EA040466B1 - FRICTION SHOCK ABSORBER - Google Patents

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.

A friction shock absorber is known ([1], patent RU 2380257, priority 11/13/2007, published on 01/27/2010, bull. No. 3), containing a body in the form of a glass, in which a pressure cone, a pair of friction wedges with a base plate, are placed symmetrically to its walls, by a pair of movable and fixed friction plates, as well as a reciprocating device located together with the base plate and wedges between the pressure cone and the bottom of the housing. The pressure cone perceives external force, which is redistributed through the wedge system of friction wedges, one part of which provides compression of the reciprocating device, and the other part provides pressing of the friction wedges against the housing walls.

The more intense the impact of the external force, the greater the pressing of the friction wedges against the walls. This, on the one hand, is useful and contributes to greater energy absorption of the friction damper due to the work of friction forces, but on the other hand, it sharply increases the final force at the end of its working stroke. Based on the fact that the value of the final force is strictly regulated and cannot exceed the set value, the applicability of such a friction damper design is limited and cannot be applied to high-energy devices of a higher class. In addition, the more the friction wedges are pressed against the housing walls, the greater the likelihood of their mutual setting and welding, which contributes to jamming and intense wear of the friction shock absorber.

These problems are partially solved in the shock absorber ([2], SU No. 109722, priority 05/15/1956, published 01/01/1957), taken as a prototype, in the body of which friction elements are placed, between which spring elements are installed. The friction wedges rest on the guide sleeve, from the other end of which a washer is placed through the gap. The washer separates the spring elements into sections. When an external force is applied to the cone, the spring elements are compressed, and the friction elements are pressed against the walls of the housing.

After the gap between the end of the guide cup and the washer is selected, the resistance of the shock absorber increases significantly.

The energy introduced into the shock absorber by an external force is absorbed due to the work expended on compressing the spring elements and overcoming the friction forces between the friction elements and the housing walls. That is, after closing the guide cup with the washer, the forces are redistributed to several friction elements, reducing the specific pressure on them, however, a significant increase in the final force of the shock absorber is not excluded.

Moreover, the gradual increase in the spacer forces between the friction elements and the walls of the housing, as well as in the analog [1], is preserved.

Thus, the gradual actuation of the spring elements closest to the cone provides a low stiffness of the shock absorber at the beginning of the working stroke and high stiffness at the end, with an increase in the final force, which also does not allow creating high-energy devices of a higher class on its basis.

The above disadvantages of shock absorbers similar to [1] and prototype [2] reduce the stability and reliability of their work, and also limit their applicability for high-energy devices.

Therefore, the objective of the invention is to achieve a technical result aimed at improving the stability and reliability of the friction damper, as well as increasing its energy intensity.

The problem is solved by the fact that the friction shock absorber (Fig. 1-18), containing a housing (1) with a bottom (2) and with a neck (4) formed by walls (3), in which a wedge assembly (5) is located, containing a pressure wedge (6) and spacer wedges (7), and between the bottom (2) and the wedge assembly (5) there is an elastic device (8) formed by a spacer damper (9) and a retaining damper (10), between which a separator (11) is located, at the same time, the spacer wedges (7) are made with the possibility of ensuring their contact with the guide elements (N) in the neck (4) and are equipped with supporting elements (E) facing the bottom (2) so that they can interact with the spacer damper (9) when applied external forces (q, Q) to the wedge assembly (5), in addition, in the direction to the top of the neck (4), starting from the divider (11), the pusher (12) is located, has a distinctive feature: the pusher (12) is located without the possibility transfer of the entire load to the retaining damper (10) from the expansion wedges ( 7) when external forces (q, Q) are applied to the wedge assembly (5).

Such a distinctive feature makes it possible to ensure that the spacer wedges are pressed against the guide elements using a spacer damper and significantly limit the intensity or even eliminate the increase in the force of such pressing, provide a low final force with the help of a retaining damper, but at the same time ensure high energy consumption of the elastic device and the friction damper as a whole.

