US3837293A

US3837293A - Railway truck bolster and side frame

Info

Publication number: US3837293A
Application number: US00296876A
Authority: US
Inventors: O Neumann; F Korpics
Original assignee: Amsted Industries Inc
Current assignee: Amsted Industries Inc
Priority date: 1972-10-12
Filing date: 1972-10-12
Publication date: 1974-09-24
Anticipated expiration: 1991-09-24
Also published as: CA984224A

Abstract

A railway truck wherein a bolster is supported in the windows by a pair of side frames and said bolster has a U-shaped stiffening member raised above the bolster top wall on each end thereof, said member extending from side to side intermediate friction shoe pockets defined by said bolster. The compresssion member of said side frame defines a downwardly opening U-shaped channel capable of receiving therein said U-shaped stiffening member of the bolster in a telescoping relationship. The arrangement provides for greater length of both the control spring columns and load spring columns.

Description

United States Patent n 1 Neumann et al.

[451 Sept. 24, 1974 RAILWAY TRUCK BOLSTER AND SIDE FRAME [75] Inventors: Otto Walter Neumann, Chicago;

' Frank Joseph Korpics, Streamwood,

both of 111.

[73] Assignee: Amsted Industries Incorporated,

Chicago, 111.

[22] Filed: Oct. 12, 1972 [21] Appl. No.: 296,876

[52] US. Cl 105/197 DB, 105/202, 105/206 R,

[51] Int. Cl. B6lf 5/06, B61f 5/12, Fl6f1/06 [58] Field of Search 105/197 DB, 202, 206 R, 105/226 [56] References Cited UNITED STATES PATENTS 9/1953 Clasen 105/197 DB 11/1955 Settles 105/206 R X 2,805,630 9/1957 Couch 105/197 DB 2,974,610 3/1961 Quinn et al 105/197 DB R20,723 5/1938 Webb 105/197 DB Primary Examiner-M. Henson Wood, Jr. Assistant Examiner-l-loward Beltran [5 7 ABSTRACT 4 Claims, 10 Drawing Figures mmwsmmw 3,831,293

'I'IIIIIIII I 55 win RAILWAY TRUCK BOLSTER AND SIDE FRAME This invention relates to railway vehicles and more particularly to improvements in cast steel truck bolsters and side frames.

With the advent of larger railway vehicles and heavier loading, the need has arisen to structurally improve certain parts of the car truck that are subject to high stresses during actual service conditions.

Hoowever, it is imperative that any improvements advanced to structurally improve components of the railway car truck also exhibit satisfactory ride characteristics. As the capacity of railway vehicles increased, it has become increasingly more difficult to maintain the required ride characteristics merely because of the increased load range. This is due to the fact that a given load for a railway car under service conditions may range from a capacity load to near empty car conditions.

Accordingly, an object of this invention is to provide an improved railway truck with considerably improved strength qualities that is capable of withstanding severe dynamic service loading while at the same time providing improved ride characteristics over a continuous range of car loads.

Other objects will become apparent from the following description and appended claims, taken in conjunction with the accompanying drawings wherein:

FIG. 1 is a fragmentary perspective view of a freight car truck embodying a preferred form of the invention, the view'being taken from one outboard end of the bolster;

FIG. 2 is a partial sectional view taken in the transverse vertical plane indicated by the line 2-2 of FIG.

FIG. 3 is an outboard side elevational view of a railway car truck side frame;

FIG. 4 represents a top plan view of a portion of the compression member of the side frame shown in FIG. 3;

FIG. 5 is a further fragmentary sectional view taken in the vertical transverse plane indicated by the line 55 of FIG. 3 which passes through the compression member of the side frame;

FIG. 6 is a side elevation of one end of the bolster;

FIG. 7 is a top plan view showing one end of the bolster structure;

FIG. 8 is a top plan view representing another embodiment of the compression member of the side frame;

FIG. 9 is a sectional view taken in the vertical transverse plane indicated by the line 9-9 of FIG. 8 which passes through the compression member of the side frame; and

FIG. 10 is an exploded perspective view of the truck bolster, friction shoes and control springs showing more clearly the improved construction.

