How to optimize the design of rotating components for high-speed, high-pressure axial plunger pumps.

Abstract

This provides a method for optimally designing the rotating components of a high-speed, high-pressure axial plunger pump. [Solution] The method includes the steps of: inputting design targets, plunger pump discharge volume, rotational speed, and rated pressure; designing and optimizing the configuration parameters for the rotating parts of the plunger pump based on the target discharge volume; constructing a three-dimensional model of the rotating parts, determining the member strength at the rated pressure based on the configuration deformation principle, and feeding this back into the optimization process; determining and optimizing for slipper overturning, cylinder body overturning, and cavitation erosion failures when the rotating parts are operating at high speed, based on speed limitations; and outputting the configuration parameters, member materials, and processes for the rotating parts of the plunger pump. The present invention enables the rapid and optimal design of the rotating parts of a plunger pump, thereby increasing the reliability of the operation of the plunger pump.

Description

Technical Field

[0001] The present invention relates to the technical field of axial plunger pumps, and particularly to a method for optimizing the design of rotating parts of high-speed and high-pressure axial plunger pumps.

Background Art

[0002] As a power system element in a fluid system, hydraulic pumps are widely applied in technical fields such as the aerospace industry, machine tools, and national defense and military. With the development of the industry that manufactures high-class machines, plunger pumps are gradually developing in the direction of higher pressure and faster rotational speed so as to obtain higher efficiency and power-to-weight ratio in the system.

[0003] Rotating parts, as crucial parts in a plunger pump, are in the main positions where failures occur. When operating under high pressure, if the rotating parts are affected by high-pressure fluid, the members are likely to be torn or deformed and thus easily fail. When operating at high speed, there is a risk of failures such as slipper overturning, cylinder body overturning, and cavitation erosion in the plunger pump. All conventional design methods are either for single elements or based on empirical rules, and there are problems such as over-complicated design or long design cycles.

Summary of the Invention

Problems to be Solved by the Invention

[0004] To address the problems present in the prior art, the present invention provides a method for optimizing the design of rotating components for a high-speed, high-pressure axial plunger pump, which takes expected discharge rate, expected rotational speed, and expected rated pressure as inputs, and designs the parameters of the basic configuration of the plunger pump based on the discharge rate limit. By simulating and analyzing finite elements, the safety and reliability of the components are determined when operating at the rated pressure, and the parameters of the configuration, materials, and processes related to the rotating components are optimized. Based on the rotational speed limit, parameters are determined and the configuration is optimized for slipper overturning failure, cylinder body overturning failure, and cavitation erosion failure, respectively. If the discharge rate limit, pressure limit, and rotational speed limit meet the needs, the configuration parameters, component materials, and processes related to the rotating components of the plunger pump are ultimately output. [Means for solving the problem]

[0005] The present invention Step S1 involves first identifying the constituent material properties and design objectives for the rotating parts of the plunger pump, including the maximum target discharge, maximum rotational speed, and rated pressure of the plunger pump. Step S2 involves identifying configuration parameters for the rotating parts of the plunger pump based on the maximum target emissions, Step S3 involves constructing a three-dimensional model of the rotating part of the plunger pump based on the configuration parameters identified in step S2, setting initial material attributes and processes for the member, determining the strength of the member under conditions where the plunger pump operates at rated pressure based on configuration deformation, determining whether the rated pressure is met, executing step S4 if it is met, otherwise optimizing the parameters and then repeating steps S2 and S3, Step S3 is Step S31 involves constructing a three-dimensional model of the rotating part and initially setting the material and process for the component, Step S32, which determines the strength of the member structure at the rated pressure based on the principle of structural deformation, Substep S321 divides a solid region mesh for analysis using finite elements based on the component structure of the rotating part, The structural deformation and stress in the rotating parts are influenced by the temperature field and fluid field when the plunger pump is operating, and are transmitted between the components. Substep S322 applies an instantaneous pressure load obtained by calculating the fluid field at the interface between the liquid and solid, applies a temperature load to the rotating parts when the plunger pump is operating, and restricts the movement of the rotating parts according to the operating conditions actually applied. For rotating parts, multiple fields act in a coupled manner, and the structural deformation, including structural deformation and stress due to temperature load and fluid load, is analyzed. Rotating parts deform when subjected to force. JPEG0007876918000002.jpg18170 Thermal deformation of rotating parts JPEG0007876918000003.jpg20170 For rotating parts, a cloud diagram of structural deformation and stress response is extracted. If it is determined that there is no interference in the oil film gap of the rotating part after structural deformation, and that the structural stress is smaller than the material required stress, it is calculated whether the maximum pressure due to the current material required stress is greater than the rated pressure. If it is calculated to be greater, the next step is executed. Otherwise, the third parameter is optimized and steps S2 and S3 are executed again in step S33. Step S3 specifically includes calculating whether the maximum pressure due to the current material stress is less than 1.1 times the rated pressure, and if it is calculated to be less, the next step is performed, otherwise the fourth parameter is optimized and steps S2 and S3 are performed again, and step S34 is performed. Step S4 involves determining and optimizing the parameters for each rotating part of the plunger pump based on the configuration parameters identified in step S2, the parameters for failures when the rotating part is operating at the rated speed, determining whether the maximum rotational speed requirement is met, executing step S5 if it is met, otherwise optimizing the parameters and repeating steps S2 to S4. The present invention provides a method for designing the rotating components of a high-speed, high-pressure axial plunger pump to be optimized, including step S5, which outputs optimized configuration parameters for the rotating components of the plunger pump, and optimized material attributes and processes for the components.

