A pre-engagement structure calibration method and system

Abstract

The present application discloses a pre-meshing structure verification method and system, which belongs to the field of motor technology. The pre-meshing structure verification method includes: obtaining a pre-meshing structure model based on the mechanical structure and design parameters of the pre-meshing structure; establishing a drive model, and obtaining the test air pressure of the piston element in the pre-meshing structure model and the test displacement of the threaded element in the pre-meshing structure model based on the drive model and the pre-meshing structure model; verifying whether the test air pressure of the piston element is consistent with the preset air pressure of the piston element, and whether the test displacement of the threaded element is consistent with the preset displacement of the threaded element. Through this modeling and simulation method, the setting parameters of the actual pre-meshing structure can be accurately simulated, and there is no need to actually design the pre-meshing structure for testing, which reduces the processing cost of the pre-meshing structure and does not require repeated physical testing, greatly shortening the design cycle of the pre-meshing structure and improving the efficiency of the design.

Description

Technical Field

[0001] The present application belongs to the field of motor technology, and in particular relates to a pre-engagement structure calibration method and system. Background Art

[0002] Marine diesel engine turbine starter motors feature a pre-engagement mechanism, enabling easy engagement between the motor and the flywheel. However, the design of this pre-engagement mechanism is primarily based on imported starter motors. This design requires extensive testing and optimization, which can be time-consuming and labor-intensive, resulting in lengthy project cycles and significant cost. Summary of the Invention

[0003] Purpose of the invention: The embodiment of the present application provides a pre-meshing structure verification method, which aims to overcome the technical problem that the design of the pre-meshing structure requires optimization and confirmation through a large number of experiments, which takes a lot of time.

[0004] Technical solution: A pre-engagement structure calibration method described in an embodiment of the present application includes:

[0005] Based on the mechanical structure and design parameters of the pre-meshing structure, a pre-meshing structure model is obtained;

[0006] Establishing a driving model, and obtaining a test air pressure of a piston element in the pre-meshing structure model and a test displacement of a threaded element in the pre-meshing structure model based on the driving model and the pre-meshing structure model;

[0007] Verifying whether the test air pressure of the piston element is consistent with the preset air pressure of the piston element, and whether the test displacement of the threaded element is consistent with the preset displacement of the threaded element;

[0008] The design parameters of the pre-engagement structure model are adjusted so that the test air pressure of the piston element is consistent with the preset air pressure of the piston element, and the test displacement of the threaded element is consistent with the preset displacement of the threaded element.

[0009] In some embodiments, obtaining a pre-meshing structure model based on the mechanical structure and design parameters of the pre-meshing structure includes:

[0010] obtaining the piston element based on the air pressure parameters and mechanical parameters of the design parameters;

[0011] The piston element includes a cylinder, a piston, a spring and a piston rod;

[0012] The air pressure parameters include: the inner diameter of the cylinder, the outer diameter of the piston rod, and the length of the inner cavity enclosed by the piston and the cylinder in the initial state;

[0013] The mechanical parameters include: the stiffness of the spring and the preload force of the spring.

[0014] In some embodiments, the obtaining of the piston element based on the mechanical structure, the air pressure parameter and the mechanical parameter in the design parameters includes:

[0015] Based on the design parameters, obtaining a first mass element;

[0016] The design parameters include the mass of the piston, the maximum displacement of the piston, the minimum displacement of the piston and the friction force exerted on the piston;

[0017] The first mass element includes a first test end and a second test end. Based on the first test end and the second test end, the velocity and displacement of the piston are obtained to be input into the piston element of the pre-meshing structural model.

[0018] In some embodiments, the piston element is provided with a first port and a second port;

[0019] Based on the first port, input a pressure parameter to obtain the volume of the inner cavity and the flow rate change of the gas in the inner cavity;

[0020] Based on the second port, input the speed and displacement of the piston to obtain the pressure exerted on the piston;

[0021] The test gas pressure in the inner cavity is obtained based on the volume of the inner cavity, the flow change of the gas in the inner cavity, and the pressure exerted on the piston.

[0022] In some embodiments, obtaining a pre-meshing structure model based on the mechanical structure and design parameters of the pre-meshing structure includes:

[0023] obtaining the threaded element based on the mechanical structure and the design parameters;

[0024] The threaded element includes a screw and a nut, wherein the surface of the screw has threads, and the screw is rotatably connected to the nut through the threads;

[0025] The design parameters include the inclination angle of the thread, the lead of the thread, the pitch diameter of the thread, the normal pressure perpendicular to the thread, the tangential force parallel to the thread, the force acting on the nut, and the torque acting on the nut.

[0026] In some embodiments, the threaded element includes a first interface;

[0027] Based on the first interface, a thrust force acting on the screw is obtained.

