KR960002026B1 - Energy damping device - Google Patents

Abstract

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Description

[Name of invention]

Energy attenuator

[Brief Description of Drawings]

1 is a cross-sectional front view of an energy damping device constructed in accordance with the present invention, showing the support of a pipe structure.

2 is an enlarged cross-sectional view of the energy attenuation device taken along line 2-2 of FIG.

3 is a cross-sectional view of another type of energy attenuation device made in accordance with the present invention.

4 is a cross-sectional view of another form of energy attenuation device made in accordance with the present invention.

5 is an enlarged cross sectional view showing an internal compression ring that is part of the damping device of FIG.

6 is an enlarged partial side view showing a wedge that is part of the damping device of FIG.

FIG. 7 is an enlarged side view showing an external compression ring that is part of the damping device of FIG.

8 is a cross-sectional view of another form of energy attenuation device made in accordance with the present invention.

Detailed description of the invention

[Technical Field]

The present invention relates generally to energy damping devices, and more particularly to devices for absorbing impact loads, distributing kinetic energy, controlling vibrations, and limiting the movement of loads.

Background Technology

Energy attenuation devices are well known, widely used in many industries, and in a variety of applications. For example, the railroad industry uses frictional, wedge-shaped shock absorbing systems to disperse vibrational kinetic energy.

Conventional damping devices are a representative example of a damping device marketed under the trademark of Houdaille Friction Snubber by Houdaille Industries Inc., Buffalo, New York. In general, the Haudale damping device comprises a tubular barrel that holds pre-compressed springs and granular contact portions to frictionally engage the interior of the barrel during operation of the operating elements. The spring pre-compressed so that the contacts cause a thermal resistance displacement with respect to the inner lining of the barrel causes the contacts to move outward until they engage the barrel. However, the linings of the contacts and barrel wear out rapidly because the contacts move in friction. Therefore, conventional damping devices require frequent maintenance and replacement of parts.

Howale damping devices as well as similar conventional damping devices absorb the kinetic energy by vibrating motion of the supported system, while they do not achieve satisfactory results in dispersing relatively large transient kinetic energy. In this regard, only a suitable frictional resistance generated by the thermal movement of moving parts, such as the contacts of the Howdale damping device, is needed to disperse the vibration energy. However, the relatively large and transient kinetic energy dissipation causes the energy attenuator to work in an unpredictable and unwanted way. Water hammer caused by rapid valve actuation or sudden movement of a broken pipe fixed to the damping device when the pipe is broken is a representative example of such undesirable effects.

Unsuccessful solutions have been tried to temporarily solve the problems associated with the dispersion of large kinetic energy. One of the solutions is to increase the displacement or displacement of the resistive elements, such as the contacts of the Howdale damping device. Another attempted solution is to increase the length of the spring. Each of the proposed solutions can dissipate relatively large transient kinetic energy, but the solutions were not completely satisfactory. In this regard, increasing the movement of the resistance elements or increasing the length of the spring elements increases the overall size of the damping device. Therefore, since large damping devices cannot be used in limited places or elsewhere space is not acceptable, such solutions have not been fully satisfactory in some applications. Moreover, such solutions increase the cost of production, which is an important problem.

Therefore, it is highly desirable to fabricate new and improved energy attenuation devices that can effectively dissipate vibration as well as transient energy. The damping device must generate a relatively large resistance to minimum movement along the path. The damping device should be relatively small in size, inexpensive to produce and simple to install. In addition, damping devices must operate in a predictable manner and minimize parts replacement or maintenance.

Damping devices are widely used in modern practical terms, and they are suitable for everyday use, such as locomotive plants and nuclear power plants. Damping devices must be relatively light, small in size, and sensitive enough for use in military equipment or space.

DESCRIPTION OF THE INVENTION

It is therefore a primary object of the present invention to provide a new and improved energy damping device suitable for efficiently distributing transient energy and vibration by generating relatively large resistance to minimal movement along the path.

Another object of the present invention is to provide a new and improved energy attenuation device which is relatively small in size, inexpensive to manufacture and easy to install.

