RU2467901C2 - Axlebox guide - Google Patents

Abstract

FIELD: transport.

SUBSTANCE: invention relates to railway rolling stock. Proposed axlebox guide comprises bearing devices. Bearing device consists of thrusts with concaved surfaces fitted on bogie frame and axlebox and rod arranged there between and having bulged surfaces on ends. Radius of curvature of the latter is one and a half to three times smaller than that of concaved surfaces. Rated length of the rod along the axis of symmetry should equal the quotient of the division of double product of radii of both surfaces by their difference.

EFFECT: simplified design.

10 dwg, 1 tbl

Description

The present invention relates to rolling stock of railway transport and is intended for use in axle boxes of locomotives and wagons, and can also be used in cars, swinging conveyors and other machines.

There are various designs of axle boxes: jaw, cylindrical, with rubber-metal hinges, etc. Each design has positive qualities and disadvantages.

The disadvantages of the jaw and cylindrical guides include abrasive wear of rubber joints, a significant increase in the stiffness of spring suspension.

Closest to the claimed proposed invention is the design of jet thrust according to [1].

In the design of such reactive thrust, we used jumpers and crackers with concave surfaces rolling over the convex surfaces of the supports and contactor, since the radii of concave surfaces are one and a half to three times larger than the convex radii, due to which rolling occurs instead of sliding, which significantly reduces wear of surfaces compared to hinges of sliding. The thrust works in tension and compression.

A significant drawback of this design when used in the axle box assembly is its complexity, since seventeen parts and six higher kinematic rolling pairs are used in it.

The technical result of the invention is to simplify the design of the axle box assembly.

The technical result is achieved by the fact that instead of complex structures in the horizontal plane, the axle box and sidewall brackets are connected by simplified supporting devices, each of which consists of two stops with concave surfaces rigidly connected to the axle box and the frame of the cart, and a rod installed between them with convex surfaces at the ends while the radius of the concave surfaces is one and a half to three times the radius of the convex surfaces. The number of parts was reduced to three, and the highest kinematic rolling pairs - to two. To ensure rectilinear movement of the axle box, the length of the rod along the axis of symmetry should be dependent on the radii of the surfaces and be within the limits defined by the formula

where L is the length of the rod;

R is the radius of concave surfaces;

r is the radius of convex surfaces.

The figure 1 shows the axle box with two load-bearing devices 1 located on both sides of the axle box, and in figures 2 and 3 the design of the device on an enlarged scale in two projections.

Each device consists of a rod 2 with convex surfaces of radius r at the ends and two stops with concave cylindrical surfaces of radius R: an emphasis 3 mounted on the axle box, and an emphasis 4 rigidly mounted on the bracket of the trolley frame. The length of the rod at the points lying at the intersection of convex surfaces with the axis of symmetry is indicated by the letter L.

In addition to the general view, detailed drawings are shown in two projections: in Figures 4 and 5, a rod drawing, in Figures 6 and 7 a drawing of an emphasis mounted on an axle box, and in Figures 8 and 9 a drawing of an emphasis on the frame of the cart.

To transfer the gravity of the rod and the tangential forces, cylindrical surfaces 5 of radius ρ are provided with centers at points 6 and 7 on the rod. These surfaces are in contact with the surfaces of the grooves 8 and 9 on the stops 3 and 4.

Frame forces from the trolley frame to the rods and from the rods to the axle box are transmitted through surfaces 10 on the rods and surfaces 11 and 12 on the stops.

Box guide works as follows.

With vertical vibrations of the trolley frame, the convex surfaces of the rod 2 roll over the concave surfaces of the stops 3 and 4. Lateral vibrations of the trolley frame relative to the longitudinal horizontal axis are provided with the ability to rotate the stops 3 relative to the axle box due to the spike 13 on the emphasis and jacks in the axle box.

Disclosure of invention

On the rolling stock of railways, the axle box oscillates with the upper structure of the track, and the frame of the trolley is relative to the axle box. The figure 10 shows the design scheme in which the frame of the trolley is stationary, and the axle box vibrates relative to the frame of the trolley. The horizontal connection between the axle box and axle box opening of the trolley frame is carried out by two rods 1, on the ends of each of which convex surfaces of radius r are made. Each rod rests on concave surfaces of radius R of the stop 2 mounted on the axle box and the stop 3 on the frame of the trolley. The bar length is L.