[0028] In some embodiments, obtaining a pre-meshing structure model based on the mechanical structure and design parameters of the pre-meshing structure further includes:

[0029] obtaining an elastic element based on the design parameters;

[0030] The design parameters include: the stiffness of the elastic element and the preload force of the elastic element.

[0031] In some embodiments, the elastic element includes a first connecting end and a second connecting end, and the first connecting end and the second connecting end are both used to input the displacement of the elastic element and output the force of the elastic element.

[0032] In some embodiments, obtaining the threaded element based on the mechanical structure and the design parameters includes:

[0033] Based on the design parameters, obtaining a second mass element;

[0034] The design parameters include the mass of the screw, the maximum displacement of the screw, the minimum displacement of the screw, and the friction force exerted on the screw;

[0035] The second mass element includes a third test end and a fourth test end, and the test displacement of the screw is obtained based on the third test end, the fourth test end, the thrust acting on the screw, and the force of the elastic element.

[0036] In some embodiments, obtaining a pre-meshing structure model based on the mechanical structure and design parameters of the pre-meshing structure further includes:

[0037] Based on the design parameters, obtaining a limiting element;

[0038] The limiting element includes a first limiting member and a second limiting member, and the design parameters include a maximum relative displacement between the first limiting member and the second limiting member, and a minimum relative displacement between the first limiting member and the second limiting member.

[0039] In some embodiments, the limiting element includes a third connecting end and a fourth connecting end, and the third connecting end and the fourth connecting end are both used for inputting displacement and outputting constraint reaction force.

[0040] A pre-engagement structure verification system, comprising:

[0041] A first building module is used to obtain a pre-meshing structure model according to the mechanical structure and design parameters of the pre-meshing structure;

[0042] a second construction module, configured to establish a driving model, and based on the driving model and the pre-meshing structure model, obtain a test air pressure of a piston element in the pre-meshing structure model and a test displacement of a threaded element in the pre-meshing structure model;

[0043] a third building block, configured to verify whether the test air pressure of the piston element is consistent with the preset air pressure of the piston element, and whether the test displacement of the threaded element is consistent with the preset displacement of the threaded element;

[0044] The fourth construction module is used to adjust the design parameters of the pre-meshing structure model so that the test air pressure of the piston element is consistent with the preset air pressure of the piston element, and the test displacement of the threaded element is consistent with the preset displacement of the threaded element.

[0045] Beneficial effect: The pre-meshing structure verification method of the embodiment of the present application includes: obtaining a pre-meshing structure model based on the mechanical structure and design parameters of the pre-meshing structure; establishing a drive model, and obtaining the test air pressure of the piston element in the pre-meshing structure model and the test displacement of the threaded element in the pre-meshing structure model based on the drive model and the pre-meshing structure model; verifying whether the test air pressure of the piston element is consistent with the preset air pressure of the piston element, and whether the test displacement of the threaded element is consistent with the preset displacement of the threaded element; adjusting the design parameters of the pre-meshing structure model so that the test air pressure of the piston element is consistent with the preset air pressure of the piston element, and the test displacement of the threaded element is consistent with the preset displacement of the threaded element. Through this modeling and simulation method, the setting parameters of the actual pre-meshing structure can be accurately simulated, and there is no need to actually design the pre-meshing structure for testing, which reduces the processing cost of the pre-meshing structure, does not require repeated physical testing, greatly shortens the design cycle of the pre-meshing structure, and improves the efficiency of the design. BRIEF DESCRIPTION OF THE DRAWINGS

[0046] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the following briefly introduces the drawings required for use in the description of the embodiments. Obviously, the drawings described below are only some embodiments of the present application. For those skilled in the art, other drawings can be obtained based on these drawings without creative work.

[0047] Figure 1 This is a flow chart of the pre-engagement structure verification method in an embodiment of the present application;

[0048] Figure 2 This is a simulation diagram of the pre-meshing structure verification method according to an embodiment of the present application;

[0049] Figure 3 This is a schematic diagram of the simulated structure of the piston element according to an embodiment of the present application;

[0050] Figure 4 This is a schematic structural diagram of the first mass element according to an embodiment of the present application;

[0051] Figure 5 This is a schematic diagram of the simulated structure of the threaded element according to an embodiment of the present application;

[0052] Figure 6 This is a schematic structural diagram of the second mass element according to an embodiment of the present application;

[0053] Figure 7 This is a schematic diagram of the simulation structure of the elastic element according to an embodiment of the present application;

[0054] Figure 8 This is a schematic diagram of the simulation structure of the limiting element of the embodiment of the present application;

[0055] Figure 9 Schematic diagram of the pre-engagement structure of the starter motor according to an embodiment of the present application;

