JP2005289370A - Railway vehicle - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To suppress vibrations of a railway rolling stock truck caused by an unbalanced drive system, and to reduce noise in a railway rolling stock due to the vibrations. <P>SOLUTION: According to the railway rolling stock, a connecting member 25 of a car body 20 is linked to an undercarriage frame 11 via a link 30, and a container containing granules made of an iron or lead material is attached to the outer periphery of the link 30. Rotational vibrations, generated from the drive system, including a running motor, a speed reducer, and a shaft coupler, are transmitted to the link 30 to generate vibrational energy therein. This vibrational energy is converted into kinetic energy due to the granules in the container colliding with each other, so that the vibrations of the link 30 is reduced, which suppresses the transmission of the vibrations to the car body. The granules may be placed inside the cylinder 31 of the link 30. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a railway vehicle carriage. A railway vehicle is a vehicle that travels on a track.

  As described in Patent Document 1, a bogie frame and a vehicle body of a railway vehicle are connected by a tow link (hereinafter referred to as a link). Rubber bushes are arranged at both ends of the link, that is, in the front-rear direction. The rubber bush is designed to sufficiently withstand a large longitudinal compressive load (link direction) that occurs from time to time. The rubber bush is used for running stability. The cart and the vehicle body are connected by a yaw damper.

Moreover, there exists patent document 2 as a sound insulation panel using a granular material. In this case, in a floor of a vehicle body using an aluminum honeycomb panel, powder having a particle size of 30 μm to 1000 μm is accommodated inside the panel to suppress vibration in the vertical direction of the floor of the vehicle body.
Japanese Utility Model Publication No.58-1406 Japanese Patent Laid-Open No. 10-266388

  The vibration in the front-rear direction (vehicle traveling direction) generated on the trolley side is transmitted to the vehicle body side via two rubber bushes, links, and a connecting portion such as a yaw damper. For this reason, the noise in the vehicle is high. In particular, there is a problem that solid propagation vibration in the 80 to 300 Hz band of the rotational frequency component resulting from drive system imbalance is transmitted to the bogie frame, and the floor is vibrated to increase in-vehicle noise.

The rotational vibration generated due to the unbalance of the drive system is relatively remarkable as a component having a magnitude of 10 m / s ² or less, which is 1 to 3 times the rotational vibration component f ₁ of the motor shaft. These rotational vibration components f ₁ ~3f ₁ is transmitted as a structure-borne vibration to the vehicle body via a link becomes a vertical vibration of the vehicle body floor surface, it appears as vehicle interior noise. In particular, at the time of acceleration while the vehicle is running, twice the 2f ₁ component is generated in the front-rear direction, the left-right direction, and the up-down direction. Furthermore, during deceleration and coasting is 1 × f ₁ component, results in significant increase of longitudinal vibrations of 3 times the 3f ₁ component. For example, if f ₁ is 80 Hz, 2f ₁ is 160 Hz and 3f ₁ is 240 Hz. For this reason, it is required to reduce vibrations of about 100 Hz or more.

  An object of the present invention is to reduce vehicle interior noise with a simple configuration.

  The above-described object can be achieved by installing a container containing an object movable with respect to the connecting member on the connecting member between the vehicle body and the connecting member between the vehicle body and the bogie frame. The connecting member includes a traction link, a yaw damper, a left-right motion damper, a front-rear damper between vehicles, a bolster anchor, and the like.

  According to this, the vibration energy generated in the connecting member is converted into the kinetic energy of the object by the collision of the object, and the vibration in the connecting member is reduced. For this reason, propagation of vibration to the vehicle body can be suppressed, and vehicle interior noise can be reduced.

Vehicle interior noise is generated by vibration of the floor of the vehicle body. The vibration source is a rotational unbalance of the drive system of the vehicle body. The connecting member is located between the vibration source and the floor of the vehicle body, and mainly vibrates in the front-rear direction. For this reason, the object inside a connection member moves to the front-back direction. For this reason, since there is no need for vibration of 10 m / s ² against the gravity in the movement of the object, the object moves actively even with a small excitation force. Therefore, it is possible to suppress the vibration source on the vehicle body floor surface and reduce in-vehicle noise.

  Since this connecting member is relatively light, vibration can be suppressed with a simple device.

  According to the present invention, it is possible to suppress transmission of vibrations generated from the drive system and to reduce vehicle interior noise with a simple configuration in which an object is movably provided on a connecting member that connects the vehicle body and the connecting member that connects the carriage and the vehicle body. It can be reduced.

  An embodiment of a railcar bogie according to the present invention will be described with reference to FIGS. The bogie frame 11 of the bogie is supported by two axles 13 having wheels 12, and supports a motor 14 that drives the axle 13 and a speed reducer that includes gears. The carriage frame 11 supports the vehicle body 20 via the air spring 15.

