequence optimization module 3405 is used to select the target crank arrangement sequence from the crank pin arrangement sequence based on the bearing seat support reaction force data, inertial torque data and suction pipe flow data.

[0214] In some embodiments, the sequence generation module includes:

[0215] The power interval angle determination unit is used to determine the power interval angle of the hydraulic cylinder based on structural feature data. The structural feature data includes the type of reciprocating pump to which the target crankshaft belongs and the number of hydraulic cylinders corresponding to the target crankshaft. The power interval angle is used to indicate the angle between the phase angles of the crank pins.

[0216] The initial phase angle selection unit is used to select the phase angle of any crank pin as the initial phase angle and determine the range of values ​​for the initial phase angle.

[0217] The correspondence establishment unit is used to determine the phase angle of other crank pins based on the value range of the initial phase angle and the power interval angle, and to establish the correspondence between the value range of the phase angle of the crank pins.

[0218] The combined deduplication unit is used to arrange and combine crank pins based on correspondence to remove duplicates, resulting in multiple crank pin arrangement sequences.

[0219] In some embodiments, the bearing housing support reaction force data includes the bearing housing support reaction force of the bearing housing where the crank pin is located and the force characteristics of the pump frame; the inertial moment data includes the inertial moment and the excitation load characteristics; and the suction pipe flow rate data includes the cross-sectional flow rate of the main suction pipe corresponding to the crank pin and the flow balance characteristics.

[0220] The calculation module includes:

[0221] The parameter calculation unit is used to determine the bearing seat support reaction force, inertial moment, and cross-sectional flow rate of the main suction pipe based on the motion model. The inertial moment includes torsional moment and roll moment.

[0222] The feature calculation unit is used to traverse the value range of crank pins in the crank pin arrangement sequence based on the correspondence relationship, and determine the pump frame force characteristics, excitation load characteristics and flow balance characteristics of each crank pin arrangement sequence.

[0223] The pump frame stress characteristics include the maximum value of the bearing seat reaction force and the resultant force of the bearing seat reaction force; the excitation load characteristics include the maximum value of the torsional moment, the fluctuation difference of the torsional moment, the maximum value of the roll moment, and the fluctuation difference of the roll moment. The fluctuation difference of the torsional moment is determined by the difference between the maximum and minimum values ​​of the torsional moment, and the fluctuation difference of the roll moment is determined by the difference between the maximum and minimum values ​​of the roll moment; the flow balance characteristics include the flow fluctuation value and the flow interruption angle. The flow fluctuation value is determined by the difference between the maximum and minimum values ​​of the cross-sectional flow rate, and the flow interruption angle is determined by the cross-sectional flow rate.

[0224] In some embodiments, the parameter calculation unit includes:

[0225] The crank pin force analysis unit is used to obtain the force exerted by the connecting rod on the corresponding crank pin and the inertial force of the crank pin based on the motion model and the phase angle of the crank pin.

[0226] The crankpin total support reaction force calculation unit is used to determine the crankpin total support reaction force based on the applied force and the inertial force of the crankpin.

[0227] The bearing housing support reaction force calculation unit is used to determine the bearing housing support reaction force based on the total support reaction force of the crank pin.

[0228] In some embodiments, the parameter calculation unit includes:

[0229] An inertial force feature acquisition unit is used to acquire inertial force features during the coordinated motion process based on the motion model and the phase angle of the crank pin. The inertial force features include a first inertial force related to the rotating motion component and a second inertial force related to the reciprocating motion component. The reciprocating motion component includes a piston structure, and the rotating motion component includes a crank structure.

[0230] The total inertial force calculation unit for the crank pin is used to determine the total inertial force of the crank pin based on the first inertial force and the second inertial force.

[0231] The torsional moment and roll moment calculation unit is used to determine the torsional moment and roll moment of the crankpin arrangement sequence based on the total inertial force of the crankpins in the crankpin arrangement sequence and the spacing between adjacent crankpins in the structural feature data.

[0232] In some embodiments, the parameter calculation unit includes:

[0233] The instantaneous flow calculation unit of the branch inlet pipe is used to determine the instantaneous flow of the branch inlet pipe corresponding to the crank pin based on the phase angle of the crank pin.

