CN113188741A

CN113188741A - Excitation test equipment

Info

Publication number: CN113188741A
Application number: CN202110319677.1A
Authority: CN
Inventors: 叶阳升; 蔡德钩; 尧俊凯; 闫宏业; 朱忠林; 张千里; 陈锋; 姚建平; 魏少伟; 毕宗琦; 朱宏伟
Original assignee: China Academy of Railway Sciences Corp Ltd CARS; Railway Engineering Research Institute of CARS; Beijing Tieke Special Engineering Technology Co Ltd
Current assignee: China Academy of Railway Sciences Corp Ltd CARS; Railway Engineering Research Institute of CARS; Beijing Tieke Special Engineering Technology Co Ltd
Priority date: 2021-03-25
Filing date: 2021-03-25
Publication date: 2021-07-30
Anticipated expiration: 2041-03-25
Also published as: CN113188741B

Abstract

The invention discloses excitation test equipment. Wherein, this equipment includes: the vibration exciter is used for generating exciting force, and the lubricating oil pump and the oil discharge pump are in rigid connection. The invention solves the technical problems that the core rotating shaft is protected by an inorganic shell, has poor durability when exposed in a natural environment, has short continuous working time, is inconvenient to install and debug and move parts with scattered whole mass, and is insufficient only by mass counterforce of a machine.

Description

Excitation test equipment

Technical Field

The invention relates to the field of excitation tests, in particular to excitation test equipment.

Background

The high smoothness of the high-speed railway puts extremely high requirements on the dynamic performance, stability and durability of the roadbed. In the design service life of a high-speed railway, the roadbed can bear hundreds of millions of cyclic dynamic loads generated by train operation for a long time. The method is characterized by simulating, acquiring and analyzing the relevant technical parameters of roadbed dynamic stress response under the action of the high-frequency dynamic load long-term power, determining the power performance of the roadbed, and investigating whether the roadbed is deformed for a long time to meet the control requirement of the high-speed railway, and is a key premise for guiding the design and construction of the roadbed of the high-speed railway and ensuring the safe operation of the high-speed railway.

At present, the power loading test means of the high-speed railway roadbed mainly comprises an indoor model test and a field in-situ test, and the field excitation simulation comprises three types:

(1) and an indoor dynamic loading simulation test means based on a reduced scale or full scale roadbed model.

The indoor test can analyze the dynamic response of the roadbed by applying simulated cyclic dynamic load, plays an important role in explaining the dynamic characteristic rule of the roadbed and verifying the theoretical mechanism, but the indoor model test means is generally limited by the conditions of site size, model boundary, loading apparatus and the like, so that the indoor model test means is difficult to establish and strictly meet similar conditions or meet the site conditionsThe test model of the condition has errors such as a scale effect, a boundary effect and the like, and is difficult to meet the dynamic simulation loading requirements under the actual roadbed and foundation structure, the actual vehicle load magnitude, the frequency or the vibration frequency. The existing technical scheme of Zhejiang university, namely a simulation loading system (CN102109419A) of high-speed railway train running load and a high-speed railway ballastless track roadbed dynamics model test system (CN102108656A), is characterized in that a model test box of the model test box is a rectangular steel structure model groove consisting of a main steel structure beam column 5 and a main structure side steel plate 6, and the size of the model test box is 15m in length, 5m in width and 6m in height. The roadbed model is a trapezoid with the gradient of 1:1.5, wherein the thickness of the concrete base is 0.3m, the thickness of the surface layer of the foundation bed is 0.4m, the thickness of the bottom layer of the foundation bed is 2.3m, and the thickness of the foundation is 2.5 m; the simulation frequency range of the M-type wave of the load of the simulated train of the distributed loading system is 1.28Hz to 19.23Hz, and the phase range of the adjacent actuators is 5.04 multiplied by 10^-3～7.56×10^-2And the maximum value of the simulated track slab stress waveform curve is about 3.4 MPa. However, the indoor model test means is usually limited by conditions such as field size, model boundary, loading apparatus, etc., so that it is difficult to establish a test model that strictly meets similar conditions or matches the field situation, and there are errors such as scale effect and boundary effect, which are difficult to meet the requirements of dynamic simulation loading under the load magnitude, frequency or vibration frequency of actual roadbed and foundation structure, actual vehicle.