[0056] Figure markings: 10-pre-engaged structure model; 11-piston element; 111-cylinder; 112-piston; 113-spring; 114-piston rod; 115-first port; 116-second port; 118-inner cavity; 12-first mass element; 121-first test end; 122-second test end; 13-threaded element; 131-screw; 132-nut; 133-thread; 134-first interface; 135-second interface; 136-third interface; 137-fourth interface; 14-second mass element; 141-third test end; 142-fourth test end; 15-elastic element; 151-first connecting end; 152-second connecting end; 16-limiting element; 161-first limiting member; 162-second limiting member; 163-third connecting end; 164-fourth connecting end; 20-piston structure; 30-ratchet; 40-output shaft. DETAILED DESCRIPTION

[0057] The following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the technical solutions in the embodiments of the present application. Obviously, the embodiments described are only part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without making creative efforts are within the scope of protection of this application.

[0058] In the description of this application, it should be understood that the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include one or more features. In the description of this application, "plurality" means two or more, and at least one means one, two, or more, unless otherwise clearly and specifically defined.

[0059] Marine diesel engine turbine starter motors feature a pre-engagement mechanism, enabling easy engagement between the motor and the flywheel. However, the design of this pre-engagement mechanism is primarily based on imported starter motors. This design requires extensive testing and optimization, which can be time-consuming and labor-intensive, resulting in lengthy project cycles and significant cost.

[0060] Marine diesel engine turbine starter motors feature a pre-engagement mechanism, enabling easy engagement between the motor and flywheel. The pre-engagement mechanism's main components are a piston, an output shaft, and a ratchet mechanism. Pre-engagement works by pushing compressed air into the piston before starting, extending the output shaft and engaging it with the ring gear. This pre-engagement is achieved through the helical splines of the ratchet mechanism. High-pressure air enters the piston, causing it to move. The force of the gas inside the piston overcomes the force of an external spring, acting on the ratchet, which pushes the output shaft axially outward. Upon impact with the flywheel, a different contact state is created. The force of the gas inside the piston overcomes the external spring force, acting on the ratchet. The output shaft, restrained by the flywheel, is no longer able to move axially. The applied force is converted along the helical splines into axial and circumferential forces. The axial force presses the output shaft against the flywheel end face, while the circumferential force rotates the output shaft, aligning it with the flywheel teeth. The output shaft gear meshes with the gear on the engine flywheel, starting the air motor and driving the engine crankshaft. When the engine crankshaft reaches a certain speed, the high-pressure gas is released, and the ratchet mechanism returns to its original position under the action of the spring force. The output shaft also returns to its original position and disengages from the gear of the engine flywheel.

[0061] However, the design of the pre-engagement structure of the starter motor mainly refers to imported starter motors. The design of the pre-engagement structure needs to be optimized and confirmed through a large number of tests, which takes a lot of time, resulting in a long project cycle, low efficiency, and time-consuming and labor-intensive.

[0062] In view of this, an embodiment of the present application provides a pre-engagement structure calibration method to overcome at least one of the above-mentioned technical problems.

[0063] See also Figure 1 、 Figure 2 、 Figure 3 and Figure 5In an embodiment of the present application, the pre-engagement structure verification method includes the following steps:

[0064] S101: obtaining a pre-meshing structure model 10 based on the mechanical structure and design parameters of the pre-meshing structure;

[0065] S102: establishing a driving model, and obtaining a test air pressure of the piston element 11 in the pre-meshing structure model 10 and a test displacement of the threaded element 13 in the pre-meshing structure model 10 based on the driving model and the pre-meshing structure model 10;

[0066] S103: Verifying whether the test air pressure of the piston element 11 is consistent with the preset air pressure of the piston element 11, and whether the test displacement of the threaded element 13 is consistent with the preset displacement of the threaded element 13;

[0067] S104 : Adjusting the design parameters of the pre-engaging structure model 10 so that the test air pressure of the piston element 11 is consistent with the preset air pressure of the piston element 11 , and the test displacement of the threaded element 13 is consistent with the preset displacement of the threaded element 13 .