  A connecting member (generally called a center pin) 25 that protrudes downward from the lower surface of the vehicle body and the carriage frame 11 are connected by a traction link (hereinafter referred to as a link) 30. The link 30 transmits a longitudinal force and is along the horizontal direction of the traveling direction.

  The left and right ends of the carriage frame 11 are connected to the vehicle body 20 via yaw dampers 28 and 28. Both ends of the yaw damper 28 are connected to the bogie frame 11 and the vehicle body 20 through rubber bushes in the same manner as the link 30. The yaw damper 28 is for preventing the snake behavior during traveling. In addition, a left and right motion damper (not shown) that prevents left and right vibrations of the vehicle body is installed between the vehicle body and the carriage.

  Both ends of the link 30 are connected to the carriage 11 and the connecting member 25 through rubber bushes 35, pins 36, and the like. The connecting member 25 is arranged to be inclined from the vehicle body 20 toward the connecting portion with the link 30. The cross-section of the lower end portion of the connecting member 25 is an inverted U shape. The inclined portion is along the traveling direction of the vehicle body. The link 30 is arranged in the horizontal direction of the traveling direction of the vehicle body and penetrates the U-shaped part. A central portion of the link 30 is a cylinder 31.

  Since vibration using the drive system of the motor 14, its speed reducer, and the shaft joint as a vibration source is mainly transmitted to the vehicle body via the link 30, an example in which measures against vibration are applied to the link 30 will be described below.

  A vibration damping device 40 is attached to the outer periphery of the cylindrical portion 31 of the link 30 on the connecting portion side with the carriage frame 11. Since the connecting member 25 is on the side of the connecting portion with the connecting member 25, the vibration damping device 40 is not installed.

  The vibration damping device 40 is mainly composed of a container 42 for storing the granular material 41. The container 42 is divided into two vertically. The containers 42, 42 divided into two in the upper and lower directions are composed of an outer plate 43 having a semicircular cross section and an inner plate 44 having a semicircular cross section. The outer plate 43 is a container for storing the granular material 41. The inner plate 44 covers the container 43. After the granular material 41 is put in the container 43 and covered with the container 44, the horizontal flanges 43b and 44b on the four sides of the containers 43 and 44 are spot-welded, and the plates 43 and 44 are integrated to form the container 42. Yes. A sealing agent is applied to the mating surfaces of the plates 43 and 44 to seal water and spot welding is performed. The plates 43 and 44 are manufactured by press working or the like.

  Instead of spot welding, the entire circumference may be welded and the sealant may be eliminated. Moreover, you may provide the insertion hole which can insert the granular material 41 from the outside.

  A rubber sheet 46 is attached to the arc-shaped inner surface of the inner plate 44. The flanges 43 b and 44 b along the axial direction of the link 30 are connected by bolts and nuts 47 and fixed to the outer surface of the link 30. The outer surface of the link 30 is circular. An inner semicircle of the inner plate 44 is determined corresponding to the diameter of the link 30.

  The inner plate 44 is overlapped and covered with the granular material 41 having a predetermined weight placed in the outer plate (container) 43, and the flanges 43b and 44b are spot-welded.

  Ends 44c and 44c of the inner plate 44 on the side of the carriage frame 11 protrude so as to face the flat part of the joint 32 at the end of the link 30. The end of the link 30 has a large diameter for inserting the rubber bush 35. The end face of the joint 32 in the insertion direction (axial direction) of the rubber bush 35 and the pin 36 is flat. The protruding pieces 44c and 44c overlap this flat surface. For this reason, even if the fixing force of the bolt / nut 47 is small, the vibration damping device 40 does not rotate.

  Further, in order to prevent the movement of the link 30 in the axial direction, a fixed piece 39 is welded to the outer surface of the cylindrical portion 31. The bases of the protruding pieces 44c and 44c are positioned in the vicinity of the joint 32 to prevent the movement toward the joint 32 side.

  The granular body 41 is a spherical body using an iron-based or lead-based material. The particle size is about 0.1 mm to 10 mm. When the packing density of the granular material 41 is small, the damping effect is small, and when it is too large, the movement of the granular material is deteriorated and the damping effect is reduced. The packing density is preferably about 70 to 95%.

  The packing density will be described. For example, when it is desired to actually use the granular material 41 having a particle diameter of 1 mm, the granular material 41 having a particle diameter of 1 mm is filled in a target container, and the weight at this time is measured. This state is a packing density of 100%. The filling density of 70% is a state in which the same granular material 41 as in the case of the filling density of 100% is put in 70% by weight.

  In order to prevent rust, corrosion or wear of the granular material 41, a hygroscopic material (for example, bengara) may be enclosed.

