EA039274B1 - Friction shock absorber - Google Patents

Abstract

The invention relates to the field of transport engineering, in particular, to vehicle shock absorbers. The objective is to improve efficiency and reliability of the absorbing device. The shock absorbing device (Fig. 1) comprises a housing (1) formed by wide walls (2), narrow walls (2') and a bottom (3), accommodating a friction unit (4) consisting of a cavity (P) with a bottom (5') and protruding with its outer end (T) from the body (1) of the pressure wedge (5), spacer wedges (6), fixed plates (7) equipped with lateral supports (8') of movable plates (8) and a base plate (9). Between the base plate (9) and the bottom (3), along the longitudinal axis (01) of the housing (1), a back-and-forth device (10) is located that is braced through a centering rod connection (13, 16), resting at one end in a bush (14) of the bottom (3) of the housing (1), and on the other end on the bottom (5') of the cavity (P) of the pressure wedge (5). The pressing wedge (5) is provided with projections (11), the ends (V) of which face the bottom (3) of the housing (1); on the projections (11) of the pressure wedge (5), curved surfaces (f) are formed, between which and the wide walls (2) of the housing (1) said gaps (z) are formed to provide the possibility of free rotation of the pressure wedge (5) relative to the longitudinal axis (O1). Other distinctive features of this invention and links between them are also described.

Description

The invention relates to the field of transport engineering and relates to friction shock absorbers of vehicles, mainly draft gears installed between train cars.

Known friction shock absorber [1, Patent RU164701, priority 11/11/2015, published 09/10/2016, bul. No. 25], containing a body with a neck formed by its walls and bottom, on which a pre-compressed reciprocating device is located, on top of which a friction assembly is located, consisting of a pressure wedge, friction wedges, a base plate, guide plates and movable plates. During operation and during transportation of such a friction damper, there is a risk of displacement of the friction assembly: the pressure wedge, friction wedges, base plate, movable plates and fixed plates can move in the transverse direction of the body due to gravity, wear of parts or shocks during transportation. This can lead to the fact that the friction assembly is displaced with its distortion, which in the future can lead to the loss of the specified characteristics of the apparatus, its jamming and failure.

This problem is solved in a friction shock absorber [2, Patent RU 2659366, priority 05/12/2017, published 06/29/2018, Bull. No. 19], taken as a prototype.

It contains a body having a bottom and a side wall defining an internal space of the body open from one end, a friction spacer block consisting of a pressure cone, friction wedges, fixed friction plates, movable friction plates, a base plate resting on a retaining-return device. The pressure cone is equipped with a limit stop with a width h for supporting, limiting displacement and/or warping in the transverse direction of the body wall with a width H. The fit of such a limit stop to the longitudinal wall with a width H of the body is provided by the contact of the flat surface of this limit stop with a width h, and, as described in the prototype [2], the ratio must be fulfilled, at which h is not less than 0.1*N. However, in practice, the flat shape of the limiting stop surface adjacent to the longitudinal wall of the housing with a width h has advantages inherent only in housings whose shape is close to ideal, namely when its transverse walls are perpendicular to the longitudinal ones, and their inner surfaces are flat. Otherwise, the flat shape of the restrictive stops adjacent to the walls of the housing turns out to be harmful, and the mentioned ratio, in which h is not less than 0.1*N, only exacerbates this harmful effect.

This is due to the fact that the housings of modern friction shock absorbers (draft absorbers) are made exclusively by casting, which undoubtedly causes errors in their shape, expressed in the non-perpendicularity of the transverse and longitudinal walls, as well as the non-flatness of their internal surfaces. Most often, this manifests itself in the fact that the walls form the shape of a parallelogram, and on their inner surfaces sagging, concavity or convexity are formed. In this case, the movable plates are arranged parallel to the transverse walls of the housing, but not perpendicular to its longitudinal walls, as a result of which the entire friction spacer block tends to rotate relative to the longitudinal axis, but flat limit stops adjacent to the longitudinal walls of the housing, as in the prototype [2], do not allow pressure the cone to make such a turn, since their edges (edges) are rested against the longitudinal walls. Moreover, the width h of the limit stops is greater than 0.1*H, the more difficult is the possibility of such a rotation of the pressure cone. As a result, the mutual fit of the parts of the friction spacer block is violated, which makes the draft gear inefficient and unable to dampen the shock external load.