The above objects and features of the present invention can be achieved by providing a new and improved energy damping device comprising a piston-cylinder assembly having a cylinder and a piston movable therein. The precompressed dual action spring and friction assembly is completely contained within the cylinder and is concentrically coupled to the piston. The spring acts on the friction assembly to apply a force to frictionally engage the inner surface of the cylinder and the friction assembly.

The friction assembly includes at least one wedge for engaging the inner surface of the cylinder. The friction assembly also includes a plurality of spaced apart compression rings sandwiched between the wedges that are forced to frictionally engage the cylinder inner surface by pushing the wedges radially outward.

In one form of the present invention, the energy damping device comprises one friction assembly and one precompressed spring. Therefore, when the damping device is subjected to a temporary kinetic load or a shock load of vibration, the generated energy is converted into thermal energy and distributed along the inner wall of the cylinder. In this respect, the spring exerts an axial force on the adjacent outer compression ring so that the compression ring is more tightly coupled with the adjacent wedge. Therefore, the wedge is forced radially outward to frictionally engage the inner wall of the cylinder. Similarly, depending on the amount of force applied, the wedges in the friction assembly are forced to frictionally engage the inner wall of the cylinder.

Another form of the invention includes an energy damping device having a pair of spaced friction assemblies disposed opposite the spring.

Another aspect of the invention is an energy damping device comprising a pair of spaced friction assemblies installed opposite to a spring and a stop mechanism for limiting free movement of the piston within the cylinder and limiting movement of one of the friction assemblies therein. It is characterized by. A gap or space is provided between a stop and an adjacent friction assembly to allow the piston to have limited free movement in the cylinder.

Another form of the invention features an energy damping device comprising a friction assembly installed between two dual action precompressed springs.

The device of the present invention is relatively small in size, inexpensive to manufacture, easy to install and can operate in a predictable manner. The device of the present invention generates a relatively large resistance to a relatively short path.

The device of the present invention should be relatively light and sufficiently sensitive so that it may be suitable for a wide range of modern applications.

With respect to the accompanying drawings, the objects and features of the present invention mentioned above and methods for achieving the objects will become apparent, and the present invention itself will be better understood by reference to the embodiments described below.

Best Mode for Carrying Out the Invention

Referring to the drawings, in FIG. 1, an energy attenuation device 10 is constructed according to the invention and attached to a high pressure pipe system 11. The damping device 10 will be described in more detail below, but the damping device 10 controls the vibration and limits the movement of the pipe system 11 in the event of a rupture.

In general, the damping device 10 has a piston-cylinder assembly 12, which assembly supports a pipe system 11 for supporting one end and a pipe system 11 fixed to a rigid support 13 which is immovable. And the opposite end connected to The pre-compressed dual action spring 16 is installed inside the piston-cylinder assembly 12 to act along the axis with respect to the friction assembly 14.

The friction assembly 14 is generally a series of similarly spaced apart wedges 25, 26 optionally installed between a series of compression rings, such as compression rings 30, 33, 36. Wedges. For purposes of example only, the friction assembly 14 is equipped with two wedges and three compression rings. However, it will be apparent to those skilled in the art that more than one such number of wedges or compression rings may be used in one damping device 10.

The friction assembly 14 is concentrically coupled with the piston of the cylinder assembly 12 and is engaged to friction with the inner wall or the outer circumferential surface of the piston 22 in the cylinder assembly 12. Thus, the movement of the friction assembly 14 relative to the inner wall of the piston-cylinder assembly 12 generates a resistive friction force to convert the kinetic energy of the system into thermal energy, and the thermal energy causes the wall of the piston-cylinder assembly 12 to break down. Distributed through.

As shown in FIG. 6, the wedge 25 generally has an annular member 40 having a central passage 50 for simultaneously engaging with a pair of compression rings 30, 33 which are complementary in shape. Include. Also, as shown in FIG. 2, when the compression rings 30, 33 are forced into the inner side of the central passage 50, the wedge 25 is pushed outward in the radial direction so that the inner wall 21 of the cylinder 20 The wedge 25 includes a slit-shaped gap 42 extending along an axis about its periphery so as to be frictionally coupled thereto. The wedge 25 is therefore suitable for dispersing not only temporary kinetic energy but also vibration. In this regard, as the energy absorbed increases, the wedge 25 is adjusted to increase frictional engagement with the inner wall 21 to disperse a greater amount of energy.