  As will be described later, since the vibration damping effect increases as the weight ratio of the granular body 41 increases, the granular body 41 is preferably made of a material having a large specific gravity, for example, a lead-based material. Lead is relatively inexpensive. If specific gravity is large, the magnitude | size of the container which accommodates the granular material 41 can be made small. Moreover, since it will become expensive if the diameter of the granular material 41 is made small, about 1 mm is generally good. If the diameter of the granular material 41 is reduced, the packing density increases and the container can be made smaller.

According to such a configuration, when the link 30 vibrates due to the vibration of the drive system, the granular body 41 also vibrates, and the granular bodies 41 collide with each other, and the plates 43 and 44 (because they are integral with the link 30, correspond to the link 30. ) And the granular material 41 increase the frictional resistance of the granular material 41. For this reason, the vibration in the damping device 40 is reduced and the vibration of the link 30 can be absorbed. Further, the vibration energy of the link 30 at the time of the collision is efficiently converted into the kinetic energy of the granular body 41 in proportion to the specific gravity of the granular body 41 becoming larger. Thereby, vibration energy becomes small and vibration of the link 30 can be reduced. In particular, the motion of the granular material inside the vibration damping device 40 in the longitudinal direction does not need to resist gravity due to vibration of the drive system (vibration of 10 m / s ² or more is not necessary), so even with a small excitation force. Be activated. For this reason, the vibration of the front-back direction which is solid-propagated from the link 30 to the vehicle body side is reduced. Therefore, the vibration in the vertical direction of the vehicle floor is reduced, and the in-vehicle noise radiated from the floor can be reduced.

That is, the granular material 41 repeatedly collides within a minute range due to the longitudinal vibration that is solid-propagated through the link 30 with respect to the relatively remarkable 2f ₁ vibration component during acceleration. For this reason, the vibration energy generated in the link 30 is converted into the kinetic energy of the granular material 41. Further, vibration is reduced by the frictional resistance between the granular bodies 41. Thereby, the vibration in the link 30 is reduced.

It is more effective to reduce the vibration in the front-rear direction of the link 30 that is the transmission path before the vibration is diffused to the vehicle body floor surface, compared to the case where the granular material is installed on the vehicle body floor surface. This is because the granular body 41 actively moves against the vibration in the front-rear direction of the link 30 (no vibration of 10 m / s ² or more against gravity is required). Therefore, by suppressing the longitudinal vibration at the link 30, an increase in the vertical vibration of the vehicle body floor can be suppressed, and the vehicle interior noise can be reduced. Further, since the link 30 is relatively light, vibration can be suppressed with a light device.

  Further, during acceleration / deceleration and coasting, the vibration in the front-rear direction at the link 30 is further increased, so that the damping effect becomes even more remarkable. In this case, the movement of the granular body 41 further causes the granular body 41 to move actively even with a large excitation force, and the vibration damping effect is increased.

  FIG. 7 to FIG. 11 show the vibration damping effect of the granular material 41 by the element test. In this element test, the pins 36 and 36 at both ends of the link 30 are fixed to a jig, and the vibration transmissibility to the cylindrical portion 31 of the link 30 when the pin 36 at one end is vibrated with an electrodynamic shaker is measured. It is a thing. The link 30 is used for an actual product, and is provided with pins 36 via rubber bushes 35 at both ends. A pin 36 at one end is connected to an electrodynamic exciter. A vibration measuring device is installed in the output part of the electrodynamic exciter and the cylinder part 31 of the link 30. The vibration transmissibility is the ratio of the vibration acceleration of the link 30 to the vibration acceleration on the shaker side.

In FIG. 7 to FIG. 11, “Excitation small” means that the excitation amplitude is 0.1 m / s ² , and “Exciting” means that the excitation amplitude is 0.25 m / s ² . “Excitation large” is when the excitation amplitude is 0.5 m / s ² . “Excitation small”, “During excitation” and “Excitation large” are cases where the vibration damping device of the present invention is installed. “Link only” is the case of the conventional link 30 and the excitation amplitude is 0.5 m / s ² . In the case of the conventional link 30 alone, the vibration transmissibility characteristics are almost the same as in the case of 0.5 m / s ² even if the excitation amplitude is changed to medium or small.

  The granular body 41 of the vibration damping device 40 is lead-based, has a particle diameter of 1 mm, a weight ratio with respect to the link 30 (including rubber bushes and pins) of 28%, and a packing density of about 95%.

  7 and 8, the vibration damping device is provided on the outer peripheral portion of the link 30, but the rubber sheet 46 is not provided. The vibration damping device is not the vibration damping device 40 itself.

