CN117367780A - Test bench and test method for heavy vehicle damper - Google Patents
Test bench and test method for heavy vehicle damper Download PDFInfo
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- CN117367780A CN117367780A CN202311606399.3A CN202311606399A CN117367780A CN 117367780 A CN117367780 A CN 117367780A CN 202311606399 A CN202311606399 A CN 202311606399A CN 117367780 A CN117367780 A CN 117367780A
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- 238000012360 testing method Methods 0.000 title claims abstract description 62
- 238000010998 test method Methods 0.000 title claims abstract description 8
- 230000005284 excitation Effects 0.000 claims abstract description 54
- 230000007246 mechanism Effects 0.000 claims abstract description 36
- 238000004088 simulation Methods 0.000 claims abstract description 21
- 238000013016 damping Methods 0.000 claims description 20
- 230000000694 effects Effects 0.000 claims description 12
- 238000000034 method Methods 0.000 claims description 5
- 238000004891 communication Methods 0.000 claims description 2
- 238000009661 fatigue test Methods 0.000 claims description 2
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- 238000006073 displacement reaction Methods 0.000 description 6
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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
- G01M13/00—Testing of machine parts
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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
- G01M17/007—Wheeled or endless-tracked vehicles
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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
- G01M7/00—Vibration-testing of structures; Shock-testing of structures
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Abstract
The invention discloses a test board and a test method of a heavy vehicle damper, wherein the test board comprises a simulated vehicle body, a first connecting rod mechanism, a bearing wall, an excitation platform, a hydraulic vibration exciter, an air spring, a load wheel and a second connecting rod mechanism, wherein the hydraulic vibration exciter is connected with the excitation platform, the air spring is positioned between the simulated vehicle body and the excitation platform, the internal pressure is adjustable, the simulated vehicle body is connected with the bearing wall through the first connecting rod mechanism, the first connecting rod mechanism comprises two parallel pull rods with equal length, two ends of each pull rod are respectively hinged with the bearing wall and the simulated vehicle body, the plane where the two pull rods are positioned together is perpendicular to a horizontal plane, one end of the second connecting rod mechanism is hinged with the load wheel, the other end of each of the second connecting rod mechanism is connected with the tested damper, the damper is detachably connected with the simulated vehicle body, and the load wheel is supported on the excitation platform. The invention allows the simulation of the up-down and overturning movement of the vehicle body, better simulates the real situation, is more suitable for heavy load test, can change the natural frequency of the simulation vehicle body, and is suitable for the simulation of different vehicles.
Description
Technical Field
The invention belongs to the technical field of performance test of heavy vehicles, and particularly relates to a test bench and a test method of a heavy vehicle damper.
Background
For some heavy vehicles, the weight of the vehicle is up to tens of tons, the vehicle runs on some very severe roads, the displacement of the up-and-down vibration of the vehicle body is up to hundreds of millimeters, and the damper is a great test under the working condition. In order to improve the dynamic performance and damping characteristics of the heavy vehicle damper, a vibration test platform needs to be established for testing vibration. The existing test platform carries out guide constraint of the simulated vehicle body through a guide post or a sliding rail, and only allows the simulated vehicle body to move up and down. As shown in fig. 1, when the mass M of the simulated vehicle body is large, the exciting force Ft of the test system will increase, resulting in a very large unbalanced load moment of the whole system, and the alternating load Fr borne by the guide post or the slide rail will increase, so that the service life of the guide system will be greatly reduced under the condition of high-speed vibration by the exciting force Ft. And secondly, the friction resistance of the guide system is rapidly increased under the vibration test condition of large displacement and high speed by simulating the vehicle body, the measured data can be seriously disturbed, and the characteristics of the damping system cannot be truly reflected. In addition, under the real situation, the vehicle body moves up and down in the movement process, and overturning movement exists, and the general guiding system which depends on the bearing or the sliding rail limits the movement freedom degree of the simulated vehicle body, so that the difference between the test result and the actual situation is larger, and the worse the situation is along with the increase of the weight of the tested simulated vehicle body, a test platform which is closer to the real environment needs to be established for the movement of the more real simulated vehicle body.