The above-described disadvantages of the friction damper according to the prototype [2] reduce the efficiency and reliability of its operation.

Therefore, the objective of the invention is to increase the efficiency and reliability of the draft gear by achieving a technical result to increase its ability to compensate for shape errors in the manufacture of its body, which would increase the prospects for the use of such a draft gear.

The problem is solved by the fact that the draft gear, containing a body (1) formed by the bottom (3), wide walls (2) and narrow walls (2'), inside which the friction assembly (4) is located, consisting of a cavity (P) with bottom (5') and protruding with its outer end (T) from the body (1) of the pressure wedge (5), spacer wedges (6), fixed plates (7), base plate (9) and movable plates (8) associated with narrow walls (2') of the body (1) and equipped with side supports (8'), while between the base plate (9) and the bottom (3), along the longitudinal axis (O1) of the body (1), a reciprocating device ( 10), pulled together through a centering rod connection (13, 16), resting at one end on the bong (14) of the bottom (3) of the body (1), and at the other end on the bottom (5') of the cavity (P) of the pressure wedge (5 ), which is placed with the formation of gaps (z) between it and the wide walls (2) of the housing (1), has distinctive features: projections (11) are formed on the pressure wedge (5), the ends (V) of which facing the bottom (3) of the housing (1), as well as on the protrusions (11) of the pressure wedge (5) curved surfaces (f) are formed, between which and the wide walls (2) of the housing (1) the said gaps (z) are formed with ensuring the possibility of free rotation of the pressure

- 1 039274 wedges (5) relative to the longitudinal axis (O1).

Such distinctive features make it possible to increase the efficiency and reliability of the draft gear due to the ability to adapt its friction assembly to shape errors in the manufacture of its body, as well as by increasing its working stroke together with reducing the mass of materials for its production.

Additional distinctive features of the invention, aimed at enhancing the above-mentioned advantages:

the mentioned curved surfaces (f) of the pressure wedge (5) are made inclined to the longitudinal axis (O1) of the body (1) and are continued with an inclination to it by bevels (F) located in the direction from the outer end (T) of the pressure wedge (5) to its ledges (11);

the protrusions (11) are made in the form of a trapezoid (B), the larger base (B1) of which is located on the side of the outer end (T) of the pressure wedge (5) and parallel to it, and the smaller base (B2) is placed along the ends (V) of the protrusions (11 ), and the length (Lv) of the smaller base (B2) of the trapezoid (B) at the protrusions (11) does not exceed 32 mm;

curved surfaces (f) are made of radius, the radius (R) of curvature of which is not more than 200 mm;

wide walls (2) of the housing (1) are made of variable thickness, and their thickness (a) at the interface with its narrow walls (2') is greater than their thickness (b) near the protrusions (11) of the pressure wedge (5);

the size of the gaps (z) between the wide walls (2) of the housing (1) and the curved surfaces (f) of the pressure wedge (5) is selected from the range of 1-6 mm;

the height (h) of the protrusions (11) does not exceed the length (Lv) of the smaller base of the trapezoid (B) at their ends (V);

the width (c) of the side supports (8') is variable decreasing in the direction away from the narrow walls (2') of the housing (1), while the outer surfaces (n) of the side supports (8') facing the wide walls (2) do not perpendicular to the plane (p) of contact of the movable plates (8) with narrow walls (2') and not parallel to the inner surfaces (m) of these side supports (8'), and the places of formation of the side supports (8') facing the fixed plates (7 ), machined, and the length (d) of the side supports (8') is variable with increasing in the direction from the pressure wedge (5) to the base plate (9);