[0068] It is understandable that in the simulation software, a pre-meshing structure model 10 can be established through the actual mechanical structure of the pre-meshing structure and the corresponding design parameters, and a driving model needs to be established at the same time to provide driving force for the pre-meshing structure model 10. The driving model can be a model established for the turbine chamber of the motor. The driving model can drive the piston element 11 on the pre-meshing structure model 10 to move (the piston element 11 is equivalent to the piston structure 20 in the actual pre-meshing structure). During this process, the air pressure inside the piston element 11 will change. According to the established model, the internal test air pressure of the piston element 11 can be obtained. During the movement of the piston element 11, the threaded element 13 will be driven to move (the threaded element 13 is equivalent to the ratchet 30 and the output shaft 40 in the actual pre-meshing structure). During this process, the threaded element 13 undergoes a certain displacement. According to the established model, the test displacement of the threaded element 13 can be obtained. Then compare the test air pressure and test displacement obtained through the simulation model with the actual pre-set air pressure and displacement. If the test air pressure is the same as the preset air pressure, and the test displacement is the same as the preset displacement, then the established simulation model has a high accuracy and does not require further debugging and optimization. If there are deviations between the test air pressure and the preset air pressure, and the test displacement and the preset displacement, it is necessary to adjust the input design parameters, re-input some of the adjusted design parameters into the pre-meshing structure model, and observe whether the test air pressure and test displacement obtained by the model are the same as the actual pre-set air pressure and displacement. If they are not the same, readjust the corresponding design parameters until the air pressure and displacement tested by the model are the same as the preset air pressure and displacement. Through this modeling and simulation method, the setting parameters of the actual pre-meshing structure can be accurately simulated. There is no need to actually design the pre-meshing structure for testing, which reduces the processing cost of the pre-meshing structure and does not require repeated physical testing, greatly shortening the design cycle of the pre-meshing structure and improving design efficiency.

[0069] See also Figure 1 、 Figure 2 and Figure 3 In combination with the above embodiments, in some embodiments, based on the mechanical structure and design parameters of the pre-meshing structure, a pre-meshing structure model 10 is obtained, including obtaining a piston element 11 based on the air pressure parameters and mechanical parameters in the design parameters.

[0070] The piston element 11 includes a cylinder 111, a piston 112, a spring 113 and a piston rod 114;

[0071] The air pressure parameters include the inner diameter of the cylinder 111, the outer diameter of the piston rod 114, and the length of the inner cavity 118 enclosed by the piston 112 and the cylinder 111 in the initial state. The mechanical parameters include the stiffness of the spring 113 and the preload force of the spring 113.

[0072] It is understandable that the interior of the pre-engagement structure model 10 includes a piston element 11, which also needs to be modeled. The piston element 11 can be established in the simulation software through the actual structure of the piston element 11: cylinder 111, piston 112, spring 113 and piston rod 114, as well as the corresponding design parameters. The piston element 11 is connected to the drive model, and the drive model can drive the piston 112 in the piston element 11 to move, so that the piston element 11 can drive the threaded element 13 to move accordingly, thereby simulating the movement of the piston structure 20, ratchet 30 and output shaft 40 on the actual pre-engagement structure, making the simulated data more accurate.

[0073] See also Figure 1 、 Figure 2 and Figure 4 In combination with the above embodiments, in some embodiments, the piston element 11 is obtained based on the air pressure parameters and mechanical parameters in the mechanical structure and design parameters, including: obtaining the first mass element 12 based on the design parameters.

[0074] The design parameters include the mass of the piston 112 , the maximum displacement of the piston 112 , the minimum displacement of the piston 112 , and the friction force experienced by the piston 112 .

[0075] The first mass element 12 includes a first test end 121 and a second test end 122 . Based on the first test end 121 and the second test end 122 , the velocity and displacement of the piston 112 are obtained to be input into the piston element 11 of the pre-meshing structural model 10 .

[0076] It is understood that the piston 112 in the piston element 11 requires further modeling in the simulation software, namely, the first mass element 12. By establishing this first mass element 12, the motion of the piston 112 can be simulated. The first test end 121 and the second test end 122 of the first mass element 12 can be used to input corresponding force parameters, thereby obtaining the corresponding velocity and displacement of the piston 112. The velocity and displacement parameters of the piston 112 can be used to further supplement the parameters of the piston element 11 in the model, making the model more complete and the simulation results more accurate.

[0077] During the simulation, the thrust F2 of the piston 112 (thrust is the driving force provided by the driving model) needs to be input to the first test end 121, and the resistance F1 of the piston 112 (resistance includes the friction force on the piston 112 and the reaction force of other structures on the piston 112) needs to be input to the second test end 122. Then, calculation is performed according to the following formula:

[0078]

[0079] Where acc1 is the acceleration of the piston 112, mass is the mass of the piston 112, and F fric is the friction force on the piston 112, r visc is the damping of the piston 112 , v1 is the speed of the piston 112 , t is the movement time of the piston 112 , and x1 is the displacement of the piston 112 .

[0080] See also Figure 1 、 Figure 2 and Figure 3 , in combination with the above embodiments, in some embodiments, the piston element 11 is provided with a first port 115 and a second port 116;

[0081] Through the first port 115, pressure parameters are input to obtain the volume of the inner cavity 118 and the change in the flow rate of the gas in the inner cavity 118. Through the second port 116, the velocity and displacement of the piston 112 are input to obtain the pressure applied to the piston 112. Based on the volume of the inner cavity 118, the change in the flow rate of the gas in the inner cavity 118, and the pressure applied to the piston 112, the test gas pressure within the inner cavity 118 is obtained.

