CN104713708A - Spindle fatigue test device - Google Patents
Spindle fatigue test device Download PDFInfo
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- CN104713708A CN104713708A CN201310676760.XA CN201310676760A CN104713708A CN 104713708 A CN104713708 A CN 104713708A CN 201310676760 A CN201310676760 A CN 201310676760A CN 104713708 A CN104713708 A CN 104713708A
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Abstract
The invention relates to a spindle fatigue test device comprising a base block, a motor, and a transmission mechanism. The spindle fatigue test device further comprises a vertical test piece fixing mechanism and a rotational bending moment loading mechanism. The vertical test piece fixing mechanism and the rotation bending moment loading mechanism are arranged on the base block. The vertical test piece fixing mechanism is used for fixing a vertical spindle test piece. The rotation bending moment loading mechanism is connected with the end of the spindle test piece. The motor transfers power to the rotation bending moment loading mechanism through the transmission mechanism. The rotation bending moment loading mechanism forms rotation bending moment on the end of the spindle test piece through eccentric rotation during test. According to the invention, centrifugal load is generated by eccentric rotation, continuous rotation bending moment can be formed on the end of the spindle test piece, rotation bending moment borne by the spindle test piece in actual operation can be simulated more realistically, the loading frequency is less constrained, the requirement of high loading frequency for spindle fatigue test can be met, the test cycle is shortened, and the probability of test failure is reduced.
Description
Technical field
The present invention relates to engine spindle fatigue test technology, particularly relate to a kind of main shaft fatigue experimental device.
Background technology
Main shaft is the strength member of engine, and its main function is transmitted power and each rotatable parts of connection.In engine working process, main shaft subjects the load such as larger moment of torsion, moment of flexure, axial force, gyroscopic couple, centrifugal force and vibration, also subjects thermal force at high-temperature area main shaft.Due to the needs of structure, main shaft often has step, hole, the geometric configuration such as groove and spline, easily occur concentrating at these positions, produce very high local stress, thus the generation of fatigue crack may be caused.Main shaft fracture generally all causes great aircraft accident.Typical case as engine limits longevity part, and according to the requirement of CCAR33 portion about aero-turbine limit longevity part clause 33.70, by test or use experience, main shaft must determine that it meets life requirements.
General bench test drive, is difficult to reproduce during flight uses the gyroscopic couple and moment of flexure that cause due to maneuvering flight, needs to carry out main shaft fatigue life test by exerciser.In present stage main shaft fatigue tester design, usual employing hydraulic actuator in groups carries out the loading of multiple spot moment of flexure to the main shaft of standing test state, to simulate main shaft in practical work process being in High Rotation Speed state, gyroscopic couple and moment of flexure circumferentially go up the rotation Moment of any point to main shaft.But be subject to the restriction of installing space and control system, the load mode of pressurized strut is in groups difficult to realize the loading of real rotation moment of flexure, thus the prediction of impact to main shaft fatigue lifetime.
Meanwhile, because main shaft test load is usually comparatively large, pressurized strut adopts hydraulic way to apply power, comprise the process of pressurization and release, and pressure process exists rate limit, and the height of therefore pressurized strut carries that loading frequency is the highest only has several hertz.And main shaft torture test period reaches several ten thousand usually to hundreds of thousands time circulation, if loading frequency only has several hertz, then common main shaft torture test needs lasting some months, even half a year, and in the so long test period, be easy to occur the change of loading accuracy that the problem such as unit exception, web member wearing and tearing causes, measuring accuracy, finally cause the failure of main shaft torture test.
Summary of the invention
The object of the invention is to propose a kind of main shaft fatigue experimental device, the rotation moment of flexure load condition of main shaft in real work can be simulated more really, and then realize more precisely predicting main shaft fatigue lifetime.
For achieving the above object, the invention provides a kind of main shaft fatigue experimental device, comprise: base block, motor and gear train, wherein also comprise: vertical testpieces fixed mechanism and rotation bending moment loading mechanism, described vertical testpieces fixed mechanism and rotation bending moment loading mechanism are all arranged in described base block, the vertical main shaft testpieces of described vertical testpieces fixed mechanism is fixed, described rotation bending moment loading mechanism is connected with the end of described main shaft testpieces, described motor transmits power by described gear train to described rotation bending moment loading mechanism, described rotation bending moment loading mechanism forms the rotation moment of flexure of the end to described main shaft testpieces at the trial by the mode of eccentric rotary.
