JP3972592B2 - Damping structure of traction device in railway vehicle - Google Patents

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a damping structure for a traction device in a railway vehicle.
[0002]
[Prior art]
In a railway vehicle, the driving force of a driving motor mounted and held on a carriage is output to a driving shaft and transmitted to a driven shaft connected to the driving shaft via a gear coupling device, and then to the axle and wheels via a gear device. The trolley and the vehicle body via a traction device having a center pin whose upper part is coupled to the vehicle body, and a link having each end coupled to the trolley frame and the lower part of the central pin via rubber bushes, respectively Is known in the art to pull the vehicle body.
[0003]
FIG. 3 shows a traction device to which the embodiment of the present invention is applied and its peripheral part. In FIG. 3, 12 is a center pin, and the upper part is coupled to the vehicle body.
Reference numeral 26 denotes a link (one link) provided in a state extending in the front-rear direction so as to connect the cross beam 11B and the center pin 12, and one end of the link is coupled to the lower portion of the center pin 12 via the rubber bush 28. Also, the other end is coupled to the horizontal beam 11B of the carriage via the rubber bush 28.
[0004]
As a gear coupling device for connecting the drive shaft and the driven shaft in an integrally rotated state, one having an internal gear and an external gear is used.
Specifically, (a) an internal gear having internal teeth formed on the inner peripheral side of a cylindrical housing, and (b) a drive shaft and a follower that have arc-shaped external teeth and are tiltably engaged with the internal teeth. A gear coupling device is used that includes a first and a second pair of external gears fixed to a shaft in an integrally rotated state.
[0005]
The gear coupling device of this embodiment absorbs the relative swing even when the carriage is displaced up and down due to increase or decrease of passengers and the drive shaft and the driven shaft swing relative to it. The driving force can be reliably transmitted from the drive shaft to the driven shaft.
[0006]
[Problems to be solved by the invention]
On the other hand, in the case of this gear coupling device, a relative shift in the axial center position between the internal gear and the external gear occurs due to backlash in the gear, that is, play between the tooth surfaces. Has become a cause of generation of high-frequency (100 to 200 Hz) vibration noise.
[0007]
That is, the vibration generated in the gear coupling device is transmitted from the lower part of the vehicle body to the floor of the passenger compartment via the traction device having the cross beam 11B, the link 26 and the center pin 12 shown in FIG. This produces a roaring sound such as “goo” in the passenger compartment.
[0008]
The above is a major cause of the roaring noise in the passenger compartment, but in addition to this, various other vibrations in the drive motor, gear device, and gear coupling device contribute to the rotational speed of the drive motor. This occurs in response to changes, which are transmitted to the vehicle body and cause vibration noise in the passenger compartment.
[0009]
[Means for Solving the Problems]
The vibration damping structure for a traction device in a railway vehicle according to the present invention has been devised to solve such a problem.
Thus, according to the first aspect of the present invention, there is provided a traction device having a center pin whose upper part is coupled to the vehicle body, and each end having a carriage frame and a link coupled to the lower part of the center pin via a rubber bush. In the railway vehicle that connects the carriage and the vehicle body and pulls the vehicle body, the rigid contact portion and the corresponding portion are provided in a floating state at a predetermined position of the towing device, and are applicable at the time of vibration. A collision mass that collides with the ridge, a gap for moving the collision mass in the vibration direction, and a contact between at least one of the contact portion and the collision mass. The rubber bush has a rigid outer cylinder member and a central inner member, and a rubber elastic body sandwiched between them. And the inner member forms the contact portion. The vibration damping device is incorporated in the inner member by the collision mass being movably accommodated in a floating chamber in the housing, and the inner member has a shaft at the center. A hollow structure having a cavity penetrating in the direction, and a large-diameter portion at both ends, a small-diameter portion therebetween, and a step between the large-diameter portion and the small-diameter portion in the void. The idler chamber having an attached portion is provided, and the idler chamber has a circular cross-section and a longitudinal shape in the axial direction, a relatively large-diameter head at both ends, and a relatively small-diameter barrel between them. The collision mass having a free movement is accommodated movably, and the contact surface of at least one of the large-diameter portions at both ends of the floating chamber and the pair of head outer peripheral surfaces of the collision mass is on the contact surface An elastic body is formed, and the outer peripheral surface of the head and the front of the collision mass The clearance between the inner diameter surface of the large-diameter portion in the idle chamber is made smaller than the clearance between the outer peripheral surface of the trunk portion in the collision mass and the inner peripheral surface of the small-diameter portion in the idle chamber. The collision mass is movable in a direction perpendicular to the axis with respect to the inner member .
