JPH10253483A - Wheel set dynamic balance measuring instrument - Google Patents

Abstract

PROBLEM TO BE SOLVED: To stop the rotation of a wheel set rapidly when measurement of the dynamic balance of the wheel set has been finished and to prevent damage to a power supply. SOLUTION: A pair of driving rollers 23 are pressed against the wheels 1 of a wheel set W and are driven and rotated by a driving motor M to rotate the wheel set W. Once the number of rotation of the wheel set W has reached a set value, the power supply to the driving motor M is shut off, the pressure applied to the wheel set W by the pair of driving rollers 23 is eliminated, and after measurement of dynamic pressure is finished, the pair of driving rollers 23 are rotated together as they are again pressed against the wheel set W, to apply two braking, i.e., regenerative braking by the driving motor M and braking by a powder brake Br, to the wheel set W via the driving rollers 23 to stop rotation of the wheel set W.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a wheel axle dynamic balance measuring machine for measuring the dynamic balance of a wheel axle used for a certain period mainly in a railway vehicle such as a Shinkansen.
More specifically, when stopping the rotation of the wheel axle, at least one of the two types of braking, the regenerative braking of the drive motor and the braking device, is applied to the wheel axle to stop the rotation of the wheel axle. It is related to a combined measuring device.

[0002]

2. Description of the Related Art Wheelsets constituting railway vehicles such as bullet trains are disassembled and inspected when used for a certain period to ensure safety. The wheel set will be described. As shown in FIG. 9, the wheel set W of the Shinkansen motor car has a wheel set 2 concentrically mounted on a pair of wheels 1 arranged at regular intervals. Each wheel 1 is composed of a tread portion 1a in contact with the rail 3 laid on the floor F, and a flange portion 1b provided inside each tread portion 1a. Axle 2
The two ends 2a of each of the wheels 1 are stepped and protrude outside the respective wheels 1. The outer diameter of each wheel 1 is about 910 mm, and the total weight of the wheel set W is about 2 tons. Reference numeral 4 denotes a gear box.

[0003] A conventional wheel set dynamic balance measuring machine R 'will be described. As shown in FIGS. 10 and 11, the wheel set W mounted on the transfer rail 51 is supported by the pair of vibrating tables 52 when the transfer rail 51 is lowered, and at the same time, the wheel set W Wheel 1 is pressed by a pair of drive rollers 53. In this state, the pair of drive rollers 53 is driven and rotated by the drive motor M, and the wheel shaft W rotates. The pair of drive rollers 53 are connected to a drive motor M via a belt transmission 54. The rotation speed of the wheel set W is equal to the set value (normally 4
(About 00 rpm), the power supply of the drive motor M is cut off and the pressing of the pair of drive rollers 53 is released, and the dynamic balance is measured. At this time, the wheel set W and the pair of drive rollers 53 are freely rotating. After measuring the dynamic balance, the pair of drive rollers 53 is pressed against the wheel 1 of the wheel axle W again, and the drive roller 53 is braked while the wheel axle W and the pair of drive rollers 53 are rotating together. The rotation of the wheel set W is stopped.

[0004] The state from the rotation of the wheel set W to the stop thereof will be described with reference to FIGS. 8 and 11. Wheel axis W, a pair of driving rollers 5 in its driving rotation range E ₁
3 while being pressed by the drive roller 5.
As the speed increases, the rotation speed of the wheel set W also increases. After driving the rotation time t _1, the rotation speed of the wheel axis W reaches the set value. Driving rotation time t ₁ is usually 2 to 3 minutes. Here, the power of the drive motor M that drives and rotates the pair of drive rollers 53 is shut off, and the pressing of the drive rollers 53 is temporarily released. In the measurement zone E ₂ in this state, balancing movement of the wheel axis W is measured. The measurement time t ₂ is usually 1
It is about 0 seconds. In the braking range E ₃ ′, the pair of drive rollers 53 is pressed against the wheel 1 of the wheel set W again. The regenerative braking is applied to the drive motor M to apply a brake to the pair of drive rollers 53. Then, the wheel shaft W is also braked via the drive roller 53. After the lapse of the braking time t ₃ ′, the rotation of the wheel set W stops. The state in which the rotation speed of the wheel set W is reduced and stopped after the dynamic balance measurement is indicated by a chain line. Braking time t ₃ 'is usually 3 to 4 minutes.