[0006] Preferably, step S2 is The cylinder body parameters are identified, and these parameters include the plunger hole diameter, the plunger distribution circle diameter, the wall thickness between the plunger holes in the cylinder body, and the length of the cylinder body. Of these, the relationship between the plunger hole diameter, the plunger distribution circle diameter, and the maximum target discharge is JPEG0007876918000004.jpg20170 By calculating the average positive stress received in the plunger holes of the cylinder body, it is possible to determine whether the wall thickness between the plunger holes of the cylinder body meets the requirements, and the formula for calculating the average positive stress received in the plunger holes of the cylinder body is JPEG0007876918000005.jpg208170 Identify the retainer parameters, which include the retainer plunger distribution circle diameter and the retainer hole diameter. The formula for calculating the diameter of the retainer plunger distribution circle is JPEG0007876918000006.jpg210170JPEG0007876918000007.jpg33170 Based on the configuration parameters, the discharge amount of the plunger pump is calculated, and it is determined whether the discharge amount of the plunger pump is greater than the target discharge amount. If it is greater, the next step is performed, and if it is less than or equal to the target, the first parameter is optimized and the process returns to step S21, and step S2 is performed again in step S27. The procedure specifically includes determining whether the discharge from the plunger pump is less than 1.1 times the target discharge, and if so, performing the next step; otherwise, optimizing the second parameter and returning to step S21, and repeating step S28.

[0007] Preferably, in step S2, the configuration parameters for the rotating parts of the plunger pump include cylinder body parameters, plunger parameters, slipper parameters, retainer parameters, port plate parameters, and swashplate parameters.

[0008] Preferably, if the rated pressure configuration is not met even after performing step S33 N times, an output indicating that the current parameters cannot meet the rated pressure requirement is displayed.

[0009] Preferably, step S4 is We created a formula to calculate the maximum speed before a slipper overturns, and verified the failure of overturning in a slipper with rotating parts. JPEG0007876918000008.jpg73170JPEG0007876918000009.jpg39170 A formula was created to calculate the maximum speed before cavitation erosion failure occurs in a Langer pump, and cavitation erosion failure was verified in rotating parts. JPEG0007876918000010.jpg51170JPEG0007876918000011.jpg71170

[0010] Preferably, in step S432, the continuity equation and the Navier-Stokes equation are constructed for the fluid region of the rotating parts of the plunger pump using the fundamental theorem of fluid rotation.

[0011] Preferably, step S432 is Substep S4321 involves creating an equation that expresses the continuity equation in detail for the mass of the rotating part, Substep S4322 constructs the Navier-Stokes equations for compressible fluids of rotating parts, Based on the design pressure and design rotational speed of the plunger pump, the load characteristics and motion characteristics during the use of the plunger pump are applied to the continuity equation and the Navier-Stokes equation for the fluid region of the rotating parts in sub-step S4323, Specifically, it includes sub-step S4324 of performing analysis by finite elements to obtain a cloud diagram of the fraction of gas volume in the fluid region of the rotating parts, and expressing the cavitation erosion characteristics of the rotating parts.

[0012] JPEG0007876918000012.jpg30170

[0013] Preferably, the specific steps for optimizing the first parameter in step S27 are to increase the number of plungers, the diameter of the plungers, the pitch circle diameter of the plungers, and the inclination angle of the swash plate. The specific steps for optimizing the second parameter in step S28 are to decrease the number of plungers, the diameter of the plungers, the pitch circle diameter of the plungers, and the inclination angle of the swash plate. The specific steps for optimizing the third parameter in step S33 are to increase the structural strength and structural rigidity of the material, decrease the thermal expansion coefficient of the material, and strengthen the wall thickness in the region where the rated pressure is not satisfied. The specific steps for optimizing the fourth parameter in step S34 are to lower the structural strength and structural rigidity of the entire material. The specific steps for optimizing the fifth parameter in step S44 are JPEG0007876918000013.jpg58170

Advantages of the Invention

[0014] Compared with the prior art, the present invention has the following advantages.