[0010]
[Operation and effect of the invention]
As described above, the present invention provides a rigid contact portion, a collision mass provided in a floating state with respect to the contact portion, a gap formed therebetween, and a contact portion and a predetermined portion of the traction device. A vibration damping device having an elastic body interposed between the collision mass and the collision mass is attached to suppress the vibration of the traction device.
[0011]
This damping device works as follows.
In other words, in the case of this vibration damping device, when the mounting position of the vibration damping device in the traction device starts to vibrate, the contact portion is displaced integrally with the vibration portion, and starts to vibrate in synchronization therewith.
On the other hand, since the collision mass is in a floating state in the vibration direction with respect to the contact portion, that is, freely moves independently in the same direction with respect to the contact portion, it collides with the contact portion when the contact portion vibrates, It acts so as to cancel the vibration, that is, the vibration at the mounting portion (vibrating portion) of the vibration damping device in the traction device.
[0012]
At this time, the kinetic energy is given to the collision mass colliding with the hitting part in the opposite direction (therefore, part of the vibration energy of the hitting part is absorbed as the kinetic energy of the collision mass), and the collision mass is in the reverse direction. Do exercise.
Then, it collides again with the contact surface at a position opposite to the first contact surface, and then acts again to cancel the vibration of the contact portion, that is, the traction device.
[0013]
After that, the collision mass repeats the same movement in the opposite phase or different phase from the hit part, absorbs the vibration energy of the traction device at each collision, and converts it into its own kinetic energy and vibrates. Continue to collide with the department. As a result of the energy absorption, the vibration energy of the traction device is attenuated and the vibration is effectively suppressed.
[0014]
If both the contact portion and the collision mass are made of a rigid body, a large abnormal noise (collision noise) is generated at the time of collision.
However, in the vibration damping device according to the present invention, since an elastic body such as rubber or resin is formed on at least one contact surface of the contact portion and the collision mass, there is no problem that a large abnormal noise is generated at the time of the collision, and the collision The vibration damping of the traction device is promoted by the vibration control effect caused by the sliding friction and the viscous behavior of the elastic body.
[0015]
It is also conceivable to attach a dynamic damper to the vibration part of the traction device to suppress vibration.
In this dynamic damper, a damper mass is added to a vibration part via a spring, and the natural frequency of the additional vibration system composed of the damper mass and the spring is changed to the natural frequency of the main vibration system (the natural frequency of the vibration part). ) Can be damped by reducing the resonance magnification of the vibration part.
[0016]
However, the vibration suppression by the dynamic damper only exhibits an effect on the vibration of a single resonance frequency, and cannot effectively prevent the resonance of other frequencies. That is, it is not effective for resonance at a plurality of frequencies.
In addition, in the case of a dynamic damper, there is a problem that another new resonance occurs before and after the resonance point.
In addition, when a rubber elastic body is used as the spring, the spring constant of the rubber elastic body changes depending on the temperature, so that the temperature dependence of the vibration damping characteristic is high, and the vibration damping efficiency decreases at high and low temperatures.
[0017]
Furthermore, a dynamic damper requires a large mass as a damper mass (necessary a mass of about 10% of the vibration part), which increases the weight of the entire device, requires a large installation space, and can be further damped. Various problems are inherent in that the direction is fixed and does not work effectively against multi-directional vibrations.
[0018]
However, in the vibration damping device according to the present invention, the collision mass is provided so as to be able to move independently, and is moved in a phase opposite to or different from that of the vibration damping object, so that vibration energy is absorbed and attenuated. There is no particular problem, vibration can be suppressed over a wide frequency range, and the collision direction can be easily and easily set in multiple directions. It exhibits low vibration and exhibits a good damping effect over a wide temperature range from high to low.