[0082] It is understood that in the simulation software, the piston element 11 has a first port 115 and a second port 116. The first port 115 is a hydraulic port that inputs pressure parameters (the pressure parameter in this project is standard atmospheric pressure, 0 bar) and outputs the volume of the piston element's inner cavity 118 and the change in the gas flow rate in the inner cavity 118. The second port 116 is used to input the displacement and speed of the piston 112. In conjunction with the first port 115, it outputs the force applied to the piston 112. The force applied to the piston 112 is also the pressure of the gas in the inner cavity 118. The test pressure of the gas in the inner cavity 118 is then calculated using the corresponding pressure and pressure calculation formulas. The test pressure is compared with the preset pressure to see if they are consistent. If not, the parameters can be readjusted for simulation.

[0083] During the simulation, the pressure parameter p1 is input to the first port 115 (the pressure parameter in this project is standard atmospheric pressure, which is 0 bar), and the displacement x2 and velocity v2 of the piston 112 are input to the second port 116 (x2 is the same as the displacement x1 calculated from the first mass element 12, and v2 is the same as the velocity v1 calculated from the first mass element 12). Then, calculations are performed according to the following formula:

[0084] length = x2 + x0;

[0085]

[0086] Among them, length is an intermediate variable, x0 is the length of the inner cavity 118 in the initial state, that is, the distance between the piston 112 and the bottom of the cylinder 111 when it is not moving, H1 is the volume of the inner cavity 118, d p is the inner diameter of the cylinder 111, d r is the outer diameter of the piston rod 114, q1 is the flow rate of the gas in the inner cavity 118, f2 is the pressure exerted on the piston 112 output from the second port 116, f3 is 0, K is the stiffness of the spring 113, P is the test air pressure, and S is the force-bearing area.

[0087] See also Figure 1 、 Figure 2 and Figure 5 In combination with the above embodiments, in some embodiments, based on the mechanical structure and design parameters of the pre-meshing structure, a pre-meshing structure model 10 is obtained, including: based on the mechanical structure and design parameters, a threaded element 13 is obtained.

[0088] The threaded element 13 includes a screw 131 and a nut 132. The surface of the screw 131 has a thread 133. The screw 131 is rotatably connected to the nut 132 through the thread 133.

[0089] The design parameters include the inclination angle of the thread 133 , the lead of the thread 133 , the pitch diameter of the thread 133 , the normal pressure perpendicular to the thread 133 , the tangential force parallel to the thread 133 , the force acting on the nut 132 , and the torque acting on the nut 132 .

[0090] It can be understood that the threaded element 13 is part of the model. The ratchet 30 and the output shaft 40 are simulated by the threaded element 13 in the pre-engaged structure model 10. The nut 132 in the threaded element 13 is equivalent to the ratchet 30, and the screw 131 in the threaded element 13 is equivalent to the output shaft 40. The piston element 11 is connected to the nut 132. When the piston 112 in the piston element 11 moves, it can drive the nut 132 to move. The nut 132 drives the screw 131 to move through the thread 133. When the screw 131 is blocked and can no longer move, if the nut 132 is driven by the piston element 11 and continues to move, the screw 131 can be rotated due to the action of the thread structure between the screw 131 and the nut 132. (In the application scenario of the screw 131 and the nut 132, by rotating the nut 132 to apply torque, the nut 132 will produce axial linear displacement on the screw 131. This is because the thread structure of the nut 132 and the screw 131 converts rotational motion into linear motion. Under certain thread specifications, generally, the greater the torque, the greater the axial force of the nut 132 on the screw 131 to move forward or backward, and the distance moved may also be greater. Similarly, the nut 132 and the screw 131 can also convert linear motion into torque under the action of the thread structure, causing one of them to rotate). The motion relationship between the screw 131 and the nut 132 can be used in the simulation software to simulate the motion relationship between the ratchet 30 and the output shaft 40, and the simulation result can be made more accurate.

[0091] See also Figure 1 、 Figure 2 and Figure 5 , in combination with the above embodiments, in some embodiments, the threaded element 13 includes a first interface 134 , a second interface 135 , a third interface 136 and a fourth interface 137 ;

[0092] Based on the second interface 135 and the third interface 136 , the torques of the screw 131 and the nut 132 are obtained respectively; based on the first interface 134 and the fourth interface 137 , the corresponding forces on the screw 131 and the nut 132 are obtained.