[0234] The cross-sectional flow calculation unit is used to calculate the cross-sectional flow of multiple flow sections on the main suction pipe based on the instantaneous flow of the branch suction pipe. The flow sections are determined by the position of the branch suction pipe on the main suction pipe.

[0235] In some embodiments, the sequence selection module includes:

[0236] The screening unit is used to screen out the crank pin arrangement sequence corresponding to the pump frame stress characteristics, excitation load characteristics and flow balance characteristics that meet at least one preset screening condition, and use it as the target crank arrangement sequence.

[0237] The screening conditions include: the maximum value of the bearing seat reaction force is less than the preset first force threshold; the resultant force of the bearing seat reaction force is less than the preset second force threshold; the maximum value of the torsional torque is less than the preset first torque threshold; the fluctuation difference of the torsional torque is less than the preset first torque fluctuation difference threshold; the maximum value of the roll torque is less than the preset second torque threshold; the fluctuation difference of the roll torque is less than the preset second torque fluctuation difference threshold; the flow fluctuation value is less than the preset flow fluctuation threshold; and the flow interruption angle is less than the preset angle threshold.

[0238] The apparatus of this application embodiment can execute the method provided in this application embodiment. The implementation principle is similar. The actions performed by each module in the apparatus of each embodiment of this application correspond to the steps in the method of each embodiment of this application. For detailed functional descriptions of each module of the apparatus, please refer to the descriptions in the corresponding methods shown above, which will not be repeated here.

[0239] Figure 35 is a schematic diagram of the structure of an electronic device provided in an embodiment of this application. As shown in Figure 35, the electronic device 350 provided in this embodiment includes at least one processor 3501 and a memory 3502. Optionally, the device 3500 further includes a communication component 3503. The processor 3501, the memory 3502, and the communication component 3503 are connected via a bus.

[0240] In a specific implementation, at least one processor 3501 executes computer execution instructions stored in memory 3502, causing at least one processor 3501 to perform the above-described method.

[0241] The specific implementation process of processor 3501 can be found in the above method embodiments, and its implementation principle and technical effect are similar. It will not be repeated here.

[0242] In the above embodiments, it should be understood that the processor can be a Central Processing Unit (CPU), or other general-purpose processors, digital signal processors (DSPs), application-specific integrated circuits (ASICs), etc. The general-purpose processor can be a microprocessor or any conventional processor. The steps of the method disclosed in this invention can be directly implemented by a hardware processor, or implemented by a combination of hardware and software modules within the processor.

[0243] The memory may include random access memory (RAM) and may also include non-volatile memory (NVM), such as at least one disk storage device.

[0244] The bus can be an Industry Standard Architecture (ISA) bus, a Peripheral Component Interconnect (PCI) bus, or an Extended Industry Standard Architecture (EISA) bus, etc. Buses can be categorized as address buses, data buses, control buses, etc. For ease of illustration, the buses shown in the accompanying drawings are not limited to a single bus or a single type of bus.

[0245] This application also provides a computer program product, including a computer program that, when executed by a processor, implements the above-described crankshaft crank arrangement method.

[0246] This application also provides a computer-readable storage medium storing computer-executable instructions, which, when executed by a processor, implement the aforementioned crankshaft crank arrangement method.

[0247] The aforementioned readable storage medium can be implemented by any type of volatile or non-volatile storage device or a combination thereof, such as static random access memory (SRAM), electrically erasable programmable read-only memory (EEPROM), erasable programmable read-only memory (EPROM), programmable read-only memory (PROM), read-only memory (ROM), magnetic storage, flash memory, magnetic disk, or optical disk. The readable storage medium can be any available medium accessible to a general-purpose or special-purpose computer.

[0248] An exemplary readable storage medium is coupled to a processor, enabling the processor to read information from and write information to the readable storage medium. Of course, the readable storage medium can also be a component of the processor. The processor and the readable storage medium can reside in an Application Specific Integrated Circuit (ASIC). Alternatively, the processor and the readable storage medium can exist as discrete components in the device.

[0249] The division of units is merely a logical functional division; 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. Furthermore, the coupling or direct coupling or communication connection shown or discussed may be indirect coupling or communication connection through some interfaces, devices, or units, and may be electrical, mechanical, or other forms.

