End-tooth connection structure large load dynamic characteristic test equipment and design method thereof

Abstract

The application discloses a large-load dynamic characteristic test equipment of an end tooth connection structure and a design method thereof. The equipment comprises a rotor front section and a rotor rear section arranged coaxially, a counterweight wheel disc, a ball bearing, a roller bearing, a center pull rod, a rotating nut and an end tooth connection structure. The rotor front section and the rotor rear section are drivingly connected through the end tooth connection structure. An outer thread is arranged on an outer peripheral wall of the rotor rear section. The counterweight wheel disc is connected with the outer thread through an inner thread. A center hole is arranged in the rotor rear section in an axial direction. One end of the center pull rod is connected with the rotor front section, and the other end of the center pull rod is threadedly connected with the rotating nut through the center hole of the rotor rear section. The ball bearing is connected with a journal of one end of the rotor front section away from the end tooth connection structure. The roller bearing is connected with the rotor rear section. The application can determine the influence of pre-tightening force and transverse load on the dynamic characteristics of the end tooth connection structure under the loss of large-load limit stiffness.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of engine component testing, in particular, relates to a large-load dynamic characteristic test device for an end-tooth connection structure and a design method thereof. BACKGROUND

[0002] As a high-speed rotating complex machine, an aero-engine has a large temperature gradient of a compressor part and a turbine part, and a strength and an assembly structure design requirement of each part, and therefore, a rotor system composed of different materials needs a connection structure in the rotor structure design. Different structural units (members, assemblies, parts) need to be connected to form a rotor structure system through an interface, and for a rotor system with a connection interface, because the structure geometry and the mechanical characteristics thereof are discontinuous, the rotor system with the connection structure is called a discontinuous rotor structure system. The existence of the contact interface in the structure system makes the structure geometry and material properties discontinuous, and further causes the mechanical characteristic parameters (such as stiffness, damping and the like) in the structure to be discontinuous, so that the stiffness characteristics are different from those of the overall structure.

[0003] The advanced turboshaft / turboprop engine fuel engine rotor has a circular arc end-tooth connection structure connection, a long pull rod axial segmented compression structure form between the stages of the compressor, between the compressor and the turbine and between the two stages of the turbine, which is a typical discontinuous structure. In order to explore the stiffness loss degree of the end-tooth connection structure-pull rod connection rotor under a large load, and the influence law of the structure and mechanical parameters of the rotor system on the dynamic characteristics of the connection structure, a set of simple end-tooth connection structure-pull rod connection structure large load limit dynamic stiffness loss test verification scheme is proposed from the structure and mechanical characteristics of the end-tooth connection structure-pull rod connection structure of the typical turboshaft / turboprop engine, and the feasibility of the test piece design is verified through simulation calculation, so as to provide a basis and support for further research on the dynamic characteristics of the end-tooth connection structure-pull rod rotor connection structure under the influence of external load and deformation.

[0004] According to the analysis of the bending stiffness loss mechanism of the discontinuous structure, the local bending deformation of the connecting structure will cause the change of the bending stiffness characteristics, and the discontinuous structure will exhibit different bending stiffness characteristics under different bending curvatures. For the end-tooth connecting structure, when the local bending deformation of the connecting structure occurs, one side is compressed, and the other side is opened. The local bending deformation of the end-tooth connecting structure will cause the change of the bending stiffness characteristics, and the discontinuous structure will exhibit different bending stiffness characteristics under different bending curvatures. Compared with no bending deformation, the end-tooth connecting structure tooth surface contact area is reduced, resulting in bending stiffness loss; after the structure is bent, the contact area is still under the action of the initial load and the additional bending compression force, and the contact stress is increased compared with no bending, but the influence on the overall bending stiffness is small; therefore, the stiffness loss of the connecting structure under bending deformation can be evaluated by the change of the interface contact area.

[0005] The rotor structure of an aero-engine has complex characteristics, and the test piece is usually designed according to the whole dynamics similarity and local geometric structure dissimilarity criteria, such as a simulation rotor containing an end-tooth connecting structure. This method simplifies the blade structure and reduces the cost, and can also better reproduce the stiffness loss under the real state. However, due to the limitation of test conditions, it is difficult to realize the limit stiffness loss of the end-tooth connecting structure under large load, because the large stiffness loss of the end-tooth connecting structure in the engine generally occurs when the engine bears a large unbalanced load, such as blade loss. In this case, it is difficult to apply the load directly according to the actual working condition, that is, to simulate the blade loss to apply the load. Moreover, the simulation of the high-speed working condition of the real engine itself has high requirements for the machining and assembly of the test piece, resulting in a significant increase in cost, which ultimately leads to the following problems:

[0006] 1) The pre-tightening force and transverse load have little effect on the stiffness change of the contact interface of the end-tooth connecting structure rotor, and the measurement results are easily disturbed by other factors, so the stiffness loss measurement is not accurate. This is because when the real engine applies a small load, the stiffness loss of the end-tooth connecting structure is not obvious, and a small measurement value is easily affected by various interference factors.