Disclosure of Invention
Aiming at the problems existing in the prior art, the invention aims to provide a test bench and a test method for a heavy vehicle damper, which allow the simulation of the up-and-down motion of a vehicle body and the overturning motion in the plane of the parallelogram by utilizing the principle of the parallelogram, can better simulate the real situation, and the first link mechanism only bears the tensile force and the pressure under the action of external load and is not influenced by the unbalanced load moment, so that the first link mechanism cannot influence the measured data, the test result is more accurate and is more suitable for the heavy load test, the natural frequency of the test vehicle damper can be changed by adopting an air spring, and the damping vibration attenuation effect of the vehicle damper under different resonance frequencies can be conveniently researched.
In order to achieve the above purpose, the technical scheme adopted by the invention is as follows:
the utility model provides a testboard of heavy vehicle attenuator, including the simulation automobile body, first link mechanism, the bearing wall, the excitation platform, hydraulic vibration exciter, air spring, the bogie wheel, second link mechanism, hydraulic vibration exciter connects and drives the excitation platform vibration, the simulation automobile body is located the top of excitation platform, an air spring for adjusting the simulation automobile body natural frequency is located between simulation automobile body and the excitation platform, air spring internal pressure is adjustable, the bearing wall is all connected through first link mechanism to two adjacent sides of simulation automobile body, first link mechanism includes two parallel pull rods that length equals, the bearing wall and the simulation automobile body are articulated respectively to the both ends of pull rod, the plane perpendicular to horizontal plane that two pull rods together lie in, the bogie wheel is articulated to one end of second link mechanism, the test attenuator is connected to the other end, the detachable connection simulation automobile body of test attenuator, the bogie wheel supports on the excitation platform.
As a further improvement of the above technical scheme:
preferably, the two ends of the pull rod are respectively hinged with the bearing wall and the simulated vehicle body through ball joint bearings.
Preferably, the air spring is mounted on the air spring supporting device, the air spring is provided with at least two, the air spring supporting device comprises guide posts and a plurality of connecting plates, the connecting plates are arranged along the direction vertical to the excitation platform, the topmost connecting plates are fixedly connected with the simulation vehicle body, the bottommost connecting plates are mounted on the excitation platform, the air spring is arranged between two adjacent connecting plates, the guide posts serve as guiding functions, at least one group of guide posts are arranged, one group of guide posts are connected with two adjacent connecting plates, so that the two adjacent connecting plates are kept parallel when being close to or far away from each other, and at least two adjacent connecting plates which are not connected by the guide posts exist.
Preferably, the top-most connecting plate is a fixed upper plate, the bottom-most connecting plate is a fixed bottom plate, the connecting plate between the fixed upper plate and the fixed bottom plate is a middle connecting plate, the middle connecting plate is triangular, and when two or more middle connecting plates are arranged, the projections of all vertexes of two adjacent middle connecting plates on the excitation platform are not overlapped with each other.
Preferably, the test bench further comprises an air pressure adjusting device for adjusting the pressure in the air spring, and the air pressure adjusting device is communicated with the air spring.
Preferably, the test board further comprises a torsion spring for providing restoring force for the bogie wheel, and two ends of the torsion spring are respectively connected with the bogie wheel and the second link mechanism.
Preferably, the test bench further comprises a damper fixing plate, the damper is detachably mounted on the damper fixing plate, two ends of the second connecting rod mechanism are respectively hinged with the bogie wheel and the damper fixing plate, and the damper fixing plate is detachably mounted on the simulated vehicle body.
A test method of a heavy vehicle damper is based on the test bench and comprises the following steps:
step S1: installing a tested piece;
step S2: performing damper resonance searching;
step S3: damping self-adaptive function test of the damper;
step S4: testing and analyzing the damping self-adaptive function effect of the damper under different resonance frequencies;
step S5: and (5) testing fatigue of the damper.
Preferably, in step S3, the damping adaptive function of the damper is tested by changing the vibration input by the hydraulic vibration exciter, and in step S4, the natural frequency of the simulated vehicle body is changed by adjusting the air pressure of the air spring by the air pressure adjusting device, so that the damping adaptive function of the damper under different resonance frequencies is tested.