The regenerative braking by the drive motor M will be described with reference to FIG. As described above, the wheel set W
When the number of rotations reaches the set value, the power of the drive motor M is shut off and the pressing of the drive roller 53 is once released, so that the pair of drive rollers 53 freely rotates.
By controlling the inverter, which is the power supply of the drive motor M, to be able to perform regenerative braking, the drive motor M is freely rotated by inertia and becomes a generator. After the dynamic balance measurement, the pair of drive rollers 53 is pressed against the wheel 1 of the wheel set W again. If power generated by the driving motor M serving as a generator is supplied to a resistor or the like by a means (not shown) to apply a load, a rotor (not shown) constituting the driving motor M becomes difficult to rotate. That is, braking is applied to the drive motor M. This is because the force that the induced current receives from the magnetic field acts in a direction that hinders the rotation of the rotor. Further, the generated power (regenerated power) can be sent back to the primary power supply 56 via the control panel 55 to be used for other purposes. This is regenerative braking.

Since the GD ^{2 of the} wheel set W is extremely large, the rotation speed of the wheel set W in the measurement area E ₂ hardly changes.
In order to quickly stop the rotation of the wheel set W, a large regenerative braking is applied to the pair of drive rollers 53 in a direction opposite to the rotation of the wheel set W. However, when the regenerative braking is large, the generated regenerative power also increases. When the inverter 57 is used as the power source of the drive motor M, the regenerative power returned to the inverter 57 increases, and a problem such as an overcurrent trip of the inverter 57 occurs. Therefore, it is necessary to equip the inverter 57 with a resistor for braking. Further, the drive motor M generates heat, and the life of the motor M is shortened.

In order to avoid these problems, the regenerative braking may be reduced, but the braking time t ₃ ′ is prolonged and the working efficiency is reduced. In the case where the regenerative braking is not used and the rotation of the wheel set W is to be stopped naturally, the GD ^{2 of the} wheel set W is large, so that an extremely long time t ₃ ”is required in the braking range E ₃ ". This state is shown by a two-dot chain line in FIG.

[0008]

SUMMARY OF THE INVENTION In view of the above-mentioned problems, the present invention reduces the time required to stop the rotation of a wheelset in a wheelset dynamic balance measuring machine so that dynamic balance can be measured efficiently. That is the task.

[0009]

In order to solve this problem, the present invention employs a pair of vibrating tables arranged in a pit at intervals corresponding to the length of a wheel axle; A drive roller device configured to rotate a pair of drive rollers while pressing the pair of drive rollers against the wheels of the wheel set supported by the vibrating table, and the drive force of the drive motor to the drive roller. And a transmission device for transmitting power to the wheel set, and rotating the wheel set in a state where the drive roller is pressed against the wheel set supported by the pair of vibrating tables, measuring the dynamic balance thereof, and then braking the wheel set. In the wheel axle dynamic balance measuring machine configured to stop the rotation, a braking device for braking the wheel axle is provided, and after the dynamic balance of the wheel axle is measured, the regenerative braking and the braking by the drive motor are performed. Equipment Among two kinds of braking and the braking that is by being configured to apply braking by at least the braking system.

The wheel set transferred to the transfer rail is supported by a pair of vibrating tables, and the drive roller is driven and rotated by a drive motor to rotate the wheel set. When the rotation speed of the wheel set reaches a set value, the power supply of the drive motor is shut off,
The pressing of the driving roller is released once, and the dynamic balance of the wheel set is measured. After the dynamic balance measurement, the drive roller is pressed against the wheel of the wheel set again, and the wheel set and the drive roller are rotated together. In this state, by applying at least braking by the braking device, of the two types of braking, that is, regenerative braking by the driving motor and braking by the braking device, the wheel shaft is braked via the driving roller, and the rotation is performed. Stop.