[0007] 2) Due to the limitation of test conditions, it is difficult to reproduce the limit stiffness loss of the end-tooth connecting structure under large load, which brings difficulties to the dynamic property evaluation. SUMMARY

[0008] The present application provides an end-tooth connecting structure large load dynamic property test equipment to solve the technical problems of inaccurate stiffness loss measurement, difficult test, high cost, and difficulty in reproducing the limit stiffness loss of the end-tooth connecting structure under large load.

[0009] The technical scheme adopted by the present application is as follows:

[0010] The utility model provides a kind of end tooth connection structure big load dynamic characteristic test equipment, including coaxial setting rotor front section and rotor rear section, counterweight wheel disc, ball bearing, roller bearing, center pull rod, rotating nut, end tooth connection structure, wherein:

[0011] The rotor front section and the rotor rear section are connected by the end tooth connection structure, the outer peripheral wall of the rotor rear section is provided with external threads, the counterweight wheel disc is connected with the external threads by internal threads, the center hole is provided in the rotor rear section along the axial direction, one end of the center pull rod is connected with the rotor front section, and the other end is connected with the rotating nut through the center hole of the rotor rear section.

[0012] Further, the end of the rotor front section towards the end tooth connection structure is provided with a threaded hole, and the end of the center pull rod is provided with external threads connected with the threaded hole.

[0013] Further, the end face of the counterweight wheel disc is provided with a plurality of bolt holes of different diameters along different arc radii, and the bolt holes are screwed into counterweight bolts of corresponding diameters.

[0014] Further, the counterweight wheel disc includes coaxially arranged first disc and second disc, the first disc and the second disc are connected with the external threads of the outer peripheral wall of the rotor rear section through internal screw holes, and the end faces of the first disc and the second disc away from each other are provided with a plurality of bolt holes of different diameters along different arc radii, and the bolt holes are screwed into counterweight bolts of corresponding diameters.

[0015] Further, a positioning pull rod is further connected between the mounting seats of the ball bearing and the roller bearing.

[0016] Another aspect of the present application also provides a design method of an end tooth connection structure big load dynamic characteristic test device, including the following steps:

[0017] S1, analyze the real engine end tooth connection structure, and obtain the original size of the end tooth connection structure itself;

[0018] S2, according to the test bench, preliminarily design the finite element model of the equivalent test piece of the end tooth connection structure big load dynamic characteristic test device, the finite element model of the equivalent test piece adopts eight-node quadrilateral element to divide the rotor grid, uses bearing unit to simulate support, and uses continuous structure to replace the end tooth connection structure;

[0019] S3, checking the bending critical speed and the lateral load position of the equivalent test piece by using the finite element model, if the first order bending critical speed is lower than the limit speed, and the end tooth connecting structure is located at the maximum deformation position of the bending vibration mode, then the design of the equivalent test piece is completed, otherwise, the axial size, support stiffness and axial position of the lateral load of the equivalent test piece are adjusted until the first order bending critical speed is lower than the limit speed, and the end tooth connecting structure is located at the maximum deformation position of the bending vibration mode.

[0020] Further, the step S3 specifically comprises the steps of:

[0021] S31, calculating the first order bending critical speed and the vibration mode of the end tooth connecting structure without considering the stiffness loss;

[0022] S32, if the first order bending critical speed of the original rotor is lower than the limit speed, and the end tooth connecting structure is located at the maximum deformation position of the bending vibration mode in the first order bending vibration mode, then the design of the simplified equivalent test piece is completed, otherwise, the axial size, support stiffness and axial position of the lateral load of the simplified equivalent test piece are adjusted and returned to step S31;

[0023] S33, establishing a finite element model of the real equivalent test piece by considering the real end tooth connecting structure of the simplified equivalent test piece, and the end tooth connecting structure in the finite element model of the real equivalent test piece is a discontinuous structure;

[0024] S34, performing statics calculation according to the assembly condition and the lateral load of the finite element model of the real equivalent test piece to obtain the contact state of the connecting interface of the end tooth connecting structure;

[0025] S35, calculating the stiffness loss correction coefficient under the current assembly condition and the lateral load according to the contact state, and substituting the stiffness loss correction coefficient into step S31 to calculate the first order bending critical speed and the bending vibration mode of the end tooth connecting structure under the condition of considering the stiffness loss;

[0026] S36, if the first order bending critical speed of the real rotor is lower than the limit speed, and the end tooth connecting structure is still located at the maximum deformation position of the bending vibration mode in the first order bending vibration mode, then the design of the equivalent test piece is completed, otherwise, the axial size, support stiffness and axial position of the lateral load of the equivalent test piece are adjusted and the steps S31-S36 are repeated until the design of the equivalent test piece is completed.

