JP2003322586A - Train running load simulating exciter and train running load simulating excitation method - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a train running load simulating exciter capable of preferably executing a test for comprehending the frequency characteristics of a ground side system having a test rail track or an accelerated test for simulating a multitude of passages of train wheels on the test rail track in a short period of time, and a train running load simulating excitation method for preferably executing the tests. <P>SOLUTION: After the rotation of an unbalanced weight is started and exciting force generated from the unbalanced weight reaches a set value, a relative phase angle between a movable eccentric weight and a fixed eccentric weight is set so that the phase angle corresponds to the rotational frequency of the unbalanced weight detected with a velocity sensor by using map data expressing relation of the rotational frequency of the unbalanced weight with a relative phase angle between the movable eccentric weight and the fixed eccentric weight in the unbalanced weight in order to keep the exciting force constant. <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an exciter simulating train running.

[0002]

2. Description of the Related Art Conventionally, when a railway vehicle (train) is running, the characteristics of vibration propagating to a system consisting of a train, a track and a test track having a member supporting the track, and a roadbed below the test track. It is recognized that it is important to confirm the durability of the track member and the like against the vibration in order to speed up the train.

In order to understand such characteristics, it is conceivable to carry out a running test on a commercial line using an actual vehicle. With such a method, the soil condition and the track condition due to the weather change, etc. There are problems that it is difficult to keep the conditions constant with good reproducibility, and that it is difficult to perform a large number of tests because the sales line is used.

Therefore, conventionally, in order to solve such a problem, it is possible to use an exciter (train traveling load simulated exciter) which simulates a load (train traveling load) acting on a track when the train is traveling. Has been done. This exciter includes a test track formed of various track members such as a track provided for testing and a member supporting the track, and a static load for applying a load equivalent to the static load of a train to the test track. It is provided with an additional weight and a drive frequency variable exciter for applying a vertical excitatory force to the test track so as to simulate the load acting on the track when passing through the wheels of the train.

Of these, the track is composed of two rails arranged in parallel and having a length of about 10 m, and the member for supporting the track is a single sleeper supporting the track, and a track for the sleeper. It is configured to have a rail fastening device that fastens, a roadbed, a ballast mat, and the like. Further, the static load applying weight is configured as a weight attached to both axial end portions of the two rails.

The vibrating section is constructed as a so-called biaxial inversion unbalanced weight vibrating system and is arranged so as to abut the track. That is, the two unbalanced weights arranged substantially horizontally are synchronized with each other and are rotated in opposite directions to cancel the centrifugal force in the horizontal direction and generate the exciting force only by the centrifugal force in the vertical direction. By doing so, the load when the wheels of the train pass on the test track can be simulated.

[0007]

However, in the above-described conventional train running load simulation vibrator, when the drive frequency (rotation frequency) of the unbalanced weight is changed, the generated vibratory force also changes accordingly. The vibrating section was configured so that it would end up. Therefore, the amplitude of the vibration that occurs in the system on the ground side having the test track when the vibration unit is driven naturally changes according to the drive frequency of the vibration unit, and the frequency characteristics (resonance) of the system on the ground side are changed. There was a problem that it was not possible to accurately check the frequency etc.).

[0008] Further, various other tests for increasing the rotation frequency of the vibrating section while keeping the vibrating force applied to the test track from the vibrating section constant, for example, testing a train wheel many times in a short time. There is a problem that the accelerated test that simulates the load acting on the test track when passing on the track cannot be performed accurately.

More specifically, first, in the train traveling load simulation vibrator, the vibratory force generated by the vibrator for one cycle (corresponding to one vertical vibration) passes through one train wheel. In order to simulate the load when the train wheels pass on the test track a number of times in a short time, it is necessary to increase the rotation frequency of the vibrating section. .

However, in the conventional train running load simulated vibration generator, in the process of increasing the rotation frequency of the vibration generator, the vibration force applied from the vibration generator is not constant as described above. Therefore, in the meantime, the oscillating force generated by the oscillating unit for each cycle does not accurately simulate the load when the train wheels pass, that is, the acceleration test cannot be performed accurately as a result. There was a problem.

The present invention has been made to solve the above problems, and an object thereof is to carry out a test for grasping the frequency characteristic of a system on the ground side having a test track, or a train wheel in a short time. A train running load simulation exciter capable of suitably performing an accelerated test that simulates a load when passing through a multi-test test track, and a train traveling load simulation exciting method for suitably performing those tests Is to provide.

[0012]

Means for Solving the Problems and Effects of the Invention In order to achieve such an object, a train running load simulation vibrator of the present invention comprises a test track provided for testing and a static train load on the test track. A static load adding weight for applying a load equivalent to, and a drive frequency variable oscillating section for applying an oscillating force to the test track, and a train traveling load simulated oscillating machine, A vibrating force holding means for holding a vibrating force applied to the test track via the vibrating section constant even if the drive frequency of the vibrating section changes.

According to the train running load simulation vibrator of the present invention, since the test track provided for the test is used instead of the commercial line, the reproducibility of the track condition is high and the evaluation accuracy is high. It is possible to obtain the same effect as the conventional train running load simulated vibration exciter in that the rolling test is also easy.

Further, since the train traveling load simulation vibration oscillating machine of the present invention is provided with the vibration motive force holding means, the train oscillating force applied to the test track via the vibration oscillating portion is maintained while being kept constant. The drive frequency of the vibration unit can be changed. Therefore, when changing the drive frequency in this way, looking at the change in the vibration state (amplitude of vibration, etc.) of the system on the ground side having the test track, the drive frequency at which the change in the vibration state occurs, that is, It is possible to accurately confirm the resonance frequency of the system on the ground side.