(2) On-site in-situ dynamic test means under on-site train operation state

The field in-situ test is a more direct test means for researching the dynamic characteristics of the roadbed, can provide first-hand data information for research, and is used for carrying out field roadbed dynamic tests on Daqin lines, Chengnian lines, Baoling lines and the like in China. However, the field in-situ test also has certain limitations, and although the acquisition of power response can be realized through the real train operation, the environment is complex and is not suitable for manual control. And because the number of train passes is limited every day, the test efficiency of the on-site in-situ dynamic test is low, and the accumulated deformation characteristic caused by long-term train load is difficult to test and simulate.

(3) On-site dynamic loading simulation test means based on large-scale excitation device

The field loading simulation test is to utilize a large vibration exciter to be installed on a field roadbed surface or a track structure to generate an exciting force for simulating train load and test the dynamic performance and the long-term deformation characteristic of an actual roadbed. The technical scheme is that in the prior art of southwest traffic university, namely a dynamic load field simulation test system (CN101465575) of a high-speed railway, the maximum value of a movable counterweight of a vibration frame is 10624kg, a vibration exciter mainly comprises a speed increaser, a baffle plate and an eccentric block, an input shaft is connected with an output shaft of a motor through a universal coupling, a transmission system is a hemispherical cage type universal coupling and can axially extend and retract by 100mm, and the height difference and the left-right deviation between the output shaft of the motor and the input shaft of the speed increaser are not more than 5mm when the system is used, so that the coupling is not damaged. The main technical parameters of system loading are as follows: the size of the loading surface of the vibration frame is 2.22m multiplied by 2.22 m; the frequency modulation range is 5-50 Hz, and the motor rotating speed is 300-3000 r/min; the motor power is 75kW, and the maximum exciting force is 340 kN. However, the technical scheme has the problems that the core rotating shaft is not protected by a shell, the durability is poor when the rotating shaft is exposed in a natural environment, the continuous working time is short, the components of each part are scattered, the whole mass is overlarge, the installation and debugging and the position movement are inconvenient, the counter force of a just excited vibration block is insufficient, and the like, and the improvement space is still left in the application aspect of on-site dynamic simulation loading of the high-speed railway roadbed.

In view of the above problems, no effective solution has been proposed.

Disclosure of Invention

The embodiment of the invention provides excitation test equipment, which at least solves the technical problems that the core rotating shaft is not protected by a shell, the durability is poor when the core rotating shaft is exposed in a natural environment, the continuous working time is short, the assembly of each part is scattered, the whole mass is overlarge, the installation and debugging and the position movement are inconvenient, and the shortage is provided only through the mass counter force of a machine.

According to an aspect of an embodiment of the present invention, there is provided a vibration excitation testing apparatus including: the vibration exciter is used for generating exciting force, and the lubricating oil pump and the oil discharge pump are in rigid connection.

Optionally, the excitation test apparatus further includes: the oil drain plug is connected with the oil pipe through a screw thread.

Optionally, an oil surface observation hole is embedded in the eccentric adjustment mechanism protective cover and used for observing the oil level of the excitation test equipment.

Optionally, the vibration exciter comprises: a vibration-resistant motor, a narrow high-strength belt transmission device, a box body, four eccentric shafts and a static eccentric block.

Optionally, the vibration exciter further comprises: two circumferential fixed gears, three circumferential sliding gears and three gear coupling type eccentric torque adjusting mechanisms.

