WO2024088286A1 - 激振试验台及激振试验装置 - Google Patents

激振试验台及激振试验装置 Download PDF

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Publication number
WO2024088286A1
WO2024088286A1 PCT/CN2023/126363 CN2023126363W WO2024088286A1 WO 2024088286 A1 WO2024088286 A1 WO 2024088286A1 CN 2023126363 W CN2023126363 W CN 2023126363W WO 2024088286 A1 WO2024088286 A1 WO 2024088286A1
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WIPO (PCT)
Prior art keywords
test
coupling
gearbox
platform
track
Prior art date
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Ceased
Application number
PCT/CN2023/126363
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English (en)
French (fr)
Inventor
庞会文
李永生
丁鑫
张磊
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CRRC Changchun Railway Vehicles Co Ltd
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CRRC Changchun Railway Vehicles Co Ltd
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Publication date
Application filed by CRRC Changchun Railway Vehicles Co Ltd filed Critical CRRC Changchun Railway Vehicles Co Ltd
Publication of WO2024088286A1 publication Critical patent/WO2024088286A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M17/00—Testing of vehicles
    • G01M17/08—Railway vehicles
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M7/00—Vibration-testing of structures; Shock-testing of structures
    • G01M7/02—Vibration-testing by means of a shake table
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M7/00—Vibration-testing of structures; Shock-testing of structures
    • G01M7/02—Vibration-testing by means of a shake table
    • G01M7/06—Multidirectional test stands

Definitions

  • the present application relates to the field of bogie testing, and in particular to a vibration test bench and a vibration test device.
  • the bogie high-frequency excitation test bench is of great significance for the forward design of the bogie and its components in a high-frequency vibration environment and for solving the quality problems caused by the high-frequency vibration of the bogie.
  • the existing test bench mainly adopts the structure of motor + gear box + track wheel, and realizes the synchronization of the front and rear axles of the bogie through electrical synchronization.
  • the electrical synchronization accuracy of the above method is low; and the outer edge of the track wheel is circular, and the excitation frequency effect is not good, and high-frequency excitation under power test conditions cannot be achieved, which affects the test effect.
  • the purpose of the present application is to provide a vibration test bench and a vibration test device, so as to solve the problem that the synchronization of the front and rear axles of the bogie achieved by the existing vibration test bench has low precision and cannot achieve high-frequency vibration under power test conditions.
  • a vibration test bench comprising two groups of test mechanisms, any one group of the test mechanisms comprising a motor, a synchronous gearbox, a speed gearbox and a track wheel device, the track wheel device comprising two track wheels, the motor included in any one group of the test mechanisms being connected to a first end of the synchronous gearbox, the second end of the synchronous gearbox being connected to a first end of the speed gearbox, the second end of the speed gearbox being connected to the two track wheels to drive the two track wheels to rotate, the third end of the synchronous gearbox included in one of the two groups of the test mechanisms being connected to the synchronous gearbox included in the other group of the test mechanisms
  • the third end of the gear box is connected, the outer edge of the track wheel is a polygon, and the polygon distribution is a sine wave.
  • the frequency excitation test bench of the present application is configured to simulate the working conditions of large mass, high frequency and large amplitude excitation that are unique to high-speed trains, and relevant research tests under full-frequency domain excitation of bogies can be carried out on the test bench. That is, by controlling the test variables (excitation roller roughness and polygon order, etc.), the vehicle line operation conditions are reproduced to study the impact of wheel polygons and rail corrugation and other diseases on various vehicle components.
  • any group of the test mechanisms also includes a first coupling, a second coupling, a third coupling, a fourth coupling and a fifth coupling
  • the motor of any group of the test mechanisms is connected to the first end of the synchronous gearbox through the first coupling
  • the second end of the synchronous gearbox is connected to the first end of the speed change gearbox through the second coupling
  • the second end of the speed change gearbox is connected to one of the track wheels through the third coupling
  • one of the track wheels is connected to another track wheel through the fourth coupling
  • the third end of the synchronous gearbox is connected to the third end of the synchronous gearbox of another group through the second coupling
  • the axial directions of the second coupling, the third coupling and the fourth coupling all extend in the first direction
  • the axial directions of the first coupling and the fifth coupling all extend in the second direction
  • the first direction is perpendicular to the second direction.
  • the vibration test bench also includes two groups of tracks, and any group of the test mechanisms also includes a transmission platform and a first platform.
  • the motor, the synchronous gear box and the speed change gear box of any group of the test mechanisms are all arranged on the transmission platform, and the transmission platform is slidably connected to one group of the tracks and can slide along the second direction on the current track.
  • the two track wheels of any group of the test mechanisms are both arranged on the first platform, and the first platform is slidably connected to the other group of the tracks and can slide along the second direction on the current track.
  • the wheelbase of the test bench can be adjusted to match the wheelbase of the tested vehicle or bogie by telescoping the fifth coupling or replacing the intermediate section.
  • the position between the two rail wheels in the rail wheel device can be adjusted along the length direction of the first platform, that is, by replacing the length of the fourth coupling or the intermediate section to match the gauge of the tested vehicle or bogie.
  • the rail wheel device also includes a speed sensor, the speed The sensor is configured to detect a rotational speed of the rail wheel.
  • the rotation speed sensor can more accurately measure the rotation speed of the rail wheel side.
  • any group of the test mechanisms also includes a second platform and a center pin, the second platform is connected to the first platform, the two track wheels of any group of the test mechanisms are both arranged on the second platform, the center pin passes through the first platform and connects the second platform, and the second platform can rotate around the center pin relative to the first platform.
  • a vibration test device comprising the vibration test bench as described above.
  • the vibration test device includes a base, the base is provided with a groove, the vibration test bench is arranged in the groove, the vibration test device also includes a traction device, the traction device is arranged on the base, and the traction device is configured to connect to the tested bogie so that the tested bogie moves in the second direction.
  • the traction device includes a traction cylinder and a pull rod
  • the vibration test device also includes a crossbeam, a column, a compression cylinder and a dummy car body, the bottom of the dummy car body is configured to connect to the tested bogie, the four wheels of the tested bogie are in contact with the four track wheels, the column is connected to the track, the crossbeam is connected to the column, the two ends of the compression cylinder are respectively connected to the crossbeam and the top of the dummy car body, and the traction cylinder is connected to the end of the dummy car body through the pull rod.
  • the traction device includes a traction cylinder and a pull rod
  • the vibration test device also includes a rail
  • the rail is set on the base
  • the non-tested bogie of the tested vehicle is placed on the rail
  • the four wheels of the tested bogie are in contact with the four rail wheels
  • the traction cylinder is connected to the end of the tested vehicle through the pull rod.
