A forward design method and system for the layout parameters of a three-point supported transmission chain

Abstract

The present invention discloses a forward design method and system for three-point support transmission chain layout parameters. The method includes: determining the parameters of the wind turbine transmission chain layout, establishing a force and torque balance equation for the load at the center of the stationary hub, and equating it to the center of the main bearing and the gearbox torque arm; using the transmission chain layout parameters as design variables, and conducting an experimental design with the goal of minimizing the load at the center of the main bearing and the gearbox torque arm, to obtain the contribution rate, main effect, and correlation of the transmission chain layout parameters to the load; optimizing the design variables based on the DOE experimental design results, with minimizing the load at the center of the main bearing and the gearbox torque arm as the optimization goal, and integrating the selection of the main bearing and gearbox elastic support to perform an integrated optimization design, thereby determining the selection of the main bearing and gearbox elastic support elastomer; and the transmission chain layout parameters that are at the lowest cost are considered optimal. The present invention can improve the level of refined design of wind turbines and reduce the design cost of wind turbines.

Description

Technical Field

[0001] The present invention mainly relates to the field of wind power technology, and in particular to a forward design method and system for layout parameters of a three-point supported transmission chain. Background Art

[0002] The drive train is the most important mechanical component of a wind turbine. Its primary function is to convert wind energy captured by the rotor into mechanical energy, which is then transferred through a series of mechanical components to electrical energy in the generator. Key drive train layout parameters include the axial distance A from the hub center to the main bearing center, the axial distance C from the main bearing center to the center of the gearbox torque arm, and the longitudinal distance E between the gearbox's elastic supports. These three parameters directly determine the selection of the three key load-bearing components: the main bearing, gearbox, and gearbox elastic element. They also indirectly influence the design weight of the front frame and main shaft. The selection of these three parameters directly impacts the manufacturing cost of the wind turbine.

[0003] The gearbox is usually supported by a gearbox elastic element and is installed on the front frame, with the front end of the gearbox connected to the main shaft. The main shaft is supported by the main bearing, and the wind rotor is suspended at its front end. Therefore, the weight of the entire wind rotor is concentrated on the two elastic supports of the main bearing and the gearbox. This support method of the doubly fed wind turbine is called three-point support. At present, the transmission chain layout parameters are generally obtained by investigating the transmission chain layout parameters of the wind turbine capacity and blade length of the same level in the industry as the initial value, and then the main bearing, gearbox and gearbox elastic element strength are calculated by load to meet the design requirements. This layout parameter is selected. As wind turbines are connected to the grid at a parity price, low-cost wind turbines have become the current development trend, and the application of refined design in wind turbine design is becoming increasingly important. Summary of the Invention

[0004] The technical problem to be solved by the present invention is: in response to the technical problems existing in the prior art, the present invention provides a three-point support transmission chain layout parameter forward design method and system that improves the degree of refined design of the fan and reduces the design cost of the fan while ensuring the reliability of the main components of the transmission chain.

[0005] In order to solve the above technical problems, the technical solution proposed by the present invention is:

[0006] A forward design method for layout parameters of a three-point support transmission chain comprises the following steps:

[0007] Preliminarily determine the parameters of the wind turbine drive train layout, and use theoretical mechanics to establish the force and torque balance equation for the load at the center of the stationary hub, thereby equating it to the center of the main bearing and gearbox torque arm;

[0008] By applying the DOE experimental design method, the layout parameters of the transmission chain are used as design variables. The experimental design is carried out with the goal of minimizing the load at the center of the main bearing and the gearbox torque arm. The contribution rate, main effect and correlation of the transmission chain layout parameters to the load that meet the target requirements are obtained.

[0009] Based on the results of the DOE experimental design, the design variables were optimized, with minimizing the load at the center of the main bearing and gearbox torque arm as the optimization goal. The selection of the main bearing and gearbox elastic support was integrated into an integrated optimization design to determine the selection of the main bearing and gearbox elastic support elastomers.

[0010] On the premise that each component model meets the load requirements, the layout parameters of the transmission chain with the lowest cost are considered optimal.

[0011] Preferably, the layout parameters of the transmission chain include the axial distance A from the hub center to the main bearing center, the axial distance C from the main bearing center to the gearbox torque arm center, and the longitudinal distance E between the gearbox elastic supports.