the centering rod connection (13, 16) is made of a centering rod (13) with a head (13') and a nut (16) screwed onto it, and the bottom bolt (14) is made with a stepped hole (15) in which the head (13) is located ') passed through the reciprocating device (10) and the friction assembly (4) of the centering rod (13), on the opposite threaded end of which the nut (16) is screwed, placed on the bottom (5') of the cavity (P) of the pressure wedge (5) , in addition, roundings (r) and slopes (e) are made on the movable plates (8), and the value of which from the plane (p) of their fit to the narrow walls (2') is selected from the range of 10-30°, while the diameter (D ) of the centering rod (13) is not less than 32 mm, and the thickness (a, b) of the wide walls (2) and the thickness (g) of the narrow walls (2') of the housing (1) are selected from the range of 15-25 mm, and the thickness (t ) the movable plates (8) between the narrow walls (2') of the body (1) and the fixed plates (7) are selected from the range of 16-20 mm, and the height (H) of the bolt (14) is from 45 to 55 mm, its diameter (S) is from 55 to 65 mm, while the smaller diameter (s) of the stepped hole (15) in the bonk (14) is not less than 32 mm, and the larger diameter (s') of the stepped hole (15) is not more than 70 mm ;

spacer wedges (6) with their surfaces in contact with the pressure wedge (5), base plate (9) and fixed plates (7), as well as movable plates (8) with their contact with fixed plates (7) and narrow walls (2' ) surfaces, form friction pairs of friction, and the roughness of these contacting surfaces is not less than 2.5 microns.

The essence of the invention is illustrated by illustrations, where in Fig. 1 shows a plan view of a draft gear according to the invention; in fig. 2 view A in Fig. 1 on the draft gear according to the invention with local cuts; in fig. 3 shows the pressure wedge of the draft gear; in fig. 4 shows the pressure wedge in section C-C of FIG. 3; in fig. 5 shows a plan view of a draft gear according to the invention in a housing made with shape errors; in fig. 6 shows a separate top view of the movable plate; in fig. 7 shows view D of FIG. 6 on the movable plate; in fig. Figures 8 and 9 show variants of a stepped hole in a bonk on the bottom of the housing with a centering rod placed in it.

The draft gear (Fig. 1, 2, 5) contains a housing 1 formed by wide walls 2, narrow walls 2' and a bottom 3. Inside the housing 1 there is a friction assembly 4, consisting of a pressure wedge 5 provided with a cavity P with a bottom 5' (Fig. . 1-5), expansion wedges 6, fixed plates 7 (Fig. 1, 2, 5), movable plates 8 (Fig. 1, 2, 5-7) and base plate 9 (Fig. 1, 2, 5) . Between the base plate 9 and the bottom 3 placed reciprocating device 10, formed, for example, polymer elastic elements or steel springs.

The pressure wedge 5 is placed in the body 1 so that its outer end T, intended for the perception of external load Q (Fig. 2), is made protruding from the body 1, and the distance from the outer

- 2 039274 end T to the housing 1 corresponds to the working stroke of the draft gear, and the pressure wedge 5 is installed with the formation of gaps z between its curved surfaces f (Fig. 1, 3-5) and the wide walls 2 of the housing 1. It is more rational to perform curved surfaces f with radius , radius R (Fig. 1) curvature of which is not more than 200 mm. Otherwise, the shape of the curved surfaces f will be close to rectilinear, and there will be disadvantages inherent in the design of the prototype [2].

