Method for optimizing performance of high-power pump set transmission system

Abstract

The invention discloses a method for optimizing the performance of a transmission system of a high-power pump set, which comprises the following steps of: establishing constraint conditions of an optimization problem according to a two-stage gear transmission system of a high-power drilling mud pump; according to the total volume of the two-stage gear transmission system of the high-power drilling mud pump, the mass of the two-stage gear transmission system of the high-power drilling mud pump and the gear contact ratio, an objective function of an optimization problem is established; and solving the optimization problem according to the maximum torque of the motor for gear transmission and the total traditional ratio of the gear transmission system to obtain the optimal parameter group of the two-stage gear transmission system of the high-power drilling mud pump. According to the method, the optimization problems of multiple parameters, multiple targets, strong nonlinearity and complex parameter characteristics are solved, the method can be used for achieving rapid design of a gear transmission system, the performance of a pump set can be improved, the manufacturing cost can be reduced, and a large amount of manpower waste caused by repeated design can be saved.

Description

Technical Field

[0001] The present invention relates to the field of performance optimization of a high-power pump group gear transmission system, and in particular to a method for optimizing the performance of a high-power pump group transmission system. Background Art

[0002] As the heart of the drilling rig, the performance, quality, and service life of the drilling mud pump are directly correlated with drilling rate and cost. The primary function of a mud pump is to circulate drilling fluid in and out of the wellbore, flushing the bottomhole, cooling the drill bit, securing the wellbore wall, and carrying rock cuttings to the surface. When using downhole power drilling tools, the mud pump generates high-pressure drilling fluid to transfer energy, propelling the downhole power drilling tools. If a jet drill bit is used, the high-pressure drilling fluid generated by the mud pump can also be ejected from the drill bit's water holes to break up the rock formation and increase drilling speed. Currently, drilling pumps with power ranging from 500hp to 2200hp (367.5kW to 1617.0kW) are primarily triplex single-acting drilling pumps (referred to as triplex pumps). Drilling pumps with power below 1600hp (1176.0kW) were introduced in the 1970s. As drilling depths continue to increase, the demand for high-power drilling pumps is growing. Consequently, this century saw the introduction of even higher-power (2600hp) quintuple drilling pumps (quintuple pumps for short). Quintuple pumps are a new generation of equipment, more popular than triplex pumps. Their theoretical displacement is greater than triplex pumps, and their operating pressure fluctuations are smaller, resulting in superior performance and stability.

[0003] However, high-power five-cylinder pump sets also have higher requirements for the transmission system. In terms of the power chain of the five-cylinder pump, the single-side motor drives the gear reducer under high power demand, resulting in high load on the transmission chain and great difficulty in balancing. Therefore, it is often adopted Figure 1 The dual-drive two-stage gear transmission system shown in the figure has a first motor M1 and a second motor M2 driven by the crankshaft (i.e. Figure 1The output shaft in the pump is synchronously powered by a two-stage reduction gear set at both ends, wherein the first motor M1 and the second motor M2 are connected to the input shaft via input splines, and an input gear is installed on the input shaft. The input gear and the idler gear installed on the intermediate shaft form a high-speed gear pair, while the idler gear and the output gear installed on the output shaft form a low-speed gear pair, and a spline connection is used between the output gear and the output shaft. Compared with single-sided motor drive, double-sided motor drive can greatly reduce the strength requirements of various parts of the drive chain, reduce the wear rate of gears and bearings, increase the service life of the pump group, and improve transmission stability. However, the dual-drive two-stage gear transmission system has a more complex structure, high transmission reliability requirements, greater design difficulty, higher cost, and a larger crankshaft load. However, gear transmission involves many parameters such as gear sets, shaft system structures, bearing characteristics, materials, operating speed, etc. During design, it is necessary to comprehensively consider parameters such as strength, weight (volume), tooth surface overlap (transmission stability), transmission efficiency, and manufacturing cost. There are many parameters involved and the nonlinear relationship between parameters is complex. Therefore, the nonlinear mathematical model required for the design of the gear transmission system is complex, and a large number of parameters are selected based on experience. The design process is highly dependent on the experience of the designer. The design process is complicated, the workload is large, and the design effect is difficult to guarantee: the operating performance and cost are in a trade-off. Either the safety margin is large, resulting in a heavy pump set and high cost, or the transmission performance is poor.