  In FIG. 7, when the excitation amplitude is small, the peak frequency of the link 30 is reduced by about 40 Hz due to the weight increase due to the granular material 41 and the like. As the excitation amplitude is increased, the peak frequency approaches the original peak frequency, but the vibration transmissibility is reduced. The vibration suppression effect in the 200 Hz band or higher is obtained at about -6 dB when the excitation amplitude is large.

  FIG. 8 shows a case where the granular material 41 is sealed in the cylindrical portion 31 of the link 30 in addition to the vibration damping device installed outside of FIG. 7. The link 30 welds a joint 32 that fixes the rubber bush 35 to both ends of the cylindrical portion 31. For this reason, after putting the granular material 41 in the cylinder 31, the joint 32 is welded. The cylindrical portion 31, that is, the link 30 is a container. The granular material 41 is the same as that of FIG. The packing density is the same. The weight ratio of the inner and outer granules 41 to the link 30 is 44%. According to this, a vibration damping effect of about −7 dB can be obtained. Thus, the vibration damping effect increases as the weight ratio of the granular material 41 increases.

Next, the effect of the rubber sheet 46 will be described with reference to FIGS. Since the containers 42 and 42 of the vibration damping device 40 are fixed to the link 30 via the rubber sheet 46, the containers 42 and 42 act like a dynamic vibration absorber and increase the vibration damping effect of the link 30.

  FIG. 9 shows a case where the thickness of the rubber sheet 46 is 3 mm, and FIG. 10 shows a case where the thickness of the rubber sheet 46 is 1 mm. In any case, the structure of the vibration damping device is the same as that shown in FIG. According to this, in the case of 3 mm, the vibration damping effect of about −7 dB and 1 mm in the case of 1 mm can be obtained.

  The effect of the tightening force of the rubber sheet 46 will be described with reference to FIG. This is a case where the tightening force of the bolt and nut 47 is loosened as compared with FIG. However, the vibration damping device does not rotate or move in the axial direction. The thickness of the rubber sheet 46 is 1 mm. According to this, the vibration transmissibility is reduced in the frequency range of about 175 Hz to about 270 Hz. Moreover, the maximum vibration transmissibility is reduced. This is considered to be because the friction resistance is generated on the surface of the rubber sheet due to the interposition of the rubber sheet 46, and the vibration damping effect due to the friction is increased.

  As described above, the rubber sheet 46 may be formed into a plurality of layers. For example, when a rubber sheet having a thickness of 1 mm is formed into three layers, an effect of -2 dB is further obtained in the case of FIG.

  The embodiment of FIG. 12 will be described. The storage space for the granular material 41 is partitioned by 49. The partition plate 49 is fixed to the inner plate 44. According to this, the collision area with the granular material 41 is increased by the partition plate 49, and a further vibration damping effect can be obtained.

  The embodiment of FIG. 13 will be described. The container 42 b is installed only on the lower surface of the link 30. The cylindrical portion 31 is sandwiched and fixed by a plate 44b corresponding to the inner plate 44 of the upper container 42 and the lower container 42b.

  The embodiment of FIGS. 14 to 17 will be described. The height dimension of the cylinder part 51 of the link 50 is larger on the cart frame 11 side than on the connecting member 25 side. The height of the connecting portion 25 side of the cylindrical portion 51 is reduced so as not to contact the connecting member 25. The vertical cross section of the cylinder part 51 is oval. The cylindrical part 51 is formed by welding a plate that has been formed into a halved shape by pressing. Moreover, you may weld to a longitudinal direction for every site | part where the cross section changed. At both ends, annular joints 52 and 52 for press-fitting the rubber bush 55 are welded. After welding the joint 52 at one end, the granular material 41 is put into the cylindrical portion 51, and then the joint 52 at the other end is welded.

Moreover, the joint of both ends can be welded to the cylinder part 51, and a granule can be put after the incineration process for the removal of welding distortion. For this reason, the joint 52 at one end is provided with a hole 51 g that opens into the cylindrical portion 51. After welding, the granular material 41 is put through the hole 61g. Thereafter, the rubber bush 55 is press-fitted into the joint 52 and attached. This closes the hole 51g. According to this, incineration processing for removing welding distortion can be performed. Moreover, since the hole 51g which puts the granular material 41 is block | closed with the rubber bush 55, the special member for plugging the hole 51g can be made unnecessary. Moreover, although the cylinder part 51 is changing height in three steps, you may change it linearly. According to this, welding can be reduced.

  According to this, the internal volume of the link 50 can be increased, and the vibration damping effect by the granular material 41 is increased. Moreover, compared with the case where it installs outside, the fall of a damping device and the scattering of a granular material can be prevented.