[0027] Another aspect of the present application also provides an end tooth connecting structure large load dynamic characteristic test device, comprising:

[0028] An original size acquisition module is configured to analyze the real engine end tooth connecting structure, and acquire the original size of the end tooth connecting structure itself;

[0029] a finite element model design module, configured to preliminarily design an equivalent test piece of the large-load dynamic characteristic test device of the end-tooth connection structure according to the test bench condition, and establish a finite element model of the equivalent test piece;

[0030] an equivalent test piece iterative checking module, configured to check the bending critical speed and the transverse load position of the equivalent test piece,

[0031] if the first-order bending critical speed of the end-tooth connection structure is lower than the limit speed, and the end-tooth connection structure is located at the maximum deformation position of the bending vibration mode, the design of the equivalent test piece is completed, otherwise, the axial size, the support stiffness and the transverse load axial position of the equivalent test piece are adjusted until the first-order bending critical speed is lower than the limit speed, and the end-tooth connection structure is located at the maximum deformation position of the bending vibration mode.

[0032] Another aspect of the present application also provides an electronic device, comprising a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor implements the steps of the large-load dynamic characteristic test method of the end-tooth connection structure when executing the computer program.

[0033] Another aspect of the present application also provides a storage medium, comprising a stored program, wherein the program controls the device where the storage medium is located to execute the steps of the large-load dynamic characteristic test method of the end-tooth connection structure when the program is executed.

[0034] Compared with the prior art, the present application has the following beneficial effects:

[0035] 1) The end-tooth position has sufficient loading space, facilitating the load loading of the statics test or the dynamic stiffness test, and ensuring the measurability of the displacement of the end-tooth position;

[0036] 2) The unbalanced mass loading structure is designed to apply the transverse load, ensuring the controllability of the rotor deformation, and facilitating the research on the influence of the structural deformation degree on the end-tooth stiffness;

[0037] 3) The bending vibration mode of the test piece rotor has integrity, and no obvious local vibration occurs;

[0038] 4) The end-tooth connection structure is designed at the maximum deformation position of the bending vibration mode, i.e., the end-tooth connection structure is located at the maximum curvature of the elastic line of the rotor, facilitating the realization of the limit stiffness loss;

[0039] 5) The bending deformation is mainly the deformation of the rotor, so that the relative deformation of the rotor is obviously larger than the deformation of the support structure.

[0040] In addition to the objects, features and advantages described above, the present application has other objects, features and advantages. The present application will be further described in detail below with reference to the accompanying drawings. BRIEF DESCRIPTION OF DRAWINGS

[0041] The accompanying drawings, which form a part of the present application, are intended to provide further understanding of the present application and are incorporated herein in conjunction with the description. The drawings are as follows:

[0042] Figure 1 A front view schematic diagram of a large load dynamic characteristic test device of an end tooth connection structure according to an embodiment of the present application.

[0043] Figure 2 A perspective view schematic diagram of a large load dynamic characteristic test device of an end tooth connection structure according to an embodiment of the present application.

[0044] Figure 3 A partial sectional view schematic diagram of a large load dynamic characteristic test device of an end tooth connection structure according to an embodiment of the present application.

[0045] Figure 4 A flowchart of a large load dynamic characteristic test method of an end tooth connection structure according to an embodiment of the present application.

[0046] Figure 5 A finite element model schematic diagram of an equivalent test piece of an embodiment of the present application.

[0047] Figure 6 A sub-flowchart of step S3 of an embodiment of the present application.

[0048] Figure 7 A first-order bending mode schematic diagram of a finite element model of an embodiment of the present application when not considering stiffness loss.

[0049] Figure 8 A first-order bending mode schematic diagram of a finite element model of an embodiment of the present application when considering stiffness loss.

[0050] Figure 9 A module schematic diagram of a large load dynamic characteristic test device of an end tooth connection structure according to an embodiment of the present application.

[0051] Figure 10 A module schematic diagram of an electronic device according to an embodiment of the present application.

[0052] Figure 11 A module schematic diagram of a computer device according to an embodiment of the present application.

[0053] As shown in the drawings: 1, a ball bearing; 2, a front section of a rotor; 3, an end tooth connection structure; 4, a first disc; 5, a second disc; 6, a rear section of a rotor; 7, a roller bearing; 8, a rotating nut; 9, a positioning pull rod; 10, a counterweight bolt; 11, a center pull rod. DETAILED DESCRIPTION

[0054] It should be noted that the embodiments in the present application and the features in the embodiments can be combined with each other without conflict. The present application will be described in detail below with reference to the drawings and in combination with the embodiments.