  • the vibration test bench includes two groups of test mechanisms, wherein any group of the test mechanisms includes a motor, a synchronous gearbox, a speed change gearbox and a track wheel device, the track wheel device includes two track wheels, the motor of any group is connected to the first end of the synchronous gearbox, the second end of the synchronous gearbox is connected to the first end of the speed change gearbox, the second end of the speed change gearbox is connected to the two track wheels to drive the two track wheels to rotate, the third end of the synchronous gearbox is connected to the third end of the synchronous gearbox of the other group, the outer edge of the track wheel is a polygon, and the polygon distributes a sine wave.
  • any group of the test mechanisms includes a motor, a synchronous gearbox, a speed change gearbox and a track wheel device
  • the track wheel device includes two track wheels
  • the motor of any group is connected to the first end of the synchronous gearbox
  • the second end of the synchronous gearbox is connected to the first end of the speed change gearbox
  • the test bench of the present application is a structure of a motor plus a synchronous gearbox plus a speed change gearbox plus a track wheel device.
  • the form is used to achieve mechanical synchronization of the front and rear axles of the bogie, with high synchronization accuracy and reliability.
  • the rail wheels are processed into a polygonal form, which can simulate high-frequency excitation under load tests, and the test is closer to the actual situation.
  • FIG1 shows a top view of a vibration test bench according to an embodiment of the present application
  • FIG2 shows a top view of a traction device and a rail according to an embodiment of the present application
  • FIG3 is a top view showing a partial structure of a vibration test device according to an embodiment of the present application.
  • FIG4 is a schematic diagram showing a test process of a vehicle to be tested according to an embodiment of the present application.
  • FIG5 is a schematic diagram showing a bogie test process according to an embodiment of the present application.
  • FIG6 shows a side view of a vibration test bench according to an embodiment of the present application.
  • FIG7 is a schematic structural diagram of a rail wheel device according to an embodiment of the present application.
  • FIG. 8 is a schematic diagram showing an outer edge profile of a rail wheel according to an embodiment of the present application.
  • Icons 1-track; 2-transmission platform; 3-motor; 4-first coupling; 5-synchronous gearbox; 6-second coupling; 7-speed gearbox; 8-third coupling; 9-lubrication mechanism; 10-track wheel device; 11-fourth coupling; 12-first platform; 13-second platform; 14-attack angle adjustment mechanism; 15-traction device; 16-pull rod; 17-test vehicle; 18-guide rail; 19-rail; 20-T-shaped slot plate; 21-weight iron; 22-test bogie; 23-dummy vehicle body; 24- Compression cylinder; 25-gantry; 26-speed sensor bracket; 27-speed sensor; 28-speed gear flange; 29-center pin; 101-mounting seat; 102-bearing seat; 103-track wheel; 104-sensor; 151-mounting base; 152-traction base; 153-traction cylinder; 154-hydraulic station; 231-dummy body frame; 232-vertical beam; 233-connecting rod; 234-mounting frame; 251-mounting base; 252-colum
  • first”, “second”, and “third” may be used herein to describe various components, assemblies, regions, layers, or portions, these components, assemblies, regions, layers, or portions are not limited by these terms. Rather, these terms are only used to distinguish one component, component, region, layer, or portion from another component, component, region, layer, or portion. Therefore, without departing from the teachings of the examples described herein, the first component, component, region, layer, or portion referred to may also be referred to as the second component, component, region, layer, or portion.
  • spatial relationship terms such as “above”, “upper”, “below”, and “lower” may be used herein to describe the relationship of one element to another element as shown in the accompanying drawings. Such spatial relationship terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the accompanying drawings. For example, if the device in the accompanying drawings is turned over, an element described as being “above” or “upper” relative to another element would subsequently be located “below” or “lower” relative to the other element. Therefore, the term “above” includes both the orientations of “above” and “below”, depending on the spatial orientation of the device. The device may also be positioned in other ways (e.g., rotated 90 degrees or in other orientations) and the spatial relationship terms used herein will not be affected. The terms are explained accordingly.
  • the present application provides a vibration test bench and a vibration test device, thereby solving the problem that the synchronization of the front and rear axles of the bogie achieved by the existing vibration test bench has low precision and cannot achieve high-frequency vibration under power test conditions.
  • the bogie high-frequency excitation test bench is of great significance for the forward design of the bogie and its components in a high-frequency vibration environment and for solving the quality problems caused by the high-frequency vibration of the bogie.
  • the existing test bench mainly adopted the structure of motor + gear box + track wheel, and achieved the synchronization of the front and rear axles of the bogie through electrical synchronization.
  • the electrical synchronization accuracy of the above method was low; and the outer edge of the track wheel was circular, and the excitation frequency effect was not good, and high-frequency excitation under power test conditions could not be achieved, which affected the test effect.
  • a vibration test bench which includes two groups of test mechanisms, wherein any group of test mechanisms includes a motor 3, a synchronous gearbox 5, a speed gearbox 7 and a track wheel device 10, the track wheel device 10 includes two track wheels 103, the motor 3 of any group is connected to the first end of the synchronous gearbox 5, the second end of the synchronous gearbox 5 is connected to the first end of the speed gearbox 7, the second end of the speed gearbox 7 is connected to the two track wheels 103 to drive the two track wheels 103 to rotate, the third end of the synchronous gearbox 5 is connected to the third end of the synchronous gearbox 5 of the other group, the outer edge of the track wheel 103 is a polygon, and the polygon distributes a sinusoidal wave.
  • the test bench of the present application uses a structure of a motor 3 plus a synchronous gearbox 5 plus a speed change gearbox 7 plus a track wheel device 10 to achieve mechanical synchronization of the front and rear axles of the bogie, with high synchronization accuracy and high reliability.
  • the track wheel 103 is processed into a polygonal form, which can simulate high-frequency excitation under load test, and the test is closer to the actual situation.
  • the track wheel 103 processed into a polygonal form can also carry (simulate) a high-speed train with a large mass.
  • the outer edge of the track wheel 103 is a polygon, and the polygons are distributed in a sinusoidal wave.
  • the relationship between the rotation speed of the motor 3 and the excitation frequency is as follows:
  • f nN/60i (where f is the excitation frequency, Hz; n is the speed of the motor 3, r/min; i is the total transmission ratio of the synchronous gearbox 5 and the speed change gearbox 7; N is the number of sides of the polygon of the track wheel 103). Furthermore, according to the above formula, the following multiple situations can be simulated according to requirements.
  • the frequency excitation test bench of the present application is configured to simulate the working conditions of large mass, high frequency and large amplitude excitation that are unique to high-speed trains, and relevant research tests under full-frequency domain excitation of the bogie can be carried out on the test bench. That is, by controlling the test variables (excitation roller roughness and polygon order, etc.), the vehicle line operation conditions are reproduced to study the impact of wheel polygons and track corrugation and other diseases on various vehicle components.
  • the vibration and stress effects of the bogie system under conditions of different operating speeds, different loading conditions, line diseases, vehicle failures, and wheel wear (polygons and abrasions) are reproduced, and a mapping relationship is generated with the actual vehicle operation status to achieve rapid diagnosis of vehicle and track faults;
  • any group of test mechanisms also includes a first coupling 4, a second coupling 6, a third coupling 8, a fourth coupling 11 and a fifth coupling.