Wide walls 2 of the body 1, remote from the curved surfaces f of the pressure wedge 5 by the amount of gaps z, it is useful to perform a variable thickness, and their thickness a in places of interface with narrow walls 2' should be greater than their thickness b near the curved surfaces f of the pressure wedge 5 (Fig. 1). This is due to the fact that when an external load Q is applied, a spacer force acts on the narrow walls 2' from the side of the friction assembly 4, while the wide walls 2 have the ability to bend inside the housing 1. Such a bending is accompanied by a decrease in the distance between them, which can lead to clamping wide walls 2 of the pressure wedge 5. Therefore, to avoid such a phenomenon, the implementation of wide walls 2 of the body 1 of variable thickness is an effective way to prevent the pressure wedge 5 from jamming between them. In addition to this, the non-flatness of the curved surfaces f, in contrast to the prototype [2], allows you to keep constant gaps z between them and the wide walls 2 (Fig. 1), providing both a free rotation of the friction assembly 4 at an angle x (Fig. 5) to compensate for errors in the manufacture of housing 1, and the margin of the distance between the wide walls 2, selected by their protrusion into the housing 1 under the influence of an external load Q. The value of the gaps z, sufficient to achieve the above effect, is from 1 to 6 mm.

The possibility of adaptation of the friction unit 4 to the errors in the shape of the body 1 due to rotation through the angle x (Fig. 5) is also provided due to the configuration of the movable plates 8 (Fig. 1, 2, 5-7), on which the side supports 8' are formed, in contact with base plate 9. The width c of the side supports 8' is variable with decreasing in the direction from the narrow walls 2' of the body 1 due to the fact that the outer surfaces n of the side supports 8' facing the wide walls 2 are not perpendicular to the plane p of contact of the movable plates 8 with narrow walls 2'. The places of formation of the side supports 8', facing the body 1, are made with slopes e and roundings r, due to which it is possible both to fit the movable plates 8 to the narrow walls 2' of the body 1 in the contact plane p, and to freely rotate at an angle x relative to longitudinal axis O1 (Fig. 5), if necessary, while the outer surfaces of the n side supports 8' do not abut against the wide walls 2. The slope e, sufficient to ensure the above effect, should be from 10 to 30 °, and the amount of rounding r not less than 1 mm.

The inner surfaces m of the side supports 8' are not parallel to their outer surfaces n, and the places of formation of the side supports 8' facing the fixed plates 7 are machined, which ensures the most complete and reliable contact of the movable plates 8 with the fixed plates 7.

The length d of the side supports 8' is variable (Fig. 7) with an increase in the direction from the pressure wedge 5 to the base plate 9 in order to minimize costs and rational use of material in production, as well as a more correct distribution of loads on the side supports 8'.

In the draft gear according to the invention, there is also the possibility of increasing its efficiency, which is also achieved by the possibility of reducing material costs for its production. Reducing the height of the body of the pressure wedge 5 from its outer end T towards the bottom 3 of the body 1 and increasing the working stroke of the draft gear contributes to an increase in its energy consumption due to the distance of the friction assembly 4 from the bottom 3 of the body 1 and the formation of more space for the reciprocating device due to this 10, which allows you to increase its volume and, together with a large stroke, energy consumption. In this case, the pressure wedge 5 will have a significantly lower mass compared to the prototype [2]. However, in this case, (Fig. 2) the pressure wedge 5 would be completely outside the body 1, which would cause the disadvantages inherent in analogue [1]. To prevent this, protrusions 11 are formed on the pressure wedge 5, the ends V of which face the bottom 3 of the body 1 and are placed in the body 1 between its wide walls 2, and the sides of these protrusions 11 facing the wide walls 2 are formed by the said curved surfaces f. The presence of such protrusions 11 also contributes to the simplification and accuracy of the assembly of the draft gear when the pressure wedge 5 is installed inside the housing 1.