[0250] The units described 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 this embodiment according to actual needs.

[0251] In addition, 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.

[0252] If a function is implemented as a software functional unit and sold or used as an independent product, it can be stored in a computer-readable storage medium. Based on this understanding, the technical solution of this invention, or the part that contributes to the prior art, or a 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 of 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.

[0253] Those skilled in the art will understand that all or part of the steps of the above-described method embodiments can be implemented by hardware related to program instructions. The aforementioned program can be stored in a computer-readable storage medium. When executed, the program performs the steps of the above-described method embodiments; and the aforementioned storage medium includes various media capable of storing program code, such as ROM, RAM, magnetic disks, or optical disks.

[0254] Other embodiments of this application will readily occur to those skilled in the art upon consideration of the specification and practice of the invention disclosed herein. This application is intended to cover any variations, uses, or adaptations of this application that follow the general principles of this application and include common knowledge or customary techniques in the art not disclosed herein. The specification and examples are to be considered exemplary only, and the true scope and spirit of this application are indicated by the following claims.

[0255] It should be understood that this application is not limited to the precise structure described above and shown in the accompanying drawings, and various modifications and changes can be made without departing from its scope. The scope of this application is limited only by the appended claims.

Claims

1. A method for arranging crankshaft cranks, characterized in that, include: Obtain structural feature data of a target crankshaft with multiple crank structures; Based on the structural feature data, a sequence of multiple crank pin arrangements for the target crankshaft is determined. The crank pin arrangement sequence is used to indicate the working order of the hydraulic cylinders corresponding to the crank pins in the crankshaft structure. Based on the structural feature data, a motion model is established, which is used to describe the coordinated motion process of the crank structure, the corresponding connecting rod, and the piston structure in the hydraulic cylinder. Based on the motion model, the bearing seat support reaction force data, inertial torque data, and intake pipe flow rate data for the crank pin arrangement sequence are determined. The intake pipe flow rate data is used to describe the cross-sectional flow rate of the main intake pipe corresponding to the crank pin. Based on the bearing seat reaction force data, the inertial torque data, and the intake pipe flow rate data, a target crank arrangement sequence is selected from the crank pin arrangement sequence.

2. The crankshaft crankpin arrangement method according to claim 1, characterized in that, The step of determining the sequence of multiple crankpin arrangements for the target crankshaft based on the structural feature data includes: Based on the structural feature data, the power interval angle of the hydraulic cylinder is determined, wherein the structural feature data includes the reciprocating pump type to which the target crankshaft belongs and the number of hydraulic cylinders corresponding to the target crankshaft, and the power interval angle is used to indicate the angle between the phase angles of the crank pins; Select the phase angle of any crank pin as the initial phase angle, and determine the range of values ​​for the initial phase angle; Based on the range of values ​​of the initial phase angle and the work interval angle, the phase angles of other crank pins are determined, and a correspondence is established between the crank pins and the range of values ​​of the phase angles of the crank pins. Based on the aforementioned correspondence, the crank pins are arranged and combined to remove duplicates, resulting in multiple crank pin arrangement sequences.

3. The crankshaft crankpin arrangement method according to claim 2, characterized in that, The bearing housing support reaction force data includes the bearing housing support reaction force of the bearing housing where the crank pin is located and the force characteristics of the pump frame; the inertial torque data includes the inertial torque and excitation load characteristics; and the suction pipe flow rate data includes the cross-sectional flow rate and flow balance characteristics of the main suction pipe corresponding to the crank pin. The determination of bearing seat reaction force data, inertial moment data, and intake pipe flow rate data for the crank pin arrangement sequence based on the motion model includes: Based on the motion model, the bearing seat support reaction force, the inertial torque, and the cross-sectional flow rate of the main suction pipe are determined. The inertial torque includes torsional torque and yaw torque. Based on the correspondence, the value range of the crank pins in the crank pin arrangement sequence is traversed to determine the pump frame force characteristics, excitation load characteristics, and flow balance characteristics of each crank pin arrangement sequence. The force characteristics of the pump frame include the maximum value of the bearing seat reaction force and the resultant force of the bearing seat reaction force; the excitation load characteristics include the maximum value of the torsional moment, the fluctuation difference of the torsional moment, the maximum value of the roll moment, and the fluctuation difference of the roll moment, wherein the fluctuation difference of the torsional moment is determined by the difference between the maximum and minimum values ​​of the torsional moment, and the fluctuation difference of the roll moment is determined by the difference between the maximum and minimum values ​​of the roll moment; the flow balance characteristics include the flow fluctuation value and the flow interruption angle, wherein the flow fluctuation value is determined by the difference between the maximum and minimum values ​​of the cross-sectional flow rate, and the flow interruption angle is determined by the cross-sectional flow rate.