[0015] (1) The present invention comprehensively considers the configuration design and optimization of rotating components under the conditions of discharge amount limitation, pressure limitation, and rotational speed limitation for a plunger pump. Therefore, it can accurately obtain the deformation and stress cloud diagrams of key components, as well as the cloud diagram of cavitation erosion in the internal flow field of the rotating components. By combining the plunger pump boundary condition logical formulas, it can determine whether the designed parameters meet the expected requirements, and through multiple closed-loop feedbacks for optimization, it can obtain the optimal plunger pump parameters that meet the requirements. (2) Based on the numerical simulation and test results obtained by the method of optimizing the design of the rotating components of a high-speed high-pressure axial plunger pump, the rotating components of the plunger pump are improved and optimized multiple times. Through test comparison, it can obtain the design parameters and material processes that ensure the operating reliability of the components. Therefore, the present invention can perform simulations, calculations, and tests based on a large amount of data, establish an analysis method with high accuracy, low calculation cost, short research cycle, and in line with the actual situation of the process, and has a wide range of applications.

Brief Description of the Drawings

[0016] [Figure 1] It is a flowchart showing a method for optimizing the design of the rotating components of a high-speed high-pressure axial plunger pump according to the present invention. [Figure 2] It is a diagram showing the three-dimensional configuration of the rotating components of a method for optimizing the design of the rotating components of a high-speed high-pressure axial plunger pump according to the present invention. [Figure 3] It is a top view showing the rotating components of a method for optimizing the design of the rotating components of a high-speed high-pressure axial plunger pump according to the present invention. [Figure 4] It is a schematic diagram showing the configuration of the plunger component of a method for optimizing the design of the rotating components of a high-speed high-pressure axial plunger pump according to the present invention. [Figure 5]This is a schematic diagram showing the configuration of a plunger component, illustrating a method for optimizing the design of rotating components of a high-speed, high-pressure axial plunger pump according to the present invention. [Figure 6] This is a schematic cross-sectional view showing a rotating component of a high-speed, high-pressure axial plunger pump, illustrating a method for optimizing the design of the rotating component according to the present invention. [Figure 7] This is a cloud diagram showing deformation and stress, illustrating a method for optimizing the design of rotating components of a high-speed, high-pressure axial plunger pump according to the present invention. [Figure 8] This is a schematic diagram showing the fluid domain of a method for optimizing the design of rotating components of a high-speed, high-pressure axial plunger pump according to the present invention. [Figure 9] This figure shows a cavitation erosion cloud, illustrating a method for optimizing the design of rotating parts of a high-speed, high-pressure axial plunger pump according to the present invention. [Figure 10] This graph shows how the rate limit of cavitation erosion changes according to the change in liquid suction pressure, relating to a method for optimizing the design of rotating parts of a high-speed, high-pressure axial plunger pump according to the present invention. [Modes for carrying out the invention]

[0017] To explain the technical details, objectives, and effects of this invention in more detail, please refer to the specification and its drawings below.

[0018] The present invention provides a method for optimizing the design of rotating components for a high-speed, high-pressure axial plunger pump. Specifically, it includes the following steps, as shown in Figure 1. Step S1 identifies the design objectives and initial constituent material properties for the rotating parts of the plunger pump, with the design objectives including the maximum target discharge, maximum rotational speed, and rated pressure for the plunger pump. Step S2 identifies configuration parameters for the rotating parts of the plunger pump based on the maximum target emissions, and specifically includes the following substeps: Substep S21 identifies cylinder body parameters, which include the plunger hole diameter, the diameter of the plunger's distribution circle, the wall thickness between the plunger holes in the cylinder body, and the length of the cylinder body. When designing the cylinder body parameters, it is first necessary to satisfy the design requirements for the plunger pump discharge rate, and the relationship between the plunger diameter, the diameter of the plunger's distribution circle, and the pump discharge rate is JPEG0007876918000014.jpg18170

[0019] At the same time, when designing the cylinder body parameters, the strength of the thin walls between the plunger holes in the cylinder body and between the cylinder body holes and the inner and outer wall surfaces is taken into consideration, and the average positive stress received by the plunger holes in the cylinder body is calculated by equivalent conversion to the rated fluid pressure of the plunger pump. JPEG0007876918000015.jpg45170

[0020] When designing, the number of plungers and the inclination angle of the swashplate are initially calculated using design values. Based on the material strength of the cylinder body, the plunger diameter and the diameter of the plunger's distribution circle are calculated and obtained. Furthermore, the wall thickness between the plunger holes in the cylinder body is obtained.