Since, under the influence of an external load Q, the pressure wedge 5 has the ability to sink inside the housing 1, it is useful to make curved surfaces f obliquely to the longitudinal axis 01 (Fig. 4) to prevent or reduce the area of their possible mutual contact with the wide walls 2 of the housing 1, obstacles wear and exclude the possibility of wedging during compression of the draft gear. When the external load Q stops, in order to easily return the pressure wedge 5 to its original position, in the direction from its outer end T to its protrusions 11, bevels F are made to the longitudinal axis 01, and the direction of their slope is opposite to the direction of the slope of the curved surfaces f.

For a rational and proportional configuration of the pressure wedge 5 of the use of material, from the side of its outer end T, the pressure wedge 5 is equipped with a cavity P tapering towards the projections 11, in the continuation of which a through hole 12 is made in its bottom 5' (Fig. 4) for the location of the centering rod 13 (Fig. 2).

To ensure the manufacturability and strength of the protrusions 11, as well as the strength of the pressure wedge 5, equipped with a cavity P, it is necessary to make the protrusions 11 in the form of a trapezoid B (Fig. 3), the larger base B1 of which is located on the side of the outer end T of the pressure wedge 5 and parallel to it , and the smaller base B2 is placed at the ends V of the protrusions 11. Moreover, in order to prevent the disadvantages of the prototype [2], the length Lv of the smaller base B2 of the trapezoid B at the protrusions 11 should be no more than 32 mm, and the height h (Fig. 4) of the protrusions 11 should not must exceed this length Lv (Fig. 3).

The key differences of the draft gear according to the invention from the analog [1] and the prototype [2] is close, by the size of the gaps z, the location of the curved surfaces f of the pressure wedge 5 and the protrusions 11 to the wide walls 2, but without contact with them. This provides the possibility of free rotation of the friction assembly 4 at an angle x to adapt it to the errors in the shape of the body 1 (Fig. 5), the simplicity and clarity of the assembly of the draft gear, a significant reduction in the weight of the pressure wedge 5, preventing its wedging.

The sagging of the pressure wedge 5, as in analog [1], and its support on one of the wide walls 2 during operation of the draft gear with a horizontally oriented longitudinal axis 01 (Fig. 1), as in the prototype [2], is excluded due to the use of the following design features . First, through the reciprocating device 10 and the friction assembly 4, a centering rod 13 is passed, equipped with a head 13', placed in a stepped hole 15 formed on the bottom 3 inside the body 1 of the bail 14 (Fig. 2, 8, 9). On the opposite head 13' the threaded end of the rod 13, a nut 16 is screwed, placed in the cavity P of the pressure wedge 5 and resting on the bottom 5' of this cavity P, protected from self-loosening by welding, and between it and the threaded end of the rod 13 it is useful to make a flat 17 to get there melt metal. In the assembled draft gear, the reciprocating device 10 is located in a preloaded state, due to which spacer forces arise in the friction assembly 4, tightly pressing its components to each other and to the narrow walls 2' of the housing 1. At the same time, the friction assembly 4, adapting to shape errors of the body 1, rotates by an angle x (Fig. 5), and the movable plates 8 are supported by slopes e and roundings r in the strongest places of the body 1, namely the interface of wide walls 2 and narrow walls 2'. The mentioned mechanical processing of the place of formation of the side supports 8' in the movable plates 8 prevents the displacement of the fixed plates 7 relative to them, and the bearing of the spacer wedges 6 into the inner surfaces m of the side supports 8' prevents their displacement towards the wide walls 2. The diameter D of the centering rod 13 is commensurate with smaller diameter s of the stepped hole 15 in the bonk 14, which prevents the occurrence of backlash between them. Thus, the sagging of the pressure wedge 5 towards the wide walls 2 is excluded, and during the operation of the draft gear and its wear, it is compensated by gaps z.

Secondly, it is important that the spacer wedges 6 with their surfaces in contact with the pressure wedge 5, the base plate 9 and the fixed plates 7, as well as the movable plates 8 with their surfaces in contact with the fixed plates 7 and narrow walls 2', form friction pairs friction, and the roughness of these contacting surfaces is not less than 2.5 µm. Such rough surfaces of the friction assembly 4, in addition to the spacer forces of the preloaded reciprocating device 10, prevent the displacement (slip) of the friction assembly 4 towards the wide walls 2 due to the high static friction force.