The weight of the granular material with respect to the link in the above three types: the type in which the damping device is installed outside the link, the type in which the granular material is installed only inside the link, and the type in which the granular material is installed inside and outside the link When the damping effect on the ratio is summarized, the characteristic shown in FIG. 18 is obtained. It can be seen that the damping effect is linearly related to the weight ratio. If the weight ratio of the granular material to the link is 50%, a vibration damping effect of about 10 dB can be obtained.

  It is advisable to mix granular materials having a plurality of shapes in one container. According to this, the vibration damping effect is improved by increasing the weight ratio or increasing the frictional force. The shape in this case means a difference in particle diameter and appearance shape. The appearance need not be spherical. For example, it may be a gourd shape, a polygonal shape, or a shape having concave and convex portions on the surface. If there are a concave portion and a convex portion on the surface, the contact area between the granular materials increases, and the vibration damping effect increases. The granule having a concave portion and a convex portion on the surface can be obtained, for example, by stirring a lead-based spherical granule with a mixer. According to experiments using this, the deformed granular material has a greater vibration damping effect than the spherical shape. This is considered because there is little repulsion at the time of a collision between granular materials. Further, considering that the vibration damping effect is a weight ratio, it is considered that the granular material 41 may be powder.

  It is conceivable that the granular material is stored inside the pins 36 and 56.

  The embodiment of FIGS. 19 and 20 will be described. Between the inner plate 44 and the outer plate 43, a guide 61 and a column 62 that moves along the hole of the guide 61 are installed. The guide 61 can also move. The guide 61 has an arc shape and is provided with a plurality of holes along the axial direction. The plurality of holes are along the arc shape of the guide 61. A cylinder 62 is inserted into each hole. A seat 63 is fixed inside the axial end of the outer plate 43. The lengths of the guide 61 and the cylinder 62 are the same, and are slightly shorter than the length between the seats 63 and 63. The guide 61 and the cylinder 62 collide with the seat 63 when moved. The damping effect by the frictional resistance between the container 42 and the guide 61 and between the guide 61 and the cylinder 62 is obtained.

  Except for the guide 51, only the cylinder 62 can be formed. The cylinder 62 may be divided in the axial direction. Further, the guide 61 and the column 62 may be disposed inside the link 30. The length of the guide 61 can be shortened or the guide 61 can be removed.

  The embodiment of FIGS. 21 and 22 will be described. A linear bush, 100 and a cylinder 102 are arranged inside the cylindrical portion 31 of the link 30. The cylinder 102 is supported via a plurality of bearings inside the linear bush 100 and can move smoothly in the axial direction. The linear bush 100 is fixed to the central portion in the longitudinal direction of the cylindrical portion 31 with a snap ring 103. The length of the cylinder 102 is longer than the length of the linear bush. Both ends of the cylinder 102 are close to the end face of the joint 32b. The cylinder 102 collides with the joint 32b. The cylinder 102 is made of iron or the like and has an outer diameter of about 20 mm to 50 mm. Before the joint 32b is welded to the cylindrical portion 31, the linear bush 100 or the like is disposed. After the linear bush 100 and the cylinder 102 are assembled in the cylindrical portion 31, they are welded to the joints 32b and 32b.

  According to such a configuration, a vibration damping effect can be obtained with a minute displacement (relatively high frequency of 100 Hz or more) in the gap (the effect is slightly low). In addition, low-frequency shocking vibration components in the 0.1 Hz to 50 Hz band generated in the front-rear direction during traveling can be absorbed.

  Also, a plurality of bolts penetrating into the cylinder from the outside in the radial direction of the cylinder portion 31 can be provided, and the linear bush 100 inside can be pressed and fixed with these bolts. Moreover, the linear bush 100 can be provided long and the cylinder 102 can be divided into a plurality of parts in the axial direction.

  You may put the granular material 41 in the cylinder 102. FIG. According to this, both of the effects described above can be obtained.

  The embodiment of FIG. 23 will be described. A coil spring 105 is installed at one end of the cylinder 102. The coil spring 105 can hit the joint 32b. The other end of the cylinder 102 is in contact with the end face of the other joint 32b. According to this, the contact state between the cylinder 102 and the joint 32b can always be maintained, and the damping effect can be maintained even for a minute vibration component. In addition, since the natural frequency determined by the spring constant of the coil 105 and the mass of the cylinder 102 can be set to an appropriate value, an action like a dynamic vibration absorber can be expected.

  The embodiment of FIG. 24 will be described. The cylinder 102 is divided into three in the axial direction, and coil springs 105 are provided at both ends of the center cylinder 102b. The coil spring 105 can hit the adjacent cylinders 102a and 102c. The cylinders 102a and 102c are in contact with the end faces of the joints 32b and 32b.

