Simulation loading device for abrasion condition of swing mechanism of swing type bogie

Abstract

The invention relates to a simulation loading device for the abrasion condition of a swing mechanism of a swing type bogie, and relates to the technical field of bogies. Comprising a support, an actuator assembly and a simulation beam. The mounting end of the actuator assembly is mounted on the support, the output end of the actuator assembly is connected with the simulation beam, and the actuator assembly is matched with the support to apply loading force in multiple directions to the simulation beam; the simulation beam is installed on a simulation axle through the swing mechanism and used for simulating the abrasion condition of the swing mechanism. Loads in multiple directions are applied to the simulation beam through the actuator assembly, and the motion and stress characteristics of the swing mechanism in a real motion state are simulated, so that the reason of eccentric wear of the upper swing point of the vehicle swing mechanism can be conveniently researched.

Description

Technical Field

[0001] The present invention relates to the technical field of bogies, and particularly to a simulation loading device for the wear condition of a swing mechanism of a swing-type bogie. Background Art

[0002] The main principle of the swing mechanism is to change the axle box spring suspension structure of traditional railway vehicles into a cooperating guide frame rocker seat and a bearing saddle. The lower surface of the guide frame rocker seat and the upper surface of the bearing saddle cooperate with each other. The lower contact surface of the guide frame rocker seat is an outer arc surface, while the upper contact surface of the bearing saddle is an inner arc surface, forming the upper swing point of the swing mechanism. At the same time, a spring support plate is added on the basis of the original traditional freight car bogie. The spring support plate is also located at the lower part of the bogie side frame in the form of inner and outer arc cooperation, forming the lower swing point of the swing mechanism. When the vehicle is subjected to a lateral load, the inner and outer contact arcs of the upper and lower swing points rotate relative to each other, converting the lateral load into a rotational displacement, thereby reducing the lateral force of the vehicle and improving the lateral dynamic performance of the vehicle.

[0003] However, it is found in the application process of swing-type vehicles that the arc mating surfaces of the guide frame rocker seat and the bearing saddle at the upper swing point of the swing mechanism often undergo eccentric wear, resulting in an unsatisfactory swing effect. In order to study the cause of the eccentric wear at the upper swing point of the vehicle swing mechanism, a simulation loading device for the wear condition of the swing mechanism of a swing-type bogie is proposed. Summary of the Invention

[0004] The present invention provides a simulation loading device for the wear condition of a swing mechanism of a swing-type bogie, which is used to simulate the wear condition of the swing mechanism installed on the bogie side frame of a freight car, so as to find out the reason for the eccentric wear of the swing point of the swing mechanism.

[0005] The present invention provides a simulation loading device for the wear condition of a swing mechanism of a swing-type bogie, including a bracket, an actuator assembly and a simulation beam;

[0006] The installation end of the actuator assembly is installed on the bracket, the output end of the actuator assembly is connected to the simulation beam, and the actuator assembly and the bracket cooperate to apply loading forces in multiple directions to the simulation beam;

[0007] The simulation beam is installed on a simulation axle through the swing mechanism, and is used to simulate the wear condition of the swing mechanism.

[0008] In one embodiment, the swing mechanism includes a guide frame rocker seat, the lower end of the guide frame rocker seat cooperates with a bearing saddle, and the bottom of the bearing saddle is cooperatively installed with the simulation axle.

[0009] In one embodiment, the bracket includes a plurality of columns and a plurality of reaction seats. The tops of the plurality of columns are respectively connected to the ends of the cross beam. The reaction seats are respectively provided on both sides of the cross beam, and the cross beam is parallel to the simulated beam.