The head 13' of the centering rod 13 can be made cylindrical (Fig. 8) or conical (Fig. 9), which even more effectively prevents the occurrence of backlash between the centering rod 13 and the stepped hole 15 in the bonk 14.

The high durability and reliability of the draft gear according to the invention is achieved by its ability to adapt to shape errors of the body 1 caused by manufacturing or wear, as well as by the strict ratios of the dimensions of its components. The diameter D of the centering rod 13 to ensure its sufficient tensile strength on the side of the pressed back-support device 10 must be at least 32 millimeters, while the smaller diameter s of the stepped hole 15 in the boom 14 to prevent backlash must also be at least 32 millimeters (Fig. 8 , 9). The thickness a, b of the wide walls 2 and the thickness g of the narrow walls 2' of the housing 1 are selected from the range of 15-25 mm, and the thickness t (Fig. 1, 6) of the movable plates 8 is from 16 to 20 mm. The height H of the boom 14 due to the increased working stroke of the draft gear should be from 45 to 55 mm, and its diameter S from 55 to 65 mm. The larger diameter s' of the stepped hole 15 in the bonk 14, to prevent its separation from the bottom 3, does not exceed 70 mm.

The results of applying the advantages of the draft gear according to the invention can be a reduction in material costs for its production, simplification of assembly and reduction of losses due to the rejection of expensive cases. The rational use of a sufficient minimum of materials for the production of its parts, as well as the possibility of using cases with a shape error without their refinement, increases the prospects and economic efficiency of such a draft gear.

- 4 039274

The principle of operation of the draft gear is based on the fact that under the influence of an external load Q (Fig. 2) applied to the pressure wedge 5, for example, from the side of the coupling device (not shown) when the cars collide, the reciprocating device 10 is compressed. Pressure wedge 5 plunges into the body 1, while the spacer wedges 6 are displaced with friction along the fixed plates 7 towards the bottom 3.

At a certain period of the working stroke, the stop plate of the car coupler (not shown) begins to put pressure on the movable plates 8. Under the influence of this, they enter the inside of the body 1 with friction on the fixed plates 7 and narrow walls 2', while intensive absorption of energy occurs, caused by an external load Q.

When the external load Q ceases, the reciprocating device 10 expands, pushing the friction assembly 4 to its original position.

Sources of information:

1) Patent RU 164701, priority 11/11/2015, publ. 09/10/2016, bul. No. 25

2) Patent RU 2659366, priority 05/12/2017, publ. 06/29/2018, Bull. No. 19 (prototype)

Claims (10)