We assume that the axle box does not rotate about its axis. This can be achieved by installing springs of equal stiffness, as well as installing three or four load-bearing devices.

Consider only the left leash. We introduce a fixed coordinate system zox: the x axis is directed horizontally, z is vertically. For an independent variable, we take the angle φ. On the axle of symmetry of the surface R on the axle box, we select a point S and two contact points: K with a stop 3 and K 'with a stop 2.

When moving the axle box (point S) upward by the value Z, the bar will rotate through an angle φ. The length of the arc traversed by the contact point along the convex surface from the middle position is rα, and along the concave R (α-φ). If rolling occurs without sliding, then these arcs are equal, i.e.

From this equality we express the kinematic relationship between the angles

We write the parametric equations of motion of the points S and K depending on the angles φ and α, while the coordinates of the point S are written without indices, and the points K with the index k .

After substituting instead of α-φ from (3) we get:

The horizontal forces from the axle box to the carriage frame and vice versa are transmitted along the line K'K connecting the contact points K 'on the axle box and K on the carriage frame. The tangent of the angle Θ of the slope of the line K'K to the horizontal axis is determined by the ratio of the difference in the vertical coordinates of these points to the difference in horizontal.

After the stand (8) ... (11) and transformations

Our analysis showed that the allowable angular amplitude of the rod oscillations should be limited to 30 °. So that the horizontal forces of the rods do not affect the vertical vibrations, tgΘ must tend to zero. The denominator in formula (13) is always positive, since the cosine of the angle with positive and negative φ is positive, therefore, so that tgΘ is equal to zero, the numerator must be equal to zero.

From the expression of the numerator equal to zero, we express the length of the rod L

In the middle position (φ = 0) there is a% uncertainty. After disclosing it according to the rule of Lital,

If φ ≠ 0, but R = 2r, then the length of the rod L does not depend on the angle φ and is equal to

If φ ≠ 0 and R ≠ 2r, then, so that the trajectory of the point K 'represents a straight line, the length of the rod L must be variable and dependent on the change in the angle φ. Structurally, this is not possible.

Therefore, we take the value of L constant determined by the formula (15). In special cases: with R = 1,5r, L = 6r, with R = 3r, L = 3r.

и φ, проведены расчеты кинематических характеристик буксового узла.By formulas (15), (8) and (9), substituting the values of L,

and φ, the kinematic characteristics of the axle box assembly were calculated.

The results are shown in the table, where Δx = f (0) -f (φ).

To determine the characteristics z _S , x _S and Δx, the data from the table must be multiplied by the radius r.

Conclusions from the analysis of the table.

.1. The first option is optimal

.

2. In the second embodiment, the maximum angular amplitude of the rod should be limited to 20 °.

с увеличением угла φ параметр x_S(φ), хотя и незначительно, возрастает. Поэтому, чтобы избежать заклинивания буксы, необходимо обеспечить начальный зазор при установке буксы.3. In the third embodiment

with an increase in the angle φ, the parameter x _S (φ), although slightly, increases. Therefore, in order to avoid jamming of the axle box, it is necessary to provide an initial clearance when installing the axle box.

в диапазоне от 1,5 до 3. По мере приближения отношения

к двум как с одной, так и с другой стороны, все характеристики будут приближаться к варианту 1.4. It is allowed to try on any values of the ratio of radii

in the range of 1.5 to 3. As the ratio approaches

to two, both on the one and on the other hand, all the characteristics will approach option 1.

The source of information

1. A.S. USSR No. 1687486, MKI B61F 5/00, declared 01.25.89, No. 4641385/11 and published on 10/30/91 in bull. Number 40.

Claims (1)

The axle box, including supporting devices, each of which consists of stops fixed to the trolley frame and axle box with concave surfaces and a rod installed between them with convex surfaces at the ends, the radius of which is one and a half to three times smaller than the radius of the concave surfaces, characterized in that the nominal the length of the rod along the axis of symmetry should be equal to the quotient of dividing the double product of the radii of the concave and convex surfaces by their difference.

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