[0021] The length of the cylinder body is an important design parameter for the cylinder body, and the length of the cylinder body consists of the minimum length of the plunger in the cylinder body, the plunger stroke, the safety distance, and the spline protrusion portion of the cylinder body. JPEG0007876918000016.jpg50170

[0022] Substep S22 identifies the plunger parameters, which include the plunger length and the plunger head diameter. The plunger length mainly consists of the minimum axial extension length of the plunger relative to the swashplate, the plunger stroke, and the minimum joining length. JPEG0007876918000017.jpg31170

[0023] JPEG0007876918000018.jpg16170

[0024] Substep S23 identifies the slipper parameters, which include the slipper ball diameter, the inner diameter of the slipper sealing belt, the outer diameter of the slipper sealing belt, the outer diameter of the slipper ball cup, and the diameter of the slipper damping hole. JPEG0007876918000019.jpg61170

[0025] JPEG0007876918000020.jpg46170

[0026] The flow rate that has passed through the damping hole is JPEG0007876918000021.jpg45170

[0027] A parallel oil film forms between the slipper and the swashplate, and the pressure distribution within it provides a force that supports the oil film. JPEG0007876918000022.jpg21170

[0028] JPEG0007876918000023.jpg24170

[0029] Since the flow rate is continuous, the flow rate with fixed damping is equal to the gap flow rate of the parallel disks, and the remaining tightening coefficient balances the force acting on the slipper. JPEG0007876918000024.jpg14170

[0030] JPEG0007876918000025.jpg11170

[0031] Substep S24 identifies the retainer parameters, which include the distribution circle diameter of the retainer plunger and the retainer hole diameter. When the swashplate is tilted, the wear reduction plate rotates in conjunction with the swashplate, and the slipper moves in an elliptical motion on the wear reduction plate. To ensure that it does not interfere with the retainer while the pump is operating, the diameter of the retainer plunger's distribution circle is taken as the average value of the major and minor axes in the ellipse. JPEG0007876918000026.jpg19170

[0032] The radial deviation between the elliptical trajectory of the slipper's center and the distribution circle of the retainer is JPEG0007876918000027.jpg18170

[0033] Therefore, the retainer hole diameter is JPEG0007876918000028.jpg41170

[0034] Substep S25 identifies the port plate parameters and verifies whether the port plate meets the requirements, and the port plate parameters include the port sub-sealing belt size and deflection angle.

[0035] The radius of the waist-shaped groove in the cylinder body and the radius of the center of the waist-shaped groove in the port plate should not be greater than the radius of the plunger's distribution circle; their ratio should be between 0.7 and 1.0. The width of the waist-shaped groove in the cylinder body and the waist-shaped groove in the port plate should be 0.35 to 0.5 times the plunger diameter, and the width of the sealing belt inside and outside the port plate may be 0.1 to 0.2 times the plunger diameter.

[0036] By determining the radius of the center of the groove that forms the waist of the cylinder body and port plate, it is determined whether the linear velocity at that center meets the usable range, and the calculation formula is JPEG0007876918000029.jpg19170

[0037] JPEG0007876918000030.jpg5170

[0038] In order to effectively reduce pressure collisions and plunger pump noise, it is common practice to deflect the waist-shaped opening in the port plate to achieve predetermined pressure increases and decreases.

[0039] When the pressure increases from the initial pressure to a predetermined increased pressure, the volume compression amount is JPEG0007876918000031.jpg26170

[0040] JPEG0007876918000032.jpg29170

[0041] By combining the above formulas, the design value for the deflection angle of the port plate can be obtained.

[0042] Substep S26 involves designing the swashplate parameters, which include the inclination angle of the swashplate and the minimum distance between the ends of the slope on the swashplate. JPEG0007876918000033.jpg47170

[0043] Substep S27 calculates the discharge amount of the plunger pump based on the configuration parameters, determines whether the discharge amount of the plunger pump is greater than the target discharge amount, executes the next step if it is greater, and if it is less than or equal to the target, optimizes the first parameter and returns to step S21 and executes step S2 again.

[0044] Substep S28 determines whether the discharge from the plunger pump is less than 1.1 times the target discharge. If it is less, it executes the next step; otherwise, it optimizes the second parameter and returns to step S21, and steps S2 are executed again.