[0055] Reference Figures 1 to 3 The preferred embodiment of the present application provides a large-load dynamic characteristic test device for end-tooth connection structure, which comprises a rotor front section 2 and a rotor rear section 6 arranged coaxially, a counterweight disc, a ball bearing 1, a roller bearing 7, a center pull rod 11, a rotating nut 8 and an end-tooth connection structure 3, wherein:

[0056] The rotor front section 2 and the rotor rear section 6 are drivingly connected through the end-tooth connection structure 3, an outer peripheral wall of the rotor rear section 6 is provided with external threads, the counterweight disc is connected with the external threads through internal threads, and the counterweight disc is rotated to conveniently adjust the position of the transverse load. The rotor rear section 6 is provided with a center hole in the axial direction. One end of the center pull rod 11 is connected with the rotor front section 2, and the other end of the center pull rod 11 is threadedly connected with the rotating nut 8 through the center hole of the rotor rear section 6. The ball bearing 1 is connected with the journal of the end of the rotor front section 2 away from the end-tooth connection structure 3, and the roller bearing 7 is connected with the journal of the end of the rotor rear section 6 away from the end-tooth connection structure 3.

[0057] The test device of the embodiment mainly comprises the rotor front section 2 and the rotor rear section 6, the counterweight disc, the center pull rod 11 and other parts. The rotor front section 2 and the rotor rear section 6 are drivingly connected through the end-tooth connection structure 3 and are axially compressed through the center pull rod 11 and the rotating nut 8. The test device adopts a double fulcrum design, and the support scheme is 1-0-1. The front fulcrum is the ball bearing 1 installed on the front journal of the rotor front section 2 to realize the axial positioning of the rotor and the outward transmission of the axial force and the radial force. The rear fulcrum is the roller bearing 7 installed on the rear journal of the rotor rear section 6 to realize the outward transmission of the radial force.

[0058] In order to reduce the processing difficulty and the assembly of the end-tooth connection structure 3, the rotor front section 2 is designed as a solid front section and a hollow rear section. Through preliminary calculation, it is known that the center pull rod 11 is installed on the left end journal, and the length-diameter ratio of the center pull rod 11 is large, which will cause a low-frequency bending vibration mode mainly with the pull rod vibration. In order to ensure the integrity of the rotor vibration, it is necessary to reduce the length-diameter ratio of the center pull rod 11 (≤30), and the following methods are adopted in the design to improve the bending stiffness of the center pull rod 11:

[0059] 1) A solid design is adopted;

[0060] 2) The center pull rod 11 span is reduced by moving the position of the roller bearing to the left.

[0061] Specifically, the rotor front section 2 is provided with a threaded hole at one end of the end tooth connection structure 3, and the center pull rod 11 is provided with an external thread at the end thereof and is connected to the threaded hole.

[0062] Preferably, the end faces of the counterweight wheel disc are provided with a plurality of bolt holes of different diameters along different arc radii, and the counterweight bolts 10 of corresponding diameters are screwed into the bolt holes, so that the lateral load can be adjusted by screwing in counterweight bolts 10 of different sizes.

[0063] Preferably, the counterweight wheel disc comprises coaxially arranged first wheel disc 4 and second wheel disc 5, the first wheel disc 4 and the second wheel disc 5 are connected to the outer thread of the outer peripheral wall of the rotor rear section 6 through the inner screw hole, and the end faces of the first wheel disc 4 and the second wheel disc 5 away from each other are provided with a plurality of bolt holes of different diameters along different arc radii, and the counterweight bolts 10 of corresponding diameters are screwed into the bolt holes.

[0064] Unlike the above embodiment, the counterweight wheel disc of the present embodiment is composed of coaxially arranged first wheel disc 4 and second wheel disc 5, the lateral load is applied through the two wheel disc structures, the connecting bolts of the wheel disc structure are consistent with the axis, the stress level of the connecting bolts during rotation of the rotor is reduced, and the operation reliability of the structure is improved.

[0065] Preferably, positioning pull rods 9 are further connected between the mounting seats of the ball bearing 1 and the roller bearing 7 to facilitate the definition and adjustment of the axial distance between the ball bearing 1 and the roller bearing 7.