Further, described rotation bending moment loading mechanism comprises: load axle and eccentric rotor structure, described loading axle is arranged on the top of described main shaft testpieces, and carry out bolt with the end of described main shaft testpieces to be connected, described eccentric rotor structure is arranged on described loading axle by bearing, described eccentric rotor structure is all connected with described gear train with described motor, described motor transmits power by described gear train to described eccentric rotor structure at the trial, and described eccentric rotor structure is rotated relative to described loading axle.
Further, described eccentric rotor structure comprises: loading disc and at least two balancing weights, and described at least two balancing weights are arranged on described loading disc, forms eccentric structure, and avoids the impact introducing additional lateral power.
Further, described eccentric rotor structure comprises the equal balancing weight of two quality, symmetrical on described loading disc respectively and out-of-alignment is installed, described loading disc is arranged on described loading axle by two bearings, and the setting height(from bottom) of the balancing weight that described two quality are equal is corresponding with the setting height(from bottom) of described two bearings respectively.
Further, described eccentric rotor structure also comprises locating ring, and described locating ring is set on described loading axle, and between the inner ring being arranged on two bearings on described loading axle.
Further, also comprise the hydraulic actuator be arranged on above described loading axle, one end of described hydraulic actuator is connected with described base block, and the other end connects described loading axle, is described rotation bending moment loading mechanism offsetting influence of gravity at the trial.
Further, described gear train comprises: driving gear, follower gear and toothed timing belt, the rotating shaft of described driving gear is connected with the output shaft of described motor, described follower gear is located at the top of described loading disc, and be connected with described loading disc by bolt, described driving gear and described follower gear carry out transmission by described toothed timing belt, and under the drive of described driving gear, described follower gear drives described loading disc and balancing weight to rotate around described loading axle.
Further, described vertical testpieces fixed mechanism comprises: base, the first mounting assembly and the second mounting assembly, described base is fixed in described base block, the below of described main shaft testpieces is fixed, described base is provided with sun cover tooth, overlap tooth with the moon of described main shaft testpieces to match, in order to limit the rotation of described main shaft testpieces; Described first mounting assembly is fixed in described base block, described second mounting assembly is fixed on described first mounting assembly, and described first mounting assembly and the second mounting assembly support described main shaft testpieces respectively by two boundary condition Support Positions of bearing on described main shaft testpieces vertical direction.
Based on technique scheme, the present invention adopts vertical testpieces fixed mechanism to carry out vertical fixing to main shaft testpieces, and the eccentric rotary function provided by rotating bending moment loading mechanism forms the rotation moment of flexure to main shaft testpieces end, compared to the test unit of existing rotation moment of flexure, the Lateral Force that the present invention adopts vertical structure can avoid testpieces quality itself to bring, fixed main shaft testpieces then can ensure the static of in process of the test testpieces, thus the structure of test unit is more simplified, eccentric rotary mode is adopted to produce centrifugal load, continuous print can be formed in the end of main shaft testpieces and rotate moment of flexure, simulate the rotation moment of flexure situation that main shaft testpieces is suffered in actual motion more really, and loading frequency can be determined by angular velocity of rotation, lower loading frequency no longer by hydraulic actuator limits, the requirement of high loading frequency under can meeting main shaft torture test, shorten the test period, reduce and cause the probability of main shaft torture test failure because test unit itself goes wrong.
Accompanying drawing explanation
Accompanying drawing described herein is used to provide a further understanding of the present invention, and form a application's part, schematic description and description of the present invention, for explaining the present invention, does not form inappropriate limitation of the present invention.In the accompanying drawings:
Fig. 1 is the structural representation of an embodiment of main shaft fatigue experimental device of the present invention.
Embodiment
Below by drawings and Examples, technical scheme of the present invention is described in further detail.
As shown in Figure 1, be the structural representation of an embodiment of main shaft fatigue experimental device of the present invention.In the present embodiment, main shaft fatigue experimental device comprises: base block 16, vertical testpieces fixed mechanism, rotate bending moment loading mechanism, motor 6 and gear train, vertical testpieces fixed mechanism and rotation bending moment loading mechanism are all arranged in base block 16, the vertical main shaft testpieces 10 of vertical testpieces fixed mechanism is fixed, rotate bending moment loading mechanism to be connected with the end of main shaft testpieces 10, motor 6 transmits power by gear train to rotation bending moment loading mechanism, rotate bending moment loading mechanism forms the end to main shaft testpieces 10 at the trial rotation moment of flexure by the mode of eccentric rotary.