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, the present invention will be described in more detail by way of examples. In describing the embodiments of the present invention,
The same reference numerals are given to the same portions as those described in the section of "Prior Art", and only the characteristic portions of the present invention will be described, avoiding redundant description. As shown in FIGS. 1 to 3, the frame 5 of the wheel axle dynamic balance measuring machine R is installed in a pit H of a predetermined depth provided on a floor surface F. A transfer rail device A and two drive roller devices B are disposed on the upper surface of a substantially central portion of the frame 5. Further, a pair of vibrating tables 6 are provided on both sides thereof.

First, the pair of vibrating tables 6 will be described. As shown in FIG. 2, a plurality of (four in this embodiment) punched holes 7a, 7b, 7c,
7d are formed in parallel. And the holes 7 at both ends
A notch 8 having a slight gap is formed between a, 7d and the upper part of each vibrating table 6. As a result, each of the vibration detectors 6 a to which a pair of support rollers 9 (described later) is attached above the respective vibrating tables 6 is connected to each of the vibrating tables 6 by the thin connecting portion 11. The reason why the thickness of each connecting portion 11 is reduced is that the rigidity of connection between each vibration detecting portion 6a and each vibration table 6 is reduced so that the vibration of the vibration detecting portion 6a can be easily detected. To do that.

As shown in FIGS. 1 and 2, a pair of support rollers 9 are supported in parallel at substantially the center of the upper part of each vibration detecting section 6a along the longitudinal direction of the frame 5. The wheel set W is supported by placing both ends 2a of the axle 2 of the wheel set W between these two pairs of support rollers 9. In the vicinity of the cut 8 of each vibration table 6, a vibration detection sensor 12 is attached. The vibration of the wheel set W, which is supported by the two pairs of support rollers 9 and rotates at high speed, is detected by the respective vibration detection sensors 12 via the respective vibration detection units 6a, so that the dynamic balance of the wheel set W is measured. You. Nearly at the center of the vibration detection unit 6a on one side,
A bracket 13 is attached to the outside of the vibrating table 6, and a rotation speed detection sensor 14 is attached to an upper portion of the bracket 13. The rotation speed of the wheel set W is detected by the rotation speed detection sensor 14. A substantially L-shaped regulating arm 15 is attached to one upper portion of each of the vibration detecting sections 6a. Each regulating arm 15 is rotatable about a fulcrum pin 16. Each regulation arm 15
At the positions corresponding to the two ends 2a of the axle 2 of the wheel set W, regulating members 15a are respectively attached. By rotating each regulating arm 15, each regulating member 15 a is attached to both ends 2 of the axle 2 supported by the two pairs of support rollers 9.
By arranging it with a small gap from “a”, movement of the rotating wheel set W in the vertical direction is restricted. In addition, since these restricting members 15a also come into contact with the stepped portions of both ends 2a of the axle 2, movement of the rotating wheel set W in the longitudinal direction is also restricted. In addition, a pair of shaking tables 6
Can be moved along the longitudinal direction of the frame 5. The position where the rotation speed detection sensor 14 is provided may be a side surface of the wheel 1.

Next, the transfer rail device A will be described. As shown in FIG. 1, the transfer rail device A includes a plate-shaped transfer rail 17 and elevating means for moving the transfer rail 17 up and down. On the upper surface of the transfer rail 17, a pair of flange portions 1 of the wheel set W is provided.
A pair of rail grooves 18 for guiding b are formed. The interval between the pair of rail grooves 18 corresponds to the interval between the flange portions 1b of the pair of wheels 1 of the wheel set W. As shown in FIG. 3, the pair of transfer rails 17 is separated from the pair of rails 3 laid on the floor F, and is connected via a slight gap. The upper surface of the transfer rail 17 in a horizontal state is substantially the same as the floor surface F. The wheel set W rolled on the pair of rails 3 laid on the floor surface F and carried in is guided by the pair of rail grooves 18 and placed at substantially the center of the transfer rail 17.