[0093] It is understood that the threaded element 13 has a first interface 134, a second interface 135, a third interface 136, and a fourth interface 137. In the simulation software, the torque and force of the screw 131 and the nut 132 can be obtained through these four interfaces. The calculation formula for the thrust F4 acting on the screw 131 obtained through the first interface 134 is as follows:

[0094] L pitch =abs(tan(L α ))π·D pith ;

[0095] F4=Fn ·cos(L α )-F t ·sin(L α );

[0096] Among them, L pitch is the lead of thread 133, L a is the inclination angle of thread 133, D pitch is the mean diameter of the thread 133, F4 is the thrust acting on the screw 131, and F n and F t These are known parameters set within the software.

[0097] See also Figure 1 、 Figure 2 and Figure 7 In combination with the above embodiments, in some embodiments, obtaining the pre-meshing structure model 10 based on the mechanical structure and design parameters of the pre-meshing structure further includes obtaining the elastic element 15 based on the design parameters. The design parameters include the stiffness of the elastic element 15 and the preload force of the elastic element 15.

[0098] It is understood that the pre-engaged structural model 10 also includes an elastic element 15, which can be an elastic structure such as a spring or spring. When modeling the elastic element 15, the stiffness and preload force of the elastic element 15 are input to establish the model. The elastic element 15 is connected between the screw 131 and the nut 132. When the driving force on the piston element 11 is removed, the elastic element 15 resets the screw 131 and the nut 132.

[0099] See also Figure 1 、 Figure 2 and Figure 7 In combination with the above embodiments, in some embodiments, the elastic element 15 includes a first connection end 151 and a second connection end 152, and the first connection end 151 and the second connection end 152 are both used to input the displacement of the elastic element 15 and output the force of the elastic element 15.

[0100] It is understood that the elastic element 15 has a first connection end 151 and a second connection end 152. In the simulation software, the force applied by the elastic element 15, i.e., the elastic force of the elastic element 15, can be obtained through these two connection ends. This force parameter can be used to simulate the movement of the elastic element 15 causing the screw 131 and the nut 132 to reposition, making the model more realistic and reliable.

[0101] During the simulation, the displacement L1 of one end of the elastic element 15 needs to be input to the first connection end 151 to output the force N1 of the elastic element 15, and the displacement L2 of the other end of the elastic element 15 needs to be input to the second connection end 152 to output the corresponding force N2, where N1 and N2 are equal. Then, the calculation is performed according to the following formula:

[0102]

[0103] L = L0 + L1 + L2;

[0104] N1=K·L=K(L0+L1+L2);

[0105] Wherein, L0 is the pre-compression amount of the elastic element 15 , N0 is the pre-tightening force of the elastic element 15 , K is the stiffness of the elastic element 15 , and L is the total displacement of the elastic element 15 .

[0106] See also Figure 1 、 Figure 2 and Figure 6 , in combination with the above embodiments, in some embodiments, obtaining the threaded element 13 based on the mechanical structure and the design parameters includes: obtaining the second mass element 14 based on the design parameters;

[0107] The design parameters include the mass of the screw 131 , the maximum displacement of the screw 131 , the minimum displacement of the screw 131 , and the friction force experienced by the screw 131 ;

[0108] The second mass element 14 includes a third test end 141 and a fourth test end 142 , and obtains a test displacement of the screw 131 based on the third test end 141 , the fourth test end 142 , the thrust acting on the screw 131 , and the force of the elastic element 15 .

[0109] It is understandable that the screw 131 in the threaded element 13 needs to be further modeled in the simulation software, namely: the second mass element 14. By establishing the second mass element 14, the movement of the screw 131 can be simulated, wherein the screw 131 is pushed by the nut 132 (the nut 132 is pushed by the piston element 11), and the elastic element 15 is connected to the screw 131 to facilitate the resetting of the screw. At the same time, when the screw 131 is pushed, the elastic element 15 will generate a force on the screw 131 (that is, generate resistance to the screw 131). The third test end 141 on the second mass element 14 can input the thrust acting on the screw 131, and the fourth test end 142 can input the force of the elastic element 15. The test displacement of the screw 131 can be obtained by the following formula:

[0110]

[0111] Among them, acc2 is the acceleration of the screw 131, m is the mass of the screw 131, F4 is the thrust acting on the screw 131, N1 is the force of the elastic element 15, F5 is the friction force exerted on the screw 131, R is the damping of the screw 131, v3 is the moving speed of the screw 131, t1 is the movement time of the screw 131, and x3 is the test displacement of the screw 131.

[0112] See also Figure 1 、 Figure 2 and Figure 8 In combination with the above embodiments, in some embodiments, obtaining the pre-meshing structure model 10 based on the mechanical structure and design parameters of the pre-meshing structure also includes: obtaining the limiting element 16 based on the design parameters.