4. The crankshaft crankpin arrangement method according to claim 3, characterized in that, The determination of the bearing seat support reaction force, the inertial torque, and the cross-sectional flow rate of the main suction pipe based on the motion model includes: Based on the motion model and the phase angle of the crank pin, the force exerted by the connecting rod on the corresponding crank pin and the inertial force of the crank pin are obtained. Based on the applied force and the inertial force of the crank pin, determine the total crank pin support reaction force. Based on the total support reaction force of the crankpin, the bearing housing support reaction force is determined.

5. The crankshaft crankpin arrangement method according to claim 4, characterized in that, The determination of the bearing seat support reaction force, the inertial torque, and the cross-sectional flow rate of the main suction pipe based on the motion model includes: Based on the motion model and the phase angle of the crank pin, the inertial force characteristics during the coordinated motion process are obtained. The inertial force characteristics include a first inertial force with respect to the rotating motion component and a second inertial force with respect to the reciprocating motion component. The reciprocating motion component includes the piston structure, and the rotating motion component includes the crank structure. Based on the first inertial force and the second inertial force, the total inertial force of the crank pin is determined; Based on the total inertial force of the crankpins in the crankpin arrangement sequence and the spacing between adjacent crankpins in the structural feature data, the torsional moment and yaw moment of the crankpin arrangement sequence are determined.

6. The crankshaft crankpin arrangement method according to claim 5, characterized in that, The determination of the bearing seat support reaction force, the inertial torque, and the cross-sectional flow rate of the main suction pipe based on the motion model includes: Based on the phase angle of the crank pin, determine the instantaneous flow rate of the intake pipe corresponding to the crank pin; Based on the instantaneous flow rate of the branch suction pipe, the cross-sectional flow rate of multiple flow sections on the main suction pipe is calculated, and the flow sections are determined by the position of the branch suction pipe on the main suction pipe.

7. The crankshaft crankpin arrangement method according to claim 6, characterized in that, The step of selecting a target crank arrangement sequence from the crank pin arrangement sequence based on the bearing seat reaction force data, the inertial torque data, and the intake pipe flow rate data includes: The crank pin arrangement sequence corresponding to the pump frame stress characteristics, vibration load characteristics and flow balance characteristics satisfying at least one preset screening condition is selected as the target crank arrangement sequence. The screening conditions include: the maximum value of the bearing seat reaction force is less than a preset first force threshold; the resultant force of the bearing seat reaction force is less than a preset second force threshold; the maximum value of the torsional torque is less than a preset first torque threshold; the fluctuation difference of the torsional torque is less than a preset first torque fluctuation difference threshold; the maximum value of the roll torque is less than a preset second torque threshold; the fluctuation difference of the roll torque is less than a preset second torque fluctuation difference threshold; the flow fluctuation value is less than a preset flow fluctuation threshold; and the flow interruption angle is less than a preset angle threshold.

8. An electronic device, comprising: A processor, and a memory communicatively connected to the processor; The memory stores computer-executed instructions; The processor executes computer execution instructions stored in the memory to implement the crankshaft crank arrangement method as described in any one of claims 1 to 7.

9. A computer-readable storage medium, characterized in that, The computer-readable storage medium stores computer-executable instructions, which, when executed by a processor, are used to implement the crankshaft crank arrangement method as described in any one of claims 1 to 7.

10. A computer program product, comprising a computer program, characterized in that, When the computer program is executed by the processor, it implements the crankshaft crank arrangement method according to any one of claims 1-7.

Images