[0004] In summary, a high-power pump group driven by dual motors requires an optimization algorithm for multi-objective, multi-parameter, and nonlinear problems to achieve efficient design of the dual-drive gear transmission system without introducing an additional automatic control system, so as to reduce the design workload and ensure the design results. Summary of the Invention

[0005] In order to overcome the problems of large workload and difficulty in balancing various objectives in existing transmission system design methods, the purpose of the present invention is to provide a method for optimizing the performance of high-power pump group transmission systems. This method uses a multi-objective intelligent optimization algorithm to solve multi-parameter, multi-objective, strong nonlinear, and complex parameter characteristics optimization problems. It can be used to achieve rapid design of gear transmission systems, which can not only improve pump group performance and reduce manufacturing costs, but also save a lot of manpower waste caused by repeated design.

[0006] In order to achieve the above object, the technical solution adopted by the present invention is as follows:

[0007] A method for optimizing the performance of a high-power pump transmission system comprises the following steps:

[0008] Based on the two-stage gear transmission system of a high-power drilling mud pump, the constraints of the optimization problem are established; the constraints include the gear transmission module, the number of gear teeth, the transmission ratio, the gear helix angle and the tooth width constraints;

[0009] According to the total volume, mass and gear overlap of the two-stage gear transmission system of the high-power drilling mud pump, the objective function of the optimization problem is established:

[0010] The optimization problem is determined according to the constraints and the objective function. The optimization problem is solved according to the maximum torque and speed of the gear-driven motor and the total conventional ratio of the gear transmission system to obtain the optimal parameter set of the two-stage gear transmission system of the high-power drilling mud pump.

[0011] Furthermore, the transmission module of the gear in the constraint condition is an integer, and the limit is: 10≤m≤32;

[0012] The number of teeth on the high-speed input gear in the constraint condition is an integer, and the limit is: 14≤Z1≤26;

[0013] The helix angles of all gears in the constraints are the same and the limit is: 8°≤β≤15°;

[0014] The constraints are that the tooth widths of all gears are equal, and the tooth width coefficient limit is:

[0015] The contact fatigue stress conditions of each gear in the constraint conditions are:

[0016] Where, σ H is the contact fatigue stress of each gear, K HN is the contact fatigue life coefficient; S H is the contact fatigue safety factor; σ H,lim is the contact fatigue limit stress of the material, MPa;

[0017] The contact fatigue stress of each gear in the gear transmission system is:

[0018] Where Z H is the area coefficient of the helical gear; Z E is the elastic influence coefficient of the material; Z ε is the coincidence coefficient; Z β is the helix angle coefficient, i is the transmission ratio, K H is the contact load coefficient, T is the motor input torque, is the tooth width coefficient, d is the pitch circle diameter of the corresponding gear;

[0019] The bending fatigue stress condition of each gear in the constraint condition is:

[0020] Where K FN is the contact fatigue life coefficient; S F is the contact fatigue safety factor; σ F,limis the bending fatigue limit stress of the material, MPa.

[0021] Furthermore, the objective function of the optimization problem is:

[0022]

[0023] Where ω1, ω2, and ω3 are the first, second, and third weight coefficients; V is the total volume of the transmission system, m 3 ; M is the mass of the transmission system, kg; ε r is the gear contact ratio.

[0024] Furthermore, the total volume V of the transmission system is:

[0025]

[0026] Where, d is the gear pitch circle diameter, mm; b is the gear tooth width; d1 is the input gear diameter, d2 is the idler gear diameter, and d3 is the output gear diameter.