  The embodiment of FIG. 25 will be described. This is the one in which a granular material, a cylinder, or a linear bush and a cylinder are inserted into the pipe 110. Both ends of the pipe are closed. The pipe 110 is fixed to the outer surface of the cylindrical portion 31 of the link 30 with a plurality of bands 115. A plurality of pipes 110 may be installed along the circumference of the cylindrical portion 31.

  The application to the single-link type tow link has been described above, but the present invention can also be applied to other types of tow links, for example, Z-type links. Further, by installing the vibration damping device 40 outside the yaw damper 19 or outside the left and right dynamic damper, an equivalent vibration damping effect can be obtained. Moreover, the installation to the axis | shaft damper which connects a vehicle body and a trolley | bogie to an up-down direction can be considered. In addition, the same effect can be obtained if the vehicle body is installed outside the damper that connects the vehicle bodies in the front-rear direction. Moreover, it is applicable also to the bolster anchor of the trolley | bogie which has a bolster.

  The embodiment of FIG. 26 will be described. The link 30 has a cylindrical shape and encloses the granular material 41 inside the end portions 32b and 32b of the shaft joint. The granular material 41 uses an iron-based material. For example, iron (SS400) has a particle size of about 1 mm to 10 mm. The packing density of the granules 41 is about 50%. Joints 13a and 13b are welded to both ends of the cylindrical portion 31. The joints 13a and 13b are welded in a state where the granular material 41 is put in the cylindrical portion 31. Others are similar to the embodiment of FIG.

  In order to lubricate or prevent corrosion of the granular material 41 in the link, a lubricant or oil may be enclosed.

  By changing the steel diameter of the granular body 41 in accordance with the frequency of the insulation vibration (decreasing the particle diameter for a high frequency), a reduction effect with minute vibration can be obtained. Moreover, you may mix the thing from which a particle size differs, and a thing with different specific gravity inside a link.

  In addition, by enclosing the granular material, the natural frequency of the link 30 determined by the spring and the mass can be adjusted to an appropriate value.

  Since the granular material is enclosed in the traction link, the problem of corrosion is eliminated.

  If the rubber bushing 35 has the same characteristics as the conventional one, the conventional running stability can be ensured, and the vibration of the 80 to 240 Hz band rotation component caused by the unbalance of the cart drive system is suppressed and generated accordingly. In-vehicle noise can be reduced.

  The cylindrical part 31 is divided into two in the longitudinal direction, and both the cylindrical parts are joined by flanges provided at both ends. According to this, the distortion removal operation | work of the link 30 by annealing can be performed after welding a flange. Then, a granular material is put and a flange is couple | bonded with a bolt nut.

  The embodiment of FIG. 27 will be described. An insertion hole through which the granular material 41 can be enclosed or taken out is provided on the side surface of the cylindrical portion 31 of the link 30. Reference numeral 70 denotes a screw-type lid for that purpose.

  According to this configuration, the granular body 41 can be easily inserted after the link 30 is attached to the vehicle body side or the cart side. Moreover, even if the characteristics of the vehicles vary, it is possible to study the optimization of the granular material 41 and fine adjustment is possible. Furthermore, when the granular material 41 is replaced, it can be easily replaced.

  The embodiment of FIGS. 28 and 29 will be described. The device 71 enclosing the granular material 41 is brought into close contact with the outer surface of the cylindrical portion 31 of the link 30 with bolts 72a and 72b.

  According to this configuration, the vibration damping device 71 can be easily removed and replaced. In addition, it is possible to easily combine the optimal arrangement of the vibration damping device 71.

  The embodiment of FIG. 30 will be described. The inside of the cylindrical portion of the link 30 is separated into right and left, and a large-diameter granule 41a is enclosed in a cylinder on one end side, and a small-diameter granule 41b is enclosed in the other cylinder.

  The diameters of the granular materials 41a and 41b are determined according to the frequency of the target insulation vibration. Optimum shaped granules 41a and 41b are arranged. The material of the granular materials 41a and 41b is determined from the same viewpoint.

According to such a configuration, one time component and granules 41a made to correspond to twice component of the rotational frequency component f ₁ of unbalance of the drive system, it is possible to place the 41b.

The embodiment of FIG. 31 will be described. The inside of the cylindrical portion 31 of the link 30 enclosing the granular material is divided into three layers by plates 73b and 73c, and the granular materials 41a, 41b and 41c having different characteristics are enclosed therein. For example, the granular materials 41a, 41b, and 41c have particle sizes corresponding to the 1-fold component, 2-fold component, and 3-fold component of f1, respectively.
According to this, vibration can be suppressed more finely.

  When the idea of FIG. 30 or FIG. 31 is applied to the embodiment of FIGS. 28 and 29, a plurality of devices 71, 71... Having different characteristics are installed on the outer periphery of the cylindrical portion 31 of the link 30.