[0010] In one embodiment, the actuator assembly cooperates with the bracket to apply loading forces to the simulated beam in at least three different directions, namely the first direction, the second direction and the third direction. The actuator assembly includes a first hydraulic actuator, a second hydraulic actuator and a third hydraulic actuator;

[0011] Wherein: the first hydraulic actuator is installed on the cross beam, and the output end of the first hydraulic actuator is hinged to the top of the simulated beam. The first hydraulic actuator is used to apply loading in the first direction to the simulated beam;

[0012] The second hydraulic actuator is hinged to the reaction seat, and the output end of the second hydraulic actuator is hinged to the side of the simulated beam. The second hydraulic actuator is used to apply loading in the second direction to the simulated beam, so that the simulated beam moves horizontally in the second direction or rotates around a vertical axis perpendicular to the center of the simulated beam; and

[0013] The third hydraulic actuator is installed on the column, and the output end of the third hydraulic actuator is hinged to the end of the simulated beam. The third hydraulic actuator is used to apply loading in the third direction to the simulated beam, so that the simulated beam moves horizontally in the third direction.

[0014] In one embodiment, a rectangular guide frame is provided at the bottom of the simulated beam. The rectangular guide frame is connected to the top end of the guide frame rocking seat. Stop plates are provided at both the front and rear ends of the rectangular guide frame, and the stop plates are perpendicular to the movement direction of the third hydraulic actuator.

[0015] In one embodiment, the first hydraulic actuator and the third hydraulic actuator are respectively installed on the cross beam and the column through installation components.

[0016] In one embodiment, the installation components include a plurality of installation plates. The plurality of installation plates are installed on the cross beam or the column through threaded components. The first hydraulic actuator and the third hydraulic actuator are respectively hinged to the installation plates close to the simulated beam.

[0017] In one embodiment, an inertial navigation device is provided at the top of the simulated beam. The inertial navigation device is used to monitor the motion state of the simulated beam during the test.

[0018] In one embodiment, it further includes a base, and the column, the reaction seat and the simulated axle are all installed on the base.

[0019] In one embodiment, multiple groups of the first hydraulic actuators are provided, and the output ends are respectively hinged to both ends of the top of the simulated beam; multiple groups of the second hydraulic actuators are provided, and the output ends are respectively hinged to two side walls of the simulated beam close to the reaction seat, and the multiple groups of the second hydraulic actuators are located on different straight lines; multiple groups of the third hydraulic actuators are provided, and the output ends are respectively connected to both ends of the simulated beam close to the column.

[0020] Compared with the prior art, the advantages of the present invention are that the actuator assembly applies loads in multiple directions to the simulated beam to simulate the movement and force characteristics of the swing mechanism in the real movement state, so as to facilitate the study of the reasons for the eccentric wear at the upper swing point of the vehicle swing mechanism. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Hereinafter, the present invention will be described in more detail based on embodiments and with reference to the drawings.

[0022] Figure 1 is the overall structural schematic diagram of the simulation loading device of the present invention;

[0023] Figure 2 is Figure 1 the front view of

[0024] Figure 3 is the three-dimensional view of the simulated beam of the present invention;

[0025] Figure 4 is the structural schematic diagram of the swing mechanism of the present invention;

[0026] Figure 5 is the structural schematic diagram of the hydraulic actuator of the present invention;

[0027] Figure 6 is the force loading curve of two groups of the first hydraulic actuators of the present invention;

[0028] Figure 7 is the displacement loading curve of two groups of the second hydraulic actuators when the simulated beam moves horizontally in the second direction of the present invention;

[0029] Figure 8 is the displacement loading curve of two groups of the second hydraulic actuators when the simulated beam shakes its head of the present invention;

[0030] Figure 9 is the displacement loading curve of two groups of the third hydraulic actuators when the simulated beam moves in the third direction of the present invention;

[0031] Figure 10 is Figure 1Schematic diagram of part A;

[0032] Reference numerals:

[0033] 1. Bracket; 101. Column; 102. Cross beam; 103. Reaction seat; 2. Swing mechanism; 201. Guide frame rocking seat; 202. Bearing saddle; 3. Actuator assembly; 301. First hydraulic actuator; 302. Second hydraulic actuator; 303. Third hydraulic actuator; 4. Simulation beam; 401. Guide frame; 4011. Stop plate; 5. Simulation axle; 6. Base; 7. Mounting component; 8. Inertial navigation device. Detailed implementation manners

[0034] The present invention will be further described below with reference to the accompanying drawings.