1. A draft gear comprising a housing (1) formed by a bottom (3), wide walls (2) and narrow walls (2'), inside which a friction assembly (4) is placed, consisting of a cavity (P) with a bottom (5' ) and protruding with its outer end (T) from the body (1) of the pressure wedge (5), spacer wedges (6), fixed plates (7), base plate (9) and movable plates (8) associated with narrow walls (2 ') of the body (1) and equipped with side supports (8'), while between the base plate (9) and the bottom (3), along the longitudinal axis (O1) of the body (1), a reciprocating device (10) is placed, tightened through the centering rod connection (13, 16), which rests at one end on the bolt (14) of the bottom (3) of the housing (1), and at the other end on the bottom (5') of the cavity (P) of the pressure wedge (5), which is placed with the formation of gaps (z) between it and the wide walls (2) of the body (1), characterized in that on the pressure wedge (5) protrusions (11) are formed, the ends (V) of which are directed towards the bottom (3) of the body (1 ), and also on the protrusions (11) of the pressure wedge (5) curved surfaces (f) are formed, between which and the wide walls (2) of the housing (1) the said gaps (z) are formed with the possibility of free rotation of the pressure wedge (5) relative to the longitudinal axis (O1). 2. Apparatus according to claim 1, characterized in that said curved surfaces (f) of the pressure wedge (5) are made inclined to the longitudinal axis (O1) of the housing (1) and are continued with bevels (F) inclined towards it, located in the direction from the outer end (T) of the pressure wedge (5) to its projections (11). 3. Apparatus according to claim 1, characterized in that the protrusions (11) are made in the form of a trapezoid (B), the larger base (B1) of which is located on the side of the outer end (T) of the pressure wedge (5) and parallel to it, and the smaller base (B2) is placed at the ends (V) of the protrusions (11), and the length (Lv) of the smaller base (B2) of the trapezoid (B) at the protrusions (11) does not exceed 32 mm. 4. Apparatus according to any one of claims 1, 2, characterized in that the curved surfaces (f) are made of radius, the radius (R) of curvature of which is not more than 200 mm. 5. The apparatus according to claim 1, characterized in that the wide walls (2) of the body (1) are made of variable thickness, and their thickness (a) at the interface with its narrow walls (2') is greater than their thickness (b) near the projections (11) of the pressure wedge (5). 6. Apparatus according to claim 1, characterized in that the size of the gaps (z) between the wide walls (2) of the housing (1) and the curved surfaces (f) of the pressure wedge (5) is selected from the range of 1-6 mm. 7. Apparatus according to claims 1, 3, characterized in that the height (h) of the protrusions (11) does not exceed the length (Lv) of the smaller base of the trapezoid (B) at their ends (V). 8. The apparatus according to claim 1, characterized in that the width (c) of the side supports (8') is variable with a decrease in the direction from the narrow walls (2') of the housing (1), while the outer surfaces (n) of the side supports (8 '), facing the wide walls (2), are not perpendicular to the plane (p) of contact of the movable plates (8) with narrow walls (2') and are not parallel to the inner surfaces (m) of these side supports (8'), and the places of formation of the side the supports (8') facing the fixed plates (7) are machined, the length (d) of the side supports (8') being variable with increasing in the direction from the pressure wedge (5) to the support plate (9). 9. Apparatus according to claim 1, characterized in that the centering rod connection (13, 16) is made of a centering rod (13) with a head (13') and a nut (16) screwed onto it, and the bottom bolt (14) is made with a stepped hole (15), in which the head (13') of the centering rod (13) passed through the reciprocating device (10) and the friction assembly (4) is located, on the opposite threaded end of which a nut (16) is screwed, placed on the bottom ( 5') of the cavity (P) of the pressure wedge (5), in addition, roundings (r) and slopes (e) are made on the movable plates (8), and the value of which from the plane (p) of their fit to the narrow walls (2') is selected from the range of 10-30°, while - 5 039274 the diameter (D) of the centering rod (13) is at least 32 mm, and the thickness (a, b) of the wide walls (2) and the thickness (g) of the narrow walls (2') of the housing (1) are selected from the range of 15-25 mm, and the thickness (t) of the movable plates (8) between the narrow walls (2') of the body (1) and the fixed plates (7) is selected from the range of 16-20 mm, and the height (H) of the bolt (14) is from 45 to 55 mm, its diameter (S) is from 55 to 65 mm, while the smaller diameter (s) of the stepped hole (15) in the bonk (14) is not less than 32 mm, and the larger diameter (s') of the stepped hole (15) is not less than over 70 mm. 10. Apparatus according to claim 1, characterized in that the spacer wedges (6) with their surfaces in contact with the pressure wedge (5), the base plate (9) and the fixed plates (7) are the same as the movable plates (8) with their contact surfaces. with fixed plates (7) and narrow walls (2') surfaces form friction pairs of friction, and the roughness of these contacting surfaces is not less than 2.5 microns.