In operation, the damping device 10 is susceptible to shock loads of vibration as well as possible temporary kinetic loads. The resulting energy is converted into thermal energy and distributed along the inner wall 21 of the cylinder 20. At this point, if the pipe system 11 is forced upwards, the piston 22 of the piston-cylinder assembly 12 moves upwards in the interior of the cylinder 20. The precompressed spring 16 then exerts a force upwardly along the axis on the lower compression ring 36, which is similar in structure or design to the upper compression ring 30 as shown in FIG.

In order to move the wedge 25 along its axis and to push it radially outward to frictionally engage the inner wall 21 of the cylinder 20, the spring 16 allows the compression ring 36 to more tightly engage the wedge 26. do. The axial movement of the wedge 26 then engages the inclined annular cam surface 78 of the adjacent compression ring 33. The inclined annular cam surface 76 of the compression ring 33 symmetrically installed on the opposite side is then engaged along the axis in engagement with the adjacent wedge 25 so that the wedge 25 moves simultaneously in the radial and axial directions.

The wedge 25 is coupled to the compression ring 30 by moving along the axis. The cam surface 76 of the compression ring 33 is engaged with the inclined annular cam surface 65A of the wedge 25 having a complementary shape to move the wedge 25 radially outward. By doing so, the gap 42 is separated and opened toward the outer circumferential surface and the wedge 25 is frictionally engaged with the inner wall 21 of the cylinder 20.

When the damping device 10 is forced downward, the piston 22 is forced downward and along the axis in the interior of the cylinder 20 such that the upper compression ring 30 is engaged with the first wedge 25. The first wedge 25 is pushed radially outward and frictionally engaged with the inner wall 21 of the cylinder 20. Therefore, if the downward force is greater than the axial frictional resistance of the wedge 25, the wedge 25 is the opposite shoulder of the compression ring 33 so that the shoulder 78 is coupled along the axis with the next adjacent wedge 26. Forced to join 76 along the axis.

Since the compression ring 33 is coupled with the wedge 26 along the axis, the wedge 26 extends radially outward so as to frictionally engage the inner wall of the cylinder 20. If the downward force along the axis is greater than the frictional resistance created by the wedges 25, 26, the entire friction assembly 14 compresses the spring 16 downward.

Therefore, the combination of the present invention with the friction assembly 14 and the spring 16 increases the load capacity of the damping device 10. The friction assembly 14 with three wedges and four compression rings increases the load capacity of the damping device 10 by about five times the load capacity with only one spring 16. Therefore, the friction assembly of the present invention substantially reduces the overall length and cost of the damping device 10 and greatly increases its application.

The friction assembly 14 will now be described in great detail, particularly in relation to the first, second, second, fifth, sixth and seventh degrees, so that the friction assembly is generally a series of spaced apart separated compression rings 30, 33, 36 ) And wedges 25 and 26 sandwiched therebetween. Since the wedge 25 is generally similar to other wedges, only the wedge 25 will be described in detail below.

The wedge 25 generally comprises an annular split ring member 40 which is hollowed through its axial overall length. The annular member 40 is disposed in the center and generally has an hourglass-like passage or hole 50 extending along the axial direction. The passage 50 forms a cam surface (shoulder portion 65A) that is tapered inwardly and an inwardly tapered cam surface (shoulder portion 63A) provided on the opposite side. To form the conical portion or space 63 of the passage 50, the outer diameter of the inner cam surface or edge 63A gradually decreases along the axis towards the central annular portion 61.

Similarly, to form the conical portion or space 65 of the passage 50, the outer diameter of the inner cam surface 65A gradually decreases along the axis towards the central annular portion 61. The space 65 defines a tapered shoulder or corner 65A. The space 65 is generally symmetrical to the space 63 about a radial axis that causes the wedge 25 to be symmetrical. The central annular portion 61 is generally circular in cross section and forms an annular space portion 67 sandwiched between the conical space 63 and the space 65.