As shown in FIGS. 1 and 2, on the upper surface of the front part of the frame 5, two columns 19 are erected at predetermined intervals along the longitudinal direction of the frame 5. The transfer rail 17 is disposed above the two columns 19. On the lower surface of the front part of the transfer rail 17, two brackets 17 a are provided corresponding to the two columns 19, and these brackets 17 a rotate with each column 19 by each fulcrum pin 21. It is connected as possible. At the rear of the transfer rail 17, the distal end of a cylinder rod 22a of a hydraulic cylinder 22 mounted substantially at the center of the rear of the frame 5 is attached. This hydraulic cylinder 22
It is an example of the elevating means described above. The lower end of the hydraulic cylinder 22 is rotatably connected to the frame 5, and the tip of the cylinder rod 22 a of the hydraulic cylinder 22 is rotatably connected to the transfer rail 17. . Therefore, by operating the hydraulic cylinder 22, the transfer rail 17 is moved around the fulcrum pin 21 and the wheel set W
Can be rotated in a plane perpendicular to the axis of the.
As a result, the wheel set W mounted on the transfer rail 17 moves up and down. A plurality of proximity switches (not shown) are attached to the hydraulic cylinder 22, and by controlling the amount of protrusion of the cylinder rod 22a by the plurality of proximity switches, the transfer rail 17 can be moved at any angle. Can be stopped.

Next, the driving roller device B will be described. As shown in FIGS. 1, 3 and 4, the drive roller device B includes a pair of drive rollers 23 (described later) disposed above the frame 5 and on both sides of the transfer rail 17, and Pressing means for rotating the supporting roller base 24 to press the pair of driving rollers 23 against the tread portion 1a of the wheel 1 of the wheel set W is provided. Two brackets 25 are erected on the upper surface of the rear part of the frame 5 at predetermined intervals along the longitudinal direction of the frame 5. A roller base 24 is arranged above the frame 5. At the rear of the roller base 24, the aforementioned 2
The overhang portions 24a are provided at two locations corresponding to the brackets 25. As shown in FIG. 3, the upper portions of the two brackets 25 have a bifurcated shape, and the respective projecting portions 24a of the roller base 24 fit into the bifurcated portions. The bifurcated portions of the brackets 25 and the overhangs 24 a of the roller base 24 are connected by fulcrum pins 26. Therefore, the roller base 24 is rotatable about the fulcrum pin 26.

As shown in FIGS. 3 and 4, a front end portion of a cylinder rod 27a of a hydraulic cylinder 27 mounted at a substantially central portion of a front portion of the frame 5 is attached to a front portion of the roller base 24. I have. This hydraulic cylinder 27
It is an example of the above-mentioned pressing means. The lower end of the hydraulic cylinder 27 is rotatably connected to the frame 5, and the tip of the cylinder rod 27 a of the hydraulic cylinder 27 is rotatably connected to the roller base 24. Therefore, by operating the hydraulic cylinder 27, the roller base 24 can be rotated about the fulcrum pin 26 in a vertical plane perpendicular to the axis of the wheel shaft W. Brackets 28 are attached to both ends of the roller base 24 in the width direction of the frame 5. Roller plates 29 are arranged almost directly above these brackets 28, respectively. On the lower surface of each roller plate 29, an overhang portion 29a is provided. The upper part of each bracket 28 has a bifurcated shape, and the projection 29a of each roller plate 29 is fitted into the bifurcated portion. The forked part of each bracket 28 and the projecting part 29a of each roller plate 29
Are connected by a fulcrum pin 31. for that reason,
Each roller plate 29 can swing freely about a fulcrum pin 31.

As shown in FIG. 4, a stopper 32 for regulating the swing angle of each roller plate 29 is provided immediately below both ends of each roller plate 29 in the roller base 24 in the longitudinal direction. , Respectively. The stopper 32 has a configuration in which an adjusting bolt 34 is screwed into each of the female screw cylinders 33 fixed to the upper surface of the roller base 24. 2
9 can be adjusted.