[0027] Furthermore, the total weight of the gear transmission system is:

[0028]

[0029] Where ρ is the density of the gear material, kg·m -3 .

[0030] Furthermore, the gear contact ratio is:

[0031]

[0032] Where, ε α is the end face overlap, ε β is the axial overlap.

[0033] Furthermore, the end face contact ratio ε of the gear pair α :

[0034]

[0035] Where, z1 is the number of teeth on the pinion of the gear pair, z2 is the number of teeth on the gear pair; β is the helix angle;

[0036] The axial contact ratio ε of the gear pair β :

[0037]

[0038] Furthermore, the optimization problem is solved using a genetic algorithm.

[0039] Furthermore, the optimal parameter set of the two-stage gear transmission system of the high-power drilling mud pump is:

[0040]

[0041] Where: m is the gear normal module, i1 is the high-speed transmission ratio, z1 is the number of input gear teeth, β is the helix angle, is the tooth width coefficient.

[0042] A system for optimizing the performance of a high-power pump transmission system, comprising:

[0043] Constraint establishment module, used to establish the constraints of the optimization problem based on the two-stage gear transmission system of a high-power drilling mud pump;

[0044] The objective function establishment module is used to establish the objective function of the optimization problem based on the total volume, mass and gear overlap of the two-stage gear transmission system of the high-power drilling mud pump:

[0045] The solving module is used to determine the optimization problem based on the constraints and objective function. The optimization problem is solved according to the maximum torque and speed of the gear-driven motor and the total conventional ratio of the gear transmission system to obtain the optimal parameter set of the two-stage gear transmission system of the high-power drilling mud pump.

[0046] Compared with the prior art, the present invention has the following beneficial effects:

[0047] The present invention comprehensively considers the total volume, mass and gear overlap (transmission reliability) of the two-stage gear transmission system of the high-power drilling mud pump as the design goal, and performs synchronous optimization design on the main parameters of the gear transmission, namely the module, number of teeth, transmission ratio distribution, helix angle and tooth width, which can realize the rapid and accurate design of the structural parameter group of the transmission system of the high-power pump group, and improve the load-bearing capacity and transmission stability of the gears. The present invention performs rapid optimization design on the two-stage gear transmission system of the high-power drilling mud pump group, and is applicable to both single-motor driven and dual-motor synchronously driven gear transmission systems, and realizes automation, efficiency and precision of the design process. The present invention utilizes the structural parameters of each part of the two-stage gear transmission system, including the module, number of teeth, transmission ratio distribution, helix angle and tooth width, to construct an objective function to reflect the operating characteristics of the system. The solution of the objective function meets the structural parameter range (empirical value) and the requirements of the national standard for its strength and stability.

[0048] Furthermore, the present invention programs the objective function of the gear transmission system, as well as the standards for strength verification and stability requirements, as constraints for the optimization problem. Next, the objective function of the optimization problem is constructed using a linear weighted combination of volume (characterizing floor space), mass (characterizing manufacturing cost), and overlap (characterizing transmission performance), thereby simultaneously considering system manufacturing cost and operational performance during the design process. Finally, an intelligent optimization algorithm for optimization problems with multiple objectives, multiple parameters, strong nonlinearity, and complex parameter characteristics (including both integers, real numbers, and non-continuous standard values) is used to solve the optimization problem and obtain the optimal gear transmission system structural parameter set.