The beneficial effects of the invention are as follows:
(1) The simulated vehicle body is suspended by the first connecting rod mechanism and floats in the air, the simulated vehicle body is connected with the first connecting rod mechanism through the spherical joint bearing, the parallelogram connecting rod mechanism principle is utilized to allow the simulated vehicle body to move up and down, meanwhile, the spherical joint bearing is utilized to allow the simulated vehicle body to overturn, the real condition can be better tested, the used pull rod is a two-force rod, only the pull force and the pressure can be born under the action of external load, the influence of unbalanced load moment can not be received, therefore, the first connecting rod mechanism can not influence the measured data, the testing result is more accurate, the problems of interference, jamming, large friction and the like can not occur like the linear bearing, the simulated vehicle body is restrained in movement by the pull rod, the structure is simpler, the service life is longer, and the device is more suitable for the heavy-load test.
(2) The natural frequency of the vehicle damper can be changed by adopting the air spring, the vehicle damper is convenient to study under different resonance frequencies, the damping vibration reduction effect of the vehicle damper is convenient, efficient and flexible to adjust, abnormal sound cannot be generated, the air spring can also be used for lifting the simulated vehicle body, a test piece to be tested is convenient to be installed between the simulated vehicle body and the excitation platform, and the guide posts above and below are arranged in a staggered manner, so that a larger allowable space is provided for the expansion and the contraction of the air spring.
Drawings
Fig. 1 is a schematic structural view of a test stand in the prior art.
Fig. 2 is a schematic diagram of the structure of an embodiment of the present invention.
Fig. 3 is a schematic top view of an embodiment of the present invention.
Fig. 4 is a schematic view of the simulated vehicle body up-down vibration range according to an embodiment of the present invention.
FIG. 5 is a schematic view of an air spring according to an embodiment of the present invention mounted on an air spring support.
Fig. 6 is a schematic top view of fig. 5.
Detailed Description
The following describes specific embodiments of the present invention in detail with reference to the drawings. It should be understood that the detailed description and specific examples, while indicating and illustrating the invention, are not intended to limit the invention.
Spatially relative terms, such as "above … …," "above … …," "upper surface at … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations of "above … …" and "below … …". The device may also be positioned in other different ways (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
The test board for the damper of the heavy vehicle comprises a simulated vehicle body 1, a first connecting rod mechanism, a bearing wall 3, an excitation platform 5, a hydraulic vibration exciter 6, an air spring supporting device 7, an air spring 8, an air pressure adjusting device 9, a bogie wheel 10, a second connecting rod mechanism 11, a torsion spring, a damper fixing plate 15 and a control system, wherein the test board is shown in figures 1-6.
The hydraulic vibration exciter 6 mainly provides road vibration test excitation for the vehicle damper, the hydraulic vibration exciter 6 is rigidly connected with the vibration excitation platform 5 to drive the vibration excitation platform 5 to vibrate, and the hydraulic vibration exciter 6 transmits the excitation to the bogie wheels 10 of the vehicle damper through the vibration excitation platform 5.
The simulated vehicle body 1 is positioned above the excitation platform 5, and an air spring 8 and a damper 12 are arranged between the simulated vehicle body 1 and the excitation platform 5.
The air spring 8 is used to adjust the natural frequency of the simulated vehicle body 1. The air springs 8 are mounted on the air spring support 7. The air spring supporting device 7 comprises a guide post 74 and a plurality of connecting plates, the connecting plates are arranged along the direction vertical to the excitation platform 5, the topmost connecting plate is fixedly connected with the simulation vehicle body 1, the bottommost connecting plate is arranged on the excitation platform 5, an air spring 8 is arranged between two adjacent connecting plates, and two ends of the air spring 8 are respectively connected with two adjacent connecting plates. Obviously, the air springs 8 are provided with at least two. The guide posts 74 are used as guiding functions, the guide posts 74 are provided with at least one group, and one group of guide posts 74 are connected with two adjacent connecting plates, so that the two adjacent connecting plates are kept parallel when approaching or separating from each other, and the two adjacent connecting plates are kept parallel when approaching or separating from each other relatively, so that the air spring 8 between the two adjacent connecting plates is ensured to be compressed and stretched only and not to be bent. There are at least two adjacent said connection plates that are not engaged by the guide posts 74.