[0045] The specific steps to optimize the first parameter are to increase the number of plungers, plunger diameter, plunger distribution circle diameter, and swashplate tilt angle. The specific steps to optimize the second parameter are to decrease the number of plungers, plunger diameter, plunger distribution circle diameter, and swashplate tilt angle.

[0046] Step S3 involves constructing a three-dimensional model of the rotating part of the plunger pump based on the configuration parameters identified for the rotating part in step S2, setting the initial material attributes and processes for the member, determining the member strength under conditions where the plunger pump operates at rated pressure based on the configuration deformation principle, determining whether the rated pressure is met, and if so, executing step S4; otherwise, optimizing the parameters and then repeating steps S2 and S3, specifically including the following steps. Step S31 constructs a three-dimensional model of the rotating part and first sets the material and process for the component, as shown in Figure 2. JPEG0007876918000034.jpg104170 Step S321 divides a solid region mesh for finite element analysis based on the component configuration of the rotating part. Step S322 involves determining that the structural deformation and stress in the rotating part are influenced by the temperature and fluid fields when the plunger pump is operating and are transmitted between the components. An instantaneous pressure load obtained by calculating the fluid field is applied to the interface between the fluid and the solid, and the temperature field in which the plunger pump is operating is applied to the rotating part, thereby limiting the movement of the rotating part according to the actual adaptive operating conditions. Step S323 analyzes the constitutive deformation, which is the result of multiple fields acting in a coupled manner, including constitutive deformation and stress due to temperature load and fluid load. The deformation caused by force on a rotating part is, Step S33 extracts the configuration deformation and stress-responsive cloud diagram of the rotating part, determines whether there is interference in the oil film gap of the rotating part when the configuration deforms, and determines whether the configuration stress is smaller than the material required stress, calculates whether the maximum pressure due to the current material required stress is greater than the rated pressure, and if it is greater, executes the next step, otherwise optimizes the third parameter and executes steps S2 and S3 again. If the rated pressure configuration is not met even after executing step S33 N times, an output is made stating that the rated pressure needs cannot be met with the current parameters. Step S34 calculates whether the maximum pressure due to the current material stress is less than 1.1 times the rated pressure. If it is found to be less, the next step is executed; otherwise, the fourth parameter is optimized, and then steps S2 and S3 are executed. The specific steps to optimize the third parameter are to increase the structural strength and structural stiffness in the region where the material does not meet the rated pressure, to lower the thermal expansion coefficient of the material, and to increase the wall thickness. The specific steps to optimize the fourth parameter are to lower the structural strength and structural stiffness of the material as a whole.

[0047] Step S4 determines and optimizes the parameters for each failure that may occur when the rotating parts are operating at the rated speed, based on the configuration parameters identified for the rotating parts in step S2. It then determines whether the maximum rotational speed requirement is met. If it is met, step S5 is executed; otherwise, the parameters are optimized and steps S2 to S4 are executed again. Specifically, this is as follows: In step S41, since the slipper is a mechanism for connecting the swashplate and the plunger, it is subjected to an axial force at high pressure in the plunger cavity, and the centrifugal force generated by the circumferential movement of the plunger causes the slipper to overturn relative to the surface of the swashplate. Such overturning can cause uneven polishing of the slipper, which can lead to the loss of the oil film and subsequent burning. Therefore, the failure of slipper overturning in rotating parts can be optimized in the design. We created a formula to calculate the maximum speed before the slipper overturns, and verified the failure of the slipper overturning in rotating parts. JPEG0007876918000037.jpg56170n is generally considered to be 3. Specifically, by using a configuration such as a plunger with a hollow interior, the mass of the plunger can be reduced, and the maximum rotational speed before a tipping failure occurs in the plunger pump slipper can be increased. By increasing the elastic force, the maximum rotational speed before a tipping failure occurs in the plunger pump slipper can be increased. The plunger anti-coating process reduces the distance from the center of gravity of the slipper to the center of the ball joint, and the centrifugal tipping torque of the slipper can be reduced. At the same time, by adopting a mechanism that fixes the gap and returns, a new tipping resistance force is introduced, and furthermore, the maximum rotational speed of the plunger pump before a tipping failure occurs in the slipper can be increased. After optimization, step S4 is executed again.