[0035] Please refer to Figures 1 to 10 , a simulation loading device for simulating the wear condition of a swing mechanism of a swing-type bogie, including a bracket 1, an actuator assembly 3 and a simulation beam 4; wherein, the installation end of the actuator assembly 3 is installed on the bracket 1, the output end of the actuator assembly 3 is connected to the simulation beam 4, and the actuator assembly 3 and the bracket 1 cooperate to apply loading forces in multiple directions to the simulation beam 4; the simulation beam 4 simulates the side frame of the bogie, the simulation beam 4 is of a box structure and has high rigidity to prevent deformation during loading, and the simulation beam 4 is installed on the simulation axle 5 through the swing mechanism 2 to simulate the wear condition of the swing mechanism 2 of the side frame of the real vehicle during the real movement process.

[0036] To better implement the present invention, refer to Figure 4 , in an embodiment, the swing mechanism 2 includes a guide frame rocking seat 201, the lower end of the guide frame rocking seat 201 cooperates with the bearing saddle 202, the lower surface of the guide frame rocking seat 201 is an outer arc surface, and the upper surface of the bearing saddle 202 is an inner arc surface, so that the lower surface of the guide frame rocking seat 201 can cooperate with the upper surface of the bearing saddle 202, the bottom of the bearing saddle 202 is cooperatively installed with the simulation axle 5, and the simulation axle 5 is installed on the base 6, as Figure 10 shown.

[0037] To better implement the present invention, refer to Figure 3 , Figure 4 and Figure 10, in one embodiment, a rectangular guide frame 401 is provided at the bottom of the simulation beam 4. The rectangular guide frame 401 is connected to the top end of the guide frame swing seat 201. Threaded holes are provided around the rectangular guide frame 401. After the guide frame swing seat 201 is embedded in the rectangular guide frame 401, bolts are inserted into the threaded holes around and torque is applied to realize the mutual restraint between the simulation beam 4 and the guide frame swing seat 201. Stop plates 4011 are provided at both the front and rear ends of the rectangular guide frame 401. The stop plates 4011 will extend into the installation grooves at both ends of the bearing saddle 202 to prevent the simulation beam 4 and the bearing saddle 202 from slipping under large movement conditions. This installation method is the same as the installation method between the side frame of the real swing-type freight car bogie and the swing mechanism 2. The stop plate 4011 is perpendicular to the movement direction of the third hydraulic actuator 303, that is, the stop plate 4011 is perpendicular to the third direction.

[0038] To better implement the present invention, refer to Figure 1 , in one embodiment, the bracket 1 includes multiple columns 101 and multiple reaction seats 103. In this embodiment, there are two columns 101. The top ends of the two columns 101 are respectively connected to both ends of the cross beam 102. Reaction seats 103 are respectively provided on both sides of the cross beam 102. The cross beam 102 is located directly above the simulation beam 4 and is parallel to the simulation beam 4.

[0039] To better implement the present invention, refer to Figure 1 , in one embodiment, the actuator assembly 3 and the bracket 1 cooperate to apply loading forces to the simulation beam 4 in at least the first direction, the second direction, and the third direction with different directions. In this embodiment, the first direction is perpendicular to the top of the simulation beam 4, the second direction is the direction perpendicular to the side of the simulation beam 4 close to the reaction seat 103, and the third direction is along the length direction of the simulation beam 4. The actuator assembly 3 includes a first hydraulic actuator 301, a second hydraulic actuator 302, and a third hydraulic actuator 303.

[0040] The first hydraulic actuator 301 is installed at the bottom of the cross beam 102. The output end of the first hydraulic actuator 301 is hinged to the top of the simulation beam 4. The first hydraulic actuator 301 is used to apply a load to the simulation beam 4 in the first direction. There are multiple groups of the first hydraulic actuator 301, and the output ends are respectively hinged to both ends of the top of the simulation beam 4. In this embodiment, two groups of the first hydraulic actuator 301 are provided. The first hydraulic actuator 301 is connected to the simulation beam 4 by a spherical hinge joint, and the first hydraulic actuator 301 is connected to the mounting plate of the mounting component 7 by a spherical hinge joint to realize that the simulation beam 4 can move under the loading action of the actuator assembly 3.