Further, in the train traveling load simulating exciter of the present invention, the oscillating section is used for conducting the accelerated test for simulating the load acting on the test track when the train wheels pass on the test track a number of times in a short time. Even in the process of increasing the driving frequency of (1), the vibrating force holding means can keep the vibrating force (corresponding to the load) applied to the test track constant. Therefore, compared to the conventional one,
The effect that the accelerated test can be accurately performed is obtained.

In the train traveling load simulation oscillating machine of the present invention, the oscillating portion has an unbalanced weight having a shaft, a fixed eccentric weight fixed to the shaft, and a movable eccentric weight rotatably provided on the shaft. A weight, a drive device for rotating the unbalanced weight, and a phase angle changing means for changing the relative phase angle between the movable eccentric weight and the fixed eccentric weight when the unbalanced weight rotates, The centrifugal force of the unbalanced weight rotated by the drive unit is configured to generate an oscillating force for the test track, and the oscillating force holding means changes the rotational frequency, which is the drive frequency of the unbalanced weight, to change. Alternatively, the phase angle changing means may be operated so that the vibration force generated by the unbalanced weight becomes constant, and the relative phase angle between the movable eccentric weight and the fixed eccentric weight may be adjusted.
Also in this case, the same effect as described above can be obtained.

Further, in this case, the exciting force holding means includes a frequency detecting means for detecting the rotational frequency of the unbalanced weight and the rotational frequency for keeping the exciting force generated by the unbalanced weight constant. A storage means for storing the relationship with the relative phase angle as map data, and a relative phase corresponding to the rotation frequency from the rotation frequency detected by the frequency detection means using the map data stored in the storage means. And a phase angle setting means for operating the phase angle changing means so as to determine the angle and obtain the relative phase angle.

In this case, even if the rotational frequency of the unbalanced weight changes, if the map data in the storage means is used on the basis of the rotational frequency of the unbalanced weight detected by the frequency detecting means, the exciting force can be kept constant. Therefore, it is possible to easily and accurately determine and set the relative phase angle between the movable eccentric weight and the fixed eccentric weight.

Further, after the relative phase angle between the movable eccentric weight and the fixed eccentric weight is set to the minimum value where the movable eccentric weight and the fixed eccentric weight are adjacent to each other, the relative phase angle is set. Initial operation setting means for starting the rotation of the unbalanced weight through the driving machine while maintaining it, and vibrating force detection means for detecting the magnitude of the exciting force generated by the unbalanced weight rotated by the driving machine When the rotation frequency of the unbalanced weight that has started to rotate increases and the vibration force detected by the vibration force detection means reaches a predetermined value, the rotation frequency of the unbalanced weight is changed according to the rotation frequency. It is preferable to have a control starting means for starting control by the phase angle setting means for performing the relative phase angle setting operation.

Here, the state in which the relative phase angle between the movable eccentric weight and the fixed eccentric weight is minimum is a state in which the vibration force generated by the rotation of the unbalanced weight is maximum. Therefore,
In this case, when the rotation of the unbalanced weight is started by the initial operation setting means, the exciting force detected by the exciting force detecting means is set to a predetermined value before the rotation frequency of the rotation is significantly increased. The value will be easily reached. That is, the exciting force generated from the unbalanced weight can be increased to a predetermined value in a short time.

Further, since the control start means starts the control by the phase angle setting means after the exciting force rises to the predetermined value in this way, even if the rotational frequency of the unbalanced weight changes thereafter. The exciting force applied to the test track is kept at a predetermined value. That is, also in the present invention,
Since the rotation frequency of the unbalanced weight is not sufficient for a predetermined time from the start of rotation of the unbalanced weight, the unbalanced weight rotates until the target exciting force that is kept constant reaches a predetermined value. It will change (increase) as the frequency increases. However, if the unbalanced weight is rotated with the relative phase angle minimized as described above, the exciting force generated by the rotation of the unbalanced weight reaches a predetermined magnitude in a short time, so It is possible to suppress the change time of the exciting force from the start of the rotation of the balance weight to the start of the control by the phase angle setting means in a short time.

On the other hand, the phase angle changing means includes an intermediate member that is movable in the axial direction of the shaft that fixes the fixed eccentric weight, and the axial movement of the intermediate member that rotates the movable eccentric weight with respect to the shaft. By converting the converting means and the intermediate member in the axial direction, the converting means rotates the movable eccentric weight with respect to the shaft, and the movable eccentric weight and the fixed eccentric weight move relative to each other. Preferably, the intermediate member moving means for changing the target phase angle is provided.

In this case, the relative phase angle between the movable eccentric weight and the fixed eccentric weight is set to correspond to the position of the intermediate member. The relative phase angle is changed when the intermediate member moving means is driven and the intermediate member is moved. That is, in this phase angle changing means, since the intermediate member moving means needs to be driven only when changing the relative phase angle, it is possible to effectively change and set the relative phase angle. To be

On the other hand, also by the vibration generating method performed by the train traveling load simulation vibrator of the present invention described above, it is possible to obtain the effect corresponding to the effect of the train traveling load simulation vibrator of the present invention. For example, a test track provided for testing is used with a vibration generator configured to add a drive frequency variable vibration force to a test track that simulates the load acting on the test track when the train is running. A method for simulating train running load by adding a method, wherein the motive force applied to the test track via the oscillating section is kept constant even if the drive frequency of the oscillating section changes. If it is one of the features, as in the above, a test for grasping the frequency characteristics of the system on the ground side having a test track, or a load when the train wheels pass on the test track many times in a short time It is possible to obtain the effect that the simulated test that is simulated can be appropriately performed.