In addition, the required mass of the collision mass is light and sufficient (about 5% of the mass of the vibration part is sufficient), the required space of the entire device is small and compact, and it can be easily attached to the vibration part. Has features.
[0019]
FIG. 1 schematically shows an example of a vibration damping device according to the present invention in comparison with a dynamic damper. In FIG. 1, 1 represents the vibration damping device and 2 represents a dynamic damper.
Reference numeral 3 denotes a collision mass in the vibration damping device 1, 4 denotes an elastic body formed on the outer peripheral surface of the collision mass 3, that is, a contact surface, 5 denotes a housing forming a contact portion, and 6 denotes a damper mass in the dynamic damper 2. , 7 indicates a spring (rubber), and 8 indicates a vibrating portion.
[0020]
FIG. 1B shows the vibration damping effect when the vibration damping device 1 is mounted on the vibration unit 8 in comparison with the case where the dynamic damper 2 is mounted and the case where the dynamic damper 2 is not mounted.
However, in FIG. 1B, c shows a case where the vibration damping device 1 is attached, b shows a case where the dynamic damper 2 is attached, and a shows a case where none of them is attached.
As can be seen from the vibration damping characteristics of FIG. 1B, when the dynamic damper 2 of FIGS. 1A and 1A is mounted, resonance is suppressed in a specific frequency region (here, the region on the high frequency side). Although it is possible, another new resonance is generated before and after the resonance point, and it is not effective for the resonance on the low frequency side, but the vibration damping device 1 of FIGS. In this case, the effect is exhibited both on the high frequency side and on the low frequency side, and another phenomenon that another new resonance occurs before and after the resonance point does not occur.
[0021]
As is clear from the above, by attaching the vibration damping device according to the present invention to the traction device, the vibration can be suppressed satisfactorily, and the vibration noise of the traction device having a frequency of 100 to 200 Hz can be satisfactorily reduced.
[0022]
In the present invention, the rigid contact portion can be made of a metal such as iron or aluminum alloy, a hard resin, or other hard material.
The collision mass itself can be formed of an elastic body such as rubber or resin. However, in this case, it is desirable to configure it as high specific gravity rubber, high specific gravity resin or the like in which metal powder or the like is mixed.
[0023]
Moreover, this collision mass can also be made into a foam, when this is comprised with an elastic body.
However, it is desirable that the collision mass is made of a metal such as iron, an aluminum alloy, or lead in order to achieve more effective vibration suppression.
[0024]
In the present invention, the gap has an important meaning in causing the collision mass to collide most effectively with the hit portion. In this sense, the gap is preferably 0.05 to 2.0 mm, and more preferably The range is 0.2 to 1.0 mm.
[0025]
In the present invention, rubber or resin can be used as the elastic body.
Here, various rubbers such as diene rubbers such as NR, SBR and BR, EPDM rubbers, urethane rubbers, and silicon rubbers can be used as the rubber.
Examples of the resin include thermoplastic resins such as polypropylene and polyamide, polyolefin, urethane, polyester-based thermoplastic elastomers, and the like.
[0026]
In the present invention, the vibration damping device is provided with a rigid housing that forms an idle chamber therein, and the collision mass is movably accommodated in the idle chamber .
[0027]
In the present invention, should be incorporated within the inner rigid member is centrally definitive in Gomubusshi Interview in traction device the vibration damping device.
In this way, it is not necessary to prepare a separate space for assembling the vibration damping device, and at the same time the rubber bushing is assembled, a vibration damping function by the vibration damping device is added to the traction device. There is an advantage that it is not necessary to install a vibration damping device separately after assembling the link.
[0028]
Further, in this case, the inner member has a hollow structure, whereby a housing is constituted by the inner member, and the collision mass is movably accommodated in the idle chamber in the housing .
In this case, since the inner member itself also serves as the housing in the vibration damping device, there is an advantage that the number of necessary members can be reduced .
[0029]
【Example】
Next, embodiments of the present invention will be described in detail with reference to the drawings.
In FIG. 2, 10 is a truck in a railway vehicle, and 11 is a truck frame. The carriage frame 11 has side beams 11A and lateral beams 11B.