[0113] The limiting element 16 includes a first limiting member 161 and a second limiting member 162 , and the design parameters include a maximum relative displacement between the first limiting member 161 and the second limiting member 162 and a minimum relative displacement between the first limiting member 161 and the second limiting member 162 .

[0114] It is understandable that the pre-engaging structure model 10 also includes a limiting element 16. When building a model of the limiting element 16, it is necessary to input the maximum relative displacement and the minimum relative displacement of the first limiting member 161 and the second limiting member 162 in the limiting element 16, so as to establish a model of the limiting element 16. The pre-engaging structure is installed in the box body, and the first limiting member 161 and the second limiting member 162 are equivalent to the outer shell of the piston and the inner wall of the box body. When the piston moves, its position relative to the inner wall of the box body will change, so a relative displacement will occur. The maximum relative displacement refers to the maximum displacement that the piston can move relative to the inner wall of the box body in the initial state (without the action of the driving force). The minimum relative displacement is generally zero. At this time, the piston can no longer move, and it is also impossible to produce a relative displacement with the inner wall of the box body.

[0115] See also Figure 1 、 Figure 2 and Figure 8 In combination with the above embodiments, in some embodiments, the limiting element 16 includes a third connecting end 163 and a fourth connecting end 164, and the third connecting end 163 and the fourth connecting end 164 are both used for inputting displacement and outputting constraint reaction force.

[0116] It is understood that the limiting element 16 has a third connection end 163 and a fourth connection end 164. In the simulation model, the corresponding displacement parameters are input through these two connection ends to obtain the constraint reaction force of the limiting element 16. The constraint reaction force parameters can be used to simulate the force acting on the piston, making the model more realistic and reliable.

[0117] A pre-engagement structure verification system, comprising:

[0118] A first building module is used to obtain a pre-meshing structure model 10 according to the mechanical structure and design parameters of the pre-meshing structure;

[0119] The second construction module is used to establish a driving model, and based on the driving model and the pre-meshing structure model 10, obtain a test air pressure of the piston element 11 in the pre-meshing structure model 10 and a test displacement of the threaded element 13 in the pre-meshing structure model 10;

[0120] A third building block is used to verify whether the test air pressure of the piston element 11 is consistent with the preset air pressure of the piston element 11, and whether the test displacement of the threaded element 13 is consistent with the preset displacement of the threaded element 13;

[0121] The fourth construction module is used to adjust the design parameters of the pre-meshing structure model 10 so that the test air pressure of the piston element 11 is consistent with the preset air pressure of the piston element 11, and the test displacement of the threaded element 13 is consistent with the preset displacement of the threaded element 13.

[0122] In the above embodiments, the description of each embodiment has its own focus. For parts that are not described in detail in a certain embodiment, reference can be made to the relevant descriptions of other embodiments.

[0123] The above is a detailed introduction to the pre-meshing structure verification method and system provided in the embodiments of the present application, and specific examples are used to illustrate the principles and implementation methods of the present application. The description of the above embodiments is only used to help understand the technical solutions and core ideas of the present application; ordinary technicians in this field should understand that: they can still modify the technical solutions recorded in the aforementioned embodiments, or make equivalent replacements for some of the technical features therein; and these modifications or replacements do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of the present application.

Claims

1. A pre-engagement structure verification method, characterized in that: include: Based on the mechanical structure and design parameters of the pre-meshing structure, a pre-meshing structure model (10) is obtained; Establishing a driving model, and obtaining a test air pressure of a piston element (11) in the pre-engaging structural model (10) and a test displacement of a threaded element (13) in the pre-engaging structural model (10) based on the driving model and the pre-engaging structural model (10); Verifying whether the test air pressure of the piston element (11) is consistent with the preset air pressure of the piston element (11), and whether the test displacement of the threaded element (13) is consistent with the preset displacement of the threaded element (13); The design parameters of the pre-engaging structure model (10) are adjusted so that the test air pressure of the piston element (11) is consistent with the preset air pressure of the piston element (11), and the test displacement of the threaded element (13) is consistent with the preset displacement of the threaded element (13).

2. The pre-meshing structure calibration method according to claim 1, characterized in that: The method of obtaining a pre-meshing structure model (10) based on the mechanical structure and design parameters of the pre-meshing structure comprises: obtaining the piston element (11) based on the air pressure parameters and mechanical parameters of the design parameters; The piston element (11) comprises a cylinder (111), a piston (112), a spring (113) and a piston rod (114); The air pressure parameters include: the inner diameter of the cylinder (111), the outer diameter of the piston rod (114), and the length of the inner cavity (118) enclosed by the piston (112) and the cylinder (111) in the initial state; The mechanical parameters include: the stiffness of the spring (113) and the preload force of the spring (113).