The top connection plate is a fixed upper plate 71, the fixed upper plate 71 is rigidly connected with the simulated vehicle body 1 through a fixed bracket, the bottom connection plate is a fixed bottom plate 72, the connection plate between the fixed upper plate 71 and the fixed bottom plate 72 is a middle connection plate 73, and obviously, at least one middle connection plate 73 is arranged. The intermediate connection plate 73 is triangular, and each set of guide posts 74 includes three guide posts 74, and the three guide posts 74 respectively pass through the vicinity of three vertexes of the intermediate connection plate 73.
In this embodiment, as shown in fig. 5 and 6, the air spring supporting device 7 has two intermediate connection plates 73 and three air springs 8. The fixed upper plate 71 and an adjacent middle connecting plate 73 (i.e. the middle connecting plate 73 positioned above) are connected through the same group of guide posts 74, specifically, three guide posts 74 are arranged in one group, the upper ends of the guide posts 74 are fixedly connected with the fixed upper plate 71, the lower ends of the guide posts 74 penetrate through the middle connecting plate 73, the three guide posts 74 are arranged at intervals in parallel, and the middle connecting plate 73 can move along the length direction of the guide posts 74. Similarly, the fixed bottom plate 72 and an adjacent middle connecting plate 73 (i.e. the middle connecting plate 73 positioned at the lower position) are connected through another group of guide posts 74, specifically, the lower ends of the guide posts 74 are fixedly connected with the fixed bottom plate 72, the upper ends of the guide posts 74 penetrate through the middle connecting plate 73, the three guide posts 74 are arranged at intervals in parallel, and the middle connecting plate 73 can move along the length direction of the guide posts 74. The two intermediate connection plates 73 are not joined by the guide posts 74.
Further, the projections of all the vertices of the two intermediate connection plates 73 on the excitation platform 5 are not overlapped with each other, so that the projections of all the guide posts 74 on the excitation platform 5 are not overlapped with each other, that is, all the guide posts 74 are staggered. Two adjacent intermediate webs 73 are shown in fig. 6 a and b, respectively.
Based on the above-described structure, in the present embodiment, the topmost air spring 8 is only elongated or shortened in the direction perpendicular to the fixed upper plate 71 by the guide post 74, and is not bent. Similarly, the bottommost air spring 8 only stretches or shortens in the direction perpendicular to the fixed bottom plate 72 under the action of the guide posts 74, and does not bend. The intermediate air spring 8 is guided by no guide post 74, and can be bent while being extended and shortened to allow the simulated vehicle body 1 to perform a tilting motion relative to the excitation platform 5. In addition, since the guide posts 74 connected to the fixed upper plate 71 and the guide posts 74 connected to the fixed lower plate 72 are arranged in a staggered manner, interference between the upper guide posts 74 and the lower guide posts 74 does not occur when the simulated vehicle body 1 vibrates in a large displacement, and thus larger displacement vibration is performed in an allowable space. Because the up-and-down motion stroke of the simulated vehicle body 1 is far greater than that of a single air spring 8, namely, the stroke of a single-bent air bag, a mode of connecting multiple-bent air bags in series is needed, and in order to ensure that the multiple-bent air bags cannot bend and deform in the large displacement working process, the multiple-bent air bags are ensured to be installed in a limited supporting space, and therefore, the guide posts 74 cannot interfere in the staggered arrangement mode of the guide posts 74.
The pressure inside the air spring 8 is adjustable, and the air pressure adjusting device 9 is used for adjusting the pressure inside the air spring 8. The air pressure adjusting device 9 is communicated with the air spring 8 and is used for inflating and deflating the air spring 8 so as to realize the adjustment of the pressure in the air spring 8. Preferably, the fixed bottom plate 72 is provided with a through hole communicated with the air spring 8 connected with the fixed bottom plate, and the air pressure adjusting device 9 is communicated with the bottommost air spring 8 through the through hole on the fixed bottom plate 72. Through holes are also formed in each intermediate connecting plate 73 to communicate two air springs 8 on both sides of the intermediate connecting plate 73, so that communication between the plurality of air springs 8 is achieved.