Additional distinguishing features of the invention:

the pusher (12) is located without contact with the supporting elements (E) of the spacer wedges (7);

- 1 040466 guide elements (N) are the walls (3) of the body (1);

guide elements (N) are made in the form of plates (13) placed in the body (1), while between them and the walls (3) of the body (1) there are movable plates (14), partially protruding from the neck (4);

the pusher (12) is made in one piece with the separator (11);

the pusher (12) is made in one piece with the pressure wedge (6);

the expansion damper (9) is supplemented with a gasket (16) in contact with the supporting elements (E) of the expansion wedges (7);

the height (H) of the retaining damper (10) is greater than the height (h) of the expansion damper (9);

the contact of the spacer wedges (7) with the guide elements (N) is supplemented by inserts (15) placed between them, made of a material different from the material of the spacer wedges (7);

the pusher (12) is provided with supports (12') that are in contact with the supporting elements (E) of the expansion wedges (7) with the possibility of transferring part of the load to the support damper (10) from the expansion wedges (7) through the pusher (12) when external forces (q , Q) to the wedge assembly (5).

The essence of the invention is illustrated by illustrations, where in Fig. 1-18 show side views with frontal cuts of various embodiments of the friction damper according to the invention in the initial, intermediate and fully compressed positions.

The friction damper in its various versions (Fig. 1-18) contains a housing 1 with a bottom 2 and with a neck 4 formed by walls 3. In the housing 1, from the side of the top of the neck 4 opposite to the bottom 2, there is a partly protruding from the neck 4 by the value of the stroke x friction shock absorber, a wedge assembly 5 formed by a pressure wedge 6 and spacer wedges 7. The spacer wedges 7 are in contact with the guide elements N, and are also provided with support elements E facing the bottom 2. An elastic device 8 is placed between the wedge assembly 5 and the bottom 2 of the housing 1 (in Fig. 1-18 it is highlighted by a dotted line and conditionally shown by inclined crossed lines), formed from the side of the wedge node 5 by a spacer damper 9 and a retaining damper 10 from the side of the bottom 2 with a separator 11 between them. The elastic device 8 can be formed by metal springs, resilient-elastic elements, rubber blocks. In the direction towards the top of the neck 4, starting from the divider 11, there is a pusher 12 with the possibility of contact with the latter.

Guide elements N can be made in various designs.

For example, in one case, to enhance the energy intensity of the wedge assembly 5, the guide elements N can be made in the form of plates 13 (Fig. 10-12, 16-18), between which and the walls 3 of the housing there are movable plates 14, partially protruding from the neck 4.

In another case, the function of the guide elements N can perform the walls 3 of the housing 1 (Fig. 19, 13-15).

In each of the cases mentioned, the contact of the expansion wedges 7 with the guide elements N can be supplemented by inserts 15 placed between them, made of a material different from the material of the expansion wedges 7. This prevents the expansion wedges 7 from mutually seizing with the guide elements N, which adversely affects the smoothness of operation. friction damper, and provides between them the coefficient of friction necessary for reliable and stable operation of its wedge assembly 5.

Inserts 15 can be made, for example, in one case of bronze or cast iron to improve sliding and prevent jamming of the friction damper (Fig. 10-12, 16-18). In another case, the inserts 15 can be made of steel (Fig. 7-9), which allows only them to be replaced during repairs, significantly reducing the wear of the massive and expensive body 1.

The spacer damper 9 can directly contact the support elements E of the spacer wedges 7 of the wedge assembly 5 (FIGS. 13-15), for example when using metal springs.

The contact of the spacer damper 9 with the supporting elements E can also be through the gasket 16 (Fig. 412, 16-18). For example, when using elastic-elastic elements in the spacer damper 9, it can be made of metal. When using both resilient-elastic elements and metal springs in the spacer damper 9, the gasket 16 can also be made of polymeric materials, both solid and elastic, with the possibility of deformation and energy absorption.