Alternatively, the two circumferentially fixed gears and the three circumferentially sliding gears each have a function of synchronizing operation and transmitting power.

Optionally, the four eccentric shafts run by means of bearings and supports in bearing seats of the box body; the movable eccentric block in the device has four-stage adjustable range relative to the static eccentric block and is locked by a bolt pin.

Optionally, the oil drainage plug is fastened or loosened by torsion through a screw thread, and is made of a waterproof heat-insulating material.

According to another aspect of the embodiments of the present invention, there is also provided a computer program product including instructions, wherein the instructions executed by the computer program product are executed on a shock excitation testing apparatus.

According to another aspect of the embodiment of the invention, a non-volatile storage medium is further provided, which is characterized in that the instructions stored in the non-volatile storage medium are executed on the excitation test equipment.

In an embodiment of the present invention, a shock excitation test apparatus is adopted, which is characterized by including: the vibration exciter is used for generating exciting force, the lubricating oil pump and the oil discharge pump are in rigid connection, the problem that a core rotating shaft is not protected by a shell, the durability is poor when the core rotating shaft is exposed in a natural environment, the continuous working time is short, the assembly of each part is inconvenient to install and debug due to overlarge scattered overall mass and move in position, and the technical problem that the vibration exciter is insufficient due to the mass counter force of a machine is solved.

Drawings

The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the invention and together with the description serve to explain the invention without limiting the invention. In the drawings:

FIG. 1 is a schematic illustration of a shock excitation testing apparatus according to an embodiment of the present invention;

FIG. 2 is a schematic view of an exciter according to an embodiment of the present invention;

FIG. 3 is a schematic illustration of excitation force adjustment according to an embodiment of the invention;

FIG. 4 is a schematic illustration of excitation torque adjustment according to an embodiment of the present invention;

FIG. 5 is a schematic illustration of ranges of actual dynamic stress versus simulated dynamic stress according to an embodiment of the invention;

fig. 6 is a schematic diagram of a simulated dynamic stress and an actual dynamic stress of a roadbed according to the embodiment of the invention.

Detailed Description

In order to make the technical solutions of the present invention better understood, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

It should be noted that the terms "first," "second," and the like in the description and claims of the present invention and in the drawings described above are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used is interchangeable under appropriate circumstances such that the embodiments of the invention described herein are capable of operation in sequences other than those illustrated or described herein. Furthermore, the terms "comprises," "comprising," and "having," and any variations thereof, are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed, but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.

In accordance with an embodiment of the present invention, there is provided a shock excitation testing apparatus embodiment, it being noted that the steps illustrated in the flowchart of the drawings may be performed in a computer system such as a set of computer executable instructions and that, although a logical ordering is illustrated in the flowchart, in some cases, the steps illustrated or described may be performed in an order different than that described herein.

Example one

FIG. 1 is a schematic illustration of a shock excitation testing apparatus according to an embodiment of the present invention, as shown in FIG. 1, comprising: the vibration exciter is used for generating exciting force, and the lubricating oil pump and the oil discharge pump are in rigid connection.

Specifically, as shown in fig. 1, the high-speed railway roadbed shock excitation test equipment mainly comprises a vibration-resistant motor 1, a high-strength belt transmission device 2, a box body 3, a lubricating oil pump 4, an oil discharge pump 5, an eccentric moment adjusting mechanism 6, an oil discharge plug 7, an oil level observation hole 8 and an eccentric adjusting mechanism protection cover 9. The specific construction is shown in fig. 1. The high-strength belt transmission device is driven by the vibration-resistant motor, 8 pairs of eccentric blocks on the four eccentric shafts generate exciting force in the vertical direction by rotating, the concrete blocks are arranged at the bottoms of the eccentric shafts and connected with vibration exciters to provide anchoring force, and the load of the vibration exciters is transmitted to a roadbed through the base to simulate train passing load. The exciter is 1.5m in maximum height, 0.8m in maximum length and 0.6m (2) in maximum width, wherein the exciter is a core part of the exciter and mainly comprises a vibration-resistant motor 1, a narrow high-strength belt transmission device 2, a box body 3, four eccentric shafts I, II, III and IV, eight pairs of movable and static