[0025]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 is a schematic diagram showing the overall configuration of a train running load simulation vibrator 1 of this embodiment. The train running load simulation vibration oscillating machine 1 of the present embodiment includes a test track including various track members such as a track 10 and a member 20 supporting the track 10, a static load applying weight 30, and an oscillating section 40. , A controller 120 and a data recording device 140.

The track 10 is a track laid for testing separately from the commercial line, and is composed of two rails arranged in parallel and having a length of about 10 m. The member 20 that supports the track 10 includes a single sleeper 12 that supports the track 10.
A rail fastening device 14 for fastening the track 10 to the sleeper 12, a ballast bed laid with crushed stone, or a ballast mat such as a rubber mat.
And the roadbed 16 interposed between the roadbed and the roadbed 18.

The static load applying weight 30 corresponds to the static load of the train, and the track 1 composed of the above two rails.
It is configured as a weight attached to both axial end portions of 0. The vibrating section 40 is arranged or fixed so as to come into contact with the track 10, and applies a vibrating force to the test track 10.

Here, the structure of the vibrating section 40 will be described with reference to FIGS. 2 (a) and 2 (b) in addition to FIG. Incidentally, FIG.
2A is a cross-sectional plan view showing a schematic configuration of an oscillating section 40 of the train traveling load simulation oscillating machine 1 shown in FIG.
(B) is an explanatory view showing a principle that an exciting force is generated by the exciting unit 40.

As shown in the figure, the vibrating section 40 includes the unbalanced weights 42 and 44, the drive motor 46, and the phase angle changing section 4.
8 and. One of the unbalanced weights 42 has a shaft 51
Fixed eccentric weights 53 attached to both ends of the shaft 51,
55, and movable eccentric weights 57 and 59 provided at both ends thereof so as to be rotatable with respect to the shaft 51.

Specifically, the disks 6 are provided on both ends of the shaft 51.
1, 63 are mounted and fixed eccentric weights 53, 55
Are provided at one end portion in the radial direction of the circular portion formed by the disks 61 and 63, respectively. Further, disks 65 and 67 are provided at both ends of the shaft 51 so as to be rotatable with respect to the shaft 51, and the movable eccentric weights 57 and 59 are provided to the disks 65 and 67.
Is provided at one end portion in the radial direction of the circular portion formed by. A gear 69 is also provided on the shaft 51.

The other unbalanced weight 44 is the unbalanced weight 42.
Are arranged substantially in parallel with each other and have the same configuration as the unbalanced weight 42. Therefore, the unbalanced weight 44 shown in the figure
The same reference numerals as the respective constituent elements of the unbalanced weight 42 are given to the respective constituent elements of, and the description thereof will be omitted. However, for convenience of distinction, the reference numeral indicating each component on the unbalanced weight 44 side is further attached with “a”.

The gear 69 on the side of the unbalanced weight 42 and the gear 69a on the side of the unbalanced weight 44 are in mesh with each other, and as will be described later, the drive motor 46 passes through the gears 69 and 69a to the shaft 51 and When the rotational driving force is applied to 51a, the unbalanced weights 42 and 44 are configured to rotate in directions opposite to each other.

In addition, the unbalanced weights 42, 44, together with the function of the phase angle changing unit 48 described later, cause the eccentric weights 53, 55, 57, 57, 59
And the eccentric weights 53a, 55a, 57 on the side of the unbalanced weight 44
When a and 59a face up and down, the unbalanced weight 4
The vertical force is generated by the centrifugal force of 2,44, and when these eccentric weights are oriented in the left-right direction,
The centrifugal force of the unbalanced weight 42 and the centrifugal force of the unbalanced weight 44 cancel each other out, so that an exciting force in the left-right direction is not generated.

The drive motor 46 is connected to a rotary connecting rod 73, to which a gear 71 is mounted, via a transmission shaft 79 having universal joints 75 and 77, and applies a rotary drive force to the rotary connecting rod 73 and the gear 71. Is configured to. The gear 71 is in mesh with the gear 69. Therefore, when the drive motor 46 rotates the gear 71, the unbalanced weights 42 and 44 are rotated in the opposite directions as described above, and the unbalanced weights 42 and 44 generate a vertical vibration force. To be done.

The phase angle changing unit 48 includes a servo motor 81.
, The rotary connecting rod 83, the universal joint 85,
It has a transmission shaft 89 having 87, a horizontal shaft 91, movable eccentric weight control shafts 93, 95, a ball screw 97, and change nut ball screws 99, 101, 103, 105.

The servo motor 81 and the rotary connecting rod 83 are
Transmission shaft 89 having universal joints 85, 87
When the servo motor 81 is driven, a rotary driving force is applied to the rotary connecting rod 83. A shaft extending from the servo motor 81 to the rotary connecting rod 83 via the transmission shaft 89 is provided between the shafts 51 and 51a so as to be substantially parallel to the shafts 51 and 51a.

The horizontal shaft 91 is a shaft portion that extends in a horizontal direction substantially perpendicular to the rotary connecting rod 83. The horizontal shaft 91 has a through hole 91a at the center and a through hole 91b at both ends. , 91c
Is provided. The rotary connecting rod 83 is passed through the through hole 91a, and the rotary connecting rod 83 is passed through the through hole 91a.
And the portion of the through hole 91a form a ball screw 97. That is, the screw shaft 97a of the ball screw 97 is provided on the outer peripheral portion of the rotary connecting rod 83 passed through the through hole 91a, and the nut portion 97b of the ball screw 97 is provided on the inner wall portion of the through hole 91a.

