JPH0640051Y2 - Railcar bogie towing structure - Google Patents

Description

[Detailed Description of the Invention] [Industrial field of application] The present invention is a bolsterless bogie and a bogie with a bolster that allow relative movement in the turning direction between the car body and the bogie while allowing the traction force in the traveling direction of the rail car between them. The present invention relates to a towing portion structure of a railway vehicle bogie, and more particularly to a towing portion structure of a railway vehicle bogie that prevents sliding between the inner and outer circumferences of a cylindrical cushioning member and a center pin and a cylindrical hole.

[Conventional technology]

In the conventional trolley structure for a bolsterless bogie and a bogie with a bolster, the center pin is fixed to the upper member that moves integrally with the vehicle body in the traveling direction and the turning direction of the railway vehicle, and the cylindrical hole is the traveling hole of the railway vehicle. Formed in the lower member that moves integrally with the bogie frame in the direction of turning and in the turning direction, the center pin is inserted, and for sliding to allow relative movement between the center pin and the lower member in the turning direction of the railway vehicle. The required small space is formed between the central pin and the cylindrical hole in the radial direction. This sliding causes wear of the parts, and the slight space (play) required for sliding causes noise due to the collision between the center pin and the lower member.

[Problems to be solved by the device]

The purpose of this invention is to eliminate the sliding parts where the center pin and the lower member move relative to each other and solve the problems of wear and noise.

[Means for Solving the Problems]

The invention will be described using the reference numerals of the drawings corresponding to the embodiments.

The traction structure for a railcar bogie according to claim 1 comprises an upper member (18,46) that moves integrally with the vehicle body (16) in the traveling direction and the turning direction of the railcar, and the upper member (18,46). A lower member (26, 35) that is arranged on the lower side and integrally moves with the bogie frame in the traveling direction and the turning direction of the railway vehicle;
The center pin (22) fixed to the upper member (18, 46) at the upper end and the center pin (2) formed on the lower member (26, 35).
2) a cylindrical hole (28) inserted therethrough, a cylindrical insertion space (39) formed between the center pin (22) and the cylindrical hole (28) in the radial direction, and a cylindrical elastic body (12). And a plurality of rigid rings (14) fixed to the cylindrical elastic body (12) at intervals in the height direction of the cylindrical elastic body (12), the height of the cylindrical insertion space (39) The cylindrical cushioning member (10, 10) that is inserted into the cylindrical insertion space (39) over the entire length
b) and a pad plate (40) fixed to the lower surface of the center pin (22) to compress the cylindrical cushioning members (10, 10b) in the height direction. The inner diameter, the outer diameter and the height of the cylindrical cushioning member (10, 10b) in the free state are larger, smaller and larger than the inner diameter, the outer diameter and the height of the cylindrical insertion space (39), respectively.

In the towing portion structure of the railcar bogie of claim 2, the bogie is a bolsterless bogie, and the upper member (18, 46) is the underframe (1
8) and the lower member (26,35) is a towbar (26,35)
Is.

In the towing portion structure of the railcar bogie of claim 3, the bogie is a bolstered bogie, and the upper member (18, 46) is a pillow (4).
6), and the lower members (26, 35) are horizontal (35).

In the towing portion structure for a railcar bogie according to claims 4 and 5, the rigid ring (14) is embedded in the cylindrical elastic body (12) or fixed to the inner circumference or outer circumference of the cylindrical elastic body (12). Has been done.