  In FIG. 26, a granular material can be enclosed in the pins 36 and 36. According to this, vibration can be suppressed by this portion.

  The case where the particulate vibration suppression device is applied to the yaw damper 28 will be described with reference to FIG. Bolts are connected to the carriages and the mounting parts 83, 84 of the vehicle body via pins 81 a, 81 b that penetrate the rubber bushes of the yaw damper 28. A granular material is sealed inside the pins 81a and 81b. The particle sizes of the granules of the pins 81a and 81b are different.

  In addition, there is a left-right motion damper between the carriage and the vehicle body. Also in this damper, a granular material is enclosed in the pin of the connection part of a damper, a trolley | bogie, and a vehicle body like a yaw damper.

  The technical scope of the present invention is not limited to the language described in each claim of the claims or the language described in the means for solving the problem, and is also within a range easily replaced by those skilled in the art. It extends.

It is a side view of the traction link part of one example of the present invention. It is an enlarged view of the principal part of FIG. FIG. 3 is a plan view of FIG. 2. FIG. 4 is a IV-IV diagram of FIG. 2. It is a top view of the trolley | bogie provided with one Example of this invention. It is a figure explaining the vibration characteristic of a trolley | bogie. It is a figure explaining the effect of one Example of this invention. It is a figure explaining the effect of the other Example of this invention. It is a figure explaining the effect of the other Example of this invention. It is a figure explaining the effect of the other Example of this invention. It is a figure explaining the effect of the other Example of this invention. It is a longitudinal cross-sectional view of the vibration damping device of the other Example of this invention. It is a longitudinal cross-sectional view of the vibration damping device of the other Example of this invention. It is a side view of the other traction link of this invention. FIG. 13 is a plan view of FIG. 12. It is XVI-XVI sectional drawing of FIG. It is XVII-XVII sectional drawing of FIG. It is the figure which put together the relationship between a damping effect and mass. It is a longitudinal cross-sectional view of the vibration damping device of the other Example of this invention. It is a longitudinal cross-sectional view of FIG. It is a longitudinal cross-sectional view of the traction link of the other Example of this invention. It is the longitudinal cross-sectional view of the center of FIG. It is a longitudinal cross-sectional view of the traction link of the other Example of this invention. It is a longitudinal cross-sectional view of the traction link of the other Example of this invention. It is a side view of the traction link of other examples of the present invention. It is a side view of the traction link of other examples of the present invention. It is a side view of the traction link of other examples of the present invention. It is a side view of the traction link of other examples of the present invention. It is a center longitudinal cross-sectional view of FIG. It is a side view of the traction link of other examples of the present invention. It is a center longitudinal cross-sectional view of the traction link of the other Example of this invention. It is a top view of the yaw damper part of the other Example of this invention.

Explanation of symbols

11 ... Bogie frame, 25 ... Connecting member, 28 ... Yaw damper, 30 ... Traction link,
DESCRIPTION OF SYMBOLS 31 ... Tube part, 32 ... Joint, 40 ... Damping device, 41 ... Granular body, 42 ... Container, 50 ... Traction link, 51 ... Tube part, 52 ... Rubber bush, 62 ... Column, 100 ... Linear bush, 102 ... Column 105, coil spring.

Claims (46)