Reference numeral 12 denotes a center pin, and reference numeral 14 denotes a drive motor attached and fixed to the cart 10.
Reference numeral 16 denotes an axle, and 18 denotes a wheel. These wheels 18 rotate on the rail.
[0030]
The axle 16 is operatively connected to the drive motor 14 via a gear coupling device 20 and a gear device 22, and a driving force from the drive motor 14 is transmitted via the gear coupling device 20 and the gear device 22. It is transmitted to the axle 16 and eventually to the wheel 18.
[0031]
As shown in FIG. 3, the center pin 12 has an upper portion fixed to the vehicle body frame in the vehicle body 24, and a lower portion through the link (one link) 26 and the rubber bush 28. Is connected to the horizontal beam 11B in the bogie frame 11.
Here, the link 26 has cylindrical holding cylinders 30 at both ends.
[0032]
On the other hand, the rubber bush 28 has a rigid outer cylinder fitting (outer cylinder member) 32 and an inner fitting (inner member) 34 as shown in FIGS. 4 and 5, and a cylindrical shape between them. The rubber elastic body 36 is vulcanized and bonded.
Thus, in the rubber bush 28, the outer cylinder fitting 32 is press-fitted into the holding cylinder 30 at both ends of the link 26, and the holding cylinder 30 is fixed to the link 26.
Of the pair of rubber bushes 28 that are press-fitted and fixed to both ends of the link 26, one has the lower portion of the center pin 12 coupled to the inner fitting 34, and the other has the transverse beam 11 </ b> B coupled to the inner fitting 34.
In FIG. 3, reference numeral 38 denotes a floor board provided on the vehicle body frame, and reference numeral 40 denotes a pillow beam.
[0033]
The inner metal fitting 34 has a hollow structure with a space that penetrates the inner metal member 34 in the axial direction, and a metal collision mass that forms the main element of the vibration damping device 42 of this example in the space. 44 is incorporated.
Specifically, in this example, an axially intermediate portion of the inner metal fitting 34 is configured as a housing 46 in the vibration damping device 42, and an idler chamber 48 is formed inside thereof. A collision mass 44 is accommodated in the floating chamber 48 so as to be movable in the direction perpendicular to the axis.
[0034]
Here, the collision mass 44 has a circular cross section and a longitudinal shape in the axial direction.
The collision mass 44 has a relatively large-diameter head 50 at both ends, and a relatively small-diameter barrel 52 therebetween.
Here, one of the heads 50 is formed separately from the body 52 and is fastened in the axial direction by bolts 54.
A layer of a rubber elastic body 56 is attached to each outer peripheral surface of the pair of heads 50 by vulcanization adhesion.
[0035]
On the other hand, the idle chamber 48 is formed in a shape corresponding to the collision mass 44.
Specifically, the idle chamber 48 has a large diameter portion 58 at both ends and a small diameter portion 60 between them. In the stepped portion 62 between the large diameter portion 58 and the small diameter portion 60, the collision mass 44 accommodated in the idle chamber 48 is prevented from coming off in the axial direction.
[0036]
Here, a gap between the outer peripheral surface of the head 50 in the collision mass 44 and the inner peripheral surface of the large-diameter portion 58 in the floating chamber 60, specifically, a layer of the rubber elastic body 56 attached to the outer peripheral surface of the head 50. The gap S ₁ (e ₁ + e ₁ ) between the large diameter portion 58 and the large diameter portion 58 is a clearance S ₂ ( e ₂ + e ₂ ).
In other words, in this example, the collision mass 44 can freely move in the direction perpendicular to the axis by the gap S ₁ inside the floating chamber 48.
[0037]
The vibration control device 42 operates as follows.
That is, when the rubber bush 28 and the inner fitting 34 start to vibrate in the direction perpendicular to the axis in the traction device, the collision mass 44 collides with the housing 46 and acts to cancel the vibration of the housing 46, that is, the vibration of the inner fitting 34.
[0038]
The collision mass 44 that has collided with the housing 46 is given kinetic energy in the opposite direction from the housing 46 (thus part of the vibration energy of the housing 46 is absorbed as the kinetic energy of the collision mass 44). Exercise in the direction.