[0066] The pre-tightening force and lateral load adjustment method of the above embodiment is as follows:

[0067] 1) The pre-tightening force is applied by tensioning the center pull rod 11, that is, the pre-tightening force of the end tooth connection structure 3 is controlled by giving different tension lengths to the center pull rod 11, and the tension length of the center pull rod 11 can be adjusted by rotating the nut 8, and the rotating nut 8 is clamped and prevented from sliding by using locking washers to prevent the structure from loosening;

[0068] 2) The lateral load is adjusted by increasing or decreasing the mass on the first wheel disc 4 and the second wheel disc 5, and the wheel discs are provided with bolt holes of different sizes in the circumferences, and different counterweight bolts 10 can be configured according to the test requirements to control the lateral load.

[0069] As shown in the drawings, another preferred embodiment of the present application also provides a design method of an end tooth connection structure large load dynamic characteristic test device, comprising the steps of: Figure 4 S1, analyzing the real engine end tooth connection structure to obtain the original size of the end tooth connection structure itself;

[0070]

[0071] ​S2, according to the test bench, preliminarily design the equivalent test piece of the end-tooth connection structure large load dynamic characteristic test device, and establish a finite element model of the equivalent test piece, the finite element model of the equivalent test piece is meshed by eight-node quadrilateral elements for the rotor, bearings are simulated by bearing units, and the end-tooth connection structure is replaced by a continuous structure (as shown in Figure 5 In the continuous structure model, the length of the rotor and the stiffness of the elastic support are adjusted to ensure that the bending critical speed can be reached under the given test conditions, and the limit stiffness loss is facilitated;

[0072] S3, the bending critical speed and the transverse load position of the equivalent test piece are checked by using the finite element model, if the first-order bending critical speed of the end-tooth connection structure is lower than the limit speed, and the end-tooth connection structure is located at the maximum deformation position of the bending vibration mode, the design of the equivalent test piece is completed, otherwise, the axial size, support stiffness and transverse load axial position of the equivalent test piece are adjusted until the first-order bending critical speed is lower than the limit speed, and the end-tooth connection structure is located at the maximum deformation position of the bending vibration mode.

[0073] Specifically, as shown in Figure 6 The step S3 specifically includes the steps of:

[0074] S31, the first three bending critical speeds of the end-tooth connection structure without considering the stiffness loss (see Table 1) and the first-order bending critical speed and vibration mode (see Figure 7 ) are calculated without considering the stiffness loss, the stiffness loss of the end-tooth connection structure 3 is caused by the connection interface slip and other reasons, which is currently difficult to calculate directly, the bending critical speed is considered as a continuous structure in the evaluation of the bending critical speed, so that the bending critical speed obtained is slightly larger than the actual bending critical speed, and the test bench can reach the bending critical speed corresponding to the continuous structure;

[0075] Table 1 critical speed without considering stiffness loss

[0076]

[0077] S32, if the first-order bending critical speed of the initial rotor is lower than the limit speed, and the end-tooth connection structure is located at the maximum deformation position of the bending vibration mode in the first-order bending vibration mode, the design of the simplified equivalent test piece is completed, otherwise, the axial size, support stiffness and transverse load axial position of the simplified equivalent test piece are adjusted and returned to step S31;

[0078] S33, in the case of considering the stiffness loss, the real end-tooth connection structure of the simplified equivalent test piece is considered to establish a real equivalent test piece finite element model, and the end-tooth connection structure in the real equivalent test piece finite element model is a non-continuous structure;

[0079] S34, statics calculation is performed according to the assembly condition and the lateral load of the finite element model of the real equivalent test piece, and a contact state of a connecting interface of the end tooth connecting structure is obtained;

[0080] S35, a stiffness loss correction coefficient under the current assembly condition and the lateral load is calculated according to the contact state, the stiffness loss correction coefficient is substituted into step S31, and the first three order bending critical speeds (see Table 2) and the first order bending mode of the end tooth connecting structure under the condition of considering the stiffness loss are calculated.

[0081] Table 2 critical speed considering stiffness loss

[0082]

[0083] S36, if the first order bending critical speed of the real rotor is lower than the limit speed, and the end tooth connecting structure is still located at the maximum deformation position of the bending mode in the first order bending mode, the design of the equivalent test piece is completed, wherein when the stiffness loss correction coefficient is 0.24, the first order bending mode of the real rotor calculated is as shown in Figure 8 It can be seen that the end tooth connecting structure 3 is located at the maximum deformation position of the bending mode, that is, the end tooth connecting structure 3 is located at the maximum curvature of the rotor elastic line, the sensitivity of the stiffness loss under different lateral loads is improved, and the limit stiffness loss is facilitated to be realized; otherwise, the axial size, support stiffness and axial position of the lateral load of the equivalent test piece are adjusted, and steps S31-S36 are repeated until the design of the equivalent test piece is completed.