  A railway vehicle characterized in that a connecting member between a vehicle body or a connecting member between a vehicle body and a bogie frame includes a container that stores an object that can move with respect to the connecting member.   The railway vehicle according to claim 1, wherein the container stores the object so as to be movable in the front-rear direction of the carriage.   The railway vehicle according to claim 1, wherein the object includes a plurality of granular bodies and is stored so that the granular bodies are in contact with each other.   The railway vehicle according to claim 3, wherein the granular material is an object having a specific gravity greater than that of an iron-based material.   The railway vehicle according to claim 4, wherein the granular material includes a plurality of types having different shapes.   2. The railway vehicle according to claim 1, wherein the connecting member is a tow link that connects the second connecting member projecting downward from the vehicle body and the bogie frame.   The railway vehicle according to claim 6, wherein the tow link is hollow, and the container is configured by using a cylindrical portion between the both ends of the tow link, and the object is placed in the cylindrical portion. , Featuring railway vehicles. The railway vehicle according to claim 7, wherein the traction link has an oval shape in which a longitudinal direction is longer than a lateral direction,
The height dimension of the ellipse of the traction link on the second connecting member side is smaller than the height dimension of the ellipse on the traction link on the cart frame side;
A railway vehicle characterized by   The railway vehicle according to claim 7 or 8, wherein the object is a granular body.   10. The railway vehicle according to claim 9, wherein there are joints for connecting to the bogie frame and the second connecting member at both ends of the cylindrical part, and at least one of the joints has a hole opened in the cylindrical part. The railway vehicle is characterized in that the opening is closed by a rubber bush disposed at the joint.   The railway vehicle according to claim 1, wherein the container is installed outside the connecting member.   The railway vehicle according to claim 11, wherein the object is a granular body.   The railway vehicle according to claim 1, wherein the connecting member is a damper.   The railway vehicle according to claim 1, further comprising a rubber seat between the container and the connecting member.   14. The railway vehicle according to claim 13, wherein the rubber seat is a multilayer. A connecting member connectable to the vehicle body;
The connecting member has a container containing a movable object;
A railcar bogie characterized by   17. The railway vehicle carriage according to claim 16, wherein the container accommodates the object so as to be movable in the horizontal direction of the carriage in the front-rear direction.   The bogie for a railway vehicle according to claim 16, wherein the object is a plurality of granular bodies and is stored so that the granular bodies are in contact with each other.   19. The railway vehicle carriage according to claim 18, wherein the granular material is an object having a specific gravity greater than that of iron.   20. The railway vehicle carriage according to claim 19, wherein the granular material includes a plurality of types having different shapes.   17. The railway vehicle carriage according to claim 16, wherein the connecting member is a tow link that connects the second connecting member protruding downward from the vehicle body and the carriage frame.   The railway vehicle carriage according to claim 21, wherein the traction link is hollow, and the container is configured by using a cylindrical portion between the both ends of the traction link, and the object is placed in the cylindrical portion. A railcar bogie characterized by having 23. The railway vehicle bogie according to claim 22, wherein the traction link has an oval shape in which the longitudinal direction is longer than the lateral direction.
A height dimension of the ellipse of the traction link on the second connecting member side is smaller than a height dimension height of the ellipse of the traction link on the carriage frame side;
A railcar bogie characterized by   24. The railway vehicle carriage according to claim 22 or 23, wherein the object is a granular body.   25. The railway vehicle bogie according to claim 24, wherein there are joints for connecting to the bogie frame and the second connecting member at both ends of the tube portion, and at least one of the joints has a hole opened in the tube portion. And the opening is closed by a rubber bush disposed at the joint.   The railway vehicle carriage according to claim 16, wherein the container is installed outside the connecting member.   27. The railway vehicle carriage according to claim 26, wherein the object is a granular body.   The railway vehicle carriage according to claim 16, wherein the connecting member is a damper.   17. The railway vehicle carriage according to claim 16, further comprising a rubber seat between the container and the connecting member.   30. The railway vehicle carriage according to claim 29, wherein the rubber seat is a multilayer.   A connecting member between a vehicle body and a vehicle body, or a connecting member between a vehicle body and a bogie frame includes a container that stores an object movable with respect to the connecting member.   32. The connecting member according to claim 31, wherein when the connecting member is connected to a carriage and a vehicle body, the container stores the object so as to be movable in the front-rear direction of the carriage.   32. The connecting member according to claim 31, wherein the object is a plurality of granular materials and is housed so that the granular materials are in contact with each other.   34. The connection member according to claim 33, wherein the granular material is an object having a specific gravity greater than that of an iron-based material.   35. The connecting member according to claim 34, wherein the granular material is composed of a plurality of types having different shapes.   32. The connecting member according to claim 31, wherein the connecting member is a traction link that connects the second connecting member projecting downward from the vehicle body and the carriage frame.   37. The connecting member according to claim 36, wherein the traction link is hollow, and the container is configured by using a cylindrical portion between the both ends of the traction link, and the object is placed in the cylindrical portion. A connecting member characterized by the above. The connecting member according to claim 37, wherein the traction link has an oval shape in which a longitudinal direction is longer than a lateral direction,
A height dimension of the ellipse of the traction link on the second connecting member side is smaller than a height dimension height of the ellipse of the traction link on the carriage frame side;
A connecting member characterized by the above.   The connecting member according to claim 37 or 38, wherein the object is a granular material.   40. The connecting member according to claim 39, wherein there are joints for connecting to the bogie frame and the second connecting member at both ends of the cylindrical part, and at least one of the joints has a hole opened in the cylindrical part. The opening is closed by a rubber bush disposed at the joint.   32. The connecting member according to claim 31, wherein the container is installed outside the connecting member.   42. The connection member according to claim 41, wherein the object is a granular body.   32. The connection member according to claim 31, wherein the connection member is a damper.   32. The connecting member according to claim 31, further comprising a rubber seat disposed between the container and the connecting member.   45. The connecting member according to claim 44, wherein the rubber seat is a multilayer.   32. The connecting member according to claim 31, wherein the connecting member is a bolster anchor.

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