The key difference between the friction damper according to the invention and the prototype [2] is either the complete exclusion of the contact of the pusher 12 with the support elements E of the spacer wedges 7, or the provision of contact between the pusher 12 and the support elements E, for example, using supports 12' (Fig. 1-3). Such supports 12' can be useful both when assembling a friction shock absorber for installing spacer wedges 7 with their help, and for controlling the degree and nature of compression of the expansion damper 9. These supports 12' can be deformed (Fig. 2, 3), or break off ( not shown), or be spring-loaded, with the possibility of transferring not all, but only part of the load to the retaining damper 10 from the expansion wedges 7 through the pusher 12 when external forces q, Q are applied to the wedge assembly 5, or part of the load to the supporting damper 10 from the expansion wedges 7 transmitted in a different way.

- 2 040466

Such a distinctive feature contributes to the distributed and independent transmission of a small external force q (Fig. 2, 5, 8, 11, 14, 17) or a maximum external force Q (Fig. 3, 6, 9, 12, 15, 18) to the expansion damper 9 and to the retaining damper 10. It is important to note that when the retaining damper 10 is compressed, the compression of the retaining damper 9 is either limited, that is, the decrease in its height h occurs much less than the decrease in the height H of the retaining damper 10, or when the retaining damper 10 is compressed by reducing its height H, compression of the spacer damper 9 and changing its height h does not occur at all (Fig. 4-6).

Moreover, options are possible (Fig. 7-12), when under the influence of a small external force q or a maximum external force Q during compression of the retaining damper 10, its height H decreases, and the height h of the expansion damper 9, on the contrary, increases. That is, during the working stroke x of the friction damper, the pressing force of the spacer wedges 7 to the guide elements N either remains unchanged or changes negligibly little.

In the design according to the prototype [2], due to the fact that the friction wedges rest on the guide cup, which acts as a pusher, the increase in the force of their pressing against the walls of the housing occurs constantly and intensively, throughout the entire working stroke.

Therefore, the reliability of the friction damper according to the invention, the stability and smoothness of its power characteristics, the safety and durability of the elastic device 8, the wedge assembly 5 and the guide elements N that do not experience overloads increase.

Variation of the sequence or nature of compression of the expansion damper 9 and the retaining damper 10 allows, with minor changes, to apply this design for the production of high-end friction shock absorbers with particularly stringent requirements for them, which ensures the prospects and competitiveness of the invention.

Due to the fact that it is necessary to provide a low pressing force of the spacer wedges 7 to the guide elements N and, at the same time, a high energy consumption of the friction damper, it is also useful to observe a proportional ratio of the height h of the spacer damper 9 and the height H of the retaining damper 10, in which H>h.

The design features of the friction damper according to the invention are disclosed by considering the operation of variants of its execution according to FIG. 1-18.

So, in Fig. 1-3 shows a variant in which the separator 11 is made in one piece with the pusher 12, and a gap z is provided between it and the pressure wedge 6 in the initial position (Fig. 1).

When a small external force q acts on the pressure wedge 6 (Fig. 2), the gap z is selected. Only after this, part of this force begins to act on the retaining damper 10 through the pusher 12 with the separator 11, and the spacer damper 9 is compressed both earlier, until the gap z is selected, and slightly during the working stroke x to the final position (Fig. 3) of the friction damper under the action of the maximum external force Q. This is due to the fact that the guide elements N in the form of walls 3 of the body 1 are made at an inclination to the longitudinal axis O1 and the spacer wedges 7 are forced to move towards it.

In FIG. 4-6 shows another variant, in which the spacer 11 is also made in one piece with the pusher 12, initially in contact with the pressure wedge 6 in the initial position (Fig. 4). When a small external force q is applied to the pressure wedge 6 (Fig. 5), part of this force begins to act on the retaining damper 10 through the pusher 12 with the separator 11, and part - on the expansion damper 9 through the wedge assembly 5. Due to the fact that the guide elements N in the form of walls 3 of the housing 1 are made parallel to the longitudinal axis O1, regardless of the impact of a small external force q (Fig. 5) or a maximum external force Q (Fig. 6), the expansion damper 9 does not compress, thereby ensuring a constant x is the pressing force of the expansion wedges 7 to the guide elements N. In this case, the height h of the expansion damper 9 does not change.