[0041] The second hydraulic actuator 302 is hinged to the reaction seat 103, and the output end of the second hydraulic actuator 302 is hinged to the side surface of the simulated beam 4. The second hydraulic actuator 302 is used to apply a load to the simulated beam 4 in the second direction, so that the simulated beam 4 moves horizontally in the second direction or rotates around a vertical axis perpendicular to the center of the simulated beam. There are multiple groups of the second hydraulic actuators 302, and the output ends are respectively hinged to two side walls of the simulated beam 4 close to the reaction seat 103. The multiple groups of the second hydraulic actuators 302 are located on different straight lines, that is, the output ends of the second hydraulic actuators 302 are respectively hinged to the front end and the rear end of the side walls on both sides of the simulated beam 4. When the second hydraulic actuator 302 applies a load to the simulated beam 4 in the second direction, the guide frame rocking seat 201 drives the simulated beam 4 to rotate relative to the carrying saddle 202, so as to move relative to the simulated axle 5, and convert the load in the second direction into a rotational displacement. In this embodiment, the second hydraulic actuator 302 and the simulated beam 4 are connected by a spherical hinge joint, and the second hydraulic actuator 302 and the reaction seat 103 are connected by a spherical hinge joint, so that the simulated beam 4 can move under the loading of the actuator assembly 3. In this embodiment, the second hydraulic actuator 302 applies a load to the simulated beam 4 in the second direction. To make the simulated beam 4 move horizontally in the second direction or rotate around a vertical axis perpendicular to the center of the simulated beam, two groups of the second hydraulic actuators 302 are provided and are respectively connected to the reaction seat 103. When the two groups of the second hydraulic actuators 302 perform anti-phase actions, the simulated beam 4 will perform horizontal movement in the second direction, simulating the eccentric wear of the swing mechanism 2 in the translational state of the real vehicle in the second direction; when the two groups of the second hydraulic actuators 302 perform in-phase actions, the simulated beam 4 will rotate around a vertical axis perpendicular to the center of the simulated beam, making the simulated beam 4 perform a yawing motion, simulating the eccentric wear of the swing mechanism 2 in the yawing motion state of the real vehicle.

[0042] The third hydraulic actuator 303 is installed on the column 101. The output end of the third hydraulic actuator 303 is hinged to the end of the simulation beam 4. The third hydraulic actuator 303 is used to apply a load to the simulation beam 4 in the third direction, so as to make the simulation beam 4 perform a horizontal movement in the third direction. There are multiple groups of the third hydraulic actuators 303, and the output ends are respectively connected to both ends of the simulation beam 4 close to the column 101. In this embodiment, to ensure the loading of the simulation beam 4 in the third direction, two groups of the third hydraulic actuators 303 are provided. The output ends of the two groups of the third hydraulic actuators 303 are respectively hinged to the front end and the rear end of the simulation beam 4, so that the two groups of the third hydraulic actuators 303 and the simulation beam 4 are on a horizontal straight line. In this embodiment, the third hydraulic actuator 303 and the simulation beam 4 are connected by a spherical hinge joint, and the third hydraulic actuator 303 and the mounting plate of the mounting component 7 are connected by a spherical hinge joint, so as to enable the simulation beam 4 to move under the loading of the actuator assembly 3. When the third hydraulic actuator 303 performs an anti-phase action, the simulation beam 4 will perform a horizontal movement in the third direction, simulating the eccentric wear condition of the swing mechanism 2 under the third-direction translational state of a real vehicle.

[0043] The first hydraulic actuator 301, the second hydraulic actuator 302 and the third hydraulic actuator 303 all include a cylinder block and an actuator rod. As Figure 4 shown, the cylinder block is used to store hydraulic oil. Under the pressure formed by the hydraulic oil in the cylinder block, the actuator rod is pushed to expand and contract. One end of the actuator rod away from the cylinder block is connected to the simulation beam 4 through a spherical hinge. The actuator assembly 3 is electrically connected to the control system, and the control system controls the actuator assembly 3 to work.