[0048] The method for creating a formula to calculate the maximum speed before the slipper overturns is as follows: By analyzing the forces acting on the slipper, the torque balance equation perpendicular to the axial direction is obtained. JPEG0007876918000038.jpg20170

[0049] The reaction force of the swashplate is due to the axial force balance of the slipper. JPEG0007876918000039.jpg21170 When calculating the sum of the circumferential forces in the plunger, the force acting between the slipper and the plunger is By combining the equations in JPEG0007876918000040.jpg21170, it is possible to obtain a formula for calculating the maximum speed before the cylinder body overturns. Step S42 is necessary because, when the plunger pump is rotating at high speed, the rotating cylinder body is affected by axial deflection load force, centrifugal force of the plunger, and flexural deformation of the main shaft, causing it to rotate relative to the port plate in an overturned position. Therefore, it is necessary to design the cylinder body of the rotating component to optimize its resistance to overturning failure. Step S42 involves creating an equation to calculate the maximum speed before the cylinder body overturns, and verifying the failure of the rotating part, the cylinder body, to overturn. JPEG0007876918000041.jpg25170

[0050] Specifically, by using a configuration such as a plunger with a hollow interior, the mass of the plunger can be reduced, thereby increasing the maximum rotational speed before a tipping failure occurs in the plunger pump cylinder body. By increasing the elastic force, the maximum rotational speed before a tipping failure occurs in the plunger pump cylinder body can be increased. At the same time, by adding an auxiliary shaft or the like to the outer circumference of the cylinder body and introducing a new support force to the cylinder body, the maximum rotational speed before a tipping failure occurs in the plunger pump cylinder body can be increased. After optimization, step S4 is executed again.

[0051] The following formula is used to calculate the maximum speed before the cylinder body overturns. The cylinder body is subjected to the centrifugal force of the plunger, the inertial reaction force between the slipper and the plunger, and the elastic force while rotating, and the torque balance equation of the cylinder body is JPEG0007876918000043.jpg35170

[0052] For plungers whose spacing is uniform in a circular matrix around the centerline of the cylinder body, Lagrange's identity shows that, JPEG0007876918000044.jpg7170 By rearranging the torque balance equation, we can obtain an equation that calculates the maximum speed before the cylinder body overturns.

[0053] Step S43 explains that when a plunger pump is rotating at high speed, the flow velocity increases in a localized area of ​​the plunger during liquid intake and discharge, increasing kinetic energy and decreasing potential energy. When the pressure is below the saturated vapor pressure, cavitation occurs, significantly impacting the performance of the plunger pump. Therefore, it becomes necessary to optimize the design to prevent cavitation-induced erosion failures of rotating parts.

[0054] By creating a formula to calculate the maximum speed before cavitation erosion failure occurs in a plunger pump, and verifying cavitation erosion failure of rotating parts, JPEG0007876918000045.jpg51170JPEG0007876918000046.jpg89170

[0055] If we divide the flow velocity in the alternating region, which is waist-shaped, into the centripetal velocity portion of the plunger motion and the tangential velocity portion of the cylinder body rotation, JPEG0007876918000047.jpg82170 By combining the above formulas, we can obtain a formula to calculate the maximum velocity before a plunger pump fails due to cavitation erosion. Based on step S3, the three-dimensional model of the rotating part is used to extract the fluid domain model of the rotating part using real-space Boolean calculation. As shown in Figure 8, the fluid domain is divided into multiple fluid domains by a mesh in preparation for finite element analysis of the flow field.

[0056] Based on the fundamental theorem of fluid rotation, we construct the continuity equation and the Navier-Stokes equation for the fluid region of the rotating parts of a plunger pump.

[0057] The increase in fluid mass within each mesh portion of the rotating part's fluid region is equal to the net mass of the fluid that entered the mesh portion during the same time interval. Specifically, when constructing the mass continuity equation for the rotating part, JPEG0007876918000048.jpg20170

[0058] Since the rate of change of the kinetic energy of each mesh portion in a rotating part with respect to time is equal to the sum of various forces applied to the same mesh portion from the outside, the density of the compressible fluid changes with time. Therefore, we construct the Navier-Stokes equations for the compressible fluid of the rotating part, and specifically, JPEG0007876918000049.jpg42170

[0059] Based on the design pressure and design rotational speed for the plunger pump, the load characteristics and motion characteristics of the plunger pump during use are added to the continuity equations and Navier-Stokes equations for the rotating component fluid domain.

[0060] Finite element analysis is performed to obtain a cloud diagram of fractional gas volume for the fluid region of the rotating part, and the cavitation erosion characteristics of the rotating part are represented as shown in Figure 9.