In the variant shown in FIG. 7-9, the divider 11 is also made in one piece with the pusher 12, which is passed through the pressure wedge 6 and protrudes outward for a distance c (Fig. 7). Here, the applied small external force q (Fig. 8) initially acts on the protruding part of the pusher 12, which transfers this force to the retaining damper 10, compressing it. In this case, the distance c is gradually selected, after which the small external force q or the maximum external force Q is distributed in such a way that one part of it continues its effect on the pusher 12, and the other part begins to act on the pressure wedge 6 and through the wedge assembly 5 acts on expansion damper 9.

A feature of this embodiment (Fig. 7-9) is the inconsistent nature of the compression of the expansion damper 9, which consists in the fact that when choosing a distance from the expansion damper 9 expands, reducing the pressing force of the expansion wedges 7 to the guide elements N formed by the walls 3 of the housing 1 and supplemented with inserts 15, and after choosing this distance c, when a small external force q or a maximum external force Q also acts on the pressure wedge 6, the expansion damper 9 is compressed due to the inclination of the guide elements N to the longitudinal axis O1.

In the variant shown in FIG. 10-12, the design of the friction damper is considered, in which the guide elements N are made in the form of plates 13 placed in the housing 1,

- 3 040466 between which and the walls 3 there are movable plates 14, partially protruding from the neck 4. In this case, the separator 11 and the pusher 12 are made as separate parts. The pusher 12 with a bulge on the outer end is passed through the pressure wedge 6 with a gap z between the bulge on the pusher 12 and the recess in the pressure wedge 6 (Fig. 10).

Under the influence of a small external force q (Fig. 11) or a maximum external force Q (Fig. 12), the gap z is selected, and the pusher 12, with its thickening, entrains the pressure wedge 6 inside the neck 4. Just as in the previous version (Fig. 7 -9), during the selection of the gap z (Fig. 12) the expansion damper 9 expands, reducing the pressing force of the expansion wedges 7 to the guide elements N, and after the gap z is selected, it is compressed due to the inclination of the guide elements N to the longitudinal axis O1. A feature of the variant (Fig. 10-12) is that the pressure wedge 6 is not directly affected by a small or maximum external force q, Q.

In FIG. 13-15 the pusher 12 is made in one piece with the pressure wedge 6, between which and the divider 11 a gap z is formed (Fig. 13). When choosing a gap z, the expansion damper 9 is compressed, during which the pressing force of the expansion wedges 7 against the guide elements N increases slightly, while the retaining damper 10 does not compress. After selecting the gap z (Fig. 14, 15) is compressed and retaining damper 10.

In the design of the friction damper in Fig. 16-18, the separator 11 and the pusher 12 are made as separate parts, and the gaps z (Fig. 16) are formed both between them and between the pusher 12 and the pressure wedge 6. When choosing the gaps z, only the expansion damper 9 is compressed, after which (Fig. 17, 18) the retaining damper 10 is also compressed.

It should be noted that the considered options (Fig. 1-3, 4-6, 7-9, 10-12, 13-15 and 16-18) are only exemplary ways to influence the power characteristic and energy consumption of the friction damper according to the invention. In each of these options, it is possible to introduce various combinations and minor improvements that significantly affect the behavior of the device. For example, the presence of such factors as the simultaneous or subsequent compression of the expansion damper 9 and the support damper 10, the incompressibility or, conversely, the expansion of the expansion damper 9 during compression of the support damper 10, the presence or absence of gaps z between the spacer 11, the pusher 12 and the pressure wedge 6, separate or their joint implementation, inclined or parallel arrangement of the guide elements N to the longitudinal axis O1, the value of the ratio of the height h of the expansion damper 9 and the height H of the retaining damper 10 and other parameters.