[0084] In summary, through simulation and simulation, the strength and dynamic characteristics of the rotor are checked, and the following conclusions are obtained:

[0085] 1) The tightness reserve of the center pull rod 11 pre-tightening force of the equivalent test piece meets the design requirements;

[0086] 2) The static strength considering the center pull rod 11 pre-tightening force meets the design requirements;

[0087] 3) The first order bending critical speed is lower than the working speed of the test bench, and has a large reserve margin;

[0088] 4) The first order bending mode has good integrity, no local vibration, and the end tooth position is located near the maximum displacement of the rotor elastic line, facilitating the realization of the limit stiffness loss of the end tooth connecting structure under large load.

[0089] As shown in Figure 9 Another preferred embodiment of the present application further provides an end tooth connecting structure large load dynamic characteristic test device, which comprises:

[0090] An original size acquisition module is configured to analyze a real engine end tooth connecting structure, and acquire original sizes of the end tooth connecting structure itself;

[0091] a finite element model design module, configured to preliminarily design an equivalent test piece of the large-load dynamic characteristic test device of the end-tooth connection structure according to the test bench condition, and establish a finite element model of the equivalent test piece;

[0092] an equivalent test piece iterative checking module, configured to check the bending critical speed and the transverse load position of the equivalent test piece, if the first-order bending critical speed of the end-tooth connection structure is lower than the limit speed, and the end-tooth connection structure is located at the maximum deformation position of the bending vibration mode, then the design of the equivalent test piece is completed, otherwise, the axial size, the support stiffness and the transverse load axial position of the equivalent test piece are adjusted until the first-order bending critical speed is lower than the limit speed, and the end-tooth connection structure is located at the maximum deformation position of the bending vibration mode.

[0093] As shown in Figure 10 , the preferred embodiment of the present application also provides an electronic device, which includes a memory, a processor and a computer program stored in the memory and executable on the processor, and the processor implements the steps of the end-tooth connection structure large-load dynamic characteristic test method in the above embodiment when executing the program.

[0094] As shown in Figure 11 , the preferred embodiment of the present application also provides a computer device, which can be a terminal or a living body detection server, and its internal structure diagram can be as shown in Figure 11 . The computer device includes a processor, a memory and a network interface connected through a system bus. Among them, the processor of the computer device is used to provide computing and control capabilities. The memory of the computer device includes a non-volatile storage medium and an internal memory. The non-volatile storage medium stores an operating system and a computer program. The internal memory provides an environment for the operating system and the computer program in the non-volatile storage medium to run. The network interface of the computer device is used to communicate with other computer devices outside through network connection. The computer program is executed by the processor to implement the steps of the end-tooth connection structure large-load dynamic characteristic test method.

[0095] Those skilled in the art can understand, Figure 11 the structure shown in the figure is only a block diagram of part of the structure related to the scheme of the present application, and does not constitute a limitation on the computer device to which the scheme of the present application is applied. The specific computer device can include more or fewer components than those shown in the figure, or combine certain components, or have a different component arrangement.

[0096] The preferred embodiment of the present application also provides a storage medium, which includes a stored program, and when the program runs, controls the device where the storage medium is located to execute the steps of the end-tooth connection structure large-load dynamic characteristic test method in the above embodiment.

[0097] It is noted that the steps illustrated in the flowcharts of the figures can be executed by computer system such as a computer readable program instructions executing with a processor. While the steps associated with the flowcharts are illustrated, ordered, and described in a particular sequence, in some embodiments, the steps can be executed in other orders than those described or illustrated (for example, using a different flowchart).

[0098] If the functions described in the method of the embodiments are implemented in the form of software function units and sold or used as independent products, they can be stored in one or more computer readable storage media. Based on such understanding, the part of the prior art or the part of the technical solutions of the embodiments of the present application can be embodied in the form of a software product, which is stored in a storage medium, and includes several instructions for causing a computing device (which can be a personal computer, a server, a mobile computing device, or a network device, etc.) to execute all or part of the steps of the methods described in the embodiments of the present application. The aforementioned storage medium includes: a U disk, a mobile hard disk, a read-only memory (ROM, Read-Only Memory), a random access memory (RAM, Random Access Memory), a magnetic disk or an optical disk, and various media that can store program codes.

[0099] Those skilled in the art should understand that the embodiments of the present application can be provided as a method, a system, or a computer program product. Therefore, the present application can take the form of an entirely hardware embodiment, an entirely software embodiment, or an embodiment combining software and hardware aspects. Moreover, the present application can take the form of a computer program product implemented on one or more computer-usable storage media (including, but not limited to, disk storage, CD-ROM, optical storage, etc.) containing computer-usable program code. The solutions in the embodiments of the present application can be implemented in various computer languages, such as object-oriented programming languages Java and interpreted scripting language JavaScript.