As shown in FIG. 2, when a compression ring, such as compression ring 33, engages annular shoulder portion 53, radially outer side such that annular member 40 engages wall 21 of cylinder 20. The annular member 40 of the wedge 25 generally includes a slit radial clearance 42 extending through its axial length and radial thickness. In general, a plurality of similar slit-like radial gaps, such as gaps 43, 44, 45, are substantially spaced apart from one another in the axial direction along the circumference of the annular member 40. The gaps 43, 44, 45 generally extend radially from the central annular portion 61, though not all of the radial thickness of the annular member 40. Therefore, the gaps 43, 44, and 45 allow the annular member 40 to be easily coupled on the inner wall of the cylinder and the radially outer side of the member so that the gap can be deformed as the gap is opened and closed thereon.

Turning now to the compression rings 30, 33, 36 in particular with reference to the first, fifth, sixth and seventh degrees in particular, the friction assembly 14 generally has a pair of outer compression rings 30, ( 36 and one inner compression ring 33. However, it will be apparent to one skilled in the art that one or more similar internal compression rings may be used.

The inner compression ring 33 is generally circular in cross section and includes an annular body 34 having an enlarged diameter extension 70 disposed between the outer ends 72 and 74. The inclined annular cam surface or shoulders 76 and 78 are symmetrically arranged at each side of the extension 70. Shoulder 76 is of complementary shape and specific dimensions to engage cam surface 65A. The shoulder portion 76 extends outward from the expanded portion 70 of increased diameter and has an outer diameter that gradually decreases along the axial direction towards the distal end 72.

Similarly, shoulder 78 is of complementary shape and specific dimensions to engage the inclined edge (not shown) of the inner annular shoulder (not shown) in the adjacently arranged wedges 26. . The shoulder portion 78 extends outward from the extension portion 70 and has an outer diameter that gradually decreases along the axial direction toward the distal end portion 72. The elongated cylindrical bore 81 engages the same center as the piston 22 of the piston-cylinder assembly 12 and extends through the entire axial length of the inner compression ring 33 for free sliding along the length of the shaft. do.

Since the outer compression rings 30 and 36 are generally similar in design or structure, only the compression ring 30 will be described in detail below with reference to FIG. The compression ring 30 comprises an annular body 83 having an enlarged diameter extension 87 which is generally circular in cross section. The annular inclined cam surface or edge 90 has the same shape and dimensions as the inclined shoulder portion 76 of the internal compression ring 33 to engage the cam surface 63A. The central elongated cylindrical hole 91 extends through the entire length of the outer compression ring 30 in order to engage concentrically with the piston 22 and to slide freely along the length of its axis. The hole 91 generally has the same diameter as the hole 81 and has a length of about one half of the axial length of the hole 81.

Referring to FIG. 3, another energy attenuation device 100 fabricated in accordance with the present invention is generally similar to the energy attenuation device 10. The damping device 100 includes a pre-compressed spring 116 and a piston-cylinder assembly 112 that completely receives a pair of friction assemblies 114 and 115.

The piston-cylinder assembly 112 generally includes the piston-cylinder assembly 12 of the energy damping device 10. The long rod-shaped piston 122 is similar to the piston 22, is similar to the cylinder 120 along the axis, and is coupled to the long cylinder 120 which is hollowed out in the length of the axis and is similar to the cylinder 20. It is concentrically coupled with the spring 116 and the friction assemblies 114, 115.

The piston-cylinder assembly 112 includes two stop mechanisms 117, 118 for limiting the movement of the spring 116 and friction assembly 114, 115 inside the cylinder. Different from the cylinder assembly 12. In this regard, the stop mechanism 118 is hollow over its entire length in the axial direction, and is a long tubular nut-shaped body which is fixed and used to be adjustable by a thread on the outer end 125 of the piston 122. 165).

In order to form the cap 130 between the stop mechanism 118 and the friction assembly so that the piston 122 can have limited free movement prior to engagement with the friction assembly 114, the stop mechanism 118 is the friction assembly 114. It may optionally be installed along the axis of the piston 122 away from the adjacent end 126 of the. Therefore, when a relatively small load causes vibration displacement of the piston 122 inside the cylinder 120, the front end 135 of the body 165 abuts against the friction assembly 114 and therefore the piston 122 is directed forward. Exercise is limited.