eccentric blocks

4 and 10, two circumferential fixed gears 7, three circumferential sliding gears 5 and three gear coupling type eccentric torque adjusting mechanisms 6. The five gears have the functions of synchronous operation and power transmission. The four shafts are supported for operation by eight

bearings

8 and 9 in the housing bearing blocks. The movable eccentric block is manually adjusted to four stages relative to the static eccentric block and is locked by a bolt pin.

The three gear coupling type eccentric moment adjusting mechanisms 6 are mounted on the shafts I, III, and IV other than the bearing supports. The hole slip of the bearings and gears is ensured by means of a forced lubrication method of the lubrication oil pump 4'. The lubrication system also has the function of controlling temperature rise. If the ambient temperature is high and the temperature of the vibrator is high, water can be introduced into the water channel at the bottom of the box body to reduce the temperature.

In addition, as shown in fig. 2, after the power of the motor is transmitted to the second shaft through the belt transmission device, the power is divided into two power transmission lines:

1, a circumferential fixed gear 7 of a shaft II is transmitted to a circumferential sliding gear 5 on the shaft 1, and power is transmitted to the shaft I through an inner gear and an outer gear of a gear coupling and a spline on the shaft I;

the other power line is transmitted to a circumferential sliding gear 5 on a shaft III from a circumferential fixed gear 7 on the shaft II, power is transmitted to the shaft III through an inner gear and an outer gear of a gear coupling and a spline on the shaft III, the circumferential fixed gear 7 on the other end of the shaft III is meshed with the circumferential sliding gear 5 on the shaft IV, and power is transmitted to the shaft IV through the gear coupling on the shaft IV. The gear coupling on the II shaft has the function of vertical vibration eccentric moment, and the gear couplings on the I shaft and the IV shaft jointly perform the function of adjusting transverse vibration eccentric moment and are divided into 35 gears.

And 3, the vibration of the eccentric vibration machine for exciting force adjustment is formed by centrifugal action generated by the rotation of the eccentric mass, as shown in fig. 3. The two eccentric shafts run in opposite directions synchronously under the action of the synchronous gear. The horizontal component force of the centrifugal force F at each moment is offset, the vertical component forces are superposed, and the period alternates. The vibrator produces vertical vibration under the action of vertical alternating inertia component force. And adjusting the excitation frequency. The change of the vibration frequency of the vibrator is realized by adjusting the output frequency of the frequency converter, the vibration frequency is changed from 0Hz to 30Hz, namely the rotating speed of an eccentric shaft of the vibrator is adjusted from 0min' l to 1800 min. When the vibrator frequency is below 5Hz, it is difficult to maintain normal operation. As shown in fig. 4, in the excitation torque adjustment, the four-axis vibrator may regard the upper and lower pairs of axes as a combination of two-axis vibrators. When the phase difference between the upper and lower pairs of shafts is changed, the equivalent eccentric moment of the four-shaft vibrating machine is changed. When the phase difference between the upper pair of shafts and the lower pair of shafts is 0 degrees (a), the equivalent eccentric moment is equal to the sum of the eccentric moments of the upper pair of eccentric shafts and the lower pair of eccentric shafts; when the phase difference between the upper pair of shafts and the lower pair of shafts is 180 degrees (b), the algebraic sum of the eccentric moments of the upper pair of eccentric shafts and the lower pair of eccentric shafts is zero, and the equivalent eccentric moment is zero. When the phase difference between the two is between 0' -180 (c), a part of the eccentric moment of the upper and lower shafts is cancelled. Therefore, the equivalent eccentric moment varies from zero to a maximum value. The phase difference of upper and lower two pairs of axles is (d) adjusted through gear coupling festival formula eccentric moment guiding mechanism 6 on the 1 st axle, every mistake a tooth, just produces one and keeps off equivalent eccentric moment, and numerical value is not the problem that a plurality of eccentric blocks of linear variation have dispersed single eccentric block overweight, and unipolar stress is big, provides the guarantee to the long-time operation of vibration exciter, has reduced the vibration exciter size simultaneously.