Then, it collides again with the contact surface at a position opposite to the first contact surface, and acts so as to cancel the vibration of the inner metal fitting 34 again.
[0039]
Thereafter, the collision mass 44 repeats the same movement with a phase opposite to or different from that of the inner metal fitting 34, absorbs the vibration energy of the inner metal fitting 34 at each collision, and converts it into its own kinetic energy. It continues to collide with the vibrating inner metal fitting 34, whereby the vibration energy of the inner metal fitting 34 in the rubber bush 28 is attenuated. That is, a good vibration damping function is given to the rubber bush 28 itself.
[0040]
Further, the vibration damping device 42 of the present example has a problem that a large abnormal noise is generated at the time of collision because the layer of the rubber elastic body 56 is attached to the outer peripheral surface of the head 50 of the collision mass 44, and at the time of the collision The vibration damping action of the rubber elastic body 56 works to promote vibration damping.
[0041]
The vibration damping device 42 of this example has no particular frequency dependence, can suppress vibration over a wide frequency range, and has little dependence on temperature, and is excellent in a wide temperature range from high temperature to low temperature. Demonstrate the vibration effect.
Further, the required mass of the collision mass 44 is light and sufficient, and since the required space of the entire damping device 42 is small and compact, it has various features such that it can be easily attached to the rubber bush 28. Yes.
[0042]
In addition, in this example, since the inner metal fitting 34 itself also serves as the housing 46 in the vibration damping device 42, the number of necessary members can be reduced, and at the same time the rubber bush 28 is assembled, the vibration damping function by the vibration damping device 42 is attached to the traction device. The advantage that can be added is obtained.
[0043]
Next, FIG. 6 shows a reference example .
In this example, a vibration damping device 42 is incorporated in the link 26.
That is, in this example, a metal housing 46 is formed at a part of the link 26, and as shown in (B) ((B) shows a longitudinal section), a rectangular cross section is formed on the inner side in the axial direction. A floating chamber 48 having a longitudinal shape is formed, and a corresponding metal collision mass 44 having a rectangular cross section and a longitudinal shape in the axial direction is accommodated therein.
[0044]
Here, a rubber elastic body 56 layer is adhered to the outer peripheral surface of the collision mass 44 by vulcanization adhesion, and a gap S ₁ (e ₁ + e) is formed between the rubber elastic body 56 layer and the inner surface of the idler chamber 48. ₁ ), a gap S ₃ (e ₃ + e ₃ ) is formed. Note longitudinal clearance S ₃ can also be reduced this to variable吸的.
[0045]
According to this example, since the vibration damping device 42 is configured to include a part of the link 26, the vibration of the traction device can be effectively damped through the link 26 by the action of the vibration damping device 42. Also in this example, after the link 26 is assembled, there is an advantage that it is not necessary to attach the vibration control device 42 separately.
[0046]
7 and 8 show still another reference example .
This example is also an example in which the vibration damping device 42 is incorporated in the link 26.
In this example, the link 26 has a plate-like portion 66 in a portion between the holding cylinders 30 and 30 at both ends, and a metal collision which is also plate-like on both the left and right outer sides of the plate-like portion 66. A mass 44 is arranged.
A layer of rubber elastic body 56 is also adhered to the outer surface of the pair of collision masses 44 on the link 26 side by vulcanization adhesion.
[0047]
Thus, the pair of collision masses 44 is separated from the plate-like portion 66 by a predetermined gap S ₁ (e ₁ ) by a restraining tool (restraint member) 70 inserted through the through hole 68 of the plate-like portion 66 of the link 26. + E ₁ ) and a gap S ₃ (e ₃ + e ₃ ) and a gap S ₄ (e ₄ + e ₄ ) are formed so as to be free to move in the gap S ₁ . ing. Here, the gap S ₃ is to be smaller than the gap S _4.
The plate-like collision mass 44 is accommodated in a corresponding recess formed in the link 26 in a freely movable state, and the collision mass 44 is also attached to the upper and lower edges 74 in FIG. It can collide vertically.