The bogie wheel 10 is connected with a tested piece, namely a damper 12, through a second link mechanism 11, two ends of the second link mechanism 11 are respectively hinged with the bogie wheel 10 and a damper fixing plate 15, and the damper fixing plate 15 is detachably connected to the simulated vehicle body 1. The bogie wheel 10 is supported on the excitation platform 5, can roll on the excitation platform 5, and the damper 12 is detachably connected to the simulated vehicle body 1 through a damper fixing plate 15. When the measured dampers 12 are different, different damper fixing plates 15 can be used to improve the application range of the test bench. The two ends of the torsion spring are respectively connected with the bogie wheel 10 and the second link mechanism 11, and the torsion spring provides restoring force for the bogie wheel 10.
The two adjacent side surfaces of the simulated vehicle body 1 are connected with the bearing wall 3 through the first connecting rod mechanism, the two adjacent side surfaces can be regarded as the right surface and the back surface of the simulated vehicle body 1, the corresponding bearing wall 3 is L-shaped, namely two wall bodies which are vertically connected with each other and are vertical to the horizontal plane, and the two wall bodies are respectively connected with the two adjacent side surfaces of the simulated vehicle body 1 through the first connecting rod mechanism. The first connecting rod mechanism comprises two parallel pull rods 21 with equal length, wherein two ends of each pull rod 21 are respectively hinged with the bearing wall 3 and the simulated vehicle body 1, preferably, two ends of each pull rod 21 are respectively hinged with the bearing wall 3 and the simulated vehicle body 1 through ball joint bearings 4, and the ball joint bearings 4 are hinged with the pull rods 21 through connecting shafts. The plane where the two pull rods 21 are located is perpendicular to the horizontal plane, so that the four points of the two hinge points of the pull rods 21 and the simulated vehicle body 1 and the two hinge points of the pull rods 21 and the bearing wall 3 are sequentially connected to form a parallelogram, and the two opposite sides of the parallelogram are always kept parallel according to the characteristics of the parallelogram. Since the line connecting the two hinge points of the tie rod 21 and the load-bearing wall 3 is perpendicular to the horizontal plane, the line connecting the two hinge points of the tie rod 21 and the simulated vehicle body 1 is also always perpendicular to the horizontal plane. The simulated body 1 is thus only allowed to translate in a plane parallel to the parallelogram and, because the ball-and-socket bearing 4 is a ball bearing, the simulated body 1 is allowed to roll over in said plane. The motion of the simulated vehicle body 1 is more fit with the actual working condition, so that the test result of the test bench is more accurate.
In this embodiment, the right side of the simulated vehicle body 1 is connected to the load bearing wall 3 through two sets of first link mechanisms, and the rear side of the simulated vehicle body 1 is connected to the load bearing wall 3 through one set of first link mechanisms.
The ratio of the displacement D of the up-and-down movement of the simulated body 1 in the plane parallel to the parallelogram to the length L of the tie rod 21 is less than 0.1, i.e., the rotation angle θ of the tie rod 21 is less than 6 °, at which time the up-and-down movement of the simulated body 1 in the plane perpendicular to the horizontal plane can be considered as a linear movement. The additional inertial load generated by the tie rod 21 for the test bench is negligible.
The control system comprises a data acquisition instrument, a controller and a display interface. The data acquisition instrument is connected with the excitation platform 5 and the simulated vehicle body 1 and is used for acquiring the vibration acceleration of the excitation platform 5 and the vibration acceleration of the simulated vehicle body 1. The controller calculates the transmission efficiency of the damper 12 according to the vibration acceleration of the excitation platform 5 and the simulated vehicle body 1 acquired by the data acquisition instrument, and judges the damping effect of the damper 12 under the vibration working condition provided by the current hydraulic vibration exciter 6 and the current resonance frequency of the simulated vehicle body 1 according to the transmission efficiency. The display interface is used for displaying data such as the vibration acceleration of the excitation platform 5, the vibration acceleration of the simulated vehicle body 1, the transmission efficiency of the damper 12, and the like.