[0049] Furthermore, compared to transmission design methods, the present invention programs the traditional design process into the constraints of an optimization problem, avoiding the design process's repeated querying of standards and reliance on the designer's work experience. The present invention's optimization process quantifies the weighted relationship between cost and performance, avoiding the problem of inaccurate design results caused by traditional design methods. The present invention employs a genetic algorithm to solve the aforementioned highly nonlinear, parameter-complex, multi-objective, and multi-parameter optimization problem, resolving the difficulty of accurately solving complex mathematical models. The present invention can quickly provide a design solution for a gear transmission system based on basic design requirements for reference, saving design time and labor costs while ensuring a reliable design result. BRIEF DESCRIPTION OF THE DRAWINGS

[0050] Figure 1 This is a simplified structural diagram of a dual-drive two-stage gear transmission system;

[0051] Figure 2 Schematic diagram of the calculation convergence process in the optimization method of the present invention;

[0052] Figure 3 Schematic diagram of the system for optimizing the performance of the transmission system of a high-power pump group. DETAILED DESCRIPTION

[0053] To facilitate understanding of the present invention, the present invention will be described more fully below with reference to the accompanying drawings. The accompanying drawings illustrate preferred embodiments of the present invention. However, the present invention may be implemented in a variety of different forms and is not limited to the embodiments described herein. Rather, these embodiments are provided to provide a more thorough and comprehensive understanding of the disclosure of the present invention.

[0054] The power of the high-power pump group in the present invention is generally 1000-2200kW. The high-power pump group transmission system is a high-power drilling mud pump group gear transmission system. Figure 1 The dual drive two-stage gear transmission system shown.

[0055] A method for optimizing the performance of a high-power pump group transmission system of the present invention comprises the following steps:

[0056] Step (1): Establish the constraints of the optimization problem for the two-stage gear transmission system of a high-power drilling mud pump;

[0057] In the constraints of step (1), the gear accuracy is selected as level 6, the gear transmission efficiency is 98%, and the basic rack profile is based on the national standard GT / T1356-2001, where the pressure angle α p =20°, the tooth top height coefficient is 1, the top clearance coefficient is 0.25, and the tooth root circle radius coefficient is 0.38;

[0058] The transmission module of the gear in the constraint condition of step (1) is an integer, and the limit is: 10≤m≤32;

[0059] In the constraint condition of step (1), the number of teeth of the high-speed input gear is an integer, and the limit is: 14≤Z1≤26;

[0060] The high-speed gear ratio in the constraint condition of step (1) is: i1=(1.3-1.4)i2; i2 is the low-speed gear ratio;

[0061] In the constraint condition of step (1), the helix angles of all gears are the same and the limit is: 8°≤β≤15°;

[0062] In the constraint condition of step (1), the tooth widths of all gears are equal, and the tooth width coefficient limit is:

[0063] Constraints also include strength constraints, which include the allowable contact fatigue stress of the gear, the contact fatigue stress of the gear, the contact load coefficient, the contact fatigue stress condition of the gear, the allowable bending fatigue stress of the gear, the bending fatigue stress of the gear, the load coefficient, and the contact fatigue stress condition constraints of the gear.

[0064] The contact fatigue stress condition of each gear in the constraint condition of step (1) is:

[0065] Where, σ H is the contact fatigue stress of each gear, K HN is the contact fatigue life coefficient; S H is the contact fatigue safety factor; σ H,lim is the contact fatigue limit stress of the material, MPa.

[0066] The contact fatigue stress of each gear in the gear transmission system is:

[0067] Where Z His the area coefficient of the helical gear; Z E is the elastic influence coefficient of the material; Z ε is the coincidence coefficient; Z β is the helix angle coefficient, i is the transmission ratio, K H is the contact load coefficient, T is the motor input torque, is the tooth width coefficient, and d is the pitch circle diameter of the corresponding gear.

[0068] The contact load factor K H K H =K A K V K Hα K Hβ

[0069] Where: K A is the service factor; K v is the dynamic load coefficient; K Hα is the inter-tooth load distribution coefficient; K Hβ is the tooth load distribution coefficient.

[0070] The bending fatigue stress condition of each gear in the constraint condition of step (1) is:

[0071] Where K FN is the contact fatigue life coefficient; S F is the contact fatigue safety factor; σ F,lim is the bending fatigue limit stress of the material, MPa.