It is important to mention that the elastic device 8 can also be formed according to the principle of one of the options described in the prototype [2], where a larger number of expansion and support dampers 9, 10 can also be used, and the separators 11 can be equipped with secondary expansion wedges (not shown), contacting, for example, with the walls 3 of the body 1 closer to its bottom 2. But it is necessary to observe the importance of the key difference from the prototype [2], where the pushers 12 should not be able to transfer the entire load to the retaining damper 10 from the spacer wedges 7 when application of external forces q, Q to the wedge node 5.

The introduction of the above distinctive features makes it possible to have a significant positive effect on the nature of the operation of the friction damper, ensuring its reliability, durability and versatility of use, including the possibility of using practically the same design for various classes of draft gear.

Information sources.

1. Patent RU 2380257, priority 11/13/2007, published 01/27/2010, bul. No. 3.

2. SU No. 109722, priority 05/15/1956, published 01/01/1957 (prototype).

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Claims (10)

List of reference designations and names of elements to which these designations refer No. NAME 1 frame 2 hull bottom 1 3 housing wall 1 4 neck 5 wedge knot 6 pressure wedge 7 expansion wedge 8 elastic device 9 expansion damper 10 retaining damper eleven delimiter 12 pusher 12' pusher supports 12 13 plates 14 moving plates 15 inserts 16 pad N guide elements E supporting elements of expansion wedges 7 q small external force Q maximum external force h expansion damper height 9 Η retaining damper height 10 01 longitudinal axis X working stroke ζ clearance with protrusion distance of the pusher 12 beyond the pressure wedge 6 CLAIM 1. Friction shock absorber containing a housing (1) with a bottom (2) and a neck (4) formed by walls (3), in which a wedge assembly (5) is located, containing a pressure wedge (6) and spacer wedges (7), moreover between the bottom (2) and the wedge assembly (5) there is an elastic device (8) formed by a spacer damper (9) and a retaining damper (10), between which a separator (11) is located, while the spacer wedges (7) are made with the possibility of providing their contact with the guide elements (N) in the neck (4) and are provided with support elements (E) facing the bottom (2) to ensure their interaction with the spacer damper (9) when external forces (q, Q) are applied to the wedge assembly ( 5), in addition, in the direction towards the top of the neck (4), starting from the divider (11), there is a pusher (12), characterized in that the pusher (12) is located without the possibility of transferring the entire load to the retaining damper (10) from the spacer wedges (7) when external forces (q, Q) are applied to the wedge node ( 5). 2. The shock absorber according to claim 1, characterized in that the pusher (12) is located without contact with the supporting elements (E) of the spacer wedges (7). 3. A shock absorber according to claim 1, characterized in that the guide elements (N) are made in the form of a wall (3) of the housing (1). 4. The shock absorber according to claim 1, characterized in that the guide elements (N) are made in the form of plates (13) placed in the housing (1), while between them and the walls (3) of the housing (1) there are movable plates (14 ), partially protruding from the neck (4). 5. Shock absorber according to claim 1, characterized in that the pusher (12) is made as one piece with the spacer (11). 6. Shock absorber according to claim 1, characterized in that the pusher (12) is made as one piece with the pressure wedge (6). 7. A shock absorber according to claim 1, characterized in that the spacer damper (9) is supplemented with a gasket (16) in contact with the supporting elements (E) of the spacer wedges (7). 8. Shock absorber according to claim 1, characterized in that the height (H) of the retaining damper (10) is greater than the height (h) of the spacer damper (9). 9. A shock absorber according to claim 1, characterized in that the contact of the spacer wedges (7) with the guide elements (N) is supplemented by inserts (15) placed between them, made of a material different from the material of the spacer wedges (7). 10. The shock absorber according to claim 1, characterized in that the pusher (12) is provided with supports (12') in contact with the supporting elements (E) of the spacer wedges (7) with the possibility of transferring part of the load to the retaining damper (10) from the spacer wedges (7 ) through the pusher (12) when external forces (q, Q) are applied to the wedge assembly (5). -