  • the motor 3 of any group is connected to the first end of the synchronous gearbox 5 through the first coupling 4, the second end of the synchronous gearbox 5 is connected to the first end of the speed change gearbox 7 through the second coupling 6, the second end of the speed change gearbox 7 is connected to one of the track wheels 103 through the third coupling 8, one of the track wheels 103 is connected to another of the track wheels 103 through the fourth coupling 11, and the third end of the synchronous gearbox 5 is connected to the third end of the synchronous gearbox 5 of another group through the second coupling 6, wherein the axial directions of the second coupling 6, the third coupling 8 and the fourth coupling 11 all extend along the first direction, the axial directions of the first coupling 4 and the fifth coupling all extend along the second direction, and the first direction is perpendicular to the second direction.
  • the vibration test bench also includes two groups of tracks 1 (any group of tracks 1 can be two tracks 1), and any group of test mechanisms also includes a transmission platform 2 and a first platform 12.
  • the motor 3, the synchronous gear box 5 and the speed change gear box 7 of any group of test mechanisms are all arranged on the transmission platform 2, and the transmission platform 2 is slidably connected to one group of tracks 1 and can slide on the current track 1 along the second direction.
  • the two track wheels 103 of any group of test mechanisms are both arranged on the first platform 12, and the first platform 12 is slidably connected to the other group of tracks 1 and can slide on the current track 1 along the second direction.
  • the wheelbase of the test bench can be adjusted to match the wheelbase L1 of the tested vehicle 17 or the tested bogie 22 (and the sliding transmission platform 2 or the first platform 12 ).
  • the position between the two rail wheels 103 in the rail wheel device 10 can also be adjusted along the length direction of the first platform 12, that is, by replacing the length or intermediate section of the fourth coupling 11 to adapt to the track gauge L2 of the tested vehicle 17 or the tested bogie 22.
  • test object test vehicle 17 or test bogie 22
  • the track wheel 103 contacts the tested wheel, and the track wheel 103 is driven to rotate through the motor 3, coupling, synchronous gear box 5 and speed gear box 7, so as to achieve vibration excitation of the test object.
  • the motor 3 is used as the load, and the motor 3 on the test object is used as the drive, so that the test object can be subjected to high-frequency vibration under load conditions.
  • the specific test process is as follows:
  • a vibration test device comprising the vibration test bench as described above.
  • the vibration test device includes a base, the base is provided with a groove, the vibration test table is arranged in the groove, the vibration test device also includes a traction device 15, the traction device 15 is arranged on the base (outside the groove of the base), and the traction device 15 is configured to connect to the tested bogie 22 so that the tested bogie 22 moves in the second direction.
  • the traction device 15 may include a mounting base 151, a traction base 152, a traction cylinder 153 and a hydraulic station 154.
  • the extension and retraction of the traction cylinder 153 is controlled by the hydraulic station 154, and the extension and retraction of the pull rod 16 are driven, so that the longitudinal movement adjustment and traction positioning (i.e., the second direction) of the test object (the tested vehicle 17 or the tested bogie 22) can be achieved, so that the four wheels of the tested bogie 22 are in contact with the four track wheels 103.
  • the gantry 25 comprises a mounting base 251, a column 252, a connecting beam 253 and a cross beam 254.
  • the column 252 of the gantry 25 is mounted on the track through the mounting base 251, and the cross beam 254 connects the column 252.
  • the dummy vehicle body 23 includes a dummy vehicle body frame 231, a vertical beam 232, a connecting rod 233 and a mounting frame 234.
  • the vehicle body of the tested bogie 22 is mainly simulated, and the dummy vehicle body 23 is used to longitudinally restrain and vertically load the tested bogie.
  • the ball joints at both ends of the compression cylinder 24 are respectively connected to the crossbeam 254 of the gantry 25 and the top of the dummy body frame 231 of the dummy body 23, the bottom of the dummy body frame 231 is connected to the bogie, and the pull rod 16 is connected to the end of the dummy body frame 231.
  • the extension and contraction of the traction cylinder 153 is controlled by the hydraulic station 154, and the extension and contraction of the pull rod 16 are driven to achieve the longitudinal movement adjustment and traction positioning (i.e., the second direction) of the tested bogie 22, and at the same time, the tested bogie 22 is simulated by the compression cylinder 24.
  • the mounting frames 234 at both ends are locked.
  • the rail 19 is pre-embedded and installed on the foundation (base) with the T-slot plate 20 installed.
  • the rail 19 is installed on the T-slot plate 20 through the pressure iron 21.
  • the rail 19 can be moved along the T-slot direction of the T-slot plate 20 to adjust the track gauge.
  • the T-slot guide rail 18 is pre-embedded and installed on the foundation.
  • the traction device 15 is installed on the T-slot guide rail 18.
  • the traction device 15 can be moved along the T-slot direction of the T-slot guide rail 18 to adapt to different test object lengths.
  • the traction cylinder 153 of the traction device 15 is connected to the end of the tested vehicle 17 through the pull rod 16.
  • the other end of the vehicle or the other end of the dummy vehicle body 23 may also be provided with a traction device 15 of the same structure.
  • both ends of the axis of any one of the track wheels 103 of the track wheel device 10 can be limited by two bearing seats 102, and the bottom of the two bearing seats 102 is installed with a mounting seat 101 and the top of the two bearing seats 102 is installed with a sensor 104.
  • the vibration test device may also be installed with an attack angle adjustment mechanism 14 , and the attack angle adjustment is completed by adjusting the attack angle adjustment mechanism 14 to realize the rotation of the track wheel device 10 .
  • any set of test mechanisms further includes a second platform 13 and a center pin 29, the second platform 13 is connected to the first platform 12, and the two track wheels 103 of any set of test mechanisms are both arranged on the second platform 13, that is, the two mounting seats 101 at the bottom of the two track wheels 103 are arranged on the second platform 13, the center pin 29 penetrates the first platform 12 and connects the second platform 13, and the second platform 13 can rotate around the center pin 29 relative to the first platform 12.
  • On-site personnel can adjust the attack angle according to needs so that the tested vehicle can pass through the four track wheels 103 more smoothly to prevent jamming due to the fixed attack angle.
  • a speed sensor bracket 26 is installed on one side of the second platform 13, and a speed sensor 27 is installed on the speed sensor bracket 26.
  • the speed measurement of the side of the rail wheel 103 is achieved through the speed measuring gear flange 28 at the shaft end of the bearing seat 102 and the speed sensor 27.
  • the speed sensor 27 can complete the measurement more accurately. Measurement of the rotational speed of the rail wheel 103 side.
  • the lubrication mechanism 9 lubricates and cools the rail wheel device 10 , the synchronous gear box 5 and the speed change gear box 7 , that is, it delivers lubricating oil to the rail wheel device 10 , the synchronous gear box 5 and the speed change gear box 7 .