[0072] The bending fatigue stress is:

[0073] Where Y Fa is the tooth form coefficient; Y sa is the stress correction factor; Y ε is the coincidence coefficient; Y β is the helix angle coefficient; K F is the load factor, m is the normal module of the gear, and Z is the number of teeth of the corresponding gear.

[0074] The load factor is: K F =K A K V K Fα K Fβ .

[0075] Where: K A is the service factor; K v is the dynamic load coefficient; K Fα is the inter-tooth load distribution coefficient; K Fβ is the tooth load distribution coefficient.

[0076] In the constraint conditions of step (1), the gear material is 18CrNiMo7-6, the contact fatigue limit stress is 1450MPa, the material bending fatigue limit stress is 450MPa, and the gear material density is 7800kg·m -3 The gear material can be adjusted according to the actual situation, and the physical parameters will change with the material.

[0077] Step (2): Based on the total volume of the transmission system, the mass of the transmission system and the gear overlap, establish the objective function of the optimization problem:

[0078]

[0079] Where ω1, ω2, and ω3 are the first, second, and third weight coefficients, and the recommended value is 1 / 3; V is the total volume of the transmission system, m 3 ; M is the mass of the transmission system, kg; ε r is the gear contact ratio. The subscript 0 in V0 and M0 represents the calculated value of the traditional empirical design method.

[0080] The first, second and third weight coefficients must satisfy ω1+ω2+ω3=1, and the values ​​can be changed according to the design requirements of the gear transmission system.

[0081] The total volume V of the transmission system is:

[0082]

[0083] Where d is the gear pitch circle diameter, in mm; b is the gear tooth width; subscripts 1 to 3 refer to the input gear, idler gear, and output gear, respectively; d1 is the input gear diameter, d2 is the idler gear diameter, and d3 is the output gear diameter.

[0084] The total weight of the gear transmission system is:

[0085]

[0086] Where ρ is the density of the gear material, kg·m -3 .

[0087] The gear contact ratio is:

[0088] ε r =ε α +ε β

[0089] Where, ε α is the end face overlap, ε β is the axial overlap.

[0090] The end face contact of the gear pair:

[0091]

[0092] Where z1 is the number of teeth on the pinion of the gear pair, z2 is the number of teeth on the gear pair, and β is the helix angle.

[0093] The axial contact ratio of the gear pair:

[0094]

[0095] Step (3): Based on the basic requirements of gear transmission, a genetic algorithm is used to solve the optimization problem consisting of the constraints described in step (1) and the objective function described in step (2), and the optimal parameter group of the two-stage gear transmission system of the high-power drilling mud pump is obtained.

[0096] The basic requirements described in step (3) include the maximum torque T of the motor and the total conventional ratio i of the gear transmission system.

[0097] The optimal parameter set x in step (3) is:

[0098]

[0099] Where: m is the gear normal module, i1 is the high-speed transmission ratio, z1 is the number of input gear teeth, β is the helix angle, is the tooth width coefficient, and the tooth width is calculated based on the tooth width coefficient, module and number of teeth.

[0100] The genetic algorithm population size in step (3) is 50, the number of generations is 200, the crossover probability is 0.8, the convergence judgment error is 1e-10, the mutation operation adopts the uniform mutation operator, and the number of elite individuals is 2.

[0101] The genetic algorithm variable encoding method in step (3) is [integer, real number, integer, real number, real number].

[0102] Comparative Example 1

[0103] A single-motor-driven two-stage gear transmission system is designed for a 2600hp drilling mud pump unit. The required design power P of the pump unit is 1939kW, the motor design speed n1 is 829rpm, and the transmission ratio is 8.29.

[0104] Traditional design methods:

[0105] Considering the balance characteristics of the strength of each gear and the transmission reliability in the two-stage transmission system, the transmission ratio i1=1.4i2 is roughly selected based on the empirical value, so i1=3.50, i2=2.55. In the calculation process, the empirical value of the tooth width coefficient is roughly selected. The helix angle is chosen to be 8°, an empirical value.