[0100] The present application is described with reference to flowcharts and / or block diagrams of methods, devices (systems), and computer program products according to embodiments of the present application. It should be understood that each flow and / or block in the flowcharts and / or block diagrams, and the combination of flows and / or blocks in the flowcharts and / or block diagrams can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, a special-purpose computer, an embedded processor, or other programmable data processing device to produce a machine, so that the instructions executed by the processor of the computer or other programmable data processing device produce a device that implements the functions specified in the flowcharts and / or block diagrams. Figure 1 The functions specified in one flow or multiple flows and / or blocks Figure 1 The functions specified in one flow or multiple flows and / or blocks

[0101] These computer program instructions can also be stored in a computer readable memory that can direct a computer or other programmable data processing apparatus to function in a particular manner, such that the instructions stored in the computer readable memory produce an article of manufacture including instructions which implement the Figure 1 function specified in the flow or flows and / or blocks Figure 1 of the block or blocks.

[0102] These computer program instructions can also be loaded onto a computer or other programmable data processing apparatus to cause a series of operational steps to be performed on the computer or other programmable apparatus to produce a computer implemented process such that the instructions that are executed on the computer or other programmable apparatus provide steps for implementing the Figure 1 function specified in the flow or flows and / or blocks Figure 1 of the block or blocks.

[0103] Although preferred embodiments of the application have been described herein, substitutions and alterations can be made to these embodiments by those skilled in the art without departing from the spirit and scope of the application. Accordingly, it is intended that the appended claims be interpreted as including all such alternatives and modifications as fall within the spirit and scope of the application.

[0104] It will be apparent to those skilled in the art that various modifications and variations can be made to the present application without departing from the spirit or scope of the application. Thus, it is intended that the present application cover modifications and variations of this application provided they come within the scope of the appended claims and their equivalents.

Claims

1. A design method of a large load dynamic characteristic test equipment of an end tooth connection structure, the large load dynamic characteristic test equipment of the end tooth connection structure comprising a rotor front section (2) and a rotor rear section (6) coaxially arranged, a counterweight disc, a ball bearing (1), a roller bearing (7), a center pull rod (11), a rotating nut (8), an end tooth connection structure (3), wherein: The rotor front section (2) and the rotor rear section (6) are connected by the end tooth connection structure (3), the outer peripheral wall of the rotor rear section (6) is provided with external threads, the counterweight wheel disc is connected with the external threads through internal threads, the rotor rear section (6) is provided with a central hole in the axial direction, one end of the central pull rod (11) is connected with the rotor front section (2), the other end passes through the central hole of the rotor rear section (6) and is connected with the rotating nut (8) through threads, the ball bearing (1) is connected with the journal of the end of the rotor front section (2) away from the end tooth connection structure (3), the roller bearing (7) is connected with the journal of the end of the rotor rear section (6) away from the end tooth connection structure (3), the end of the rotor front section (2) towards the end tooth connection structure (3) is provided with a threaded hole, the end of the central pull rod (11) is provided with external threads and is connected with the threaded hole, the end surface of the counterweight wheel disc is provided with a plurality of bolt holes with different diameters along different arc radii, the counterweight bolts (10) with corresponding diameters are screwed into the bolt holes, the counterweight wheel disc comprises coaxially arranged first and second wheel discs (4) and (5), the first and second wheel discs (4) and (5) are connected with the external threads of the outer peripheral wall of the rotor rear section (6) through internal threads, the end surfaces of the first and second wheel discs (4) and (5) away from each other are provided with a plurality of bolt holes with different diameters along different arc radii, the counterweight bolts (10) with corresponding diameters are screwed into the bolt holes, the mounting seats of the ball bearing (1) and the roller bearing (7) are further connected with the positioning pull rod (9), and the method comprises the following steps: ​ S1, the original size of the end tooth connection structure is obtained by analyzing the real engine end tooth connection structure; S2, the equivalent test piece of the end tooth connection structure large load dynamic characteristic test device is preliminarily designed according to the test bench, and a finite element model of the equivalent test piece is established, the finite element model of the equivalent test piece is meshed by using eight-node quadrilateral elements for the rotor, bearings are simulated by using bearing units, and the end tooth connection structure is replaced by a continuous structure; S3, the bending critical speed and the transverse load position of the equivalent test piece are checked by using the finite element model, if the first-order bending critical speed of the end tooth connection structure is lower than the limit speed, and the end tooth connection structure is located at the maximum deformation position of the bending vibration mode, the design of the equivalent test piece is completed, otherwise, the axial size, support stiffness and transverse load axial position of the equivalent test piece are adjusted until the first-order bending critical speed is lower than the limit speed, and the end tooth connection structure is located at the maximum deformation position of the bending vibration mode.