  • the traction device 15 may include a mounting base 151, a traction base 152, a traction cylinder 153 and a hydraulic station 154.
  • the extension and retraction of the traction cylinder 153 is controlled by the hydraulic station 154, and the extension and retraction of the pull rod 16 are driven, so that the longitudinal movement adjustment and traction positioning (i.e., the second direction) of the test object (the tested vehicle 17 or the tested bogie 22) can be achieved, so that the four wheels of the tested bogie 22 are in contact with the four track wheels 103.
  • the rail 19 is pre-embedded and installed on the foundation (base) with the T-slot plate 20 installed, and the rail 19 is installed on the T-slot plate 20 through the pressure iron 21, and the rail 19 can be moved along the T-slot direction of the T-slot plate 20 to adjust the track gauge.
  • the T-slot guide rail 18 is pre-embedded and installed on the foundation, and the traction device 15 is installed on the T-slot guide rail 18, and the traction device 15 can be moved along the T-slot direction of the T-slot guide rail 18 to adapt to different lengths of the test products.
  • any group of test mechanisms includes a motor 3, a synchronous gearbox 5, a speed change gearbox 7 and a rail wheel device 10, and any group of test mechanisms also includes a first coupling 4, a second coupling 6, a third coupling 8, a lubrication mechanism 9, a fourth coupling 11 and a first platform 12.
  • the vibration test bench includes two groups of test mechanisms, wherein any group of the test mechanisms includes a motor, a synchronous gearbox, a speed change gearbox and a track wheel device, the track wheel device includes two track wheels, the motor of any group is connected to the first end of the synchronous gearbox, the second end of the synchronous gearbox is connected to the first end of the speed change gearbox, the second end of the speed change gearbox is connected to the two track wheels to drive the two track wheels to rotate, the third end of the synchronous gearbox is connected to the third end of the synchronous gearbox of the other group, the outer edge of the track wheel is a polygon, and the polygon distributes a sine wave.
  • any group of the test mechanisms includes a motor, a synchronous gearbox, a speed change gearbox and a track wheel device
  • the track wheel device includes two track wheels
  • the motor of any group is connected to the first end of the synchronous gearbox
  • the second end of the synchronous gearbox is connected to the first end of the speed change gearbox
  • the test bench of the present application uses a structure of a motor plus a synchronous gearbox plus a speed change gearbox plus a track wheel device to achieve mechanical synchronization of the front and rear axles of the bogie.
  • the synchronization has high accuracy and reliability, and the track wheel is processed into a polygonal form, which can simulate high-frequency excitation under load testing, and the test is closer to the actual situation.