[Action]

In the free state, since the inner diameter and the outer diameter of the cylindrical cushioning member (10, 10b) are larger and smaller than the inner diameter and the outer diameter of the cylindrical insertion space (39), respectively, the cylindrical cushioning member (10, 10b) is Cylindrical insertion space (39) between the center pin (22) and the cylindrical hole (28)
To the entire height of the cylindrical insertion space (39). After the cylindrical cushioning member (10, 10b) is inserted into the cylindrical insertion space (39), the backing plate (40) is fixed to the lower surface of the center pin (22), so that the cylindrical cushioning member (10, 10b).
The cylindrical elastic body (12) of b) is compressed in the height direction to decrease and increase the inner and outer diameters, respectively. Rigid Ring (14)
Is distributed in the height direction of the cylindrical elastic body (12) and suppresses the portion of the cylindrical elastic body (12) near the rigid ring (14) from increasing the distance to the rigid ring (14), A change in the inner and outer diameters of the cylindrical elastic body (12) is suppressed. Then, as a result of the plurality of rigid rings (14) being appropriately distributed in the height direction of the cylindrical elastic body (12), the cylindrical cushioning member (10, 10).
In b), the wall thickness is made uniform in the height direction and the circumferential direction, and the surface pressure of the cylindrical buffer member (10, 10b) swells in the radial direction to the center pin (22) and the cylindrical hole (28). , Becomes uniform in the height direction. Further, due to the decrease of the inner diameter and the increase of the outer diameter of the cylindrical cushioning member (10, 10b) due to the compressive force from the contact plate (40), the inner and outer circumferences of the cylindrical cushioning member (10, 10b) are centered. The center pin (22) and the cylindrical hole (28) are engaged with the peripheral portions of the pin (22) and the cylindrical hole (28), and in the relative rotation of the central pin (22) and the cylindrical hole (28) in the turning direction. Relative sliding with the peripheral portion of the cylindrical elastic body is avoided, and the intermediate portion in the thickness direction of the cylindrical elastic body (12) is elastically deformed by the shear load in the peripheral direction.

〔Example〕

 The invention will be described below with reference to embodiments.

FIG. 6 is a side view of one half of the cylindrical cushioning member 10 in a free state as a cross section, and FIG. 7 is a bottom view of the cylindrical cushioning member 10 in a free state. The cylindrical cushioning member 10 has a cylindrical rubber 12 and a plurality of metal rings 14 embedded in the cylindrical rubber 12, and the cylindrical rubber 12 has a radial wall thickness of a height. The direction is made uniform, and the inner and outer diameters and height are D1 and
Designated as D2 and H. The metal rings 14 are arranged at equal intervals in the height direction.

FIG. 8 is a side view showing another cylindrical cushioning member 10b with one half section taken as a cross section. In the cylindrical cushioning member 10b, the metal ring 14 is not embedded in the cylindrical rubber 12,
The cylindrical rubber 12 is fitted into annular grooves formed on the outer peripheral surface of the cylindrical rubber 12 at equal intervals in the height direction. The inner and outer diameters and height of the cylindrical cushioning member 10b are set to be equal to those of the cylindrical cushioning member 10.

Although illustration is omitted, the metal ring 14 is also the cylindrical cushioning member 10 fitted in the annular groove formed in the inner peripheral surface of the cylindrical rubber 12 at equal intervals in the height direction, Fig. 6 ~
Similar to the cylindrical cushioning members 10 and 10b shown in FIG. 8, the effect (FIG. 3) described later can be obtained.

FIG. 9 is a front view of a bolsterless carriage including a towing portion structure. The vehicle body 16 has an underframe 18 at the bottom and is mounted on a bolsterless cart 20. The center pin 22 is fixed to the lower surface of the underframe 18 by a fixture 24 at the upper end, and the towbar 26 of the bolsterless bogie 20 is displaceable in the left and right directions.
A cylindrical hole 28 is formed at the center in the left-right direction. The left and right dampers 30 have a towing bar 26 and a side beam 32 at both ends.
Is rotatably connected to each other to damp the displacement of the towbar 26 with respect to the lateral beam 32 in the left-right direction. The cushioning rubbers 34, 34 are integrally fixed to the side beam 32 and fixed to the side beam 35, and restrict the lateral displacement of the towbar 26 by abutting on the side surface of the towbar 26 in the left-right direction. In addition, towbar
26 moves integrally with the side beam 32 and the side beam 35 in the traveling direction of the railway vehicle by a predetermined tow bar 101. The low lateral rigidity air spring 36 has an underframe 18 at the upper and lower ends, respectively.
And the side beam 32 so as to elastically support the vehicle body 16 on the side beam 32 in the vertical direction, and to dampen the vertical movement of the vehicle body 16 with respect to the side beam 32. The wheel 38 is integrally and rotatably fixed to an end of an axle (not shown), and the axle supports the side beam 32 via a shaft spring (not shown).