Referring first to FIG. I which illustrates a portion of a truss type railway truck, the side frame indicated generally at 10 is seen to comprise a tension member 12 and a compression member 14 interconnected by spaced vertical colums 16, the sides of which form a window 18 (FIGS. 1 and 3) substantially rectangular in shape. The side frame 10 is supported in the usual manner by wheel and axle assemblies 19, a portion of which can be seen in FIG. 1.

It should be understood that the railway truck for the purpose of the present disclosure may be considered identical at both sides thereof, and for the sake of brevity only that portion shown will be described in detail.

The window 18 is adapted to receive the end of the bolster, generally indicated at 20. The lower surface 22 at the end of the bolster 20 is supported by a plurality of support spring groups 24 which rest at their lower ends on the side frame tension member 12. In opposite side walls 26 at each end of the bolster 20 are wedgeshaped receiving pockets 28 which open outwardly toward the side frame columns 16 and have an inclined inner wall or sloped surface 30 which has a width corresponding substantially to the width of the wedgeshaped friction shoe 32 positioned therein.

The inclined inner wall 30 (FIG. 10) that projects from each pocket above the top wall 34 of the bolster 20 is connected by an integrally cast hood or stiffener 35 which extends across the width of the top wall 34. The improved construction of the bolster 20 greatly increases the strength of the inclined or sloped surface 30 in the bolster pocket 28.

The use of the arrangement hereinbefore described provides the stiffening required to insure the maximum projection of the sloped surfaces 30 of the bolster 20. This U-shaped stiffener 35 provides direct support between opposing sloped surfaces 30 and eliminates any tendency for the sloped surfaces to break off and pivot toward each other around the line of intersection formed by the bolster top wall 34 and the sloped surfaces 30.

One wedge-shaped friction shoe 32 is operatively carried in each pocket 28 and defines an inclined surface 36 corresponding to and frictionally engaging the inclined wall or sloped surface 30 of the pocket 28. The lower surface 41 of the wedge-shaped friction shoe 32 is engaged by the upper end of a control spring 38 which is disposed between said friction shoe 32 and the tension member 12 of the side frame 10. The inclined inner wall 30 therefore provides an inclined thrust area equal to, that of the engaged portion of the inclined surface 36 of the wedge-shaped friction shoe 32.

In the past such an arrangement could not have been utilized because of the additional height requirements needed to accommodate the U-shaped stiffener 35 when the end of the bolster 20 is positioned in the side frame window 18. Any attempt to use the arrangement would result in substantially increasing the height of the side frame which in turn results in prohibitive adjustments in car height and coupler height, both of which must remain within established ranges. Alternatively one would have to reduce the height of the springs which support the bolster, thereby insuring clearance for the U-shaped stiffener 30. However, such an adjustment in spring height is undesirable inasmuch as it requires an increase in the spring rate, which in turn increases the stiffness of the suspension, resulting in a harsher rebound requiring additional snubbing action. Also such a stiff suspension would result in an extremely rough ride under light car conditions.

The aforementioned problems having been overcome by improved construction of the compression member 14 of the side frame 10 to allow the U-shaped stiffener 35 to be received by the compression member 14in a telescoping manner. Such an arrangement does not require any change in the height of the side frame, nor does it require the shortening of the springs.

The improved compression member 14 is downwardly opening U-shaped channel 40, as best seen in FIG. 5, devoid of tie straps and open on the underside thereof, said opening being defined by parallel bifurcated side portions 42 that extend along the underside of the compression member intermediate the vertical columns 16 of the side frame 10.

Formed on each of the bifurcated side portions 42 is a flange 44 having external extensions 46. The flange 44 has greater thickness than either of the side portions 42 of the top wall 48 of the U-shaped channel 40. The thickness and shape of the flange 44 are determined by the load necessary to produce crippling of the compression member; the greater the load the thicker the flange 44. However, it is important to maintain adequate spacing between the flanges 44 to insure the unimpeded motion of the bolster stiffener 35 therebetween.