4, the adjustable range of the exciting force explains the adjusting mode of the exciting force, the range is exemplified in order to ensure that each eccentric shaft of the vibrating machine is not overloaded, the stepping interval of eccentric moment is smaller at high speed, the movable eccentric block on each shaft can simultaneously adjust the same angle relative to the static eccentric block, the eccentric moment of each shaft can be changed, and the effects of synchronization, balance and load limitation are achieved. The vibration exciter can be adjusted to 4 stages, and each stage is 35 stages. As shown in tables 1 to 4

Static eccentric moment K and exciting force amplitude P₀Corresponding table with vibration frequency omega (Table 1)

Note: vibration frequency omega of eccentric shaft_{1 is small}At 18Hz, the small belt pulley is arranged on the motor shaft, and the big belt pulley is arranged on the II-th eccentric shaft.

TABLE 1

Static eccentric moment K and exciting force amplitude P₀Corresponding table with vibration frequency omega (Table 2)

Note: vibration frequency omega of eccentric shaft_{1 is small}At 18Hz, the big belt pulley is arranged on the motor shaft, and the small belt pulley is arranged on the II-th eccentric shaft.

TABLE 2

Static eccentric moment K and exciting force amplitude P₀Corresponding table with vibration frequency omega (Table 3)

TABLE 3

Static eccentric moment K and exciting force amplitude P₀Corresponding table with vibration frequency omega (Table 4)

Note: vibration frequency omega 1 of eccentric shaft_{Is less than}When 18Hz, the small belt pulley is arranged on the motor shaft, and the big belt pulley is arranged on the II eccentric shaft.

TABLE 4

In order to ensure the safe and reasonable use of the vibrator, the vibrator is programmed by a P key of the frequency converter, namely P013= ω 3max is used for limiting the maximum motor frequency (namely the maximum output frequency of the frequency converter), and P005=3 is used for setting the operating frequency (namely the vibration frequency of the vibrator), so that the aims of avoiding the over-frequency and overload operation of the vibrator are fulfilled. Because the static eccentric moment and the vibration frequency of the vibrator are different under different working conditions, a static eccentric moment K and an exciting force P are established in the specification, and the tables correspond to vibration frequency omega, and tables 1, 2, 3 and 4 respectively correspond to

levels

1, 2, 3 and 4. And each 35-gear step lists the vibration parameter value corresponding to each gear step, and defines the maximum eccentric moment and the maximum output frequency of each step. The operator should strictly set according to the parameters of the table, carefully observe and timely adjust the vibration frequency, thereby meeting the test requirements and ensuring safe operation. The symbol in the table is N, the gear with 0-35 eccentric moment, Q, the vibration mass of the test system comprises the sum (t) of the mass of a component and a vibrator, K, the static eccentric moment (kg. cm) of the vibrator, P0, the amplitude (t) of the exciting force, omega 1, the vibration frequency of the vibrator with a certain gear sequence, namely the rotation frequency (Hz) of an eccentric shaft, omega 2, the rotation frequency (Hz) of the vibration-resistant motor with a certain gear sequence, omega 3, the output frequency (Hz) of the frequency converter with a certain gear sequence, omega 1max, the highest rotation frequency of the eccentric shaft with a certain level, omega 2max, the highest rotation frequency of the vibration-resistant motor with a certain level, and omega 3max, the highest output frequency of the frequency converter with a certain level.

According to the test requirements, the data in tables 1-4 can be selected and used correspondingly. When the vibration frequency omega 1 of the eccentric shaft is less than 18Hz, the small belt pulley is arranged on the motor shaft, the large belt pulley is arranged on the second eccentric shaft, when the vibration frequency of the eccentric shaft is more than 18Hz, the large belt pulley is arranged on the motor shaft, and the small belt pulley is arranged on the second eccentric shaft.

For example, when the amplitude P0 of the exciting force is 25t, the static eccentric moment K is 2808.7kg. cm, 1 level should be selected, and the gear sequence is 27, it can be known from Table 1 that the vibration frequency ω 1 of the vibrator is 15.02Hz., so the small belt pulley should be installed on the motor shaft, and the large belt pulley should be installed on the 11 th eccentric shaft; in this case, since the vibration-proof motor rotation frequency ω 2 is 18.94Hz and the inverter output frequency ω 3 is 57.97Hz., the operator should set P005 ═ ω 3 ═ 57.97H (operation frequency) and P013 ═ ω 3max ═ 69.49 Hz.

For another example, when the amplitude P0 of the exciting force is selected to be 30t, the static eccentric moment K is 2103.9kg.cm, 2 levels should be selected, and the gear sequence is 30, as can be seen from Table 2, the vibration frequency omega 1 of the vibrator is 19.01Hz., therefore, the large belt pulley should be installed on the motor shaft, and the small belt pulley should be installed on the eccentric shaft II; in this case, since the rotation frequency ω 2 of the vibration-proof motor is 15.53Hz and the output frequency ω 3 of the inverter is 47.52Hz., the power consumption of the motor should be further related to the amplitude by the operator when P0055 ═ ω 3 ═ 47.05Hz (operating frequency) and P013 ═ ω 3max ═ 53.07H1z, and the local amplitude should be controlled to 1-2 mm. The minimum quality Q of the test system is therefore set in tables 1 to 4.

5, simulating the load of the high-speed railway train road base surface

1) The top surface of the ballastless track roadbed bears uniformly distributed load, and a concrete slab block is arranged on the roadbed which is not paved with tracks to perform shock excitation. The loading flat plates are two 1.4m multiplied by 0.8m, the dynamic response of a wheel pair to the roadbed is simulated, the exciting force, the frequency and the balance weight of an exciting machine are adjusted, and the average value of the surface dynamic stress generated by the coupling vibration of an exciting system and the roadbed can reach 50kPa, which is equivalent to the dynamic stress generated by the dynamic load of a high-speed train. The slope is large and the change is steep at the boundary of the influence range from the maximum value to the dynamic stress generated by the dynamic load of the actual train on the top surface of the roadbed. When the simulation range reaches 1/2 of the influence boundary, the main load is in the simulation range, as shown in fig. 5, the dynamic stress of the roadbed surface under the action of the simulated dynamic load is equal to the actual value after the double integration, and the simulated dynamic stress distribution is equal to the actual dynamic stress distribution. By simulating the dynamic stress of the top surface of the roadbed and transferring and diffusing downwards through the surface layer of the roadbed, the dynamic response in the roadbed can be consistent with the actual situation, and the simulation loading mode can represent the actual dynamic load, thereby being convenient for theoretical analysis.

2) As shown in fig. 6, the train load borne by the railroad bed is a unidirectional pulsed stress wave. The wheelbase on the same bogie is 2.5m, the distance between two bogies of the same car is typically 18m, and the distance between two bogies of adjacent cars is typically 8 m. When the vehicle speed is 300km/h, the dynamic load frequency is 33.3Hz, 10.4Hz and 4.6 Hz. According to the transfer characteristics of low-frequency waves and high-frequency waves, the low-frequency waves carry large energy, but the excitation test is carried out at too low frequency, the time for simulating long-term train load is long for millions of times, the train load characteristics, the test period and the instrument performance are comprehensively considered, and the excitation load frequency test range is 10-20 Hz.