  • the test bench of the present application uses a structure of a motor plus a synchronous gearbox plus a speed change gearbox plus a track wheel device to achieve mechanical synchronization of the front and rear axles of the bogie.
  • the synchronization has high accuracy and reliability, and the track wheel is processed into a polygonal form, which can simulate high-frequency excitation under load testing, and the test is closer to the actual situation.

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  • General Physics & Mathematics (AREA)
  • Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)

Abstract

一种激振试验台及激振试验装置，激振试验台包括两组试验机构，任一组试验机构包括电机(3)、同步齿轮箱(5)、变速齿轮箱(7)以及轨道轮装置(10)，轨道轮装置(10)包括两个轨道轮(103)，任一组的电机(3)连接同步齿轮箱(5)的第一端，同步齿轮箱(5)的第二端连接变速齿轮箱(7)的第一端，变速齿轮箱(7)的第二端连接两个轨道轮(103)，以驱动两个轨道轮(103)旋转，同步齿轮箱(5)的第三端与另一组的同步齿轮箱(5)的第三端连接，轨道轮(103)的外缘为多边形，多边形分布为正弦波。激振试验台及激振试验装置解决了现有的激振试验台中转向架前后两轴的同步精度低，且无法实现功率试验条件下的高频激振的问题。

Description

激振试验台及激振试验装置
相关申请的交叉引用
本申请要求于2022年10月25日提交中国专利局的申请号为202211313257.3、名称为“激振试验台及激振试验装置”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。
技术领域
本申请涉及转向架试验领域，尤其是涉及一种激振试验台及激振试验装置。
背景技术
随着动车组速度的不断提高和运行里程的增加，越来越多的质量结构问题暴露出来。究其原因离不开振动破坏的影响，而高频振动是导致结构破坏的主要因素。目前现有的高频激励输入条件下动力响应特性研究主要针对单个零部件，无法满足转向架在正向设计过程中对高频振动的试验验证需求。因此，转向架高频激振试验台对转向架及其部件在高频振动环境正向设计和解决转向架高频振动所引起的质量问题具有重要意义。
对此，现有的试验台主要采用电机+齿轮箱+轨道轮的结构形式，通过电气同步实现转向架前后两轴的同步，但是以上方式电气同步精度低；且轨道轮外缘为圆形，激振频率效果不好，无法实现功率试验条件下的高频激振，进而影响试验效果。
申请内容
本申请的目的是在于提供一种激振试验台及激振试验装置，从而解决了现有的激振试验台实现的转向架前后两轴的同步，精度低，且无法实现功率试验条件下的高频激振的问题。
根据本申请第一方面提供了一种激振试验台，所述激振试验台包括两组试验机构，任一组所述试验机构包括电机、同步齿轮箱、变速齿轮箱以及轨道轮装置，所述轨道轮装置包括两个轨道轮，任一组所述试验机构所包括的所述电机连接所述同步齿轮箱的第一端，所述同步齿轮箱的第二端连接所述变速齿轮箱的第一端，所述变速齿轮箱的第二端连接两个所述轨道轮，以驱动两个所述轨道轮旋转，两组所述试验机构中的一组所述试验机构所包括的所述同步齿轮箱的第三端与另一组所述试验机构所包括的所述同步 齿轮箱的第三端连接，所述轨道轮的外缘为多边形，所述多边形分布为正弦波。
在上述任意技术方案中，进一步地，激振频率：f＝nN/60i，其中，n为所述电机的转速，N为所述轨道轮的多边形的数量，i为所述同步齿轮箱和所述变速齿轮箱的总传动比。
进而，可以根据上述公式，根据需求模拟以下多种情况。例如，本申请的频激振试验台配置成模拟高速列车特有的大质量、高频率以及大幅值激励的工况，可在试验台上开展转向架全频域激励下的相关研究试验。即通过控制试验变量(激励滚轮粗糙度和多边形阶数等)，再现车辆线路运行情况，用于研究车轮多边形以及轨道波磨等病害对车辆各部件的影响。
在上述任意技术方案中，进一步地，任一组所述试验机构还包括第一联轴器、第二联轴器、第三联轴器、第四联轴器以及第五联轴器，任一组所述试验机构的所述电机通过所述第一联轴器连接所述同步齿轮箱的第一端，所述同步齿轮箱的第二端通过所述第二联轴器连接所述变速齿轮箱的第一端，所述变速齿轮箱的第二端通过所述第三联轴器连接其中一个所述轨道轮，其中一个所述轨道轮通过所述第四联轴器连接另外一个所述轨道轮，所述同步齿轮箱的第三端与另一组的所述同步齿轮箱的第三端通过所述第二联轴器连接，所述第二联轴器、所述第三联轴器以及所述第四联轴器三者的轴向均沿第一方向延伸，所述第一联轴器和所述第五联轴器的轴向均沿第二方向延伸，所述第一方向与所述第二方向垂直。
在上述任意技术方案中，进一步地，所述激振试验台还包括两组轨道，任一组所述试验机构还包括传动平台以及第一平台，任一组所述试验机构的所述电机、所述同步齿轮箱以及所述变速齿轮箱均设置于所述传动平台，所述传动平台与其中一组所述轨道滑动连接，且能够在当前轨道上沿第二方向滑动，任一组所述试验机构的两个轨道轮均设置于所述第一平台，所述第一平台与另一组所述轨道滑动连接，且能够在当前轨道上沿第二方向滑动。
利用以上结构，通过第五联轴器的伸缩或更换中间节，可实现试验台轴距调整以适配被测试车辆或被测试转向架的轴距。此外，还可以沿第一平台的长度方向调节轨道轮装置中的两个轨道轮之间的位置，即通过更换第四联轴器的长度或中间节以适配被测试车辆或被测试转向架的轨距。
在上述任意技术方案中，进一步地，所述轨道轮装置还包括转速传感器，所述转速 传感器配置成检测所述轨道轮的转速。
利用以上结构，转速传感器可以更加准确的完成对轨道轮侧转速的测量。
在上述任意技术方案中，进一步地，任一组所述试验机构还包括第二平台和中心销，所述第二平台连接于所述第一平台，任一组所述试验机构的两个轨道轮均设置于所述第二平台，所述中心销贯穿所述第一平台且连接所述第二平台，所述第二平台能够相对于所述第一平台绕所述中心销旋转。
利用以上结构，现场人员可以根据需求调整冲角以使得被测试的车辆可以更流畅的通过四个轨道轮，防止因固定的冲角而出现卡顿现象。
根据本申请第二方面提供了一种激振试验装置，包括如上所述的激振试验台。
在上述任意技术方案中，进一步地，所述激振试验装置包括基座，所述基座设置有凹槽，所述激振试验台设置于所述凹槽内，所述激振试验装置还包括牵引装置，所述牵引装置设置于所述基座上，所述牵引装置配置成连接被测试转向架，以使所述被测试转向架在所述第二方向上移动。
在上述任意技术方案中，进一步地，所述牵引装置包括牵引油缸和拉杆，所述激振试验装置还包括横梁、立柱、压缩油缸以及假车体，所述假车体的底部配置成连接所述被测试转向架，所述被测试转向架的四个车轮与四个所述轨道轮接触，所述立柱连接所述轨道，所述横梁连接所述立柱，所述压缩油缸的两端的分别连接所述横梁和所述假车体的顶部，所述牵引油缸通过所述拉杆连接所述假车体的端部。