Based on the structure, the working principle of the test bench is as follows: when the hydraulic vibration exciter 6 provides a vibration excitation for the excitation platform 5, the vibration corresponds to the vibration provided by an uneven road for the vehicle, the vibration is transmitted to the damper 12 through the road wheels 10, and the damper 12 consumes and absorbs at least part of the vibration, so that all the vibration is prevented from being transmitted to the simulated vehicle body 1. In this process, the road wheel 10 rolls due to the change in the distance between the simulated vehicle body 1 and the excitation platform 5, and the torsion spring 14 resets the rolling road wheel 10 to return to the initial position. According to the vibration amplitude frequency of the excitation platform 5 and the response vibration amplitude frequency of the simulated vehicle body 1, which are acquired by the data acquisition instrument, the vibration transmission efficiency between the excitation platform 5 and the simulated vehicle body 1 is obtained, so that the damping effect of the damper 12 is judged, and obviously, the larger the consumption of the damper 12 for transmitting the vibration of the simulated vehicle body 1 is, the better the damping effect is. The road of different road conditions is simulated by changing the vibration input by the hydraulic vibration exciter 6, and the natural frequency of the simulated vehicle body 1 is changed by changing the air pressure in the air spring 8, so that the simulation of vehicles with different loads and types is realized.
In this embodiment, the damper 12 is a magneto-rheological damper.
Based on the test bench, the test method for the damper of the heavy vehicle comprises the following steps:
step S1: and (5) installing a test piece.
The damper 12 of the tested piece is arranged on the damper fixing plate 15, and when the damper is arranged, the air pressure of the air spring 8 can be increased, the air spring 8 stretches, the installation space of the damper 12 is enlarged, and the test piece is convenient to install. After the installation is completed, the air pressure of the air spring 8 is restored to the original pressure.
Step S2: and (5) performing resonance searching on the damper.
After the test piece is installed, the hydraulic vibration exciter 6 is started, and the hydraulic vibration exciter 6 generates continuous sweep frequency vibration excitation. As is known from the resonance theory, when the air pressure in the air spring 8 is fixed, the natural frequency of the simulated vehicle body 1 is an inherent property thereof. When the frequency of vibration excitation by the hydraulic vibration exciter 6 is equal to the natural frequency of the simulated vehicle body 1, the simulated vehicle body 1 resonates with the excitation platform 5, and the vibration of the simulated vehicle body 1 is maximum. The data acquisition instrument and the controller can search the resonance frequency of the current simulated vehicle body 1, so that the vibration frequency excited by the hydraulic vibration exciter 6 can be set conveniently.
In this embodiment, the vibration of the excitation platform 5 is transmitted to the damper through the bogie wheel 1012, the vibration transmitted to the simulated vehicle body 1 is absorbed and consumed. The data acquisition instrument acquires the vibration acceleration of the excitation platform 5 and the simulated vehicle body 1, and the controller can calculate the transmission efficiency of the damper according to the acceleration amplitude of the simulated vehicle body 1 and the excitation platform 5, namely zeta=lg (a) 2 /a 1 ) Wherein ζ is the transfer efficiency, a 1 For excitation acceleration, a, on the excitation platform 5 2 In order to simulate the response acceleration on the vehicle body 1, the resonance frequency can be directly judged and obtained through a control software interface.
Step S3: damping adaptation function test of the damper 12.
The closer the excitation frequency is to the resonance frequency of the vehicle during running of the vehicle, the greater the vehicle body vibration response of the vehicle, and the further away from the resonance frequency, the smaller the response vibration of the vehicle body. The magnitude of the vehicle body response may be reduced by increasing the damping around the resonant frequency. By changing the vibration input from the hydraulic vibration exciter 6, the change in the response amplitude of the simulated vehicle body 1 can be tested, thereby testing the vibration reduction effect of the damper 12. Judging whether the damping effect is good or bad according to the amplitude of the excitation frequency and the amplitude of the frequency of the response vibration is a technology well known to those skilled in the art, and will not be described herein.
Step S4: testing and analyzing damper damping self-adaption function effect under different resonance frequencies
The natural frequency of the simulated vehicle body 1 is changed by adjusting the air pressure of the air spring 8 by the air pressure adjusting device 9. The above operation is repeated, and one adaptive characteristic of the damper 12 under different vibration conditions is tested, thereby judging the response effect of the damper 12 adaptive control system.
Step S5: fatigue test of damper 12.
The vehicle runs on the road surface and can meet different road surface conditions, so that the vehicle needs to be tested on different road surface conditions and road tests are carried out for a long time, and the reliability and stability of the vehicle damper are checked. The specific duration setting and the road condition setting can be specifically selected according to specific tests.