[0106] The main parameters of the gear obtained by preliminary calculation are shown in Table 1:

[0107] Table 1 Design results of traditional design method

[0108]

[0109]

[0110] It can be seen from Table 1 that the safety factor of the transmission system obtained by the preliminary design based on the empirical value is too high, the safety margin is too large, the overlap is low (the overlap is generally required to be greater than 1), the gear transmission reliability is poor, and continuous iteration is required to meet the design requirements, which is a large workload.

[0111] Example 1

[0112] A single-motor-driven two-stage gear transmission system is designed for a 2600hp drilling mud pump unit. The required design power P of the pump unit is 1939kW, the motor design speed n1 is 829rpm, and the transmission ratio is 8.29.

[0113] Using the above optimization method to optimize, the genetic algorithm calculation process is as follows: Figure 2 As shown, convergence was achieved after 180 generations. The optimization results are shown in Table 2. Compared with the design results of the traditional design method in Table 1, the gear set designed in Example 1 of the present invention has a uniform safety factor, an appropriate safety margin, a high gear pair contact ratio (all greater than 1), and good transmission reliability. Furthermore, the design process of the present invention is fast and accurate, without the need for repeated iterations.

[0114] Table 2 Design results of the present invention

[0115]

[0116] The present invention designs a gear transmission system for the QDP2600 high-power pump group for rapid optimization design, which can be used for both single-motor driven and dual-motor synchronously driven gear transmission systems. For the two-stage gear transmission system with dual-motor synchronous drive, the transmission systems on both sides are completely symmetrical, and the gear sets are exactly the same. A single-side motor-driven two-stage gear transmission system can be designed according to half the power of the pump group, and a dual-motor driven transmission system can be obtained by symmetrical arrangement. The present invention comprehensively considers the volume, weight, and overlap (reliability) of the two-stage gear transmission system to establish an optimization objective function, and uses a genetic algorithm to synchronously optimize the key parameter group (module, number of teeth, transmission ratio distribution, helix angle, tooth width) of the two-stage gear transmission system.

[0117] See also Figure 3 , a system for optimizing the performance of a high-power pump transmission system, comprising:

[0118] Constraint establishment module, used to establish the constraints of the optimization problem based on the two-stage gear transmission system of a high-power drilling mud pump;

[0119] The objective function establishment module is used to establish the objective function of the optimization problem based on the total volume, mass and gear overlap of the two-stage gear transmission system of the high-power drilling mud pump:

[0120] The solving module is used to determine the optimization problem based on the constraints and the objective function. The optimization problem is solved according to the maximum torque of the gear-driven motor and the total conventional ratio of the gear transmission system to obtain the optimal parameter set of the two-stage gear transmission system of the high-power drilling mud pump.

[0121] The above description is merely a description of the preferred embodiment of the present invention and is not to be construed as limiting the claims. The present invention is not limited to the above embodiment, and variations in the specific structure are permitted. Any variations made within the scope of the independent claims of the present invention are also within the scope of protection of the present invention.

[0122] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by those skilled in the art to which this invention pertains. The terms used herein in the specification of the present invention are for the purpose of describing specific embodiments only and are not intended to limit the present invention. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

Claims

1. A method for optimizing the performance of a high-power pump group transmission system, characterized in that: The following steps are involved: Based on the two-stage gear transmission system of a high-power drilling mud pump, the constraints of the optimization problem are established; the constraints include the gear transmission module, the number of gear teeth, the transmission ratio, the gear helix angle and the tooth width constraints; According to the total volume, mass and gear overlap of the two-stage gear transmission system of the high-power drilling mud pump, the objective function of the optimization problem is established: The optimization problem is determined according to the constraints and the objective function. The optimization problem is solved according to the maximum torque and speed of the gear-driven motor and the total conventional ratio of the gear transmission system to obtain the optimal parameter set of the two-stage gear transmission system of the high-power drilling mud pump.