First composition graphs 1 has a look the realization of a kind of concrete structure rotating bending moment loading mechanism.Rotate bending moment loading mechanism can comprise: load axle 1 and eccentric rotor structure, load the top that axle 1 is arranged on main shaft testpieces 10, and carry out bolt with the end of main shaft testpieces 10 and be connected.
Eccentric rotor structure is arranged on by bearing 17,18 and loads on axle 1, eccentric rotor structure is all connected with gear train with motor 6, motor 6 can transmit power by gear train to eccentric rotor structure at the trial, load axle 1 and main shaft testpieces 10 static, eccentric rotor structure relative to loading axle 1 rotate.
Eccentric rotor structure is a kind of rotatable eccentric structure, suggestion adopts the structure of partial installation, such as adopt the form that loading disc and detachable, changeable, position adjustable at least two balancing weights combine, laboratory technician can select at least two balancing weights to be arranged on loading disc according to testing requirements, form eccentric structure with this, and avoid the effect introducing additional lateral power.Because main shaft testpieces adopts the form of vertical placement, therefore the axis of rotation of eccentric rotor structure is also perpendicular to ground.
Preferably, eccentric rotor structure can comprise the equal balancing weight of two quality, namely the balancing weight 8 in Fig. 1 and balancing weight 9, these two balancing weight quality are equal, carry out symmetrical relative to axle center respectively on loading disc 7, and be in the installation of disalignment (i.e. differing heights), and because eccentric rotor structure needs to rotate around loading axle 1 when installing, therefore loading disc 8 needs to be arranged on by two bearings 17,18 to load on axle 1.Why select the form of this pair of balancing weight, mainly be that the balancing weight of two equals in quality can realize a pair couple simulation moment of flexure, and be convenient to convert moment of flexure, the replacing of balancing weight can be carried out when needing to simulate different moment test value very easily, and there is not the problem of the transverse force added influence that single balancing weight is introduced.
Suppose that the quality of balancing weight 8 and balancing weight 9 is m, and balancing weight 8 is identical to the radial distance of axis X-X with the center of gravity of balancing weight 9, be r, and the axial distance of the center of gravity of balancing weight 8 and balancing weight 9 is L.So when testing, if the rotary rpm of balancing weight and loading disc is ω, then balancing weight 8 and balancing weight 9 produce centrifugal load mr ω respectively
2, due to balancing weight 8 and balancing weight 9 disalignment, the moment of flexure therefore produced is mr ω
2l.When rotary rpm is ω, this moment of flexure rotates around axis X-X, and rotational speed is ω.Be ω/2 π for the loading frequency of each point on test axle, wherein the unit of ω is radian per second.
Can see from above, rotate the size of moment of flexure and the quality of balancing weight, radial distance between rotating speed and balancing weight and axial distance all have relation, therefore experimenter can select according to testing requirements the balancing weight being applicable to quality, and can the axial distance between balancing weight be adjusted, change the size of L, and the change of L can be realized by the locating ring 19 of different size, locating ring 19 can be set in and load on axle 1, and be arranged on two bearings 17 loaded on axle 1, between the inner ring of 18, the balancing weight 8 that two quality are equal, the setting height(from bottom) of 9 respectively with two bearings 18, the setting height(from bottom) of 17 is corresponding, to guarantee the effective transmission in radial directions of balancing weight centrifugal load.By adjusting the axial length of locating ring 19, the loading requirement of different moment test values just can be met.
In addition, from the state seemingly contacted between figure loading disc 7 and loading axle 1, but to relatively rotate in fact between the two, therefore can not directly contact, can gap design be adopted between the two, be used for preventing the lubricating oil in formed chamber from leaking between the two, because gap is less, therefore very not directly perceived on figure, hereby illustrate.
Consider main shaft bending load usually in the magnitude of 10kN.m, load axle and need that there is certain rigidity, to realize the transmission rotating moment of flexure, in addition in order to meet the installation of locating ring and balancing weight, load axle also to need to ensure certain length, therefore the weight loading axle generally has tens kilograms, is difficult to loss of weight.And bring additional axial force owing to loading axle gravity, thus impact loads the life test result of axle, and the mode that this impact is difficult to by calculating is eliminated.Therefore in a preferred embodiment, can also arrange hydraulic actuator 5 above loading axle 1, one end of hydraulic actuator 5 is connected with base block 16, and the other end connects loading axle 1, at the trial for rotating bending moment loading mechanism offsetting influence of gravity.