[0012] Preferably, the design variables are optimized by changing the key layout parameters of the transmission chain using a full factorial experimental design algorithm and conducting repeated experimental studies.

[0013] Preferably, an optimal Latin hypercube optimization algorithm is used to obtain the optimal layout parameters of the transmission chain that minimize the reaction forces at the main bearing and the gearbox elastic support.

[0014] Preferably, when determining the selection of the main bearing and the gearbox elastic support elastic body, the load at the center of the torque arm is extracted at the same time to select the gearbox planetary carrier bearing.

[0015] Preferably, when calculating the load of the main bearing, the support reaction force acting on the main bearing is calculated, where:

[0016] F mbx =-F x

[0017]

[0018]

[0019] Among them, F mbx is the axial X force of the main bearing; F mby is the horizontal Y force on the main bearing; F mbz is the vertical Z force of the main bearing; F x is the axial force at the hub center in the stationary hub coordinate system; F y is the lateral force at the hub center in the stationary hub coordinate system; F z is the vertical force at the hub center in the stationary hub coordinate system; M yis the bending moment around the Y axis at the hub center in the stationary hub coordinate system; M z is the torque around the Z axis at the hub center in the stationary hub coordinate system; α is the elevation angle of the transmission chain; G ms is the gravity of the main axis; G gb is the weight of the gearbox.

[0020] Preferably, when calculating the load at the center of the gearbox torque arm, the support reaction force acting on the gearbox torque arm is calculated: assuming that the elastic supports on the left and right sides are elastic supports 1 to 4 when viewed from the wheel hub toward the generator, and assuming that the torque borne on the torque arm is equal to the torque transmitted on the main shaft;

[0021] Assuming that the elastic supports 1 and 2 on the left are evenly loaded, the reaction force of elastic support 1 is:

[0022]

[0023]

[0024] Among them, F army is the lateral force of each elastic support; F armz1 is the vertical force of elastic support 1; M x is the torque at the hub center in the stationary hub coordinate system;

[0025] Assuming that the elastic supports 3 and 4 on the right are evenly stressed, the reaction force of elastic support 3 is:

[0026]

[0027] Among them, F armz3 is the vertical force of the elastic support 3.

[0028] The present invention also discloses a three-point support type transmission chain layout parameter forward design system, comprising:

[0029] The first program module is used to preliminarily determine the parameters of the wind turbine drive chain layout. The load at the center of the stationary hub is applied to establish the force and torque balance equation using theoretical mechanics, thereby equating it to the center of the main bearing and gearbox torque arm.

[0030] The second program module is used to perform experimental design by applying the DOE experimental design method with the layout parameters of the transmission chain as the design variables and the load minimization at the center of the main bearing and the gearbox torque arm as the goal. The contribution rate, main effect and correlation of the transmission chain layout parameters to the load that meet the target requirements are obtained;

[0031] The third program module is used to optimize the design variables based on the results of the DOE experimental design, with the optimization goal of minimizing the load at the center of the main bearing and gearbox torque arm. It also integrates the selection of the main bearing and gearbox elastic support to perform an integrated optimization design, thereby determining the selection of the main bearing and gearbox elastic support elastomer.

[0032] The fourth program module is used to consider the layout parameters of the transmission chain as optimal when the cost is lowest, provided that the models of each component meet the load requirements.

[0033] The present invention further discloses a computer-readable storage medium having a computer program stored thereon. When the computer program is executed by a processor, the computer program executes the steps of the above-mentioned forward design method for layout parameters of a three-point support type transmission chain.

[0034] The present invention also discloses a computer device, including a memory and a processor, wherein the memory stores a computer program, and when the computer program is run by the processor, the computer program executes the steps of the above-mentioned forward design method for layout parameters of a three-point support transmission chain.

[0035] Compared with the prior art, the advantages of the present invention are:

[0036] The present invention establishes a mathematical model for calculating the support reaction forces at the elastic supports of the main bearings and the gearbox, defines the transmission chain layout parameters as design variables, and adopts a DOE experimental design method to obtain the relationship between the contribution rate, main effect and correlation of the design variable parameters to the objective function; the optimized design parameters are determined based on the analysis results, and the optimal Latin hypercube optimization algorithm is adopted to obtain the optimal transmission chain layout parameters that meet the requirements of minimizing the support reaction forces, thereby reducing the selection models of the main bearings and the gearboxes, and further reducing the manufacturing cost of the main transmission. BRIEF DESCRIPTION OF THE DRAWINGS

[0037] Figure 1 The present invention is a flowchart of an embodiment of the method.