The stop mechanism 117 is completely received in the cylinder 120 at the end 140 adjacent to it and abuts against the friction assembly 115 to prevent the friction assembly from moving forward in the cylinder 120. The stop mechanism 117 is formed of a tubular member 142, the tubular member 142 being hollowed out over its entire length and against the inner wall or circumference 121 of the cylinder 120 to fit snugly against the wall. Complementary size.

Looking now at the spring 116, it is generally similar in design or structure to the spring 16 of the damping device 10 and is mounted concentrically on the piston 122 inside the cylinder 120. The spring 116 is disposed between the friction assembly 114 and 115 to cause the damping device 100 to dissipate excess energy as the piston 122 moves along an axis within the cylinder 120. Therefore, when the piston 122 is forced forward in the cylinder 120, the front end 135 of the stop mechanism 118 contacts the friction assembly 114 and friction along the inner wall 121 so that energy is dispersed. Drive assembly 114 to friction forward. The movement of the friction assembly 115 is limited by the stop mechanism 117 while the piston 122 moves forward.

Similarly, when the piston 122 is forced outwardly outside of the cylinder 120, the cap 145 disposed at the front end 150 of the piston 122 contacts the friction assembly 115 and dissipates energy. The friction assembly 115 is moved by causing friction toward the rear along the inner wall 121. Movement of the friction assembly 114 while the piston 122 moves rearward is limited by the general disc 155 at the adjacent end 157 of the cylinder 120.

Disc 155 is generally secured to the cylinder at adjacent ends 157 of cylinder 120 to abut friction assembly 114, and springs 116 and friction assemblies 114, 115 inside cylinder 120. ) And fix it. The disc 155 is a circular passage having a shape and dimension complementary to the outer diameter of the stop mechanism 118 so that the body 165 of the stop mechanism 118 engages the cylinder and enters the cylinder through the passage 160. 160. The body 165 extends integrally to the rear side to the annular head 170 having an outer diameter larger than the diameter of the body 165 and the passage 160. Therefore, when the stop mechanism 118 is moved forward along the piston 122, the head 170 abuts the disc 155, thereby restricting the movement of the piston inside the cylinder.

Referring now to the friction assemblies 114 and 115, since they are arranged similarly, only the friction assembly 114 will be described in detail below for explanation. In reviewing this disclosure of the present invention, it will be apparent to those skilled in the art that the friction assemblies damping device 100 may be arranged differently depending on the application of the features.

The friction assembly 114 is generally similar to the friction assembly 14 of the damping device 10 and is spaced apart and separated, such as wedges 175 and 180 similar in design or structure to the wedges 25 and 26. Wedges. A series of compression rings, such as compression rings 187, 188, and 189, are sandwiched between wedges 175 and 180, which are similar to compression rings 30, 33, and 36, respectively. .

Referring now to FIG. 4, another energy attenuation device 200 made in accordance with the present invention is generally similar to the energy attenuation device 100. The damping device 200 includes a piston-cylinder assembly 212 similar to the piston-cylinder assembly 112 to receive a pre-compressed spring 216 and a pair of friction assemblies 121 and 121.

The piston-cylinder assembly 212 is generally similar to the piston-cylinder assembly 112 except that it does not have a stop mechanism similar to the stop mechanism 117. The piston-cylinder assembly 212 also includes a stop mechanism 218 similar to the stop mechanism 118 except that the front end 235 of the stop mechanism 118 is in continuous contact with the friction assembly 214. . Therefore, when the piston 222 of the piston-cylinder assembly 212 is forced to move, either inside or outside the cylinder 220, the two friction assemblies 214, 215 and the spring 216 in between The entire mass 230 formed is frictionally moved along the inner wall 221 of the cylinder 220 in the direction of the applied force.

Referring now to FIG. 8 in detail with reference to another energy attenuation device 300 fabricated in accordance with the present invention, it is generally similar to the energy attenuation device 200. The energy damping device 300 includes a piston-cylinder assembly 312 similar to the piston-cylinder assembly 212. The piston-cylinder assembly 312 also includes a cylinder 320 containing one friction assembly 314.