Because eccentric rotor structure needs to rotate with specific speed at the trial, therefore need motor by means of gear train for eccentric rotor structure provides power.Power transmission can adopt various existing common form, such as belt gear, gear drive etc.In embodiment shown in Fig. 1, gear train comprises: driving gear 3, follower gear 2 and toothed timing belt 4, the rotating shaft of driving gear 3 is connected with the output shaft of motor 6, follower gear 2 is located at the top of loading disc 7, and be connected with loading disc 7 by bolt, rely on the friction force transmitting torque in bolt presses face, drive loading disc 7 to rotate.Driving gear 3 and follower gear 2 carry out transmission by toothed timing belt 4, and under the drive of driving gear 3, follower gear 2 drives loading disc 7 and balancing weight 8,9 to rotate around loading axle 1.This drive mechanism realizes simple and reliable, is suitable for the main shaft torture test continued.
In order to better simulate main shaft testpieces 10 actual working state under installation boundary condition, the loading bottom of axle 1 is carried out bolt with the end of main shaft testpieces 10 and is connected, this is because the end of main shaft testpieces often with fan disk, fan blade and booster stage assembly connect, and when maneuvering flight, due to fan disk, the moment of inertia of fan blade and booster stage assembly, it is caused to produce Moment to spindle nose, therefore the acting surface of bending load is just at spindle nose, therefore select the end loading axle and main shaft testpieces to be fixed by bolt to be connected.
In addition, also need the installation border simulating main shaft testpieces, namely realized by vertical testpieces stationary installation, in Fig. 1, vertical testpieces fixed mechanism comprises: base 15, first mounting assembly 12 and the second mounting assembly 11, and base 15 is fixed in base block 16, the below of main shaft testpieces 10 is fixed, base 15 is provided with sun cover tooth, overlaps tooth and matches, in order to limit the rotation of main shaft testpieces 10 with the moon of main shaft testpieces 10.First mounting assembly 12 is fixed in base block 16, second mounting assembly 11 is fixed on the first mounting assembly 12, and the first mounting assembly 12 and the second mounting assembly 11 support main shaft testpieces 10 respectively by two boundary condition Support Positions of bearing 14,13 on main shaft testpieces 10 vertical direction.
Base realizes the stationary state of main shaft testpieces by the rotation of restriction main shaft testpieces, realizes the control to relative rotation speed between main shaft testpieces and charger, thus controlled loading frequency, measure the main shaft life-span exactly.Two mounting assemblies then can simulate the support stiffness of two fulcrums of main shaft testpieces, and then simulate the boundary condition of actual installation in aeromotor under duty, and the accurate simulation of boundary condition is also realize the simulation to rotating the distortion of Moment lower main axis, it is one of parameter of major control in main shaft fatigue lifetime.
Finally should be noted that: above embodiment is only in order to illustrate that technical scheme of the present invention is not intended to limit; Although with reference to preferred embodiment to invention has been detailed description, those of ordinary skill in the field are to be understood that: still can modify to the specific embodiment of the present invention or carry out equivalent replacement to portion of techniques feature; And not departing from the spirit of technical solution of the present invention, it all should be encompassed in the middle of the technical scheme scope of request of the present invention protection.
Claims (8)
1. a main shaft fatigue experimental device, comprise: base block, motor and gear train, it is characterized in that, also comprise: vertical testpieces fixed mechanism and rotation bending moment loading mechanism, described vertical testpieces fixed mechanism and rotation bending moment loading mechanism are all arranged in described base block, the vertical main shaft testpieces of described vertical testpieces fixed mechanism is fixed, described rotation bending moment loading mechanism is connected with the end of described main shaft testpieces, described motor transmits power by described gear train to described rotation bending moment loading mechanism, described rotation bending moment loading mechanism forms the rotation moment of flexure of the end to described main shaft testpieces at the trial by the mode of eccentric rotary.