[0019] Figure 1, as shown in FIGS. 3 and 4, the upper surface of the longitudinal ends of the rollers plate 29, a pair of bearings J ₁ is fixed. The pair of bearings J _1,
Each roller shaft S ₁ is fitted along the longitudinal direction of the frame 5. In each roller shaft S _1, in the longitudinal direction of the end located outside the Wajikudo balance measuring machine R, respectively are mounted a pair of drive rollers 23, the longitudinal end similarly positioned inwardly Each part has a pair of roller pulleys P
₁ is installed. These two pairs of drive rollers 23 are disposed from both ends of the transfer rail 17 with a slight gap therebetween. This is because the pair of drive rollers 23
Is pressed against the tread portions 1a of the pair of wheels 1 of the wheel set W mounted on the transfer rail 17.

Next, the transmission device D of the wheel axle dynamic balance measuring machine R of this embodiment will be described. As shown in FIGS. 3, 5, and 6, a drive motor M is provided on the upper surface of the frame 5 such that the axial direction thereof is along the longitudinal direction of the frame 5. Along the axis of the motor shaft 36 of the drive motor M, a powder brake B, which is an example of a braking device, is provided.
r is provided. In the roller base 24, a portion facing the drive motor M and the powder brake Br is cut out in advance, so that even if the roller base 24 rotates, the drive motor M and the powder brake Br do not interfere with each other.

[0021] As shown in FIGS. 3 and 5, the motor shaft 36 of the drive motor M, the motor pulley P ₂ is mounted. Then, approximately in the center of the roller base 24,
An intermediate shaft S ₂ is provided along the longitudinal direction of the frame 5. The intermediate shaft S ₂ is supported by two bearings J _2. At both ends of the intermediate shaft S ₂ 'have been wearing, the duplicate pulley P _1', respectively duplicate pulleys P ₁ each belt V ₁ between the pair of roller pulleys P ₁ and is hung . Also, one bearing in the intermediate shaft S ₂ J ₂
In the vicinity of the intermediate pulley P ₃ are mounted. And this intermediate pulley P ₃ is via two intermediate pulley P _4, P _5, the two belts V _2, V ₃ are connected to the motor pulley P _2. Activating the drive motor M, an intermediate shaft S ₂ is rotated in a predetermined direction through the respective pulleys P ₂ to P _5. Then, the pair of drive rollers 23 all rotate in the same direction via the respective pulleys P ₁ and P ₁ ′. As shown in FIG. 5, the axes of the two intermediate pulleys P ₄ and P ₅ are disposed so as to be the same as the axes of the fulcrum pins 26 which are the fulcrum of rotation of the roller base 24. . Therefore, the roller base 24
Is rotated, the center distance between the intermediate pulleys P ₃ and P ₄ does not change, so that the belt V ₂ does not expand or contract.

Next, the powder brake Br will be described. 3, as shown in FIGS. 6 and 7, the brake shaft 37 of the powder brake Br, the brake pulley P ₆ is mounted. Then, at a position corresponding to the powder brake Br in intermediate shaft S ₂ described above, the intermediate pulley P
₇ is installed. The intermediate pulley P ₇ is via two intermediate pulleys P _8, P _9, the two belts V _4, V ₅ is connected to the brake pulley P _6. Operating the powder brake Br, braking is applied to the rotation of the intermediate shaft S ₂ via the pulleys P ₆ to P _9. And each pulley P
The rotation of the pair of drive rollers 23 is braked via ₁ and P ₁ ′. As shown in FIG. 6, two intermediate pulleys P
₈ and P ₉ , as in the case of the drive motor M described above, each fulcrum pin 26 which is a rotation fulcrum of the roller base 24.
Are arranged so as to be the same as the axis of. for that reason,
Even if the roller base 24 is rotated, each intermediate pulley P ₇ , P
_{Since the} center-to-center distance of No. ₈ does not change, the belt V ₄ does not expand and contract.