[0038] Figure 2 Schematic diagram of the distance between the components of the transmission chain of the present invention.

[0039] Figure 3 Schematic diagram of the span of the torque arm in the transmission chain of the present invention.

[0040] Figure 4 It is the stationary hub coordinate system in the present invention.

[0041] Figure 5 Schematic diagram of the arrangement of elastic supports in the transmission chain of the present invention. DETAILED DESCRIPTION

[0042] The present invention will be further described below with reference to the accompanying drawings and specific embodiments.

[0043] like Figure 1 As shown, the forward design method of the layout parameters of the three-point support type transmission chain according to the embodiment of the present invention comprises the following specific steps:

[0044] Using DOE optimization design as the primary analysis method, we first preliminarily determined the parameters of the wind turbine drive train layout. Using theoretical mechanics, we established a force and torque balance equation for the load at the center of the stationary hub, thereby equating it to the center of the main bearing and gearbox torque arm.

[0045] Then, by applying the DOE experimental design method, the layout parameters of the transmission chain were used as design variables, and the experimental design was carried out with the goal of minimizing the load at the center of the main bearing and the gearbox torque arm. The contribution rate, main effect, and correlation of the transmission chain layout parameters to the load that met the target requirements were obtained.

[0046] Based on the results of the DOE experimental design, the optimization design variables are determined, with minimizing the load at the center of the main bearing and the gearbox torque arm as the optimization goal. The main bearing and gearbox elastic support selection procedures are integrated for integrated optimization design, thereby determining the selection of the main bearing and gearbox elastic support elastomer. At the same time, the load at the center of the torque arm can be extracted to select the gearbox planetary carrier bearing.

[0047] When the three models meet the load requirements and the cost is the lowest, the layout parameters of the transmission chain are considered optimal.

[0048] The method of forward designing the transmission chain layout parameters of the present invention can improve the degree of refined design of the fan, while reducing the design cost of the fan while ensuring the reliability of the main components of the transmission chain, thereby improving the competitiveness of the fan.

[0049] In one specific embodiment, the transmission chain layout parameters include the axial distance A from the hub center to the main bearing center, the axial distance C from the main bearing center to the gearbox torque arm center, and the longitudinal distance E between the gearbox elastic supports. A full-factorial design of experiments algorithm was employed to vary the key transmission chain layout parameters, conducting repeated experiments to optimize the design variables. An optimal Latin hypercube optimization algorithm was employed to determine the optimal transmission chain layout parameters that minimize the support reaction forces at the main bearings and gearbox elastic supports.

[0050] The present invention establishes a mathematical model for calculating the support reaction forces at the elastic supports of the main bearings and the gearbox, defines the transmission chain layout parameters as design variables, and adopts a DOE experimental design method to obtain the relationship between the contribution rate, main effect and correlation of the design variable parameters to the objective function; the optimized design parameters are determined based on the analysis results, and the optimal Latin hypercube optimization algorithm is adopted to obtain the optimal transmission chain layout parameters that meet the requirements of minimizing the support reaction forces, thereby reducing the selection models of the main bearings and the gearboxes, and further reducing the manufacturing cost of the main transmission.

[0051] The above design method is described in detail below in conjunction with a complete specific embodiment:

[0052] Step 1: Establish the load conversion equation at the center of the main bearing and gearbox elastic support based on theoretical mechanics and the layout of the transmission chain.

[0053] like Figure 2 and Figure 3 As shown in the figure, A is the distance from the center of the hub to the center of the main bearing; B is the distance from the center of gravity of the main shaft to the center of the main bearing; C is the distance from the center of the main bearing to the center of the torque arm; D is the distance from the center of gravity of the gearbox to the center of the torque arm; L is the span of the torque arm; α is the elevation angle of the transmission chain.

[0054] When performing load equivalence on the main bearing, gearbox elastic support, and gearbox, the stationary hub coordinate system is used, such as Figure 4 As shown in the figure, XN is along the axis of rotation; ZN is perpendicular to XN; YN is horizontal and rotates clockwise with XN and ZN.