2. main shaft fatigue experimental device according to claim 1, it is characterized in that, described rotation bending moment loading mechanism comprises: load axle and eccentric rotor structure, described loading axle is arranged on the top of described main shaft testpieces, and carry out bolt with the end of described main shaft testpieces to be connected, described eccentric rotor structure is arranged on described loading axle by bearing, described eccentric rotor structure is all connected with described gear train with described motor, described motor transmits power by described gear train to described eccentric rotor structure at the trial, described eccentric rotor structure is rotated relative to described loading axle.
3. main shaft fatigue experimental device according to claim 2, it is characterized in that, described eccentric rotor structure comprises: loading disc and at least two balancing weights, and described at least two balancing weights are arranged on described loading disc, form eccentric structure, and avoid the effect introducing additional lateral power.
4. main shaft fatigue experimental device according to claim 3, it is characterized in that, described eccentric rotor structure comprises the equal balancing weight of two quality, symmetrical on described loading disc respectively and out-of-alignment is installed, described loading disc is arranged on described loading axle by two bearings, and the setting height(from bottom) of the balancing weight that described two quality are equal is corresponding with the setting height(from bottom) of described two bearings respectively.
5. main shaft fatigue experimental device according to claim 4, is characterized in that, described eccentric rotor structure also comprises locating ring, and described locating ring is set on described loading axle, and between the inner ring being arranged on two bearings on described loading axle.
6. the main shaft fatigue experimental device according to claim 3 or 4 or 5, it is characterized in that, also comprise the hydraulic actuator be arranged on above described loading axle, one end of described hydraulic actuator is connected with described base block, the other end connects described loading axle, is described rotation bending moment loading mechanism offsetting influence of gravity at the trial.
7. main shaft fatigue experimental device according to claim 6, it is characterized in that, described gear train comprises: driving gear, follower gear and toothed timing belt, the rotating shaft of described driving gear is connected with the output shaft of described motor, described follower gear is located at the top of described loading disc, and be connected with described loading disc by bolt, described driving gear and described follower gear carry out transmission by described toothed timing belt, under the drive of described driving gear, described follower gear drives described loading disc and balancing weight to rotate around described loading axle.
8. main shaft fatigue experimental device according to claim 1, it is characterized in that, described vertical testpieces fixed mechanism comprises: base, the first mounting assembly and the second mounting assembly, described base is fixed in described base block, the below of described main shaft testpieces is fixed, described base is provided with sun cover tooth, overlaps tooth and matches, in order to limit the rotation of described main shaft testpieces with the moon of described main shaft testpieces; Described first mounting assembly is fixed in described base block, described second mounting assembly is fixed on described first mounting assembly, and described first mounting assembly and the second mounting assembly support described main shaft testpieces respectively by two boundary condition Support Positions of bearing on described main shaft testpieces vertical direction.
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Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105806617A (en) * | 2016-04-26 | 2016-07-27 | 吉林大学 | Fatigue test table for wheel axles of high speed train |
| CN108983091A (en) * | 2018-05-25 | 2018-12-11 | 东北大学 | A kind of servo motor reliability test loading device and application method |
| CN110095284A (en) * | 2019-04-17 | 2019-08-06 | 上海贝序汽车科技有限公司 | A kind of engine blower shaft member endurance test mechanism |
| CN111811800A (en) * | 2020-06-30 | 2020-10-23 | 东风马勒热***有限公司 | Durable testing arrangement of silicone oil fan flange axle bending moment |
| CN114061953A (en) * | 2021-11-02 | 2022-02-18 | 洛阳轴承研究所有限公司 | Bearing test device for butterfly separator |
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Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN105806617A (en) * | 2016-04-26 | 2016-07-27 | 吉林大学 | Fatigue test table for wheel axles of high speed train |
| CN108983091A (en) * | 2018-05-25 | 2018-12-11 | 东北大学 | A kind of servo motor reliability test loading device and application method |
| CN108983091B (en) * | 2018-05-25 | 2020-08-04 | 东北大学 | Servo motor reliability test loading device and use method |
| CN110095284A (en) * | 2019-04-17 | 2019-08-06 | 上海贝序汽车科技有限公司 | A kind of engine blower shaft member endurance test mechanism |
| CN111811800A (en) * | 2020-06-30 | 2020-10-23 | 东风马勒热***有限公司 | Durable testing arrangement of silicone oil fan flange axle bending moment |
| CN114061953A (en) * | 2021-11-02 | 2022-02-18 | 洛阳轴承研究所有限公司 | Bearing test device for butterfly separator |
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