[0044] During the test, to ensure that the simulation beam 4 can simulate the working state of a real bogie side frame, special requirements are imposed on the loading applied to the simulation beam 4 in three directions. Regarding the loading of the simulation beam 4 in the first direction, taking the force of the wheel-rail in the first direction measured on the line as the target value, the control system transmits a force output signal to the first hydraulic actuator 301, so as to control the loading received by the simulation beam 4 in the first direction. In this embodiment, taking Figure 2 the front view shown as an example, it is stipulated that Figure 2On the right side of the middle is the front end of the simulated beam 4, and on the left side is the rear end of the simulated beam 4. The first hydraulic actuator 301 connected to the front end of the simulated beam 4 is the front-end first hydraulic actuator, and the first hydraulic actuator 301 connected to the rear end of the simulated beam 4 is the rear-end first hydraulic actuator. Taking the measured values of the front-wheel rail and the rear-wheel rail in the first direction as the loading values of the front-end first hydraulic actuator and the rear-end first hydraulic actuator, a force is applied to the simulated beam 4. Through the detection of the force sensor, it is found that the force signal of the front-end first hydraulic actuator, the force signal of the rear-end first hydraulic actuator, the measured value of the force of the front-wheel rail in the first direction, and the measured value of the force of the rear-wheel rail in the first direction are basically the same. It can be shown that in the first direction, the loading of the front-end first hydraulic actuator and the rear-end first hydraulic actuator on the simulated beam 4 reaches the measured value under the actual working condition, as Figure 6 shown. Therefore, during the actual test process, the load of the wheel rail in the first direction measured on the line is directly used as the loading value of the first hydraulic actuator 301.

[0045] Regarding the loading of the simulated beam 4 in the second direction, in the second direction, the two groups of second hydraulic actuators 302 can perform anti-phase actions or in-phase actions simultaneously, and the movement of the simulated beam 4 will be different. Taking Figure 2 the front view shown as an example, the second hydraulic actuator 302 connected to the front end of the simulated beam 4 is the front-end second hydraulic actuator, and the second hydraulic actuator 302 connected to the rear end of the simulated beam 4 is the rear-end second hydraulic actuator. Taking the measured horizontal movement amount of the bogie side frame in the second direction on the line as the target value, that is, the amplitude of the deviation of the bogie side frame from the initial position as the target value, the control system controls the loading of the front-end second hydraulic actuator and the rear-end second hydraulic actuator, thereby controlling the displacement output signals of the front-end second hydraulic actuator and the rear-end second hydraulic actuator. As Figure 7 shown, when the front-end second hydraulic actuator and the rear-end second hydraulic actuator perform anti-phase actions, the simulated beam 4 will perform horizontal movement in the second direction, so as to simulate the movement of the bogie side frame in the second direction under real conditions. To reach the target value, the displacement control command of the front-end second hydraulic actuator needs to be expressed as C hq =l m ·sin(2·π·f·t), and the displacement control command of the rear-end second hydraulic actuator needs to be expressed as C hh =l m ·sin(2·π·f·t + π), where l m represents the displacement amplitude of the horizontal movement in the second direction; f represents the loading frequency, with a range of 0 to 10 Hz; t represents time. As Figure 7As shown, the test value of the horizontal movement of the simulated beam 4 designed through this displacement control command in the second direction is basically the same as the target value of the horizontal movement of the bogie side frame measured on the line. It can be shown that when the two groups of second hydraulic actuators 302 perform anti-phase actions, the movement of the simulated beam 4 can fully simulate the movement state of the bogie side frame in the real state, so as to simulate the wear of the swing point of the swing mechanism 2 connected to the bogie side frame in the real movement state.