[0055] Step 2: Load calculation

[0056] Support reaction force acting on the main bearing:

[0057] F mbx =-F x

[0058]

[0059]

[0060] Among them, F mbx is the axial X force of the main bearing;

[0061] F mby is the horizontal Y force on the main bearing;

[0062] F mbz is the vertical Z force of the main bearing;

[0063] F x is the axial force at the hub center in the stationary hub coordinate system;

[0064] F y is the lateral force at the hub center in the stationary hub coordinate system;

[0065] F z is the vertical force at the hub center in the stationary hub coordinate system;

[0066] M y is the bending moment about the Y axis at the hub center in the stationary hub coordinate system;

[0067] Mz is the torque about the Z axis at the hub center in the stationary hub coordinate system;

[0068] α is the elevation angle of the transmission chain;

[0069] G ms is the weight of the principal axis;

[0070] G gb is the weight of the gearbox;

[0071] Since the elevation angle of the main transmission system is generally around 5 degrees, the influence of gravity on the axial force is very small. Therefore, the axial component of gravity is not considered in the calculation of the axial force of the main bearing.

[0072] 2) Support reaction force acting on the torque arm:

[0073] like Figure 5 As shown, when performing this force calculation, it is assumed that the elastic supports on the left and right sides are elastic supports 1 to 4 when viewed from the hub toward the generator, and it is also assumed that the torque borne on the torque arm is equal to the torque transmitted on the main shaft.

[0074] Assuming that the elastic supports 1 and 2 on the left are evenly loaded, the reaction force of elastic support 1 is:

[0075]

[0076]

[0077] Among them, F army is the lateral force of each elastic support;

[0078] F armz1 is the vertical force of elastic support 1;

[0079] M x is the torque at the hub center in the stationary hub coordinate system;

[0080] Assuming that the elastic supports 3 and 4 on the right are evenly stressed, the reaction force of elastic support 3 is:

[0081]

[0082] Among them, F armz3 is the vertical force of elastic support 3;

[0083] Step 3: Use DOE to perform sensitivity analysis of transmission chain layout parameters

[0084] 1) Establishment of experimental design model

[0085] First, a mathematical model of experimental design was established, with the transmission chain layout parameters A, C, and E as design variables and the minimization of the support reaction forces at the main bearing seat and gearbox support as the design goal.

[0086] 2) Experimental design algorithm

[0087] By using a full factorial design, this approach allows for precise and informative assessment of the effects of factors and interactions.

[0088] 3) Determine the optimization plan based on the experimental design results

[0089] By adopting DOE experimental design, the contribution rate, main effect and correlation relationship of each design variable to the optimization target can be obtained, thereby providing a certain basis for determining the optimization design parameters.

[0090] Step 4: Use optimization design algorithm to optimize the transmission chain layout parameters

[0091] The optimized design parameters are determined based on the analysis results of the third step. The optimal Latin cube optimization algorithm is used to obtain the optimal layout parameters of the transmission chain that minimizes the support reaction forces at the main bearing and gearbox supports. The layout of the transmission chain is determined based on the optimal design variables (A, C, and E values).

[0092] This invention leverages the advantages of DOE experimental design and optimization algorithms to establish a mathematical model for optimizing the layout parameters of the transmission chain. By employing a full-factor experimental design algorithm to vary key transmission chain parameters, repeated experiments can be conducted to determine the optimal design parameters. An optimal Latin hypercube optimization algorithm is then employed to determine the optimal transmission chain layout parameters that minimize the support reaction forces at the main bearings and gearbox elastic supports. The advantages are: 1. The intelligent DOE experimental design and optimization method achieves optimal transmission chain layout design, eliminating the need for manual adjustment of transmission chain layout parameters and determining the optimal parameters through continuous iteration; 2. Automatically optimizing the support reaction forces at the main bearings and gearbox elastic supports allows for rapid selection of the main bearings and gearbox elastic supports.

[0093] The embodiment of the present invention further discloses a three-point support type transmission chain layout parameter forward design system, comprising:

[0094] The first program module is used to preliminarily determine the parameters of the wind turbine drive chain layout. The load at the center of the stationary hub is applied to establish the force and torque balance equation using theoretical mechanics, thereby equating it to the center of the main bearing and gearbox torque arm.