The friction assembly 314 is generally similar to the friction assembly 214 of the damping device 200. For illustrative purposes only, the friction assembly 314 is shown to include three consecutive wedges 322, 323, 326 similar to the wedge 25 described in connection with the damping device 10. The friction assembly 314 includes four consecutive compression rings 330, 333, 336, and 337 arranged in a sandwiched form between the wedges 322, 323, and 326. It is shown. The outer compression rings 330, 337 are generally similar in design or structure to the outer compression ring 30 of the damping device 10. The inner compression rings 333, 336 are generally similar to the compression rings 33 of the damping device 10. A pair of pre-compressed dual action springs 316, 318 are installed in the cylinder interior 320 at each end face of the friction assembly 314.

While particular embodiments of the invention have been disclosed, it is obvious that various other modifications are possible and are envisioned in the spirit or spirit of the appended claims. Therefore, there is no intention to limit the precise summary or detailed description in this proposal.

Claims (24)

A piston 22 having an enlarged distal end that engages a stop mechanism disposed in the cylinder to limit the free axial relative movement of the piston 22 and the cylinder 20 and the cylinder 20 exert an axially applied load on each other. An energy damping device having a friction assembly 14 that acts as a force to generate a resistive friction force between a hollow cylinder and an internally mounted piston for consumption, comprising: a small load axially applied between the cylinder and the piston The piston moves from a single precompressed spring 16 in the cylinder acting against one side of the friction assembly to press the friction assembly into the piston receiving space to significantly reduce the friction between the cylinder and the friction assembly to consume To form a limited travel path leading to the enlarged distal end of the piston at light loads. A piston receiving space between the locking mechanism and the friction assembly; An enlarged portion of the piston is directed toward the spring 16 along the opposite travel path such that the frictional force between the friction assembly 14 and the cylinder 20 greatly increases in order to consume large loads axially applied between the cylinder and the piston. As it moves, it prevents the enlarged portion of the piston from penetrating through, so that this enlarged portion acts against the opposite side of the friction assembly and is sufficient to pressurize the enlarged portion away from the piston receiving space and engage the spring under a large load. An energy damping device (10) characterized by a hole having a small diameter and extending axially within the friction assembly to freely receive the piston. 2. The cylinder (20) of claim 1, wherein the cylinder (20) has a friction absorbing surface (21), and the friction assembly (14) has a pair of wedges (25, 26) engaged with the absorbing surface and a plurality of spaced apart compression rings (30). , 33, 36, wherein the wedges 25, 26 and compression rings 30, 33, 36 are frictionally coupled radially outwardly with the wedges 25, 26 to the friction absorbing surface 21. An energy attenuation device, characterized in that it is fitted to facilitate movement. The energy damping device according to claim 2, wherein the compression rings are a pair of outer compression rings (30, 36) at each end of the friction assembly (14). 4. An energy damping device according to claim 3, wherein the compression ring comprises at least one inner compression ring (33). 5. An energy damping device according to claim 4, wherein the wedge (25) comprises a hollow annular member (40) over its entire axial length. 6. An energy attenuation device according to claim 5, characterized in that the annular member (40) has a passage (50) in the form of a generally hour-glass. Forced action between the piston 122 and the hollow cylinder 120 disposed in the cylinder 120 having an enlarged end engaged with the cylinder 120 to limit the free axial movement of the cylinder and the piston. To generate a resistive frictional force of a small load when the piston moves in one axial direction within the cylinder and to generate a resistive frictional force of a large load when the piston 122 moves in the opposite axial direction within the cylinder. A pair of friction assemblies 114 and 115 disposed between the stop mechanism 117 at one end of the hollow cylinder 120 and the disc at the other end; When the piston 120 responds to only a small load and moves in the first axially restricted movement path, the friction assemblies are elastically urged outwardly to the inner wall 121 of the cylinder to generate a small frictional force, An energy damping device (100) having a spring (116) disposed between and acting on the friction assembly to deflect the friction assemblies (114, 115) when reacting and moving in the opposite axial direction to generate a large friction force. A piston accommodating space at one end of the cylinder that forms a limited travel path leading to the enlarged end of the piston 122 at a small load as it moves away from 116; Extending axially within the friction assembly 115 to receive the piston 122 freely, having