One ends of the movable eccentric weight control shafts 93 and 95 are rotatably arranged in the through holes 91b and 91c. However, the movable eccentric weight control shafts 93 and 95 are held so as not to move in the axial direction with respect to the horizontal shaft 91. In the shafts 51 and 51a, there is a shaft hole 1 which is a through hole extending in the axial direction.
07, 109 are provided, and the shaft holes 10 are provided in the central portions of the disks 65, 67 and 65a, 67a on the movable eccentric weight side.
Through holes 111, 113 and 111a, 113a having the same axis as 7, 109 are provided. The movable eccentric weight control shafts 93 and 95 are provided in the shaft holes 107 and 109 and the through hole 1.
11, 113 and 111a, 113a are arranged so as to be rotatable.

Then, the movable eccentric weight passing through the through hole 111 constitutes a change nut ball screw 99 with the control shaft 93 and the through hole 111, and the movable eccentric weight passing through the through hole 113. The control nut 93 and the through hole 113 form a change nut ball screw 101. Further, the portion of the movable eccentric weight control shaft 95 passed through the through hole 111a and the portion of the through hole 111a constitute the change nut ball screw 103, and the movable eccentric weight control shaft 95 passed through the through hole 113a. And the portion of the through hole 113a constitute the change nut ball screw 105.

That is, the change nut ball screw 99 is formed by the screw shaft 99a provided on the outer peripheral portion of the movable eccentric weight control shaft 93 passed through the through hole 111 and the nut portion 99b provided on the inner wall portion of the through hole 111. The change nut ball screw 101 is formed by the screw shaft 101a provided on the outer peripheral portion of the movable eccentric weight control shaft 93 passed through the through hole 113 and the nut portion 101b provided on the inner wall portion of the through hole 113. ing. Further, the change nut ball screw 103 is formed by the screw shaft 103a provided on the outer peripheral portion of the movable eccentric weight control shaft 95 passed through the through hole 111a and the nut portion 103b provided on the inner wall portion of the through hole 111a. Through hole 113
The change nut ball screw 105 is formed by the screw shaft 105a provided on the outer peripheral portion of the movable eccentric weight control shaft 95 passed through a and the nut portion 105b provided on the inner wall portion of the through hole 113a.

Since the vibrating section 40 has the phase angle changing section 48 thus constructed, the unbalanced weights 42, 4 are
When the servo motor 81 is driven and the rotary connecting rod 83 is rotationally driven during the rotation of 4, the rotation of the rotary connecting rod 83 is caused by the action of the ball screw 97 to move in the front-back direction of the horizontal shaft 91 (see FIG. 2).
It is converted into movement in the direction of arrow X in (a).

When the horizontal shaft 91 is thus moved in the front-rear direction, the movable eccentric weight control shafts 93, 95 move in the front-rear direction together with the horizontal shaft 91. The movement of the movable eccentric weight control shafts 93 and 95 in the front-rear direction is caused by the action of the change nut ball screws 99, 101, 103 and 105, and the shafts 51 and 51 of the movable eccentric weights 57, 59 and 57a, 59a.
Rotation with respect to each a (arrows Y and Y ′ shown in FIG. 2B)
Direction rotation).

That is, by driving the servo motor 81, the movable eccentric weight 5 with respect to the fixed eccentric weights 53 and 55 is moved.
7, 59 relative phase angles and fixed eccentric weights 53a, 5
The relative phase angle of the movable eccentric weights 57a and 59a with respect to 5a can be changed.

Therefore, in the vibrating section 40, the vibrating force generated by the unbalanced weights 42 and 44 can be changed by changing the relative phase angle in this way. However, the positional relationship between the fixed eccentric weights 53, 55 and the movable eccentric weights 57, 59 on the unbalanced weight 42 side, the fixed eccentric weights 53a, 55a and the movable eccentric weights 57a on the unbalanced weight 44 side, As shown in FIG. 2B, the positional relationship of 59a is such that the unbalanced weights 42,
It is configured to be line-symmetrical with respect to the vertical centerline Z between 44.

Therefore, when the unbalanced weights 42, 44 are rotated by the drive motor 46, only the vertical exciting force is generated as described above. On the other hand, the controller 120 is a device mainly composed of a microcomputer including a CPU, a ROM, a RAM, etc. The controller 120 also has a data input means (not shown) such as a keyboard and a mouse.

The controller 120 is connected to the drive motor 46 and the servomotor 81. In addition, the drive motor 46 includes a drive frequency of the drive motor 46 (the unbalanced weight 4
A speed sensor 115 for detecting the rotational frequency of 2,44) is attached.
5 is also connected to the controller 120.

The unbalanced weights 42 and 44 include the relative phase angles of the movable eccentric weights 57 and 59 and the fixed eccentric weights 53 and 55, the movable eccentric weights 57a and 59a, and the fixed eccentric weight 53a. , 55a are attached to the phase sensor 116 for detecting the relative phase angles, and the phase sensor 116 is also connected to the controller 120.

Further, below the unbalanced weights 42 and 44,
A load cell 117 for detecting an exciting force applied to the test track 10 from the exciting unit 40 by the rotation of the unbalanced weights 42 and 44 is provided, and the load cell 117 is also connected to the controller 120.