3. The pre-engagement structure verification method according to claim 2, characterized in that: The step of obtaining the piston element (11) based on the mechanical structure, the air pressure parameter and the mechanical parameter in the design parameters comprises: Based on the design parameters, obtaining a first mass element (12); The design parameters include the mass of the piston (112), the maximum displacement of the piston (112), the minimum displacement of the piston (112), and the friction force experienced by the piston (112); The first mass element (12) includes a first test end (121) and a second test end (122). Based on the first test end (121) and the second test end (122), the velocity and displacement of the piston (112) are obtained to be input into the piston element (11) of the pre-meshing structural model (10).

4. The pre-engagement structure verification method according to claim 3, characterized in that: The piston element (11) is provided with a first port (115) and a second port (116); Based on the first port (115), a pressure parameter is input to obtain the volume of the inner cavity (118) and the flow rate change of the gas in the inner cavity (118); Based on the second port (116), the speed and displacement of the piston (112) are input to obtain the pressure exerted on the piston (112); The test gas pressure in the inner cavity (118) is obtained based on the volume of the inner cavity (118), the flow rate change of the gas in the inner cavity (118), and the pressure applied to the piston (112).

5. The pre-meshing structure calibration method according to claim 1, characterized in that: The method of obtaining a pre-meshing structure model (10) based on the mechanical structure and design parameters of the pre-meshing structure comprises: Based on the mechanical structure and the design parameters, obtaining the threaded element (13); The threaded element (13) includes a screw (131) and a nut (132), the surface of the screw (131) has a thread (133), and the screw (131) is rotatably connected to the nut (132) via the thread (133); The design parameters include the inclination angle of the thread (133), the lead of the thread (133), the median diameter of the thread (133), the normal pressure perpendicular to the thread (133), the tangential force parallel to the thread (133), the force acting on the nut (132), and the torque acting on the nut (132).

6. The pre-engagement structure verification method according to claim 5, characterized in that: The threaded element (13) includes a first interface (134); Based on the first interface (134), a thrust acting on the screw (131) is obtained.

7. The pre-engagement structure verification method according to claim 6, characterized in that: The method of obtaining a pre-meshing structure model (10) based on the mechanical structure and design parameters of the pre-meshing structure further includes: Based on the design parameters, obtaining an elastic element (15); The design parameters include: the stiffness of the elastic element (15) and the preload force of the elastic element (15).

8. The pre-meshing structure calibration method according to claim 7, characterized in that: The elastic element (15) comprises a first connecting end (151) and a second connecting end (152), wherein the first connecting end (151) and the second connecting end (152) are both used to input the displacement of the elastic element (15) and output the force of the elastic element (15).

9. The pre-meshing structure verification method according to claim 8, characterized in that: The step of obtaining the threaded element (13) based on the mechanical structure and the design parameters comprises: Based on the design parameters, obtaining a second mass element (14); The design parameters include the mass of the screw (131), the maximum displacement of the screw (131), the minimum displacement of the screw (131) and the friction force exerted on the screw (131); The second mass element (14) includes a third test end (141) and a fourth test end (142), and the test displacement of the screw (131) is obtained based on the third test end (141), the fourth test end (142), the thrust acting on the screw (131), and the force of the elastic element (15).

10. The pre-meshing structure verification method according to claim 1, characterized in that: The method of obtaining a pre-meshing structure model (10) based on the mechanical structure and design parameters of the pre-meshing structure further includes: Based on the design parameters, obtaining a limiting element (16); The limiting element (16) comprises a first limiting member (161) and a second limiting member (162), and the design parameters comprise a maximum relative displacement of the first limiting member (161) and the second limiting member (162), and a minimum relative displacement of the first limiting member (161) and the second limiting member (162).

11. The pre-engagement structure verification method according to claim 10, characterized in that: The limiting element (16) comprises a third connecting end (163) and a fourth connecting end (164), and both the third connecting end (163) and the fourth connecting end (164) are used for inputting displacement and outputting constraint reaction force.

12. A pre-engagement structure verification system, characterized in that: include: A first building module is used to obtain a pre-meshing structure model (10) based on the mechanical structure and design parameters of the pre-meshing structure; A second construction module is used to establish a driving model and, based on the driving model and the pre-engaging structural model (10), obtain a test air pressure of a piston element (11) in the pre-engaging structural model (10) and a test displacement of a threaded element (13) in the pre-engaging structural model (10); a third construction module for verifying whether the test air pressure of the piston element (11) is consistent with the preset air pressure of the piston element (11), and whether the test displacement of the threaded element (13) is consistent with the preset displacement of the threaded element (13); The fourth construction module is used to adjust the design parameters of the pre-engaging structural model (10) so that the test air pressure of the piston element (11) is consistent with the preset air pressure of the piston element (11), and the test displacement of the threaded element (13) is consistent with the preset displacement of the threaded element (13).

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