[0048]
According to this example, since the link 26 is effectively utilized as a component of the vibration damping device 42, the vibration damping device 42 can be configured with a simple configuration and a small number of parts, and the vibration damping device 42 can be configured. By virtue of the above action, the vibration of the traction device can be effectively damped through the link 26.
[0049]
Next, in the reference example of FIG. 9, a metal holder 78 having a rod-like portion (contact portion) 76 is attached to the outer surface of the link 26, and an annular (here cylindrical shape) is formed outside the rod-like portion 76. This is an example in which a vibration damping device 42 is configured by externally fitting the collision mass 44 in a state where a rubber elastic body 56 layer is adhered to the inner peripheral surface thereof by vulcanization adhesion.
Also in this example, the vibration of the traction device can be effectively damped through the link 26 by the action of the vibration damping device 42.
[0050]
Although the embodiments and reference examples of the present invention have been described in detail above, this is merely an example.
For example, in the present invention, it is possible to use a resin as the elastic body, and it is possible to configure the vibration damping device in various forms other than the above examples. It can be configured in various modified forms.
[Brief description of the drawings]
FIG. 1A is a diagram schematically showing an embodiment of a vibration damping device of the present invention in comparison with a dynamic damper.
(B): It is explanatory drawing of the effect of the damping device of (A).
FIG. 2 is a diagram showing a carriage of a railway vehicle including a traction device to which the present invention is applied.
FIG. 3 is a diagram showing the traction device and its peripheral part in FIG. 2;
4 is a view showing an example in which a vibration damping device is incorporated in a rubber bush of the traction device in FIGS. 2 and 3. FIG.
FIG. 5 is an exploded view showing each member in FIG. 4;
FIG. 6 is a diagram illustrating a reference example .
FIG. 7 is a diagram showing a reference example .
FIG. 8 is an exploded view of each member of the reference example of FIG.
FIG. 9 is a diagram showing still another reference example .
[Explanation of symbols]
10 bogie 11 bogie frame 12 center pin 24 car body 26 link 28 rubber bush 32 outer cylinder fitting (outer cylinder member)
34 Inner bracket (inner member)
36 Rubber elastic body 42 Damping device 44 Collision mass 46 Housing 48 Idle chamber 56 Rubber elastic body (elastic body)
66 Plate-shaped part
70 Restraint (restraint member)
76 Bar-shaped part
S ₁ and S ₃ gaps

Claims (1)

The carriage and the vehicle body are connected to each other via a traction device having a center pin whose upper part is coupled to the vehicle body, and each end part having a carriage frame and a link coupled to the lower part of the center pin via a rubber bush. In a predetermined position of the towing device in a railway vehicle adapted to tow the vehicle body, a rigid contact portion, a collision mass provided in an idle state with respect to the corresponding portion, and colliding with the corresponding portion during vibration, and corresponding A gap for moving the collision mass in the vibration direction, and an elastic body formed on at least one contact surface between the contact portion and the collision mass. Wear a vibration control device ,
The rubber bush has a rigid outer cylinder member, a central inner member, and a rubber elastic body sandwiched between them, and the inner member constitutes a housing that forms the contact portion. The vibration damping device is incorporated in the inner member by the collision mass being movably accommodated in the idle chamber in the housing,
The inner member has a hollow structure provided with a space penetrating in the axial direction in the central portion, and in the space, a large diameter portion at both ends, a small diameter portion between them, and the large diameter portion, The floating chamber having a stepped portion is provided between the small diameter portion, a circular section in the circular direction and a longitudinal shape in the axial direction, and relatively large-diameter heads at both ends, and between them And the collision mass having a relatively small-diameter body is movably accommodated,
The elastic body is formed on the contact surface of at least one of the large-diameter portions at both ends of the idle chamber and the pair of head outer peripheral surfaces of the collision mass,
The clearance between the outer peripheral surface of the head in the collision mass and the inner peripheral surface of the large-diameter portion in the floating chamber is the inner diameter of the outer peripheral surface of the trunk portion in the collision mass and the small-diameter portion in the floating chamber. A damping structure for a traction device in a railway vehicle , characterized in that the collision mass is made smaller than a gap between the circumferential surface and the collision mass is movable in a direction perpendicular to the axis with respect to the inner member .

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