The map data shown in FIG. 3 is stored in a storage device such as a ROM in the controller 120. This map data shows the rotational frequencies of the unbalanced weights 42 and 44 and the movable eccentric weights 57, for keeping the vibration force generated by the unbalanced weights 42 and 44 rotated by the drive motor 46 constant. 59, the relative phase angle between the fixed eccentric weights 53, 55 (or the movable eccentric weights 57a, 59a and the fixed eccentric weights 53a, 55 having the same value as the relative phase angle).
The relative phase angle between a) is shown. In FIG. 3, the vibration force generated by the unbalanced weights 42 and 44 is 20
The relationships for holding at kN, 30 kN, 40 kN, and 50 kN are shown as examples.

The controller 120 uses the speed sensor 11
5, detection values from various detection means such as the phase sensor 116 and the load cell 117, the above map data, ROM, RA
Based on the data and program in M, the drive motor 46
And a control signal for driving these to the servo motor 81.

On the other hand, the data recording device 140 is configured as a device for recording data such as a hard disk device. In the data recording device 140, as described later,
Various data (the above-mentioned exciting force and the like) which are measured in the test by the train traveling load simulation exciter 1 of the present embodiment and input to the controller 120 are sequentially recorded.

Further, a displacement sensor 118 for detecting the amount of vertical displacement of the sleeper 12 is attached to the sleeper 12, and the detection data from the displacement sensor 118 is also sequentially recorded in the data recording device 140. To be done. It should be noted that a plurality of displacement sensors 118 may be prepared so that vertical displacement amounts at a plurality of locations of the sleeper 12 can be measured. In that case, the detection data recorded in the data recording device 140 may be processed as an average value or the like of the data obtained from the plurality of displacement sensors 118.

Next, in the train running load simulation vibrator 1 of the present embodiment configured as described above, the resonance frequency of the system on the ground side including the track 10, the member 20 supporting the track 10 and the roadbed 18. Frequency measurement processing executed by the controller 120 when measuring the speed, and acceleration test (durability test) that simulates the load acting on the test track when the train wheels pass on the test track 10 multiple times in a short time. The accelerated test process executed by the controller 120 when performing the above will be described with reference to the flowcharts shown in FIGS. 4 and 5.

First, the resonance frequency measuring process is started when the information for measuring the resonance frequency is input to the data input means. Then, in the resonance frequency measurement process, as shown in FIG. 4, first, a target value is set in S100 (S represents a step). In the resonance frequency measurement, the vibration generator 4
The rotational frequency of the unbalanced weights 42, 44 is changed (increased) to a predetermined maximum rotational frequency at a predetermined rotational speed increase / decrease rate while keeping the vertical vibration force applied to the test track 10 constant from 0. The resonance frequency of the system on the ground side is confirmed by observing the change in the vibration state of the system on the ground side (the amplitude of the vertical vibration of the sleeper 12 detected by the displacement sensor 118) during the change.

At S100, the exciting force applied as a constant value from the exciting unit 40 to the test track at the time of this measurement, and the maximum rotation frequency of the unbalanced weights 42 and 44 are set as target values using the data input means. Set. The rotation increasing / decreasing speed of the unbalanced weights 42, 44 at the time of this measurement is set to a predetermined value in advance. However, it goes without saying that this rotational speed increasing / decreasing speed may also be set in S100.

Next, in S110, the movable eccentric weights 57, 59, 57 are used by using the detection signal from the phase sensor 116.
a, 59a fixed eccentric weights 53, 55, 53a, 55a
The position (relative phase angle) of each is confirmed. Then, in S120, the position detected in S110, that is, the relative phase angle is 0, that is, the movable eccentric weights 57, 5
9, 57a, 59a and fixed eccentric weights 53, 55, 53
It is confirmed whether or not a and 55a are the smallest adjacent to each other.

When it is determined in S120 that the relative phase angle is not 0 (S120: NO), S
Move to 130. In S130, the relative phase angle is corrected to 0 by driving the servo motor 81, and then the process proceeds to S110 again. On the other hand, when it is determined in S120 that the relative phase angle is 0 (S12
0: YES), and the process proceeds to S140. In S140, the drive motor 46 is driven to start the rotation of the unbalanced weights 42 and 44. However, the unbalanced weight 42 that started to rotate,
The rotation increasing / decreasing speed of 44 is controlled to be the above-mentioned predetermined value.

Next, in S150, by using the detection signal from the load cell 117, the exciting force generated from the unbalanced weights 42, 44 is increased as the rotational frequency of the unbalanced weights 42, 44 increases. It is confirmed whether or not the number has increased to reach the set value set in S100.

The confirmation processing of S150 is performed by the unbalanced weights 42,
As long as the excitation force generated from 44 does not reach the set value (S150: NO), the process is repeated, but if it is confirmed (S150: YES), the process proceeds to S160. However, in the present embodiment, as described above, the movable eccentric weight 5
7, 59, 57a, 59a and fixed eccentric weights 53, 55,
Since the unbalanced weights 42 and 44 are rotationally started in a state where the relative phase angles of the respective 53a and 55a are minimized, the vibration force generated from the unbalanced weights 42 and 44 is Before the rotation frequencies of 42 and 44 increase significantly, the set values set in S100 can be easily reached.

That is, the state in which the relative phase angle is minimized in this way is a state in which the vibration force generated by the rotation of the unbalanced weights 42, 44 is maximized, so this relative phase Compared with the case where the angle is set to be larger than the minimum value, the exciting force rises to the set value in a short time.