The structure of the powder brake Br will be described. As shown in FIG. 7, a rod 39 protrudes from a substantially central portion inside a fixing bracket 38 constituting the powder brake Br, and a distal end of the rod 39 has a disc-shaped fixing member. 41 are attached. Inside the fixing bracket 38, the rod 39 and the fixing member 4
A rotating body 42 having a short cylindrical shape is fitted on the outside of 1. The above-described brake shaft 37 is provided so as to protrude substantially at the center of one end face of the rotating body 42. The brake shaft 37 and the rotating body 42 are rotatable with respect to the fixed bracket 38 via a bearing 43. The fixing member 4
A powder 44, which is a magnetic powder, is inserted into the working gap between the outer peripheral surface of the rotary member 1 and the outer peripheral surface of the rotating body 42 over the entire circumference. A coil 45 is buried in a portion of the outer peripheral surface of the fixed bracket 38 facing the outer peripheral surface of the rotating body 42 over the entire circumference. When this coil 45 is excited by a DC power supply 46, a magnetic flux 47 is generated, and
4 are coupled in a chain along the magnetic path. The fixed member 41 and the rotating body 42 are magnetically coupled through the magnetized and coupled powder 44, and the brake shaft 37 is braked. When the power supply from the DC power supply 46 is cut off, the magnetic flux 47 disappears, and the coupling state of the powder 44 is released. Powder 44
Is pressed against the inner wall surface of the rotating body 42 by the centrifugal force of the rotating body 42, and the braking of the brake shaft 37 is released. The powder brake Br is attached to the bracket 48,
It is fixed at a predetermined position on the upper surface of the roller base 24. In FIG. 7, reference numeral 49 denotes a seal for preventing the powder 44 from leaking.

This powder brake Br has the following advantages. (1) By changing the current value, the braking force can be changed proportionally and over a wide range.
(2) Continuous operation can be performed in a sliding state, and the torque in that state is always constant. (3) Since the magnetic flux is generated instantaneously, the rise time is extremely short. (4) Since it is a dry type, lubricating oil and the like are unnecessary, and maintenance is easy.

Next, the operation of the wheel axle dynamic balance measuring machine R of this embodiment will be described. As shown in FIG. 4, the wheel set W transferred on the upper surface of the transfer rail 17 is
Lowers, the both ends 2a of the axle 2 of the wheel set W
Are supported by the pair of vibrating tables 6 in a suspended state. The hydraulic cylinder 27 is operated to rotate the roller base 24 upward. The pair of drive rollers 23 abuts on the tread portion 1a of the wheel 1 of the wheel set W while swinging, and presses the wheel 1 with a predetermined force by the action of the hydraulic cylinder 27. In this state, the drive motor M is driven to drive and rotate the pair of drive rollers 23, thereby rotating the wheel shaft W. Since the power supply of the powder brake Br is cut off, the brake shaft 37 is freely rotating and the resistance is extremely small.

As shown in FIG. 8, the drive rotation time t ₁
When the number of revolutions of the wheel set W reaches the set value after elapse, the power of the drive motor M is shut off and the pair of drive rollers 2
3 is released. In this state, the dynamic balance of the wheel set W is measured. After the dynamic balance measurement, the pair of drive rollers 23 is pressed against the wheel 1 of the wheel set W again. As a result, the wheel set W and the pair of drive rollers 23 rotate together. The braking zone E _3, by energizing the powder brake Br with applying the regenerative braking to the drive motor M, brake the wheel axis W via the pair of drive rollers 23. That is, two brakes are applied to the wheel set W. The braking force by the powder brake Br, if substantially the same as the regenerative braking by the motor M, the braking time t ₃ becomes substantially half as compared with the conventional braking time t ₃ '(3 to 4 minutes Normal) . Since the powder brake Br can be continuously operated while the rotating body 42 is slid with respect to the fixed member 41 (see FIG. 7), the braking force by the powder brake Br can be changed according to the situation. Further, the ratio between the regenerative braking and the braking by the powder brake Br can be changed according to the situation. That is,
The braking force on the wheel set W can be finely controlled. Since the braking force by the powder brake Br can be changed only by changing the current value, the operation is very simple. Further, even when the inverter 57 is used as an operation power supply,
It does not adversely affect the inverter 57. Also, no special accessory equipment such as resistors is required. After braking time t ₃ has passed, the rotation of the wheel shaft W is stopped.