[0061] The liquid suction pressure of the plunger pump can be increased by a liquid replenishment pump or a booster pump. This is the main form of increasing the speed limit of the plunger pump in the event of a cavitation erosion failure. Figure 10 shows a graph of how the speed limit of a plunger pump changes with the liquid suction pressure when a cavitation erosion failure occurs. Increasing the cavitation pressure in the medium, and increasing the flow path area of ​​the liquid suction port and the area of ​​the waist-shaped alternating region in the plunger pump can also increase the speed limit of the plunger pump in the event of a cavitation erosion failure. After optimization, perform step S4 again.

[0062] The specific steps to optimize the fifth parameter in JPEG0007876918000050.jpg27170 are as follows: JPEG0007876918000051.jpg47170 Among these, the basic emission limit formula is the relationship between the plunger hole diameter, the plunger distribution circle diameter, and the maximum target emission in step S21. Step S5 outputs the configuration parameters, material attributes, and process related to the optimized rotating parts of the plunger pump.

[0063] Based on the above results, the configuration of the rotating components of the plunger pump is optimized for limiting the plunger pump discharge volume, operating pressure, and speed. By repeating the above process, the configuration and material processes for the rotating components of a high-speed, high-pressure axial plunger pump can be obtained over a relatively short design cycle, thereby increasing the safety, stability, and service life of the fluid rotating system. At the same time, the steps according to the present invention can be adjusted, combined, or increased or decreased in order according to actual needs.

[0064] The embodiments described above are merely for illustrating embodiments of the present invention and are not intended to limit the scope of the present invention. Provided that they do not depart from the spirit of the present invention, various modifications and improvements to the technical proposal of the present invention are possible for those skilled in the art, and all of these should be included within the scope of the claims of the present invention.

Claims

1. Step S1 involves first identifying the constituent material properties and design objectives for the rotating parts of the plunger pump, including the maximum target discharge rate, maximum rotational speed, and rated pressure of the plunger pump. Step S2 involves identifying configuration parameters for the rotating parts of the plunger pump based on the maximum target emissions, Step S3 involves constructing a three-dimensional model of the rotating part of the plunger pump based on the configuration parameters identified in step S2, setting initial material attributes and processes for the member, determining the strength of the member under conditions where the plunger pump operates at rated pressure based on configuration deformation, determining whether the rated pressure is met, executing step S4 if it is met, otherwise optimizing the parameters and then repeating steps S2 and S3, Step S3 is, Step S31 involves constructing a three-dimensional model of a rotating part and initially setting the material and process for the component, Step S32, which determines the strength of the member structure at the rated pressure based on the principle of structural deformation, Substep S321 divides a solid region mesh for analysis using finite elements based on the component structure of the rotating part, The structural deformation and stress in the rotating parts are influenced by the temperature field and fluid field when the plunger pump is operating, and are transmitted between the components. Substep S322 applies an instantaneous pressure load obtained by calculating the fluid field at the interface between the liquid and solid, applies a temperature load to the rotating parts when the plunger pump is operating, and restricts the movement of the rotating parts according to the actual operating conditions. For rotating parts, multiple fields act in a coupled manner, and the structural deformation, including structural deformation and stress due to temperature load and fluid load, is analyzed. Rotating parts deform when subjected to force. For rotating parts, a cloud diagram of structural deformation and stress response is extracted. If it is determined that there is no interference in the oil film gap of the rotating part after structural deformation, and that the structural stress is smaller than the material's required stress, it is calculated whether the maximum pressure due to the current material's required stress is greater than the rated pressure. If it is calculated to be greater, the next step is executed. Otherwise, the third parameter, which is the structural strength, structural stiffness, thermal expansion coefficient, and wall thickness of the material in the region where the rated pressure is not met, is optimized, and steps S2 and S3 are executed again in step S33. Step S3 specifically includes calculating whether the maximum pressure due to the current material stress is less than 1.1 times the rated pressure, and if it is calculated to be less, the next step is performed, otherwise, the fourth parameter, which is the overall structural strength and structural stiffness of the material, is optimized, and then steps S2 and S3 are performed again in step S34, Step S4 involves determining and optimizing the parameters for failures that may occur when the rotating parts are operating at the rated speed, based on the configuration parameters identified in step S2 for the rotating parts, determining whether the maximum rotational speed requirement is met, executing step S5 if it is met, otherwise optimizing the parameters and repeating steps S2 to S4. A method for optimizing the design of rotating parts for a high-speed, high-pressure axial plunger pump, characterized by including step S5, which outputs optimized configuration parameters for the rotating parts of the plunger pump, and optimized material attributes and processes for the components.