[0046] Taking the yaw angle of the bogie side frame measured on the line around the vertical axis as the target value, the control system controls the loading of the front second hydraulic actuator and the rear second hydraulic actuator, so as to control the displacement output signals of the front second hydraulic actuator and the rear second hydraulic actuator. As Figure 8 shown, when the front second hydraulic actuator and the rear second hydraulic actuator perform in-phase actions, the simulated beam 4 rotates around the vertical axis at the center perpendicular to the simulated beam to simulate the yaw movement of the bogie side frame in the real situation. To reach the target value, the displacement control commands of the front second hydraulic actuator and the rear second hydraulic actuator at this time are expressed as C yq =C yh =p / 2·γ m ·sin(2·π·f·t), where C yq represents the displacement control command of the front second hydraulic actuator; C yh represents the displacement control command of the rear second hydraulic actuator; p represents the installation distance between the front second hydraulic actuator and the rear second hydraulic actuator; γ m represents the angle amplitude of yaw. As Figure 8 shown, the test value of the yaw angle obtained by the simulated beam 4 during yaw movement designed through this displacement control command is basically the same as the target value of the yaw angle of the bogie side frame measured on the line around the vertical axis. It can be shown that when the two groups of second hydraulic actuators 302 perform in-phase actions, the movement of the simulated beam 4 can fully simulate the movement state of the bogie side frame in the real state, so as to simulate the wear of the swing point of the swing mechanism 2 connected to the bogie side frame in the real movement state.

[0047] Comprehensively, in the actual working state of the bogie side frame, the loading force received in the second direction may cause the bogie side frame to have horizontal movement or yaw movement. Therefore, in order to enable the simulated beam 4 to have two loading force conditions in the second direction during the test, the sum of the displacements of the front second hydraulic actuator and the rear second hydraulic actuator under the two loading states received respectively during the test process is the loading state actually received by the simulated beam 4 in the second direction. During the entire test process, the displacement control command of the front second hydraulic actuator is expressed as C lq =C hq +C yq; The displacement control command of the second hydraulic actuator at the rear end is represented as C lh = C hh + C yh .

[0048] Regarding the loading of the simulated beam 4 in the third direction, taking the front view shown in Figure 2 as an example, the third hydraulic actuator 303 connected to the front end of the simulated beam 4 is the front-end third hydraulic actuator, and the third hydraulic actuator 303 connected to the rear end of the simulated beam 4 is the rear-end third hydraulic actuator. As shown in Figure 9 , taking the average value of the displacements of the bogie side frame and the front and rear wheels measured on the line in the third direction as the target value, the control system controls the loading of the front-end third hydraulic actuator and the rear-end third hydraulic actuator, thereby controlling the displacement output signals of the front-end third hydraulic actuator and the rear-end third hydraulic actuator. When the front-end third hydraulic actuator and the rear-end third hydraulic actuator 303 perform anti-phase actions, the simulated beam 4 will move in the third direction, simulating the loading of the real bogie side frame in the third direction. To achieve the target value, the displacement control command of the front-end third hydraulic actuator can be expressed as C xq = x m ·sin(2·π·f·t); The displacement control command of the rear-end third hydraulic actuator can be expressed as C xh = x m ·sin(2·π·f·t + π); where x m represents the displacement amplitude of the movement in the third direction. As shown in Figure 9 , the test value of the movement amount of the simulated beam 4 in the third direction designed by this displacement control command is basically consistent with the target value of the average value of the displacements of the bogie side frame measured on the line in the third direction, indicating that when the two groups of third hydraulic actuators 303 perform anti-phase actions, the movement of the simulated beam 4 can fully simulate the movement state of the bogie side frame in the real state, so as to simulate the wear condition of the swing point of the swing mechanism 2 connected under the real movement state of the bogie side frame.

[0049] During the entire test process, the simulated beam 4 is loaded in all three directions simultaneously to realize the simulation of the multi-degree-of-freedom composite loading of the bogie side frame in the real state, so as to test the wear condition of the swing mechanism 2 in the real state.

[0050] To better implement this invention, refer to Figure 1, in one embodiment, the first hydraulic actuator 301 and the third hydraulic actuator 303 are respectively mounted on the cross beam 102 and the column 101 through the mounting member 7. Each set of mounting members 7 includes a plurality of mounting plates. In this embodiment, each set of mounting members 7 is provided with two mounting plates. The two mounting plates clamp the cross beam 102 or the column 101 and are fixedly installed through a threaded assembly, thereby mounting the mounting member 7 on the cross beam 102 or the column 101. The threaded assembly includes a plurality of threaded rods and a plurality of nuts. The two mounting plates clamp the column 101 or the cross beam 102. The threaded rod passes through the two mounting plates. By tightening the nuts on the threaded rod, the distance between the two plates is shortened, thereby tightly clamping the plates on the cross beam 102 or the column 101. The mounting ends of the first hydraulic actuator 301 and the third hydraulic actuator 303 are respectively connected to the mounting plates of the mounting member 7 close to the simulated beam 4 through spherical hinges.

[0051] To better implement the present invention, refer to Figure 1 , in one embodiment, an inertial navigation device 8 is provided at the center of the top of the simulated beam 4. The inertial navigation device 8 is used to monitor the motion state of the simulated beam 4 during the test. The inertial navigation device includes an inertial measurement device and a gyroscope. The accelerometer in the inertial measurement device is used to measure the linear acceleration of the simulated beam 4, and the gyroscope in the inertial measurement device is used to measure the angular velocity of the simulated beam 4, thereby determining the attitude of the simulated beam 4. The inertial measurement device transmits the measured information to the computer in the control system to calculate the actual motion condition of the simulated beam 4. The inertial navigation device 8 is installed at the center position of the top of the simulated beam 4 through bolts.

[0052] To better implement the present invention, refer to Figure 1 , in one embodiment, it further includes a base 6. The column 101 and the reaction seat 103 are both installed on the base 6.

[0053] The simulation loading device based on the wear condition of the swing mechanism of the swing type bogie has the working principle as follows:

[0054] The swing mechanism 2 to be tested is installed between the guide frame of the simulated beam 4 and the simulated axle 5. The control system controls the actuator assembly 3 to work, so that the first hydraulic actuator 301 loads the simulated beam 4 with the first direction load of the wheel-rail measured in the line, thereby simulating the actual working state of the side frame of the bogie in the first direction; in the second direction, by controlling the second hydraulic actuator 302 through the control system, the two groups of second hydraulic actuators 302 perform anti-phase actions and in-phase actions. Among them, the displacement control command of the front-end second hydraulic actuator needs to satisfy C lq = C hq + C yq , where C hq = l m ·sin(2·π·f·t), Cyq = p / 2·γ m ·sin(2·π·f·t), that is, it satisfies the sum in the anti-phase action and in-phase action states; the displacement control command of the second hydraulic actuator at the rear end needs to satisfy C lh = C hh + C yh , where C hh = l m ·sin(2·π·f·t + π), C yh = p / 2·γ m ·sin(2·π·f·t), that is, it satisfies the sum in the anti-phase action and in-phase action states. Under this state, the loading on the simulated beam 4 in the second direction can fully simulate the loading condition of the bogie side frame in the second direction under the real condition; in the third direction, the control system controls the third hydraulic actuators 303 so that the two groups of third hydraulic actuators 303 perform anti-phase actions. When the displacement control command of the front-end third hydraulic actuator needs to satisfy C xq = x m ·sin(2·π·f·t); when the displacement control command of the rear-end third hydraulic actuator needs to satisfy C xh = x m ·sin(2·π·f·t + π), the loading on the simulated beam 4 in the third direction can fully simulate the loading condition of the bogie side frame in the third direction under the real state. Under the test state, the simulated beam 4 needs to be loaded in three directions simultaneously to simulate the motion state of the bogie side frame under the real state, so as to simulate the wear condition of the swing mechanism 2. During the test process, the swing mechanism 2 is regularly removed, and the wear condition between the guide frame rocker seat 201 and the bearing saddle 202 is observed, and finally the wear condition of the swing mechanism 2 connected to the bogie side frame during the actual motion process can be obtained.

[0055] Although the present invention has been described with reference to the preferred embodiments, various improvements can be made to it and components therein can be replaced with equivalents without departing from the scope of the present invention. In particular, as long as there is no structural conflict, the technical features mentioned in each embodiment can be combined in any way. The present invention is not limited to the specific embodiments disclosed in the text, but includes all technical solutions falling within the scope of the claims.