Through the embodiment, the technical problems that the core rotating shaft is not protected by a shell, the durability is poor when the core rotating shaft is exposed in a natural environment, the continuous working time is short, the assembly of each part is scattered, the whole mass is overlarge, the installation and debugging and the position movement are inconvenient, and the shortage is provided only through the mass counter force of a machine are solved.

The above-mentioned serial numbers of the embodiments of the present invention are merely for description and do not represent the merits of the embodiments.

In the above embodiments of the present invention, the descriptions of the respective embodiments have respective emphasis, and for parts that are not described in detail in a certain embodiment, reference may be made to related descriptions of other embodiments.

In the embodiments provided in the present application, it should be understood that the disclosed technology can be implemented in other ways. The above-described embodiments of the apparatus are merely illustrative, and for example, the division of the units may be a logical division, and in actual implementation, there may be another division, for example, multiple units or components may be combined or integrated into another system, or some features may be omitted, or not executed. In addition, the shown or discussed mutual coupling or direct coupling or communication connection may be an indirect coupling or communication connection through some interfaces, units or modules, and may be in an electrical or other form.

The units described as separate parts may or may not be physically separate, and parts displayed as units may or may not be physical units, may be located in one place, or may be distributed on a plurality of units. Some or all of the units can be selected according to actual needs to achieve the purpose of the solution of the embodiment.

In addition, functional units in the embodiments of the present invention may be integrated into one processing unit, or each unit may exist alone physically, or two or more units are integrated into one unit. The integrated unit can be realized in a form of hardware, and can also be realized in a form of a software functional unit.

The integrated unit, if implemented in the form of a software functional unit and sold or used as a stand-alone product, may be stored in a computer readable storage medium. Based on such understanding, the technical solution of the present invention may be embodied in the form of a software product, which is stored in a storage medium and includes instructions for causing a computer device (which may be a personal computer, a server, or a network device) to execute all or part of the steps of the method according to the embodiments of the present invention. And the aforementioned storage medium includes: a U disk, a Read-only Memory (ROM), a Random Access Memory (RAM), a removable hard disk, a magnetic disk, or an optical disk.

The foregoing is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, various modifications and decorations can be made without departing from the principle of the present invention, and these modifications and decorations should also be regarded as the protection scope of the present invention.

Claims

1. A shock excitation test apparatus, comprising: the vibration exciter is used for generating exciting force, and the lubricating oil pump and the oil discharge pump are in rigid connection.

2. The apparatus of claim 1, wherein the excitation testing apparatus further comprises: the oil drain plug is connected with the oil pipe through a screw thread.

3. The apparatus according to claim 1, wherein an oil level observation hole is inserted in the eccentricity adjustment mechanism protection cover for observing an oil level of the excitation test apparatus.

4. The apparatus of claim 1, wherein the exciter comprises: a vibration-resistant motor, a narrow high-strength belt transmission device, a box body, four eccentric shafts and a static eccentric block.

5. The apparatus of claim 4, wherein the exciter further comprises: two circumferential fixed gears, three circumferential sliding gears and three gear coupling type eccentric torque adjusting mechanisms.

6. The apparatus according to claim 5, characterized in that said two circumferentially fixed gears and said three circumferentially sliding gears each have the function of running in synchronism and of transmitting power.

7. The apparatus of claim 4, wherein the four eccentric shafts run by means of bearings and bearings in bearing housings of the casing; the movable eccentric block in the device has four-stage adjustable range relative to the static eccentric block and is locked by a bolt pin.

8. The apparatus of claim 2, wherein the oil drain plug is screwed for torque tightening or loosening removal, and the oil drain plug is made of waterproof heat insulating material.

9. A computer program product comprising instructions, characterized in that the instructions executed by the computer program product are executed on the device according to claims 1-8.

10. A non-volatile storage medium storing instructions for execution on the apparatus of claims 1-8.