Such as arrangement of bolster 20 and side frame allows for the maximum projection of the sloped surfaces 30 which enables the friction shoe 32 to be positioned higher in the pocket 28 of the bolster 20.

Thus it can be seen that the abovementioned arrangement enables the entire raised portion of the bolster stiffener 35 to be received in a complementary opening in the side frame 10 compression member 14, thereby allowing maximum elevation of the bolster in the side frame opening 18 which is required for insertion of long travel spring groups 24 with the minimum side frame opening 18. Maximum projection of the sloped surfaces 30 is also provided, thereby enabling each friction shoe 32 to be positioned higher in the bolster pockets 28 which in turn substantially increases the length of the control springs 38 associated with each of the friction shoes 32.

The resulting increased length of both the support springs 24 and control springs 38 results in a softer load rate for the springs; which insures increased reserve capacity without approaching the stress limitations of the springs. Increased spring length also means greater reserve spring travel which reduces the danger of damage to the springs and cargo by more effectively resisting a solid condition of the springs.

FIGS. 8 and 9 illustrate another embodiment of the invention wherein the compression member 14 of the side frame 10 is flared in the mid portion. That portion of the compression member 14 between the vertical columns is a flared U-shaped channel 50 opening downwardly. The flared U-shaped channel 50 has a top wall 52 and bifurcated side portions 54 all having substantially the same thickness. Extending from each of the side portions 54 intermediate the spaced vertical columns 16 are flanges 56. The flanges 56 have an external extension 58 extending the full length of the side portions 54. The flanges 56 in the mid portion of the suject to the maximum deflection. The distance between the two internal extensions 60 is greater than the width of the stiffener 35 on the bolster 20, thereby allowing the stiffener 35 to move freely inside the flared U-shaped channel 50 of compression member 14. The internal extension 60 of the flange 56 blends into the side portion 54 near the ends of the flared U-shaped channel 50.

The terms and expressions which have been employed are used as terms of description and not of limitation, and there is no intention, in the use of such terms and expressions, of excluding any equivalents of the features shown and described or portions thereof, but recognize that various modifications are possible within the scope of the invention claimed.

We claim:

1. A railway truck side frame comprising a horizontally disposed compression and tension members connected by a pair of spaced vertical columns defining an opening therebetween, said compression member defining a downwardly opening channel intermediate said spaced columns, said channel having downwardly depending legs along the edges thereof forming a generally downwardly opening U-shaped cross-section, the mid-portion of said channel being flared outwardly from said spaced columns so that said U-shaped channel has a greater width in its mid-portion than the end portions at said columns, and a flange extending along the lower extremity of each of said legs.

2. A railway car truck side frame according to claim 1 wherein said flange extends into said opening.

3. In a railway car truck, the combination comprising a side frame having compression and tension members connected by a pair of spaced columns and defining an opening therebetween, said compression member being bifurcated and having downwardly depending side portions on the underside thereof defining a downwardly opening channel intermediate said columns, said side portions being relatively closely spaced from each other at the extremities of said channel adjacent said columns, and said side portions being relatively widely spaced from each other at the mid-portion of said channel; and a bolster supported by said side frame intermediate said columns and having upper and lower walls connected by spaced side walls, said bolster defining friction shoe receiving pockets on opposite sides thereof and stiffening means extending across said upper wall and engaging said pockets, said stiffening means being receivable by said channel.

4. In a railway car truck, the combination comprising a side frame having upper and lower members spanning a pair of spaced columns defining a window, said upper member defining a downwardly opening channel wider at its mid-portion that at its extremities at said columns, a bolster supported by said side frame intermediate said members, said bolster defining friction shoe receiving pockets on opposite sides thereof, and stiffening means extending across said bolster and engaging said pockets above its upper wall, said stiffening means being receivable in said channel.