Claims

1. A simulating loading device for the wear condition of the swing mechanism of a swing bogie, characterized in that: It includes a bracket, an actuator assembly and a simulation beam; The mounting end of the actuator assembly is mounted on the bracket, the output end of the actuator assembly is connected to the simulation beam, and the actuator assembly cooperates with the bracket to apply loading forces in multiple directions to the simulation beam; The simulated beam is installed on the simulated axle through the swing mechanism to simulate the wear condition of the swing mechanism.

2. The simulating loading device for the wear condition of the swing mechanism of the swing type bogie according to claim 1 is characterized in that: The swing mechanism includes a guide frame rocking seat, the lower end of the guide frame rocking seat is matched with a load-bearing saddle, and the bottom of the load-bearing saddle is mounted in cooperation with the simulated axle.

3. The simulating loading device for the wear condition of the swing mechanism of the swing bogie according to claim 1 is characterized in that: The bracket includes a plurality of columns and a plurality of reaction seats, the top ends of the plurality of columns are respectively connected to the ends of the crossbeam, the reaction seats are respectively arranged on both sides of the crossbeam, and the crossbeam is parallel to the simulation beam.

4. The simulating loading device for the wear condition of the swing mechanism of the swing bogie according to claim 3 is characterized in that: The actuator assembly cooperates with the bracket to apply loading forces in at least a first direction, a second direction and a third direction of different directions to the simulation beam, and the actuator assembly includes a first hydraulic actuator, a second hydraulic actuator and a third hydraulic actuator; Wherein: the first hydraulic actuator is installed on the crossbeam, the output end of the first hydraulic actuator is hinged to the top of the simulation beam, and the first hydraulic actuator is used to load the simulation beam in the first direction; The second hydraulic actuator is hinged to the reaction seat, the output end of the second hydraulic actuator is hinged to the side of the simulation beam, and the second hydraulic actuator is used to load the simulation beam in the second direction, so that the simulation beam moves horizontally along the second direction or rotates around a vertical axis perpendicular to the center of the simulation beam; and The third hydraulic actuator is installed on the column, and the output end of the third hydraulic actuator is hinged to the end of the simulation beam. The third hydraulic actuator is used to load the simulation beam in the third direction to make the simulation beam perform horizontal movement in the third direction.

5. The simulating loading device for the wear condition of the swing mechanism of the swing bogie according to claim 2 or 4, characterized in that: A rectangular guide frame is provided at the bottom of the simulated beam, and the rectangular guide frame is connected to the top end of the guide frame rocking seat. Stop plates are provided at both the front and rear ends of the rectangular guide frame, and the stop plates are perpendicular to the movement direction of the third hydraulic actuator.

6. The simulating loading device for the wear condition of the swing mechanism of the swing bogie according to claim 4, characterized in that: The first hydraulic actuator and the third hydraulic actuator are respectively mounted on the crossbeam and the column through mounting components.

7. The simulating loading device for the wear condition of the swing mechanism of the swing type bogie according to claim 6, characterized in that: The mounting component includes a plurality of mounting plates, and the plurality of mounting plates are mounted on the cross beam or the column through threaded components. The first hydraulic actuator and the third hydraulic actuator are respectively hinged to the mounting plates close to the simulation beam.

8. The simulating loading device for the wear condition of the swing mechanism of the swing bogie according to claim 3, characterized in that: An inertial navigation device is provided on the top of the simulation beam, and the inertial navigation device is used to monitor the motion state of the simulation beam during the test.

9. The simulating loading device for the wear condition of the swing mechanism of the swing bogie according to claim 3, characterized in that: It also includes a base, and the column, the reaction seat and the simulated axle are all installed on the base.

10. The simulating loading device for the wear condition of the swing mechanism of the swing bogie according to claim 4, characterized in that: The first hydraulic actuator is provided with multiple groups, and the output ends are respectively hinged to the two ends of the top of the simulation beam; the second hydraulic actuator is provided with multiple groups, and the output ends are respectively hinged to the two side walls of the simulation beam close to the reaction seat, and the multiple groups of the second hydraulic actuators are located on different straight lines; the third hydraulic actuator is provided with multiple groups, and the output ends are respectively connected to the two ends of the simulation beam close to the column.

Images