1 and 2 are an exploded view and an assembly view of a towing portion structure of the bolsterless truck 20. The center pin 22 is inserted into the cylindrical hole 28 of the towing bar 26 from above, and a cylindrical insertion space 39 is formed between the center pin 22 and the cylindrical hole 28 in the radial direction of the center pin 22. d1, d2 and h are the inner diameter of the cylindrical insertion space 39 (= the diameter of the center pin 22),
The external diameter (= the diameter of the cylindrical hole 28) and the height are shown, and the following relationships are given between the respective dimensions of the cylindrical insertion space 39 and the respective dimensions of the cylindrical cushioning member 10.

D1> d1, D2 <d2 and H> h The cylindrical cushioning member 10 is inserted into the cylindrical insertion space 39 so as to be fitted to the outside of the center pin 22, and the insertion is D1>
Smoothing due to d1 and D2 <d2. The pad plate 40 is put on the lower surface of the cylindrical cushioning member 10 after the cylindrical cushioning member 10 is inserted into the cylindrical insertion space 39, and the plurality of bolts 42 are attached to the pad plate 40.
After being inserted into the center pin 22, the contact plate 40 is screwed into the lower end portion of the center pin 22, and the contact plate 40 is tightened to the lower surface of the center pin 22, whereby the cylindrical cushioning member 10 has the cylindrical insertion space 39 by the above H> h. Inside is compressed in the height direction. Although illustration is omitted, the cylindrical cushioning member 10b of FIG. 8 is also assembled in the same manner as the cylindrical cushioning member 10.

Here, a metal ring is used as the cylindrical cushioning member 10.
The significance of using the cylindrical rubber 12 in which 14 is fixed will be described. FIGS. 3 (a) and 3 (b) show changes in shape of the vertical cross section of the cylindrical cushioning member 10 when free and when compressed in the height direction. When the cylindrical cushioning member 10 is compressed in the height direction, the inner and outer diameters thereof are reduced and increased, respectively. The metal ring 14 is distributed in the height direction of the cylindrical rubber 12 and suppresses the portion of the cylindrical rubber 12 in the vicinity of the metal ring 14 from increasing the distance to the metal ring 14 and the cylindrical rubber 12 Suppress changes in inner and outer diameters of. And multiple metal rings
As a result of 14 being appropriately distributed in the height direction of the cylindrical rubber 12, the cylindrical cushioning member 10 expands in the radial direction while the wall thickness is made uniform in the height direction and the circumferential direction. On the other hand, FIGS. 4 (a) and 4 (b) show changes in the shape of the vertical cross section of the cylindrical rubber 12 when the cylindrical rubber 12 is free and when it is compressed in the height direction. As a result of the absence of the metal ring 14, the cylindrical rubber 12 has a shape that is significantly bulged in the radial direction at the central portion in the height direction as compared with both end portions.

Therefore, when the cylindrical cushioning member 10 consisting of only the cylindrical rubber 12 as shown in FIGS. 4 (a) and 4 (b) is used, the entire inner peripheral surface of the cylindrical cushioning member 10 is covered. The surface pressure between the center pin 22 and the peripheral portion of the cylindrical hole 28 becomes non-uniform, which causes various adverse effects such as wear due to partial sliding and shortened life. On the other hand, the surface pressures between the inner and outer circumferences of the cylindrical cushioning member 10 and the center pin 22 and the cylindrical hole 28 of FIGS. 3 (a) and (b) are substantially uniform in the height direction and the circumferential direction of the cylindrical cushioning member, The above-mentioned harmful effects hardly occur.