[0095] The second program module is used to perform experimental design by applying the DOE experimental design method with the layout parameters of the transmission chain as the design variables and the load minimization at the center of the main bearing and the gearbox torque arm as the goal. The contribution rate, main effect and correlation of the transmission chain layout parameters to the load that meet the target requirements are obtained;

[0096] The third program module is used to optimize the design variables based on the results of the DOE experimental design, with the optimization goal of minimizing the load at the center of the main bearing and gearbox torque arm. It also integrates the selection of the main bearing and gearbox elastic support to perform an integrated optimization design, thereby determining the selection of the main bearing and gearbox elastic support elastomer.

[0097] The fourth program module is used to consider the layout parameters of the transmission chain as optimal when the cost is lowest, provided that the models of each component meet the load requirements.

[0098] The design system of the present invention corresponds to the above-mentioned design method and also has the advantages described in the above-mentioned design method.

[0099] The present invention also discloses a computer-readable storage medium having a computer program stored thereon. When executed by a processor, the computer program performs the steps of the above-described forward design method for layout parameters of a three-point supported transmission chain. The present invention also discloses a computer device comprising a memory and a processor. The memory has a computer program stored thereon. When executed by the processor, the computer program performs the steps of the above-described forward design method for layout parameters of a three-point supported transmission chain. The present invention can implement all or part of the processes in the above-described method embodiments by instructing related hardware through a computer program. The computer program can be stored in a computer-readable storage medium. When executed by the processor, the computer program can implement the steps of each of the above-described method embodiments. The computer program includes computer program code, which can be in source code form, object code form, executable file, or some intermediate form. Computer-readable media can include any entity or device capable of carrying computer program code, a recording medium, a USB flash drive, a mobile hard drive, a magnetic disk, an optical disk, a computer memory, a read-only memory (ROM), a random access memory (RAM), an electrical carrier signal, a telecommunications signal, and a software distribution medium. The memory can be used to store computer programs and / or modules. The processor implements various functions by running or executing the computer programs and / or modules stored in the memory, and accessing the data stored in the memory. The memory can include high-speed random access memory and non-volatile memory, such as a hard disk, internal memory, a plug-in hard disk, a smart media card (SMC), a secure digital (SD) card, a flash card, at least one disk storage device, a flash memory device, or other volatile solid-state storage device.

[0100] The above are merely preferred embodiments of the present invention. The scope of protection of the present invention is not limited to the above embodiments. All technical solutions based on the principles of the present invention are within the scope of protection of the present invention. It should be noted that for those skilled in the art, various improvements and modifications that do not depart from the principles of the present invention should be considered within the scope of protection of the present invention.

Claims

1. A forward design method for layout parameters of a three-point support transmission chain, characterized in that: Including steps: Preliminarily determine the parameters of the wind turbine drive train layout, and use theoretical mechanics to establish the force and torque balance equation for the load at the center of the stationary hub, thereby equating it to the center of the main bearing and gearbox torque arm; By applying the DOE experimental design method, the layout parameters of the transmission chain are used as design variables. The experimental design is carried out with the goal of minimizing the load at the center of the main bearing and the gearbox torque arm. The contribution rate, main effect and correlation of the transmission chain layout parameters to the load that meet the target requirements are obtained. Based on the results of the DOE experimental design, the design variables were optimized, with minimizing the load at the center of the main bearing and gearbox torque arm as the optimization goal. The selection of the main bearing and gearbox elastic support was integrated into an integrated optimization design to determine the selection of the main bearing and gearbox elastic support elastomers. On the premise that each component model meets the load requirements, the layout parameters of the transmission chain with the lowest cost are considered optimal; When calculating the load at the center of the gearbox torque arm, calculate the support reaction force acting on the gearbox torque arm: set the elastic supports on the left and right sides as elastic supports 1 to 4, as viewed from the hub toward the generator, and set the torque on the torque arm to be equal to the torque transmitted on the main shaft; Assuming that the elastic supports 1 and 2 on the left are evenly loaded, the reaction force of elastic support 1 is: ； ； in, is the lateral force of each elastic support; is the vertical force of elastic support 1; is the torque at the hub center in the stationary hub coordinate system; is the bending moment of the hub center around the Y axis in the stationary hub coordinate system; is the torque about the Z axis at the hub center in the stationary hub coordinate system; is the lateral force at the hub center in the stationary hub coordinate system; is the vertical force at the hub center in the stationary hub coordinate system; is the weight of the principal axis; is the gravity of the gearbox; A is the distance from the hub center to the main bearing center; B is the distance from the main shaft center of gravity to the main bearing center; C is the distance from the main bearing center to the torque arm center; D is the distance from the gearbox center of gravity to the torque arm center; E is the longitudinal distance between the gearbox elastic supports; is the elevation angle of the transmission chain; Assuming that the elastic supports 3 and 4 on the right are evenly loaded, the reaction force of the elastic support 3 is: in, is the vertical force of the elastic support 3.