2. The method for optimizing the performance of a high-power pump group transmission system according to claim 1, characterized in that: The transmission module of the gear in the constraint condition is an integer, and the limit is: 10≤m≤32; The number of teeth on the high-speed input gear in the constraint condition is an integer, and the limit is: 14≤Z1≤26; The helix angles of all gears in the constraints are the same and the limit is: 8°≤β≤15°; The constraints are that the tooth widths of all gears are equal, and the tooth width coefficient limit is: The contact fatigue stress conditions of each gear in the constraint conditions are: Where, σ H is the contact fatigue stress of each gear, K HN is the contact fatigue life coefficient; S H is the contact fatigue safety factor; σ H,lim is the contact fatigue limit stress of the material, MPa; The contact fatigue stress of each gear in the gear transmission system is: Where Z H is the area coefficient of the helical gear; Z E is the elastic influence coefficient of the material; Z ε is the coincidence coefficient; Z β is the helix angle coefficient, i is the transmission ratio, K H is the contact load coefficient, T is the motor input torque, is the tooth width coefficient, d is the pitch circle diameter of the corresponding gear; The bending fatigue stress condition of each gear in the constraint condition is: Where K FN is the contact fatigue life coefficient; S F is the contact fatigue safety factor; σ F,lim is the bending fatigue limit stress of the material, MPa.

3. The method for optimizing the performance of a high-power pump group transmission system according to claim 1, characterized in that: The objective function of the optimization problem is: Where ω1, ω2, and ω3 are the first, second, and third weight coefficients; V is the total volume of the transmission system, m 3 ; M is the mass of the transmission system, kg; ε r is the gear contact ratio.

4. The method for optimizing the performance of a high-power pump group transmission system according to claim 3, characterized in that: The total volume V of the transmission system is: Where, d is the gear pitch circle diameter, mm; b is the gear tooth width; d1 is the input gear diameter, d2 is the idler gear diameter, and d3 is the output gear diameter.

5. The method for optimizing the performance of a high-power pump group transmission system according to claim 3, characterized in that: The total weight of the gear transmission system is: Where ρ is the density of the gear material, kg·m -3 .

6. The method for optimizing the performance of a high-power pump group transmission system according to claim 3, characterized in that: The gear contact ratio is: e r =e α +e β Where, ε α is the end face overlap, ε β is the axial overlap.

7. The method for optimizing the performance of a high-power pump group transmission system according to claim 6, characterized in that: The end face contact ratio ε of the gear pair α : Where, z1 is the number of teeth on the pinion of the gear pair, z2 is the number of teeth on the gear pair; β is the helix angle; The axial contact ratio ε of the gear pair β :

8. The method for optimizing the performance of a high-power pump group transmission system according to claim 1, characterized in that: The optimization problem is solved using genetic algorithm.

9. The method for optimizing the performance of a high-power pump group transmission system according to claim 1, characterized in that: The optimal parameter set for the two-stage gear transmission system of a high-power drilling mud pump is: Where: m is the gear normal module, i1 is the high-speed transmission ratio, z1 is the number of input gear teeth, β is the helix angle, is the tooth width coefficient.

10. A system for optimizing the performance of a high-power pump transmission system, characterized in that: include: Constraint establishment module, used to establish the constraints of the optimization problem based on the two-stage gear transmission system of a high-power drilling mud pump; The objective function establishment module is used to establish the objective function of the optimization problem based on the total volume, mass and gear overlap of the two-stage gear transmission system of the high-power drilling mud pump: The solving module is used to determine the optimization problem based on the constraints and objective function. The optimization problem is solved according to the maximum torque and speed of the gear-driven motor and the total conventional ratio of the gear transmission system to obtain the optimal parameter set of the two-stage gear transmission system of the high-power drilling mud pump.

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