FIGS. 5 (a) and 5 (b) show the state of the cylindrical cushioning member 10 when the center pin 22 and the towbar 26 are in the neutral relative rotational position and when they are relatively rotated. The cylindrical cushioning member 10 uniformly reduces and increases the inner and outer diameters in the height direction by the compressive force from the contact plate 40. As a result, the inner and outer circumferences of the cylindrical cushioning member 10 have a center pin 22 and a cylindrical hole.
In the relative rotation of the center pin 22 and the cylindrical hole 28 in the turning direction by engaging with the peripheral portion of 28, relative sliding between the center pin 22 and the peripheral portion of the cylindrical hole 28 is avoided, and the cylindrical rubber 12 The middle portion in the thickness direction elastically deforms due to the shear load in the circumferential direction.

FIG. 10 shows a trolley with a bolster equipped with a cylindrical cushioning member 10.
FIG. 44 is a front view of 44. The same parts as those in FIG. 9 are designated by the same reference numerals and the description thereof is omitted. Bogie with bolster 44
The pillow baffle 46 is disposed between the underframe 18 and the lateral beam 35 in the vertical direction, and the air springs 48 are fixed to the underframe 18 and the pillow brace 46 at the upper and lower ends, respectively. It is fixed to the burr 46 and allows relative movement of the both in the vertical direction and attenuates it. The left-right damper 50 extends in the left-right direction,
Both ends are rotatably coupled to the pillow beam 46 and the side beam 32, respectively, to allow the relative movement of the pillow beam 46 and the side beam 32 in the left-right direction, and to attenuate them. The bogie with bolster 44 has a pillow brace in the traveling direction and the turning direction of the railway vehicle.
46 moves with the underframe 18 and the horizontal beam 35 with the side beam 32 integrally, the center pin 22 is fixed to the lower surface of the pillow beam 46, and the cylindrical hole 28 is formed in the horizontal beam 35. The cushioning member 10 includes a cylindrical insertion space 39 between the center pin 22 and the cylindrical hole 28.
In the same manner as in the case of the cylindrical cushioning member 10 in FIG. 9, the same effect is obtained as in the case of FIG.

[Effect of device]

In this invention, a cylindrical cushioning member interposed in a cylindrical insertion space between a center pin as a vehicle body side portion and a cylindrical hole as a bogie frame portion for transmitting a traction force in a traveling direction of a railway vehicle has a cylindrical shape. An elastic body and a plurality of rigid rings fixed to the cylindrical elastic body at intervals in the height direction of the cylindrical elastic body are provided. Therefore, when the cylindrical cushioning member is compressed in the height direction by the contact plate, the rigid ring suppresses the deformation of the cylindrical elastic body in the vicinity thereof,
Since a plurality of such rigid rings are appropriately distributed in the height direction of the cylindrical elastic body and arranged, the bulge of the cylindrical cushioning member during compression in the height direction is uniform in the height direction. Also, when the pulling force acts on the cylindrical cushioning member, the radial thickness of the cylindrical cushioning member is suppressed from being uneven in the circumferential direction. In this way, the center pin and the cylindrical hole and the cylindrical cushioning member are engaged with each other with an appropriate surface pressure over the entire contact surface, so that the life and function of the cylindrical cushioning member can be improved.

In the free state, the inner diameter and outer diameter of the cylindrical cushioning member are larger and smaller than the inner diameter and outer diameter of the cylindrical insertion space, so the cylindrical insertion between the center pin and the cylindrical hole during assembly and disassembly The insertion of the cylindrical cushioning member into the space becomes very smooth. Further, after the cylindrical cushioning member is inserted into the cylindrical insertion space, the cylindrical cushioning member swells in the radial direction uniformly in the height direction and engages the inner and outer circumferences with the center pin and the cylindrical hole. Even when the carriage and the carriage are relatively turned, relative sliding between the cylindrical cushioning member and the center pin and the cylindrical hole is avoided, and the durability and life of the cylindrical cushioning member are improved.