2. The method of designing according to claim 1, characterized in that: The step S3 specifically comprises the following steps: S31, the first-order bending critical speed and the vibration mode of the simplified rotor containing the end tooth connection structure are calculated without considering the stiffness loss. S32, if the initial rotor first-order bending critical speed is lower than the limit speed, and the end tooth connection structure in the first-order bending mode is located at the maximum deformation position of the bending mode, the design of the simplified equivalent test piece is completed, otherwise, the axial size, support stiffness and axial position of the lateral load of the simplified equivalent test piece are adjusted and returned to step S31; S33, in consideration of the stiffness loss, a real equivalent test piece finite element model is established considering the real end tooth connection structure of the simplified equivalent test piece, and a non-continuous structure is adopted for the end tooth connection structure in the real equivalent test piece finite element model; S34, according to the assembly condition and lateral load of the real equivalent test piece finite element model, static calculation is carried out to obtain the contact state of the connection interface of the end tooth connection structure; S35, according to the contact state, the stiffness loss correction coefficient under the current assembly condition and lateral load is calculated, and the stiffness loss correction coefficient is substituted into step S31 to calculate the first-order bending critical speed and bending mode of the end tooth connection structure considering the stiffness loss; S36, if the real rotor first-order bending critical speed is lower than the limit speed, and the end tooth connection structure in the first-order bending mode is still located at the maximum deformation position of the bending mode, the design of the equivalent test piece is completed, otherwise, the axial size, support stiffness and axial position of the lateral load of the equivalent test piece are adjusted and the steps S31-S36 are repeated until the design of the equivalent test piece is completed.

3. A design device of a large load dynamic characteristic test device of a face gear connection structure, the large load dynamic characteristic test device of the face gear connection structure comprising a rotor front section (2) and a rotor rear section (6) coaxially arranged, a counterweight wheel disc, a ball bearing (1), a roller bearing (7), a center pull rod (11), a rotating nut (8), a face gear connection structure (3), wherein: The rotor front section (2) and the rotor rear section (6) are connected through the end tooth connection structure (3), the outer peripheral wall of the rotor rear section (6) is provided with external threads, the counterweight disc is connected with the external threads through internal threads, the center hole is arranged in the rotor rear section (6) in the axial direction, one end of the center pull rod (11) is connected with the rotor front section (2), the other end passes through the center hole of the rotor rear section (6) and is threadedly connected with the rotating nut (8); the ball bearing (1) is connected with the journal of the end of the rotor front section (2) away from the end tooth connection structure (3), the roller bearing (7) is connected with the journal of the end of the rotor rear section (6) away from the end tooth connection structure (3); the end of the rotor front section (2) towards the end tooth connection structure (3) is provided with a threaded hole, the end of the center pull rod (11) is provided with external threads and is connected with the threaded hole; the end surface of the counterweight disc is provided with a plurality of bolt holes with different diameters along different arc radii, the counterweight bolts (10) with corresponding diameters are screwed into the bolt holes; the counterweight disc comprises coaxially arranged first and second discs (4) and (5), the first and second discs (4) and (5) are connected with the external threads of the outer peripheral wall of the rotor rear section (6) through internal threads, the end surfaces of the first and second discs (4) and (5) away from each other are provided with a plurality of bolt holes with different diameters along different arc radii, and the counterweight bolts (10) with corresponding diameters are screwed into the bolt holes; the mounting seats of the ball bearing (1) and the roller bearing (7) are further connected with the positioning pull rod (9); characterized by comprising: An original size acquisition module is configured to analyze a real engine end-tooth connection structure and acquire original sizes of the end-tooth connection structure itself; A finite element model design module is configured to preliminarily design an equivalent test piece of the end-tooth connection structure large-load dynamic characteristic test device according to a test bench condition and establish a finite element model of the equivalent test piece; An equivalent test piece iterative checking module is configured to check a bending critical speed and a transverse load position of the equivalent test piece, if a first-order bending critical speed of the end-tooth connection structure is lower than a limit speed and the end-tooth connection structure is located at a maximum deformation position of a bending vibration mode, the design of the equivalent test piece is completed, otherwise, an axial size, a support stiffness and a transverse load axial position of the equivalent test piece are adjusted until the first-order bending critical speed is lower than the limit speed and the end-tooth connection structure is located at the maximum deformation position of the bending vibration mode.

4. An electronic device comprising a memory, a processor, and a computer program stored on the memory and executable on the processor, characterized in that, The processor executes the computer program to implement the steps of the design method in any one of claims 1 to 2.

5. A storage medium, the storage medium comprising a stored program, characterized in that, The device in which the storage medium is located is controlled to execute the steps of the design method in any one of claims 1 to 2 when the program is running.

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