2. The forward design method for layout parameters of a three-point support transmission chain according to claim 1 is characterized in that: The layout parameters of the transmission chain include the axial distance A from the center of the hub to the center of the main bearing, the axial distance C from the center of the main bearing to the center of the gearbox torque arm, and the longitudinal distance E between the elastic supports of the gearbox.

3. The forward design method for layout parameters of a three-point support transmission chain according to claim 1 is characterized in that: By adopting the full factorial experimental design algorithm to change the key layout parameters of the transmission chain, repeated experiments are carried out to optimize the design variables.

4. The forward design method for layout parameters of a three-point support transmission chain according to claim 1, characterized in that: The optimal Latin hypercube optimization algorithm is used to obtain the optimal layout parameters of the transmission chain that minimizes the reaction forces at the main bearing and gearbox elastic supports.

5. The forward design method for layout parameters of a three-point support transmission chain according to any one of claims 1 to 4, characterized in that: When determining the selection of the main bearing and the gearbox elastic support elastomer, the load at the center of the torque arm is also extracted to select the gearbox planetary carrier bearing.

6. The forward design method for layout parameters of a three-point support transmission chain according to any one of claims 1 to 4, characterized in that: When calculating the load on the main bearing, the support reaction force acting on the main bearing is calculated, where: in, is the axial X force of the main bearing; is the horizontal Y force on the main bearing; is the vertical Z force of the main bearing; is the axial force at the hub center in the stationary hub coordinate system; is the lateral force at the hub center in the stationary hub coordinate system; is the vertical force at the hub center in the stationary hub coordinate system; is the bending moment about the Y axis at the hub center in the stationary hub coordinate system; is the torque about the Z axis at the hub center in the stationary hub coordinate system; is the weight of the principal axis; is the weight of the gearbox.

7. A three-point support type transmission chain layout parameter forward design system, used to execute the steps of the three-point support type transmission chain layout parameter forward design method according to any one of claims 1 to 6, characterized in that: include: The first program module is used to preliminarily determine the parameters of the wind turbine drive chain layout. The load at the center of the stationary hub is applied to establish the force and torque balance equation using theoretical mechanics, thereby equating it to the center of the main bearing and gearbox torque arm. The second program module is used to perform experimental design by applying the DOE experimental design method with the layout parameters of the transmission chain as the design variables and the load minimization at the center of the main bearing and the gearbox torque arm as the goal. The contribution rate, main effect and correlation of the transmission chain layout parameters to the load that meet the target requirements are obtained; The third program module is used to optimize the design variables based on the results of the DOE experimental design, with the optimization goal of minimizing the load at the center of the main bearing and gearbox torque arm. It also integrates the selection of the main bearing and gearbox elastic support to perform an integrated optimization design, thereby determining the selection of the main bearing and gearbox elastic support elastomer. The fourth program module is used to consider the layout parameters of the transmission chain as optimal when the cost is lowest, provided that the models of each component meet the load requirements.

8. A computer-readable storage medium having a computer program stored thereon, characterized in that: When the computer program is executed by a processor, the computer program executes the steps of the forward design method for layout parameters of a three-point supported transmission chain according to any one of claims 1 to 6.

9. A computer device comprising a memory and a processor, wherein a computer program is stored in the memory, wherein: When the computer program is executed by a processor, the computer program executes the steps of the forward design method for layout parameters of a three-point supported transmission chain according to any one of claims 1 to 6.

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