When the rotation of the wheel set W is stopped, the hydraulic cylinder 22 is operated to rotate the transfer rail 17 upward.
Since the rear end of the transfer rail 17 is rotated so as to be located slightly above the floor F, the wheel set W is carried out without power.

[0028] In this embodiment, incorporates a powder brake Br to the transmission device D, by braking the rotation of the intermediate shaft S _2, have been described as embodiments for braking rotation of the driving roller 23, shown in FIG. 9 as, respectively disposed powder brake Br for each roller axis S _1, it may be applied directly braking the roller shaft S _1. In FIG. 9, reference numeral 50 is a coupling for connecting the brake shaft 37 of the extension portion and the powder brake Br roller shaft S _1. Further, in the present embodiment, the powder brake has been described as an example of the braking device. However, the braking device may be other than the powder brake (for example, a disc brake) as long as it can be electrically controlled.

[0029]

According to the wheel balance dynamic balance measuring device of the present invention, when the rotation of the wheel set is stopped after the dynamic balance measurement of the wheel set is completed,
Two brakes, that is, regenerative braking by a driving motor and braking by a braking device, can be applied to the wheel set via a driving roller. Therefore, the stop time of the wheelset can be shortened,
The measuring operation can be performed efficiently. During the dynamic balance measurement, since the input shaft of the braking device is freely rotating, its resistance is extremely small, and the measurement accuracy is almost the same as the conventional case. Further, since it is not necessary to apply a large regenerative braking, even when the inverter is used as the power supply of the drive motor, the inverter is prevented from being damaged. Also, there is no need to equip the inverter with special accessory equipment.

[Brief description of the drawings]

FIG. 1 is a front view of a wheel set dynamic balance measuring machine R according to the present invention.

FIG. 2 is a side view of the same.

FIG. 3 is a plan view showing a drive system.

FIG. 4 is a partially cutaway view taken in the direction of arrow X in FIG. 1;

FIG. 5 is a side view of the transmission D on the driving side.

FIG. 6 is a side view of the transmission D on the braking side.

FIG. 7 is a side sectional view of the powder brake Br.

FIG. 8 is a graph showing a change in the rotation speed of the wheel set W with respect to an elapsed time.

9 is an embodiment in which connects the brake shaft 37 of the roller shaft S ₁ and the powder brake Br directly.

FIG. 10 is a front view of a conventional wheel set dynamic balance measuring machine R ′.

FIG. 11 is a schematic diagram of the electric circuit.

[Explanation of symbols]

 B: Drive roller device Br: Powder brake (braking device) D: Transmission device H: Pit M: Drive motor R: Wheel axle dynamic balance measuring machine W: Wheel axle 1: Wheel 6: Vibration table 23: Drive roller

Claims (3)

[Claims] 1. A pair of driving rollers are provided for a pair of vibrating tables disposed in a pit at intervals corresponding to the length of a wheel set, and a wheel of a wheel set supported by the pair of vibrating tables. A drive roller device configured to rotate the wheelset by rotating in a pressed state; and a transmission device transmitting the driving force of a drive motor to the drive roller, the wheelset supported by the pair of vibration tables A wheel set dynamic balance measuring machine configured to rotate the wheel set while pressing the drive roller against the wheel, measure its dynamic balance, and then apply braking to the wheel set to stop its rotation. A braking device for applying a brake is provided, and after the dynamic balance measurement of the wheel set, of two types of braking, that is, regenerative braking by the drive motor and braking by the braking device,
A wheel axle dynamic balance measuring machine wherein at least braking is applied by a braking device. 2. The wheel set dynamic balance measuring machine according to claim 1, wherein the braking device is incorporated in the transmission. 3. The wheel axle dynamic balance measuring machine according to claim 1, wherein said braking device is a powder brake.