在上述任意技术方案中，进一步地，所述牵引装置包括牵引油缸和拉杆，所述激振试验装置还包括钢轨，所述钢轨设置于所述基座上，所述被测试车辆的非被测试转向架落位至钢轨上，所述被测试转向架的四个车轮与四个所述轨道轮接触，所述牵引油缸通过所述拉杆连接所述被测试车辆的端部。
根据本申请的激振试验台及激振试验装置，激振试验台包括两组试验机构，其中，任一组试验机构包括电机、同步齿轮箱、变速齿轮箱以及轨道轮装置，轨道轮装置包括两个轨道轮，任一组的电机连接所述同步齿轮箱的第一端，同步齿轮箱的第二端连接变速齿轮箱的第一端，变速齿轮箱的第二端连接两个轨道轮，以驱动两个轨道轮旋转，同步齿轮箱的第三端与另一组的同步齿轮箱的第三端连接，轨道轮的外缘为多边形，多边形分布正弦波。
本申请的试验台通过电机加上同步齿轮箱加上变速齿轮箱加上轨道轮装置的结构 形式，以实现转向架前后两轴的机械同步，同步精度高和可靠性高，且轨道轮加工成多边形的形式，可模拟负载试验下高频激振，试验更加接近实际情况。
为使本申请的上述目的、特征和优点能更明显易懂，下文特举较佳实施例，并配合所附附图，作详细说明如下。
附图说明
为了更清楚地说明本申请实施例的技术方案，下面将对实施例中所需要使用的附图作简单地介绍，应当理解，以下附图仅示出了本申请的某些实施例，因此不应被看作是对范围的限定，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图获得其他相关的附图。
图1示出根据本申请的实施例的激振试验台的俯视图；
图2示出根据本申请的实施例的牵引装置和钢轨的俯视图；
图3示出根据本申请的实施例的激振试验装置的部分结构的俯视图；
图4示出根据本申请的实施例的待测试车辆试验过程中的示意图；
图5示出根据本申请的实施例的转向架试验过程中的示意图；
图6示出根据本申请的实施例的激振试验台的侧视图；
图7示出根据本申请的实施例的轨道轮装置的结构示意图；
图8示出根据本申请的实施例的轨道轮的外缘轮廓的示意图。
图标：1-轨道；2-传动平台；3-电机；4-第一联轴器；5-同步齿轮箱；6-第二联轴器；7-变速齿轮箱；8-第三联轴器；9-润滑机构；10-轨道轮装置；11-第四联轴器；12-第一平台；13-第二平台；14-冲角调整机构；15-牵引装置；16-拉杆；17-被测试车辆；18-导轨；19-钢轨；20-T形槽板；21-压铁；22-被测试转向架；23-假车体；24-压缩油缸；25-龙门架；26-转速传感器支架；27-转速传感器；28-测速齿盘法兰；29-中心销；101-安装座；102-轴承座；103-轨道轮；104-传感器；151-安装底板；152-牵引基座；153-牵引油缸；154-液压站；231-假车体框架；232-竖梁；233-连接杆；234-安装架；251-安装基座；252-立柱；253-连接梁；254-横梁。
具体实施方式
提供以下具体实施方式以帮助读者获得对这里所描述的方法、设备和/或系统的全面理解。然而，在理解本申请的公开内容之后，这里所描述的方法、设备和/或系统的 各种改变、修改及等同物将是显而易见的。例如，这里所描述的操作的顺序仅仅是示例，其并不限于这里所阐述的顺序，而是除了必须以特定顺序发生的操作之外，可做出在理解本申请的公开内容之后将是显而易见的改变。此外，为了提高清楚性和简洁性，可省略本领域中已知的特征的描述。
这里所描述的特征可以以不同的形式实施，并且不应被解释为局限于这里所描述的示例。更确切地说，已经提供了这里所描述的示例仅用于示出在理解本申请的公开内容之后将是显而易见的实现这里描述的方法、设备和/或系统的诸多可行方式中的一些方式。
在整个说明书中，当元件(诸如，层、区域或基板)被描述为“在”另一元件“上”、“连接到”另一元件、“结合到”另一元件、“在”另一元件“之上”或“覆盖”另一元件时，其可直接“在”另一元件“上”、“连接到”另一元件、“结合到”另一元件、“在”另一元件“之上”或“覆盖”另一元件，或者可存在介于它们之间的一个或更多个其他元件。相比之下，当元件被描述为“直接在”另一元件“上”、“直接连接到”另一元件、“直接结合到”另一元件、“直接在”另一元件“之上”或“直接覆盖”另一元件时，可不存在介于它们之间的其他元件。
如在此所使用的，术语“和/或”包括所列出的相关项中的任何一项和任何两项或更多项的任何组合。
尽管可在这里使用诸如“第一”、“第二”和“第三”的术语来描述各个构件、组件、区域、层或部分，但是这些构件、组件、区域、层或部分不受这些术语所限制。更确切地说，这些术语仅用于将一个构件、组件、区域、层或部分与另一构件、组件、区域、层或部分相区分。因此，在不脱离示例的教导的情况下，这里所描述的示例中所称的第一构件、组件、区域、层或部分也可被称为第二构件、组件、区域、层或部分。
为了易于描述，在这里可使用诸如“在……之上”、“上部”、“在……之下”和“下部”的空间关系术语，以描述如附图所示的一个元件与另一元件的关系。这样的空间关系术语意图除了包含在附图中所描绘的方位之外，还包含装置在使用或操作中的不同方位。例如，如果附图中的装置被翻转，则被描述为相对于另一元件位于“之上”或“上部”的元件随后将相对于另一元件位于“之下”或“下部”。因此，术语“在……之上”根据装置的空间方位而包括“在……之上”和“在……之下”两种方位。所述装置还可以以其他方式定位(例如，旋转90度或处于其他方位)，并将对在这里使用的空间关系 术语做出相应的解释。
在此使用的术语仅用于描述各种示例，并非用于限制本公开。除非上下文另外清楚地指明，否则单数的形式也意图包括复数的形式。术语“包括”、“包含”和“具有”列举存在的所陈述的特征、数量、操作、构件、元件和/或它们的组合，但不排除存在或添加一个或更多个其他特征、数量、操作、构件、元件和/或它们的组合。
由于制造技术和/或公差，可出现附图中所示的形状的变化。因此，这里所描述的示例不限于附图中所示的特定形状，而是包括在制造期间出现的形状上的改变。
这里所描述的示例的特征可按照在理解本申请的公开内容之后将是显而易见的各种方式进行组合。此外，尽管这里所描述的示例具有各种各样的构造，但是如在理解本申请的公开内容之后将显而易见的，其他构造是可能的。
本申请提供了一种激振试验台及激振试验装置，从而解决了现有的激振试验台实现的转向架前后两轴的同步，精度低，且无法实现功率试验条件下的高频激振的问题。
随着动车组速度的不断提高和运行里程的增加，越来越多的质量结构问题暴露出来。究其原因离不开振动破坏的影响，而高频振动是导致结构破坏的主要因素。目前现有的高频激励输入条件下动力响应特性研究主要针对单个零部件，无法满足转向架在正向设计过程中对高频振动的试验验证需求。因此，转向架高频激振试验台对转向架及其部件在高频振动环境正向设计和解决转向架高频振动所引起的质量问题具有重要意义。
在本申请提出之前，现有的试验台主要采用电机+齿轮箱+轨道轮的结构形式，通过电气同步实现转向架前后两轴的同步，但是以上方式电气同步精度低；且轨道轮外缘为圆形，激振频率效果不好，无法实现功率试验条件下的高频激振，进而影响试验效果。
鉴于此，根据本申请第一方面提供了一种激振试验台，激振试验台包括两组试验机构，其中，任一组试验机构包括电机3、同步齿轮箱5、变速齿轮箱7以及轨道轮装置10，轨道轮装置10包括两个轨道轮103，任一组的电机3连接所述同步齿轮箱5的第一端，同步齿轮箱5的第二端连接变速齿轮箱7的第一端，变速齿轮箱7的第二端连接两个轨道轮103，以驱动两个轨道轮103旋转，同步齿轮箱5的第三端与另一组的同步齿轮箱5的第三端连接，轨道轮103的外缘为多边形，多边形分布正弦波。