The rotation frequency of the unbalanced weights 42 and 44 is S1.
After the shift to 60, the speed increases at a predetermined rotational speed increasing / decreasing speed. In S160, the rotational frequencies of the unbalanced weights 42 and 44 are detected based on the detection signal from the speed sensor 115. Then, in subsequent S170, based on the map data shown in FIG. 3 stored in the controller 120, the exciting force generated from the unbalanced weights 42, 44 is set to the exciting force having the set value set in S100. Movable eccentric weights 57, 59, 57a, 59a and fixed eccentric weights 5 required to maintain
The relative phase angle of each of 3, 55, 53a, 55a is S
Determined as corresponding to the rotational frequency detected at 160. Then, the phase angle changing unit 48 including the servo motor 81 is operated so as to obtain such a relative phase angle.

Next, in S180, various data at the current stage are recorded in the data recording device 140. The data to be recorded are the vibration force from the unbalanced weights 42 and 44 based on the detection signal from the load cell 117 and the rotation frequency of the unbalanced weights 42 and 44 based on the detection signal from the speed sensor 115. . In addition, at this time, the vertical displacement amount of the sleeper 12 based on the detection signal from the displacement sensor 118 is also synchronized with the data recording, and the data recording device 140 is also provided.
Recorded in.

In subsequent S190, the unbalanced weights 42 and 44 are
It is determined whether or not the rotation frequency of has reached the maximum rotation frequency set in S100. While the rotation frequency of the unbalanced weights 42 and 44 has not reached this maximum rotation frequency, a negative determination is made in S190 (S190: NO), S
The processing of 160 to S190 is repeatedly executed.

Therefore, S in the process which is repeatedly executed
Through the processing of 160 and S170, the unbalanced weights 42, 4
Even if the rotation frequency of 4 increases, the vibration force applied from the unbalanced weights 42 and 44 to the test track is held at the set value set in S100. Also, in this way, the unbalanced weights 42, 4
When the rotation frequency of 4 increases, the vibration force from the unbalanced weights 42, 44, the rotation frequency of the unbalanced weights 42, 44, and the vertical displacement amount of the sleeper 12 are increased through the processing of S180. Since the data is sequentially recorded in the data recording device 140, for example, looking at the relationship between the recorded rotational frequency and the vertical displacement amount, the rotational frequency at which the vertical displacement amount changes is resonated in the system on the ground side. It can be specified as a frequency.

On the other hand, when the rotation frequency of the unbalanced weights 42, 44 reaches the maximum rotation frequency set in S100, S
An affirmative decision is made at 190 (S190: YES), S20
Move to 0. In S200, a process of stopping the rotation of the unbalanced weights 42 and 44 is performed, and the resonance frequency measurement process is ended. Specifically, the phase angle changing unit 48 is operated so that the movable eccentric weights 57, 59, 57a, 59a and the fixed eccentric weights 53, 55, 53a, 55a face each other (that is, the unbalanced weight 42). , 44 is not generated, and the drive motor 46 is stopped to stop the rotation of the unbalanced weights 42, 44.

On the other hand, the accelerated test processing is started when the information for performing the accelerated test is input by the data input means.
In the accelerated test, the unbalanced weights 42, while keeping the vertical motive force applied to the test track from the oscillating unit 40 constant,
The rotation frequency of 44 is increased at a predetermined rotation increase / decrease speed to a test rotation frequency which is a predetermined high-speed rotation frequency. After that, while maintaining the rotation frequency of the unbalanced weights 42 and 44 at this test rotation frequency, the same exciting force as when the rotation frequency is increased is continuously added to the test track for a predetermined time (number of times), thereby shortening the time. In addition, the load acting on the test track is simulated when the train wheels pass on the test track multiple times.

In the train running load simulation vibrator 1, one vertical vibration force generated by the unbalanced weights 42 and 44 per one rotation (one cycle) corresponds to one passage of the train wheels. It is added to the test track as an entity. In the accelerated test, the speed sensor 115 determines the number of repetitions of the excitation force applied to the test track.
Is recorded by using the detected value from the displacement sensor 118, and the subsidence amount of the sleeper 12 during that time is recorded sequentially by using the detected value from the displacement sensor 118 to evaluate the durability of the system on the ground side. Can be grasped.

The first half of the accelerated test, that is, the vibrating section 40.
The process of increasing the rotation frequency of the unbalanced weights 42 and 44 to a predetermined high-speed rotation frequency at a predetermined rotation increase / decrease speed while keeping the vertical vibration force applied to the test track from The process is performed in the same manner as the process during the resonance frequency measurement process.

That is, in the acceleration test process flow shown in FIG.
The processing is performed in the same manner as each processing of S180. However, in S300, instead of the maximum rotation frequency of the unbalanced weights 42, 44, the unbalanced weights 42, 4 maintained after the rotation frequency is increased.
The test rotation frequency of 4 and the test time from the start to the end of the test (or the number of repetitions of the excitation force addition) are set. still,
The magnitude of the exciting force applied as a constant value from the exciting unit 40 during the test is set as in the case of S100. In addition, the rotational increase / decrease speed of the rotational frequency of the unbalanced weights 42 and 44 is preset to a predetermined value.
As in the case of S100, the setting may be made to be 0.

Further, in S380, instead of the rotational frequency of the unbalanced weights 42 and 44 which is the recording object in S180, the cumulative number of times of adding the exciting force is recorded in the data recording device 140. Be the target. The excitation force from the unbalanced weights 42 and 44 is to be recorded in the data recording device 140 as in the case of S180. Further, at this time, similarly, the displacement amount of the sleeper 12 is recorded in the data recording device 140 in synchronization with the data recording.