a diameter small enough to prevent the enlarged end from passing therethrough, and the cylinder 120 and the piston 122 mutually At higher loads, the friction assembly is moved along the opposite travel path toward the spring 116 so that the enlarged end moves toward the spring 116 so that the friction force between the friction assembly 115 and the cylinder 120 is greatly increased to consume an axially large load. A hole acting against the friction assembly 115 to move from the piston receiving space and to engage the spring 116; And the friction assembly 114 moves into the inner wall 121 when the friction assembly 114 moves toward the spring 116 at a large load axially applied to the cylinder 120 and the piston 122 to each other to consume a large load. Gap 130 between them limiting free axial movement between the cylinder and piston so that the stop mechanism 118 and the friction assembly 114 can cooperate together to extend radially outwardly to compress the spring 116. And an external stop mechanism (118) formed in the axial direction along the piston (122) at a distance from the end (126) of the friction assembly (114). A piston 222 having an enlarged end that engages the stop mechanism in the cylinder 220 and an axially applied load between the cylinder 220 and the piston 222 to limit the free movement in the axial direction between each other. An energy damping device having a friction assembly 215 that acts as a pressurization between a hollow cylinder 220 and a piston 222 mounted therein to generate a resistive friction force therebetween for consumption. 222 and piston 220 to pressurize one side of the friction assembly into the piston receiving space to reduce friction between the friction assembly 215 and the cylinder 222 to consume small loads axially applied to each other. Subsequent to the enlarged end of the piston 222 at a small load as it moves away from one precompressed spring 216 acting on one side of the friction assembly. A piston receiving space disposed between the stop mechanism and the friction assembly 215 forming a travel path; Extending axially within the friction assembly 215 to receive the piston 222 freely and having a diameter small enough to prevent the enlarged portion of the piston from passing therethrough, such that the enlarged portion is the cylinder 220 and the piston 222. ) Move from the piston receiving space at large loads when moving along the opposite travel path towards the spring 216 so that the frictional force between the friction assembly 215 and the cylinder 220 is increased to consume large loads axially applied to each other. A hole for exerting an enlarged portion on the opposite side of the friction assembly 215 to urge to engage the spring 216, and a second friction assembly 214 disposed opposite the friction assembly 215, these Energy damping device (200), characterized in that the friction assemblies (214, 215) are separated from each other by springs (216). 9. The method of claim 8 wherein the spring 216 extends between the two friction assemblies 214 and 215 such that the friction force, which is the resistive force generated by the spring 216 and the friction assemblies 214 and 215, is adjustable. In order to adjust the length, an energy attenuation device, characterized in that a stop mechanism (218) having a front end (235) for adjoining the friction assembly (214) is arranged axially along the piston (222). 10. The energy damping device according to claim 9, wherein the stop mechanism (218) is formed such that the spring (216) has a given fixed length so that a constant force is applied between the friction assemblies (214,215). The axially applied loads on the piston and the cylinder 320 as the friction assembly 314 moves in the opposite axial direction within the cylinder 320 to consume the large loads axially applied to the cylinder 320 and the pistons to each other. A friction assembly 314 acting pressurized between the hollow cylinder 320 and the piston mounted therein to assist in generating frictional forces therebetween to consume; An attachment device for freely moving the piston and the cylinder 320 in the axial direction independently of the friction assembly and allowing a small load to move the piston and the cylinder 320 relative to each other in the axial direction; The friction assembly is urged elastically outward to generate a small frictional force when moved in one axial direction to facilitate limited free movement without acting on only a small load and generating a resistive frictional force by the friction assembly 314. A spring 316 which acts on 314 and biases the friction assembly 314 when moved in the opposite axial direction to generate a large friction force in response to only a large load; And an aperture extending axially in the friction assembly to freely receive the piston, wherein the friction assembly (314) moves in one axial direction by the force of the spring (316). 314 and springs 316 and 318 cooperate to receive a portion of the piston and friction assembly 314 disposed therein under small load conditions to limit the free movement of the piston and cylinder to generate a small resistive frictional force. A space in the cylinder with spring 318; The piston and friction assembly extends radially outwardly into the inner wall when the friction assembly 314 is moved in the opposite axial direction at large loads axially applied on the piston and cylinder 320 to consume a large load. Energy damping device (300), characterized in that the spring (318) restricts the free axial movement of the piston and cylinder to compress the spring (316). 