本申请的试验台通过电机3加上同步齿轮箱5加上变速齿轮箱7加上轨道轮装置10的结构形式，以实现转向架前后两轴的机械同步，同步精度高和可靠性高，且轨道轮103加工成多边形的形式，可模拟负载试验下高频激振，试验更加接近实际情况。此外，轨 道轮103加工成多边形的形式还可以承载(模拟)大质量的高速列车。在下文将详细描述激振试验台及激振试验装置的具体结构以及试验过程。
在本申请的实施例中，如图8所示，轨道轮103的外缘为多边形，多边形分布正弦波。当轨道轮103多边形的数量一定时，电机3转速和激振频率的关系如下：
f＝nN/60i(其中，f为激振频率，Hz；n为电机3的转速，r/min；i为同步齿轮箱5和变速齿轮箱7的总传动比；N为轨道轮103多边形的边的数量)。进而，可以根据上述公式，根据需求模拟以下多种情况。
例如，本申请的频激振试验台配置成模拟高速列车特有的大质量、高频率以及大幅值激励的工况，可在试验台上开展转向架全频域激励下的相关研究试验。即通过控制试验变量(激励滚轮粗糙度和多边形阶数等)，再现车辆线路运行情况，用于研究车轮多边形以及轨道波磨等病害对车辆各部件的影响。再现不同运行速度、不同装载工况、线路病害、车辆故障以及车轮磨耗(多边形以及擦伤)等条件下转向架系统振动和应力影响，和实车运行状态产生映射关系，实现车辆和轨道故障的快速诊断；
(1)测试转向架整体工作模态(测试频率范围0￣1200Hz)，以匹配运营条件下线路激扰，实现转向架高频振动条件下的正向设计；(2)高频冲击试验(P1力的频率在500～1200Hz，道岔、轨缝以及车轮擦伤等一系列瞬态冲击)下转向架制动、牵引以及齿轮箱吊杆等悬臂结构的颤振及应力响应；(3)研究在P2力作用下转向架系统的应力响应(P2力的频率在20Hz￣100Hz，轨道不平顺以及车轮周向不圆顺均可能引起轮轨系统的P2共振)；(4)测试高频激扰(0￣1200Hz)条件下悬挂系统自振特性以及振动传递关系；(5)实现高速列车旋转部件(轴承、车轴以及轮对等)在高速(0￣500km/h)、高频(0￣1200Hz)条件下应力和振动测试。
在本申请的实施例中，如图1所示，任一组试验机构还包括第一联轴器4、第二联轴器6、第三联轴器8、第四联轴器11以及第五联轴器，任一组的电机3通过第一联轴器4连接同步齿轮箱5的第一端，同步齿轮箱5的第二端通过第二联轴器6连接变速齿轮箱7的第一端，变速齿轮箱7的第二端通过第三联轴器8连接其中一个轨道轮103，其中一个轨道轮103通过第四联轴器11连接另外一个所述轨道轮103，同步齿轮箱5的第三端与另一组的同步齿轮箱5的第三端通过第二联轴器6连接，其中，第二联轴器6、第三联轴器8以及第四联轴器11三者的轴向均沿第一方向延伸，第一联轴器4和第五联轴器的轴向均沿第二方向延伸，第一方向与所述第二方向垂直。
进一步地，激振试验台还包括两组轨道1(任一组轨道1可以是两个轨道1)，任一组试验机构还包括传动平台2以及第一平台12，任一组试验机构的电机3、同步齿轮箱5以及变速齿轮箱7均设置于传动平台2，传动平台2与其中一组轨道1滑动连接，且能够在当前轨道1上沿第二方向滑动，任一组试验机构的两个轨道轮103均设置于第一平台12，第一平台12与另一组轨道1滑动连接，且能够在当前轨道1上沿第二方向滑动。
这里，如图1所示，通过第五联轴器的伸缩或更换中间节，可实现试验台轴距调整以适配被测试车辆17或被测试转向架22的轴距L1(同时滑动传动平台2或第一平台12)。
此外，如图6所示，还可以沿第一平台12的长度方向调节轨道轮装置10中的两个轨道轮103之间的位置，即通过更换第四联轴器11的长度或中间节以适配被测试车辆17或被测试转向架22的轨距L2。
在本申请的实施例中，被试品(被测试车辆17或被测试转向架22)进行试验时，轨道轮103与被测试车轮接触，通过电机3、联轴器、同步齿轮箱5以及变速齿轮箱7，驱动轨道轮103旋转，从而实现对被试品进行激振。根据试验需要通过电机3做负载，被试品上电机3做驱动，可对被试品进行负载条件下的高频激振。具体试验过程如下：
根据本申请第二方面提供了一种激振试验装置，包括如上所述的激振试验台。
激振试验装置包括基座，基座设置有凹槽，激振试验台设置于凹槽内，激振试验装置还包括牵引装置15，牵引装置15设置于基座上(基座的凹槽外)，牵引装置15配置成连接被测试转向架22，以使被测试转向架22在第二方向上移动。
在下文将详细描述对转向架的试验过程：
在本申请的实施例中，如图3和图5所示，牵引装置15可以包括安装底板151、牵引基座152、牵引油缸153以及液压站154，通过液压站154控制牵引油缸153的伸缩，驱动拉杆16的伸缩，可实现对被试品(被测试车辆17或被测试转向架22)的纵向移动调整和牵引定位(即第二方向)，以使得被测试转向架22的四个车轮与四个轨道轮103接触。
如图5所示，龙门架25包括安装基座251、立柱252、连接梁253以及横梁254。龙门架25的立柱252通过安装基座251安装于轨道上，横梁254连接立柱252。
假车体23包括假车体框架231、竖梁232、连接杆233以及安装架234。假车体23 主要模拟被测试转向架22的车体，用过假车体23对被试转向架进行纵向约束和垂向加载。
具体来说，压缩油缸24两端的球铰分别连接龙门架25的横梁254和假车体23的假车体框架231的顶部，假车体框架231的底部连接转向架，拉杆16连接假车体框架231的端部，通过液压站154控制牵引油缸153的伸缩，驱动拉杆16的伸缩，可实现对被测试转向架22)的纵向移动调整和牵引定位(即第二方向)，同时通过压缩油缸24对被测试转向架22模拟轴重加载。当定位完成后，锁止两端的安装架234。
在下文将详细描述对车辆的试验过程：
如图2和图4所示，钢轨19安装T形槽板20预埋安装于基础(基座)上，钢轨19通过压铁21安装于T形槽板20上，钢轨19沿T形槽板20的T形槽方向移动可以调整轨距。当被试品为被测试车辆17时，调整左侧牵引装置15的位置，同时将被试车辆的非被试转向架落位至钢轨19上。T形槽导轨18预埋安装于基础上，牵引装置15安装于T形槽导轨18上，牵引装置15沿T形槽导轨18的T形槽方向移动可适配不同被试品长度。牵引装置15的牵引油缸153通过拉杆16连接被测试车辆17的端部。
优选地，车辆的另一端或假车体23的另一端还可以设置有同样结构的牵引装置15。
在本申请的实施例中，如图7所示，轨道轮装置10的任意一个轨道轮103的轴的两端可以由两个轴承座102限位，两个轴承座102限位的底部安装有安装座101以及两个轴承座102的顶部安装有传感器104。
此外，如图6所示，激振试验装置还可以安装冲角调整机构14，通过调节冲角调整机构14实现轨道轮装置10的旋转，进而完成冲角调整。
具体来说，任一组试验机构还包括第二平台13和中心销29，第二平台13连接于第一平台12，任一组试验机构的两个轨道轮103均设置于第二平台13，即两个轨道轮103底部的两个安装座101设置于第二平台13，中心销29贯穿第一平台12且连接第二平台13，第二平台13能够相对于第一平台12绕中心销29旋转。现场人员可以根据需求调整冲角以使得被测试的车辆可以更流畅的通过四个轨道轮103，防止因固定的冲角而出现卡顿现象。