In S390 following S380, it is determined whether or not the rotation frequencies of the unbalanced weights 42 and 44 have reached the test rotation frequency set in S300. Unbalanced weight 4
While the rotation frequency of 2,44 has not reached this test rotation frequency, a negative determination is made in S390 (S390: N
O), S360 to S390 are repeatedly executed.

Therefore, S in the process which is repeatedly executed
Through the processes of 360 and S370 (the same processes as S160 and S170 above), the exciting force applied to the test track from the unbalanced weights 42 and 44 is S300 while the rotational frequency of the unbalanced weights 42 and 44 is increasing. It is held at the setting value set in.

When the rotation frequency of the unbalanced weights 42 and 44 reaches the test rotation frequency set in S300,
An affirmative decision is made in S390 (S390: YES), S4
00. In S400 and S410, the latter half of the accelerated test, that is, the same frequency as when the rotation frequency is increased for a predetermined time (number of times) while maintaining the rotation frequency of the unbalanced weights 42 and 44 at the test rotation frequency. Processing for continuing to add to the test track 10 is performed.

Specifically, first, in S400, the rotational frequencies of the unbalanced weights 42 and 44 are maintained at the test rotational frequency, and the movable eccentric weights 57, 59, 57a and 59a and the fixed eccentric weight 53, While maintaining the relative phase angle of each of 55, 53a, and 55a to the one when the affirmative determination is made in S390, the same data recording processing as in S380 is performed.

Then, in subsequent S410, it is determined whether or not the test time set in S300 has elapsed (or has reached the predetermined number of times of applying the exciting force). S300
While the test time set in step 4 has not elapsed, a negative determination is made in S410 (S410: NO), and the processes of S400 and S410 are repeatedly executed. However, when the test time has elapsed, an affirmative determination is made in S410 (S410: YES), Then, the process proceeds to next S420. Then, in S420, the same processing as in S200 described above is performed, and the acceleration test processing ends.

As described above, in this embodiment, even if the rotation frequencies of the unbalanced weights 42 and 44 change,
Unbalanced weights 42 and 44 detected by the speed sensor 115
Based on the rotation frequency of the unbalanced weights 42, 4 using the map data of FIG. 3 stored in the controller 120.
By determining and setting the relative phase angle of the eccentric weight of No. 4, the vibration force generated from the unbalanced weights 42, 44 can be kept constant (S160, S170).

Therefore, in the resonance frequency measuring process,
Accurate resonance of the system on the ground side by observing the change in the amount of vertical displacement of the sleeper 12 (vibration state of the system on the ground side) when changing the rotation frequency of the unbalanced weights 42, 44. The frequency can be properly confirmed.

In the accelerated test process, the rotation frequency of the unbalanced weights 42, 44 is set to the test rotation frequency not only after the rotation frequency of the unbalanced weights 42, 44 reaches the high-speed test rotation frequency. Even when increasing to 0, the exciting force applied to the test track can be maintained at the set value (the one set in S300) corresponding to the load when the train passes through the wheels through the processes of S360 and S370. Therefore, as compared with the conventional one, that is, the one in which the exciting force applied to the test track when the rotational frequency of the unbalanced weight is increased cannot be maintained at a constant value, the effect that the accelerated test can be performed accurately can be obtained. To be

On the other hand, also in this embodiment, the unbalanced weight 4
Unbalanced weight 4 for a predetermined time from the start of rotation of 2,44
Since the rotational frequencies of 2 and 44 are not sufficient, the target exciting force that is kept constant changes with the increase of the rotational frequency of the unbalanced weights 42 and 44 until it reaches the preset value set in S100 or S300. (Increased).

However, as described above, in this embodiment, the unbalanced weights 42 and 44 are rotated by minimizing the relative phase angle of the eccentric weights of the unbalanced weights 42 and 44 (S110).
~ S140 or S310 to S340), unbalanced weight 4
The exciting force generated by the rotation of 2,44 reaches a set value of a predetermined magnitude in a short time.

Therefore, in this embodiment, the unbalanced weights 42,
Control for keeping the vibration force generated from the unbalanced weights 42, 44 constant after the rotation of 44 starts (S160, S17).
0 or S360, S370) can be started in a relatively short time until the exciting force changes.

Further, in this embodiment, the fixed eccentric weights 53,
The relative phase angle of the movable eccentric weights 57 and 59 with respect to 55 and the relative phase angle of the movable eccentric weights 57a and 59a with respect to the fixed eccentric weights 53a and 55a are the movable eccentric weight control shafts 93 and 95 and the horizontal axis. It is set to correspond to the front-back direction position of 91, and is changed when the servomotor 81 is driven to move the movable eccentric weight control shafts 93 and 95 and the horizontal shaft 91 in the front-back direction.

That is, in the phase angle changing unit 48, the servo motor 81 needs to be driven only when changing the relative phase angle. Therefore, according to the phase angle changing unit 48, the servo motor 81 is not changed when the relative phase angle is changed. Can efficiently change and set the relative phase angle as much as the power consumption can be suppressed by stopping the servo motor 81.

In the above, the drive motor 46 corresponds to the drive machine, and the phase angle changing unit 48 corresponds to the phase angle changing means. Further, the movable eccentric weight control shafts 93 and 95 and the horizontal shaft 91 are intermediate members, and the change nut ball screws 99 and 101,
103 and 105 correspond to conversion means, and the servomotor 81 corresponds to intermediate member moving means. Further, the speed sensor 115 serves as a frequency detecting means, a storage device such as a ROM in the controller 120 serves as a storing means, and S160, S170, and S36.
0 and S370 are the phase angle setting means, and S110 to S14.
0 and S310 to S340 are the initial operation setting means, the load cell 117 is the vibrating force detecting means, and S150 and S35.
0 corresponds to the control starting means.