[Brief description of drawings]

The drawings relate to an embodiment and a comparative example of the present invention, FIGS. 1 and 2 are an exploded view and an assembly view of a towing portion structure in a bolsterless bogie, and FIGS. 3 (a) and 3 (b) are free time and a height direction. The figure which shows the shape change of the vertical cross section of the cylindrical cushioning member at the time of compression, FIG.4 (a) and (b) is a vertical cross section of the cylindrical rubber at the time of free of a cylindrical rubber alone, and a height direction compression. 5 (a) and 5 (b) are views showing the state of the cylindrical cushioning member when the center pin and the towing bar are in the neutral relative rotation position and when they are relatively rotating, 6 is a side view of one half of the cylindrical cushioning member in a free state as a cross section, FIG. 7 is a bottom view of the cylindrical cushioning member in a free state, and FIG.
The figure is a side view showing another cylindrical cushioning member with one half section taken as a cross section, Fig. 9 is a front view of a bolsterless truck including a towing portion structure, and Fig. 10 is a truck with a bolster equipped with a cylindrical cushioning member. It is a front view. 10, 10b …… Cylindrical cushioning member, 12 …… Cylindrical rubber (cylindrical elastic body), 14 …… Metal ring (rigid ring), 16 ……
Car body, 18 ... Underframe (upper member), 20 ... Bolsterless bogie (carriage), 22 ... Center pin, 26 ... Towing bar (lower member), 28 ... Cylinder hole, 32 ... Sidebar ( Trolley frame), 35 ...
… Horizontal (lower member), 39 …… Cylindrical insertion space, 40 ……
Patch plate, 44 ... Bogie with bolster (bogie), 46 ... Pillow (upper member).

 ─────────────────────────────────────────────────── ─── Continuation of the front page (56) References JP-A-56-128263 (JP, A) Jikkoku 61-14927 (JP, Y2)

Claims (5)

[Scope of utility model registration request] 1. An upper member (18, 46) that integrally moves with a vehicle body (16) in a traveling direction and a turning direction of a railway vehicle,
Lower members (26, 35) which are disposed below the upper members (18, 46) and move integrally with the bogie frame in the traveling direction and the turning direction of the railway vehicle, and the upper members (26, 35) at the upper end ( 18, 46) a center pin (22), a cylindrical hole (28) formed in the lower member (26, 35) and inserted through the center pin (22), and the center pin in the radial direction. A cylindrical insertion space (39) formed between the (22) and the cylindrical hole (28), a cylindrical elastic body (12) and a space in the height direction of the cylindrical elastic body (12). A plurality of rigid rings (14) fixed to the cylindrical elastic body (12)
And a cylindrical cushioning member (10, 10b) inserted into the cylindrical insertion space (39) over the entire height of the cylindrical insertion space (39), and fixed to the lower surface of the center pin (22). And a pad plate (40) for compressing the cylindrical cushioning member (10, 10b) in the height direction, and the inner and outer diameters of the cylindrical cushioning member (10, 10b) in a free state A traction structure for a bogie of a railcar, wherein the height is larger, smaller and larger than the inner diameter, the outer diameter and the height of the cylindrical insertion space (39), respectively. 2. The dolly is a bolsterless dolly, the upper member (18, 46) is a underframe (18), and the lower member (26, 35) is a towbar (26, 35). The traction structure for a rail car bogie according to claim 1. 3. The trolley is a bolstered trolley, the upper member (18, 46) is a pillow beam (46), and the lower member (26, 35) is a horizontal beam (35). The towing part structure of a railcar bogie according to claim 1. 4. The towing portion structure for a rail car bogie according to any one of claims 1 to 3, wherein the rigid ring (14) is embedded in the cylindrical elastic body (12). 5. The railcar bogie according to claim 1, wherein the rigid ring (14) is fixed to one of the inner and outer circumferences of the cylindrical elastic body (12). Towing structure.