此外，在本申请的实施例中，如图6所示，第二平台13的一侧安装转速传感器支架26，转速传感器27安装于转速传感器支架26上，通过轴承座102轴端测速齿盘法兰28和转速传感器27实现轨道轮103侧转速的测量。转速传感器27可以更加准确的完成 对轨道轮103侧转速的测量。
此外，在本申请的实施例中，如图1和图3所示，润滑机构9润滑冷却轨道轮装置10、同步齿轮箱5以及变速齿轮箱7，即对轨道轮装置10、同步齿轮箱5以及变速齿轮箱7输送润滑油。
此外，如图3所示，如上所述，牵引装置15可以包括安装底板151、牵引基座152、牵引油缸153以及液压站154，通过液压站154控制牵引油缸153的伸缩，驱动拉杆16的伸缩，可实现对被试品(被测试车辆17或被测试转向架22)的纵向移动调整和牵引定位(即第二方向)，以使得被测试转向架22的四个车轮与四个轨道轮103接触。
进一步如上所述，如图3所示，钢轨19安装T形槽板20预埋安装于基础(基座)上，钢轨19通过压铁21安装于T形槽板20上，钢轨19沿T形槽板20的T形槽方向移动可以调整轨距。T形槽导轨18预埋安装于基础上，牵引装置15安装于T形槽导轨18上，牵引装置15沿T形槽导轨18的T形槽方向移动可适配不同被试品长度。
此外，参见图3，进一步如上所述，任一组试验机构包括电机3、同步齿轮箱5、变速齿轮箱7以及轨道轮装置10，任一组试验机构还包括第一联轴器4、第二联轴器6、第三联轴器8、润滑机构9、第四联轴器11以及第一平台12。
根据本申请的激振试验台及激振试验装置，激振试验台包括两组试验机构，其中，任一组试验机构包括电机、同步齿轮箱、变速齿轮箱以及轨道轮装置，轨道轮装置包括两个轨道轮，任一组的电机连接所述同步齿轮箱的第一端，同步齿轮箱的第二端连接变速齿轮箱的第一端，变速齿轮箱的第二端连接两个轨道轮，以驱动两个轨道轮旋转，同步齿轮箱的第三端与另一组的同步齿轮箱的第三端连接，轨道轮的外缘为多边形，多边形分布正弦波。
本申请的试验台通过电机加上同步齿轮箱加上变速齿轮箱加上轨道轮装置的结构形式，以实现转向架前后两轴的机械同步，同步精度高和可靠性高，且轨道轮加工成多边形的形式，可模拟负载试验下高频激振，试验更加接近实际情况。
工业实用性
本申请的试验台通过电机加上同步齿轮箱加上变速齿轮箱加上轨道轮装置的结构形式，以实现转向架前后两轴的机械同步，同步精度高和可靠性高，且轨道轮加工成多边形的形式，可模拟负载试验下高频激振，试验更加接近实际情况。
最后应说明的是：以上所述实施例，仅为本申请的具体实施方式，用以说明本申请 的技术方案，而非对其限制，本申请的保护范围并不局限于此，尽管参照前述实施例对本申请进行了详细的说明，本领域的普通技术人员应当理解：任何熟悉本技术领域的技术人员在本申请揭露的技术范围内，其依然可以对前述实施例所记载的技术方案进行修改或可轻易想到变化，或者对其中部分技术特征进行等同替换；而这些修改、变化或者替换，并不使相应技术方案的本质脱离本申请实施例技术方案的精神和范围，都应涵盖在本申请的保护范围之内。因此，本申请的保护范围应以权利要求的保护范围为准。

Claims (10)

  1. 一种激振试验台，其特征在于，所述激振试验台包括两组试验机构，任一组所述试验机构包括电机、同步齿轮箱、变速齿轮箱以及轨道轮装置，所述轨道轮装置包括两个轨道轮，
    任一组所述试验机构所包括的所述电机连接所述同步齿轮箱的第一端，所述同步齿轮箱的第二端连接所述变速齿轮箱的第一端，所述变速齿轮箱的第二端连接两个所述轨道轮，以驱动两个所述轨道轮旋转，
    两组所述试验机构中的一组所述试验机构所包括的所述同步齿轮箱的第三端与另一组所述试验机构所包括的所述同步齿轮箱的第三端连接，
    所述轨道轮的外缘为多边形，所述多边形分布为正弦波。
  2. 根据权利要求1所述的激振试验台，其特征在于，激振频率：f＝nN/60i，
    其中，n为所述电机的转速，
    N为所述轨道轮的多边形的数量，
    i为所述同步齿轮箱和所述变速齿轮箱的总传动比。
  3. 根据权利要求1所述的激振试验台，其特征在于，任一组所述试验机构还包括第一联轴器、第二联轴器、第三联轴器、第四联轴器以及第五联轴器，
    任一组所述试验机构的所述电机通过所述第一联轴器连接所述同步齿轮箱的第一端，所述同步齿轮箱的第二端通过所述第二联轴器连接所述变速齿轮箱的第一端，所述变速齿轮箱的第二端通过所述第三联轴器连接其中一个所述轨道轮，其中一个所述轨道轮通过所述第四联轴器连接另外一个所述轨道轮，所述同步齿轮箱的第三端与另一组的所述同步齿轮箱的第三端通过所述第二联轴器连接，
    所述第二联轴器、所述第三联轴器以及所述第四联轴器三者的轴向均沿第一方向延伸，
    所述第一联轴器和所述第五联轴器的轴向均沿第二方向延伸，所述第一方向与所述第二方向垂直。
  4. 根据权利要求3所述的激振试验台，其特征在于，所述激振试验台还包括两组轨道，任一组所述试验机构还包括传动平台以及第一平台，
    任一组所述试验机构的所述电机、所述同步齿轮箱以及所述变速齿轮箱均设置于所述传动平台，
    所述传动平台与其中一组所述轨道滑动连接，且能够在当前轨道上沿第二方向滑动，
    任一组所述试验机构的两个轨道轮均设置于所述第一平台，
    所述第一平台与另一组所述轨道滑动连接，且能够在当前轨道上沿第二方向滑动。
  5. 根据权利要求3所述的激振试验台，其特征在于，所述轨道轮装置还包括转速传感器，所述转速传感器配置成检测所述轨道轮的转速。
  6. 根据权利要求4所述的激振试验台，其特征在于，任一组所述试验机构还包括第二平台和中心销，所述第二平台连接于所述第一平台，
    任一组所述试验机构的两个轨道轮均设置于所述第二平台，
    所述中心销贯穿所述第一平台且连接所述第二平台，所述第二平台能够相对于所述第一平台绕所述中心销旋转。
  7. 一种激振试验装置，其特征在于，所述激振试验装置包括如权利要求3-6中任一项所述的激振试验台。
  8. 根据权利要求7所述的激振试验装置，其特征在于，所述激振试验装置包括基座，所述基座设置有凹槽，所述激振试验台设置于所述凹槽内，
    所述激振试验装置还包括牵引装置，所述牵引装置设置于所述基座上，所述牵引装置配置成连接被测试转向架，以使所述被测试转向架在所述第二方向上移动。
  9. 根据权利要求8所述的激振试验装置，其特征在于，所述牵引装置包括牵引油缸和拉杆，所述激振试验装置还包括横梁、立柱、压缩油缸以及假车体，
    所述假车体的底部配置成连接所述被测试转向架，所述被测试转向架的四个车轮与四个所述轨道轮接触，
    所述立柱连接所述轨道，所述横梁连接所述立柱，
    所述压缩油缸的两端的分别连接所述横梁和所述假车体的顶部，
    所述牵引油缸通过所述拉杆连接所述假车体的端部。
  10. 根据权利要求8所述的激振试验装置，其特征在于，所述牵引装置包括牵引油缸和拉杆，所述激振试验装置还包括钢轨，
    所述钢轨设置于所述基座上，被测试车辆的非被测试转向架落位至钢轨上，所述被测试转向架的四个车轮与四个所述轨道轮接触，
    所述牵引油缸通过所述拉杆连接所述被测试车辆的端部。
PCT/CN2023/126363 2022-10-25 2023-10-25 激振试验台及激振试验装置 Ceased WO2024088286A1 (zh)

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