Finally, what is necessary here is: the above embodiments are only for further detailed description of the technical solutions of the present invention, and should not be construed as limiting the scope of the present invention, and some insubstantial modifications and adjustments made by those skilled in the art from the above description of the present invention are all within the scope of the present invention.
Claims (9)
1. The utility model provides a testboard of heavy vehicle damper, a serial communication port, including simulation automobile body (1), first link mechanism, load-carrying wall (3), excitation platform (5), hydraulic vibration exciter (6), air spring (8), bogie wheel (10), second link mechanism (11), hydraulic vibration exciter (6) are connected and drive excitation platform (5) vibration, simulation automobile body (1) is located the top of excitation platform (5), air spring (8) for adjusting simulation automobile body (1) natural frequency is located between simulation automobile body (1) and excitation platform (5), air spring (8) internal pressure is adjustable, adjacent two sides of simulation automobile body (1) are all through first link mechanism connection load-carrying wall (3), first link mechanism includes parallel pull rod (21) that two lengths are equal, the both ends of pull rod (21) articulate load-carrying wall (3) and simulation automobile body (1) respectively, the plane perpendicular to horizontal plane where two pull rod (21) are located jointly, one end articulated bogie wheel (10) of second link mechanism (11), the other end connection is surveyed automobile body (12), by the vibration damping platform (10) are dismantled in connection by the test automobile body (1).
2. The test stand according to claim 1, wherein: both ends of the pull rod (21) are respectively hinged with the bearing wall (3) and the simulated vehicle body (1) through ball joint bearings (4).
3. The test stand according to claim 1, wherein: air spring (8) are installed on air spring strutting arrangement (7), and air spring (8) are equipped with two at least, and air spring strutting arrangement (7) are including guide pillar (74) and polylith connecting plate, polylith connecting plate along the direction of perpendicular to excitation platform (5) arrange, and the top connecting plate fixed connection simulation automobile body (1), bottommost connecting plate are installed on excitation platform (5), are equipped with air spring (8) between two adjacent connecting plates, guide pillar (74) are the guide effect, and guide pillar (74) are equipped with at least a set of, and a set of guide pillar (74) link up two adjacent connecting plates, make two adjacent connecting plates keep parallel when being close to each other or keeping away from each other, have at least two adjacent connecting plates that are not linked up by guide pillar (74).
4. A test bench according to claim 3 wherein: the connecting plate at the top is a fixed upper plate (71), the connecting plate at the bottom is a fixed bottom plate (72), the connecting plate between the fixed upper plate (71) and the fixed bottom plate (72) is a middle connecting plate (73), the middle connecting plate (73) is triangular, and when two or more than two middle connecting plates (73) are arranged, the projections of all vertexes of two adjacent middle connecting plates (73) on the excitation platform (5) are not overlapped.
5. The test stand of claim 4, wherein: the test bench also comprises an air pressure adjusting device (9) for adjusting the pressure in the air spring (8), and the air pressure adjusting device (9) is communicated with the air spring (8).
6. The test stand according to claim 1, wherein: the test bench further comprises a torsion spring for providing restoring force for the bogie wheel (10), and two ends of the torsion spring are respectively connected with the bogie wheel (10) and the second connecting rod mechanism (11).
7. The test stand according to claim 1, wherein: the test bench further comprises a damper fixing plate (15), the damper (12) is detachably mounted on the damper fixing plate (15), two ends of the second connecting rod mechanism (11) are respectively hinged with the bogie wheel (10) and the damper fixing plate (15), and the damper fixing plate (15) is detachably mounted on the simulated vehicle body (1).
8. A method for testing a heavy vehicle damper based on the test bench according to any of claims 1-7, characterized in that: the method comprises the following steps:
step S1: installing a tested piece;
step S2: performing damper resonance searching;
step S3: damping self-adaptive function test of the damper (12);
step S4: testing and analyzing the damping self-adaptive function effect of the damper under different resonance frequencies;
step S5: fatigue testing of the damper (12).
9. The test method of claim 8, wherein: in the step S3, the damping self-adaption function of the damper (12) is tested by changing the vibration input by the hydraulic vibration exciter (6), and in the step S4, the natural frequency of the simulated vehicle body (1) is changed by adjusting the air pressure of the air spring (8) through the air pressure adjusting device (9), so that the damping self-adaption function of the damper (12) under different resonance frequencies is tested.
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