Although one embodiment of the present invention has been described above, the present invention is not limited to the above embodiment.
Various aspects can be adopted.

[Brief description of drawings]

FIG. 1 is a schematic diagram showing an overall configuration of a train traveling load simulation vibrator of an embodiment.

2A is a cross-sectional plan view showing a schematic configuration of an oscillating section of the train traveling load simulation oscillating machine of the embodiment, and FIG. 2B is an oscillating force generated by the oscillating section. It is explanatory drawing which shows a principle.

FIG. 3 is an explanatory diagram showing map data stored in a storage device in a controller of the train running load simulation vibrator of the embodiment.

FIG. 4 is a flowchart showing a resonance frequency measurement process executed by the controller of the train traveling load simulation vibrator of the embodiment.

FIG. 5 is a flowchart showing a promotion test process executed in the controller of the train traveling load simulation vibrator of the embodiment.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Train running load simulated vibrator, 10 ... Track, 12 ... Sleeper, 14 ... Rail fastening device, 16 ... Roadbed, 18 ... Roadbed, 20 ... Member, 30 ... Static load addition weight, 40 ... Vibration Section, 42, 44 ... unbalanced weight, 46 ... drive motor, 48
... Phase angle changing unit, 51, 51a ... Axis, 53, 55, 5
3a, 55a ... Fixed eccentric weights, 57, 59, 57a, 5
9a ... Movable eccentric weight, 81 ... Servo motor, 83 ... Rotating connecting rod, 85, 87 ... Universal joint, 89 ...
Transmission shaft, 91 ... Horizontal shaft, 93, 95 ... Movable eccentric weight control shaft, 97 ... Ball screw, 99, 101, 103, 105
… Change nut ball screw, 115… Speed sensor, 1
16 ... Phase sensor, 117 ... Load cell, 118 ... Displacement sensor, 120 ... Controller, 140 ... Data recording device

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Kiichi Masuda             3-4-5 Iwamotocho, Chiyoda-ku, Tokyo             Ceremony Company Tokyo Koki Factory F term (reference) 5D107 AA07 BB09 DD10 DD11 FF05                       FF07

Claims (6)

[Claims] 1. A test track provided for a test, a static load weight for applying a load corresponding to a static load of a train to the test track, and an exciting force applied to the test track. A train traveling load simulation oscillating machine, comprising: an oscillating unit having a variable drive frequency, wherein an oscillating unit added to the test track via the oscillating unit even if the drive frequency of the oscillating unit changes. A train running load simulation vibrator having a vibrating force holding means for holding a vibrating force constant. 2. An unbalanced weight having a shaft, a fixed eccentric weight fixed to the shaft, and a movable eccentric weight rotatably provided on the shaft, and the unbalanced weight. And a driving machine for rotating, and a phase angle changing means for changing a relative phase angle between the movable eccentric weight and the fixed eccentric weight when the unbalanced weight rotates, and is rotated by the driving machine. The unbalanced weight is configured to generate an oscillating force with respect to the test track, and the oscillating force holding unit is configured to generate the unbalanced weight even if a rotation frequency of the unbalanced weight changes. The relative phase angle between the movable eccentric weight and the fixed eccentric weight is adjusted by operating the phase angle changing means so that the vibration force generated by the weight becomes constant. The train running load simulation vibrator according to Item 1. 3. The exciting force holding means includes a frequency detecting means for detecting a rotating frequency of the unbalanced weight, and a rotating frequency for keeping the exciting force generated by the unbalanced weight constant. A storage unit that stores the relationship with the relative phase angle as map data, and a relative position corresponding to the rotation frequency from the rotation frequency detected by the frequency detection unit using the map data stored in the storage unit. 3. The train running load simulation vibrator according to claim 2, further comprising: a phase angle setting unit that determines a target phase angle and operates the phase angle changing unit so as to obtain the relative phase angle. 4. The relative phase angle between the movable eccentric weight and the fixed eccentric weight is set to a minimum value where the movable eccentric weight and the fixed eccentric weight are adjacent to each other, and then the relative phase is set. Initial operation setting means for starting rotation of the unbalanced weight through the driving machine while maintaining the angle, and detecting the magnitude of the vibration force generated by the unbalanced weight rotated by the driving machine And a vibration frequency of the unbalanced weight that has started to rotate,
When the exciting force detected by the exciting force detecting means reaches a predetermined value, the phase angle for performing the setting operation of the relative phase angle according to the rotation frequency of the unbalanced weight. 4. The train traveling load simulated vibration exciter according to claim 3, further comprising: a control start unit that starts control by the setting unit. 5. The phase angle changing means includes an intermediate member that is movable in the axial direction of a shaft that fixes the fixed eccentric weight, and a movement of the intermediate member in the axial direction of the movable eccentric weight. And a conversion means for converting the movable eccentric weight with respect to the shaft by moving the intermediate member in the axial direction. An intermediate member moving means for changing a relative phase angle with respect to a fixed eccentric weight, and a train traveling load simulated vibrator according to any one of claims 2 to 4. 6. A load applied to the test track when the train is running is simulated by using a vibration part configured to add a vibration frequency-variable vibration force to the test track provided for the test. A train traveling load simulated vibration method for applying a vibration force, wherein the vibration force applied to the test track via the vibration unit is kept constant even if the drive frequency of the vibration unit changes. A method for simulating vibration of a train running load, which comprises: