JPS6317169A - Axle load balancing device for 3-axle bogie - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed Description of the Invention] [Industrial Application Field] The present invention relates to an axle load balancing device for a three-axle bogie for a railway vehicle,
The present invention relates to a structure of a balance beam suitable for balancing axle loads and preventing pitching.

[Conventional technology]

This type of conventional device is known, for example, from Japanese Patent Application Laid-open No. 53-3436.
As described in Publication No. 4, the balancing device is a combination of a balance beam and a link, and the purpose is to facilitate the lateral movement of the intermediate shaft, and no consideration is given to the combined length of the balance beam. Also, to prevent pitching, for example,
It was necessary to use a pitching prevention device for the front and rear axle boxes as described in Japanese Patent No. 10607.

[Problem that the invention seeks to solve]

In the above conventional technique, the length of the balance beam is such that the horizontal length of the middle balance beam is La so that the link is vertical as shown in FIG. Therefore, when the balance beam is tilted as shown in the line at the start of the bogie, the horizontal dimension L4 of the vertical link connection portion becomes larger than L8, and the angle between the balance beam and the tension link becomes larger at 07 than at 08. Therefore, there was a problem in that the forces of the front and rear balance beams became unbalanced, and the axle loads on the three axes fluctuated, reducing adhesive performance.

The purpose of the present invention is to balance the force of the balance beam even when the balance beam tilts during startup, eliminate fluctuations in axle load, improve adhesive performance, and eliminate the need for a pitching prevention device. The object of the present invention is to provide a heavy balancing device.

[Means for solving problems]

The above purpose is to configure the vertical links that connect the front and rear balance beams and the middle balance beam to form a figure 7 shape, so that even if the balance beam is tilted during startup, it will still be seen as a balance beam. At the same time, the angles of the links are made to be the same at the front and rear, and at the same time, a horizontal component of force is always applied to the front and rear axle boxes, and the upper and lower vibrations of the bogie frame are distributed by the frictional force generated between the axle box and the bogie frame. This action prevents pitching.

[Effect]

The angles of the next link connecting the front and rear balance beams and the intermediate balance beam should be the same, so that when the starting balance beam is tilted, the next link will be parallel to the front and rear balance beams. Become. Therefore, the rotation angles of the front and rear balance beams are the same, so there is no unbalance of force.Also, since the next link is connected at an inclined angle to the balance beam, it supports the vehicle body acting perpendicularly to the balance beam. Since a horizontal component of force is generated, the front and rear axle boxes are pressed against the bogie frame by this horizontal component.
: Generates a frictional force that suppresses movement, so pitching of the bogie frame can be prevented.

〔Example〕

An embodiment of the present invention will be described below with reference to FIGS. 1 to 3.

A 3-axle moving bogie uses a counterbalance beam to balance the axle load.
As shown in FIG. 1, a driving electric motor 6a.

Axle boxes 7a, 7b, 7c with built-in rolling bearings are attached to the shaft ends of the moving shafts 5a+ 5b, 5c integral with the moving shafts 6b, 6c, and the bogie frame 4 engaged with the axle boxes 7a, 7b, 7c. They are placed at equal intervals.

One end of the counterbalance beams 9a, 9b is easily rotatably engaged with the lower part of the axle boxes 7a, 7c by pins 13a, 13c.
The center of the balance beam 10 is rotatably engaged with the lower part of the intermediate axle box i7b by a pin 13b. Balance beam 9a,
9b, and both ends of the counterbalance beam 10 are vertical links ll.
a, llb, are easily rotatably connected by pins 14a, 14b, 15a, and 15b. Axial springs 12a, '1 are placed above the balance beams 9a, 9b at positions where the longitudinal dimensions are 2:1 so that the loads borne by the moving shafts 5a, 5b, 5c are the same.
2b are arranged respectively. Axle boxes 7a, 7b, 7c
The bogie frame 4 that engages with is easily engaged in vertical movement,
0 bogie frame 4 supported by shaft springs 12a and 12b
Pillow springs 3a and 3b are arranged above to support the vehicle body 1. The center pin 2 fixed to the vehicle body 1 is
It is engaged with 68 of the truck frame for easy vertical movement. Further, as shown in the mechanical diagram of FIG. 2, the horizontal length Ll of the balance beam 10 is longer than the dimension L2 between the ends of the balance beams 9a and 9b, and the S links 13a and 13b are 9a, 9b
, a three-axle bogie with six or more configurations connected at an angle in a V-shape to IQ, the weight of the car body 1 is transferred to the pillow springs 3a, 3.
b, and is received by the bogie frame 4 through the bogie frame 4, and the shaft spring 12 is
a, 12b to the balance springs 9a, 9b, 10, and via the axle boxes 7a, 7b, 7c, respectively, to the dynamic shaft 5a.

It acts equally on 5b and 5c. This shaft spring 12a.

When a load is applied to 12b, horizontal component forces of Ws and W4 shown in FIG. 2 act on the balance beams 9a, 9b, and 10 due to the action of links 13a and 13b.
W4 is as follows.

Wa=V/5tan<P work Wa=Wztar+(Il s Since the loads acting on the shaft springs 12a and 12b are equal, W 1 =Wz, and Wa=W number. Therefore, the load acting on the intermediate shaft box 7b The horizontal component force is the same in the front and rear, and the axle box 7a
, 7c are pressed against the bogie frame 4 by Ws and W4, respectively. When the bogie frame 4 vibrates vertically due to this pressing force, a frictional force is generated between the axle boxes 7a, 7c and the bogie frame 4, and this frictional force acts to damp pitching vibrations of the bogie frame 4.

Further, the driving force that propels the vehicle body 1 at the time of startup is the moving shaft 5a.

5b, 5c are applied to the bogie frame 4 via the shafts WJ7a, 7b, 7c, and act on the vehicle body center pin 2 engaged with the two bogie frames 4 to propel the vehicle. At startup, a rotational moment acts on the bogie frame 4 due to the propulsive force, and as shown in FIG. 3, the bogie frame 4 is at an angle of θ! This truck frame 4 tilts at an angle of
The balance beams 9a and 9b each have an angle θ due to the inclination of
2. The balance beams 9a, 9b are tilted at θ3, and the dimension L2 between the ends thereof widens to L2'. The dimension Ll of the balance beam 10 is.

Make it equal to the dimension of L2' when it is tilted. Therefore, the angles θ2 and 08 are equal, and the throat links 13a, 1
3b and 9a are parallel and balanced.

The angle 0 of 9b, θ5, is also equal, so W1=Wx
, WIS=Ws, the horizontal forces are also equal, and the driving wheels 5B, 5b
, 5c, there is no fluctuation in the acting weight, and the weight acting on the driving wheels can be fully utilized for adhesion.

As described above, according to the present invention, not only the adhesive performance is improved, but also the frictional force that suppresses the vibration of the bogie frame is generated by the component force acting on the axle box. It has the effect of improving performance.

〔Effect of the invention〕

According to the present invention, a balanced load balance is maintained even when the bogie frame is tilted, and there is no fluctuation in the shape of the driving wheels, improving adhesion performance. Since frictional force is generated and a vibration damping effect is performed on one bogie frame, there is an effect that a separate pitching prevention device for N is not required.

[Brief explanation of drawings]

FIG. 1 is a side view of a three-axis moving truck according to an embodiment of the present invention, FIG. 2 is a side view showing the mechanism shown in FIG. 1, and FIG. 3 is a side view showing the mechanism shown in FIG. 1 at startup. FIG. 4 is a side view showing the mechanism of a conventional three-axis moving truck. 1... Vehicle body, 2... Vehicle body center pin, 3a, 3b...
・Pillow spring, 4...Bolly frame, 5 a, 5 b,
5 c-driving wheel, 6a. 6b, 6cm electric motor, 7a, 7b, 7c
=・Axle box, 8... Bogie frame hole, 9a, 9b... Balance beam, 10... Balance beam, 11 a, l l b
- Vertical link, 12a. 12 b... Axial spring, 13 a, 13 b
, 13 c-pin. 14a, 14b...pin, 15a, 15
b--pin.

Claims (1)

[Claims] In a 3-axle bogie for a railway vehicle equipped with a balancing device that balances the axle load on the 3 axles using a 1-3 split balancing beam,
The vertical link connecting the front and rear balance beams and the middle balance beam is V-shaped so that the horizontal length of the middle balance beam is longer than the end of the front and rear balance beams, so that the bogie frame is tilted. At the same time, the axle load is constantly balanced, and at the same time, the horizontal force generated when supporting the weight of the vehicle is applied to the front and rear axle boxes by the inclination angle of the vertical link connecting this balance beam, thereby suppressing the vertical vibration of the bogie frame. An axle load balancing device for a three-axle truck, characterized in that a balancing beam mechanism is configured to generate a frictional force that prevents friction.