2. Step S2 is, The cylinder body parameters are identified, and these parameters include the plunger hole diameter, the plunger distribution circle diameter, the wall thickness between the plunger holes in the cylinder body, and the length of the cylinder body. Of these, the relationship between the plunger hole diameter, the plunger distribution circle diameter, and the maximum target discharge is Identify the plunger parameters, which include the plunger length and the plunger head diameter. Plunger length The slipper parameters are identified, and these parameters include the slipper ball diameter, slipper sealing belt inner diameter, slipper sealing belt outer diameter, slipper ball cup outer diameter, and slipper damping hole diameter. Identify the retainer parameters, which include the retainer plunger distribution circle diameter and the retainer hole diameter. The formula for calculating the diameter of the retainer plunger distribution circle is The ratio between the radius of the center of the waist-shaped groove in the cylinder body and port plate and the radius of the plunger's distribution circle is 0.7 to 1.0, the width of the waist-shaped groove is 0.35 to 0.5 times the plunger diameter, and the width of the sealing belt inside and outside the port plate is 0.1 to 0.2 times the plunger diameter. The linear velocity of the groove center forming the waist shape in the cylinder body and port plate is calculated to determine whether the port plate meets the requirements, and the calculation formula is Based on the configuration parameters, the discharge rate of the plunger pump is calculated, and it is determined whether the discharge rate of the plunger pump is greater than the target discharge rate. If it is greater, the next step is performed. If not, the first parameter, which is the number of plungers, the diameter of the plungers, the diameter of the plunger distribution circle, and the inclination angle of the swashplate, is optimized, and the process returns to step S21, and step S2 is repeated in step S27. A method for optimizing the rotating components of a high-speed high-pressure axial plunger pump according to claim 1, characterized by specifically including step S28, which involves determining whether the discharge rate of the plunger pump is less than 1.1 times the target discharge rate, and if so, performing the next step, otherwise optimizing a second parameter which is the number of plungers, the diameter of the plunger, the diameter of the plunger distribution circle, and the inclination angle of the swashplate, and returning to step S2, and performing step S2 again.

3. A method for optimizing the design of rotating parts for a high-speed, high-pressure axial plunger pump according to claim 2, characterized in that in step S2, the configuration parameters for the rotating parts of the plunger pump include cylinder body parameters, plunger parameters, slipper parameters, retainer parameters, port plate parameters, and swashplate parameters.

4. A method for optimizing the design of rotating parts for a high-speed high-pressure axial plunger pump according to claim 1, characterized in that if the rated pressure configuration is not met even after step S33 is executed N times, an output is made indicating that the current parameters cannot meet the rated pressure requirements.

5. Step S4 is, We created a formula to calculate the maximum speed before a slipper overturns, and verified the failure of overturning in a slipper with rotating parts.

6. A method for optimizing the design of rotating parts of a high-speed high-pressure axial plunger pump according to Claim 5, characterized in that substep S43 of Claim 5 includes step S432 of constructing the continuity equation and the Navier-Stokes equation for the fluid region of the rotating parts of the plunger pump using the fundamental theorem of fluid rotation.

7. Step S432 is, Substep S4321 involves creating an equation that expresses the continuity equation in detail for the mass of the rotating part, Substep S4322 constructs the Navier-Stokes equations for compressible fluids of rotating parts, Substep S4323 involves applying the load characteristics and motion characteristics of the plunger pump during use to the continuity equation and the Navier-Stokes equation for the fluid region of the rotating parts, based on the design pressure and design rotational speed of the plunger pump. A method for optimizing the design of a rotating part of a high-speed, high-pressure axial plunger pump according to claim 6, characterized in that it specifically includes a substep S4324 which involves analyzing using finite elements to obtain a cloud diagram of fractional gas volumes in the fluid region of the rotating part, and expressing the cavitation erosion characteristics of the rotating part.

8.

9. The specific steps to optimize the first parameter in step S27 are to increase the number of plungers, the diameter of the plungers, the diameter of the plunger distribution circle, and the inclination angle of the swashplate. The specific steps to optimize the second parameter in step S28 are to reduce the number of plungers, the diameter of the plungers, the diameter of the plunger distribution circle, and the tilt angle of the swashplate. The specific steps to optimize the third parameter in step S33 are to increase the structural strength and structural rigidity of the material, decrease the thermal expansion coefficient of the material, and increase the wall thickness in the region where the rated pressure is not met. The specific step to optimize the fourth parameter in step S34 is to lower the overall structural strength and structural stiffness of the material. The specific step of optimizing the fifth parameter in substep S44 is: A method for optimizing the design of rotating parts for a high-speed high-pressure axial plunger pump according to claim 5, characterized in that the basic discharge limit formula is a relational expression between the plunger hole diameter, the plunger distribution circle diameter, and the maximum target discharge in step S21.

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