8. The stop mechanism (117) according to claim 7, wherein the stop mechanism (117) is tubularly disposed in the piston receiving space and adjacent to the friction assembly (115) to limit the forward movement of the friction assembly (115) in the cylinder (120). ; These stop mechanisms 117 and 118 likewise restrict the movement of the spring 116 and the friction assembly 114, 115 in the cylinder 120; The external stop mechanism 118 may, at small loads, engage the piston 122 before engaging the friction assembly 114 such that forward movement of the piston 122 inwardly within the cylinder 120 is restricted to the path of travel in the piston receiving space. Energy attenuation, characterized in that it is selected and disposed axially along the piston 122 by a distance from the end 126 of the friction assembly 114 to form a gap 130 therebetween that restricts free movement of Device. 13. The friction assembly (114) according to claim 12, wherein the friction assembly (114) has a pair of wedges (175, 180) engaged with the friction absorbing surface of the cylinder (120), and the wedges (175) with the friction absorbing surface of the cylinder (120). Energy attenuation device, characterized in that it comprises a plurality of spaced apart compression rings (187, 188, 189) fitted with the wedges (175, 180) so that 180 is easily frictionally moved radially outward. 14. The method of claim 13, wherein the compression rings 187, 188, 189 that are spaced apart from each other comprise a pair of outer compression rings 187, 189 disposed at opposite ends of the friction assembly 114, and one or more inner portions disposed therebetween. Energy damping device, characterized in that the compression ring (188). 7. The hourglass shaped passage 50 is formed by a central annular portion and two conical annular cam surfaces symmetrically disposed on both sides of the annular portion and engaged with the compression ring, each annular. And an outer diameter of the cam surface gradually decreases toward the central annular portion. 16. An annular body (83) according to claim 15, wherein one of said outer compression rings (30, 36) has an annular body (83) having an extension (87) that is generally circular in cross section, said annular body being one of the cam surfaces of said wedges. And a complementary formed annular cam surface (90), wherein the annular cam surface of the annular body gradually decreases axially outward to frictionally engage one of the cam surfaces of the annular wedge. 17. The inner compression ring (33) according to claim 16, wherein the inner compression ring (33) comprises an annular body (34) having a central expansion portion (70) that is hollow throughout the entire axial length and is evenly circular in cross section. 34 has two conical annular cam surfaces 76, 78 arranged symmetrically on either side of the extension, the outer diameter of each annular cam surface being gradually directed towards the extension to engage respective adjacent wedges. Energy attenuation device, characterized in that increasing. 7. An annular body (83) according to claim 6, wherein one of said outer compression rings (30, 36) has an annular body (83) having an extension (87) that is generally circular in cross section, wherein said annular body is one of the cam surfaces of the wedge. And an inclined annular cam surface 90 of complementary shape, the cam surface of the annular body gradually decreasing axially outward to frictionally engage one of the cam surfaces of the annular wedge. Damping device. 19. The inner compression ring (34) according to claim 18, wherein the inner compression ring (34) comprises an annular body (34) having a central expansion portion (70) that is hollow throughout the entire axial length and is evenly circular in cross section. 34 has two conical annular cam surfaces 76 and 78 disposed symmetrically on either side of the extension, the outer diameter of each annular cam surface being gradually toward the extension to engage respective adjacent wedges. Energy attenuation device, characterized in that increasing. 3. The wedge (25) according to claim 2, wherein the wedge (25) is provided with at least one axial slit-like clearance (42) for moving the annular member (40) radially outward to engage the inner surface of the cylinder when engaged with one of the compression rings. Energy attenuation device comprising a. 8. An energy damping device according to claim 7, characterized in that the first stop mechanism engages concentrically with the cylinder to stop the axial movement of the piston inside the cylinder. 22. The energy damping device of claim 21 wherein the first stop mechanism is disposed at a distance from an adjacent friction assembly to form a gap therebetween to freely move the piston axially. 23. The energy damping device of claim 22, wherein the first stop mechanism is disposed in contact with an adjacent friction assembly. 24. The energy damping device of claim 23, further comprising a second stop mechanism for stopping the axial movement of the second friction assembly inside the cylinder.