DE1803071A1 - Energy-absorbing, telescopic tubular parts with the ability to transmit torque - Google Patents

Description

dipl-ing. martin light
dr. reinhold schmidt
'Dipl.-Wirtsch.-Img. Hansmann
dipl-phys. seq. herrmann

MUNICH 2
THERESIENSTRASSE 33

Munich, October 11, 1968

AHA, INC.

Vest Covlna, California West Garvey Avenue 2017 V. St.A.

"Energy-absorbing, telescopic tubular parts old of ability for the transmission of torques. "

The present invention relates generally to that Field of devices for the absorption of energy, which are not destroyed during the energy absorption, in connection with bit telescopically fitting tubular parts, and more precisely to such a combination, the one improved device of that disclosed in U.S. Patent 3,251 disclosed type includes, in the mechanical energy through the periodic plastic deformation of a substance in solid Physical state is absorbed.

909833/1166

Although the devices for absorbing energy from of the type disclosed in U.S. Patent 3,231,049 are generally satisfactory, they have the disadvantage that the HaO of the change in energy absorption during the stroke or impact path of the damper remains essentially constant, i.e., the damping force is over the stroke or stroke distance constant.

In view of this, it is the object of the present invention to provide a novel, energy-absorbing To create a telescopic part that has the ability to transmit Has torques, and that an energy absorbing device which is not subject to the above disadvantage and which comprises means for increasing the amount of change in energy absorption by increasing or decreasing the attenuation during the lifting or pushing distance of the damper. Further According to the invention, a novel, energy-absorbing telescope part is to be created which comprises a linearly acting device for energy absorption of the type described, which is specially designed for the safe and effective absorption of energy without the ability to transfer it to limit torques of the telescopic part inappropriately.

909833/1166

Furthermore, according to the invention, a novel tele-head part is to be created which has an energy absorbing device and is not destroyed during an energy absorption cycle *.

Furthermore, according to the invention, a telescopic part is to be created containing an energy absorbing device, in ___- which absorbs energy through periodic plastic tensile deformation and compression deformation in an energy-absorbing body is absorbed.

According to the present invention, a part with the ability to transmit torques comprises first and second tubular parts which sit telescopically one inside the other, in ^ operational association with a periodically acting energy absorbing device in the form of a solid body, which is able to absorb energy through cyclic plastic Absorb tensile deformation and compression deformation on the transfer of mechanical energy through at least one of the tubular parts. Three embodiments are disclosed. Each embodiment has a device for increasing the degree of change of the periodically acting energy absorbing device on the impact or lifting path of the device by increasing or reducing the damping force over the impact or lifting path. Each embodiment also has means

909833/1 166

on, which connect the individual parts telescopically so that they have the ability to transmit torque without losing their telescopic properties. One embodiment is for the purpose of illustration, however not of limitation, shown in the form of a steering column. The other two examples are shown in the form of drive shafts for motor vehicles.

The term "mechanical energy" as used in this specification can be defined according to its conventional definition, i.e. it refers to a force which acts over a distance. Furthermore, the term "periodic" as used in this specification refers plastic deformation "refers to the deformation of a substance in a solid aggregate state around a hysteresis curve, as in FIG. 21 of the aforementioned US patent 3,231,049 illustrated. In addition, the terms "curved body", "annular body" and "spiral body" are intended to encompass any body upon which they are acted can to cause periodic tensile plastic deformation and compression deformation.

The features of the present invention believed to be novel are set out in the appended claims set out. The present invention goes both in terms of

909833/1166

their training as well as their mode of action together with other goals and advantages aa the clearest In the following description, taken in conjunction with the accompanying drawings, in which like references are used refer to like parts in the different views.

In eng drawings in which the execution examples of the of the present invention

Figure 1 is a diagram in which the acceleration versus the time is represented,

Figure 2 is a diagram in which a dimensionless stroke value is shown versus a dimensionless input acceleration parameter,

FIG. 3 is a diagram in which a dimensionless input acceleration parameter is plotted against the initial impact velocity,

Figure 4 is a diagram in which the stroke is shown versus the speed,

Figure 5 is a power diagramaa, in dea somewhat “cheaply one Energy absorbing device according to the present invention is shown when subjected to non-axial impacts will,

FIG. 6 shows a longitudinal sectional view of part of a door direction for absorbing energy that alters in connection tubular telescopic parts according to the present invention Can be used 909833/1166

FIG. 7 an enlarged partial cross-sectional view along the line 7-7 in FIG. 6,

FIG. 8 is a view similar to FIG. 7, in which a part is shown on a considerably enlarged scale, ura to illustrate certain training details more clearly,

FIG. 9 shows an enlarged cross-sectional view along the Line 9-9 in Figure 6,

FIG. 10 an enlarged partial cross-sectional view along the line 10-10 in FIG. 6,

Figure 11 is a plan view with parts broken away Illustration of the internal configuration of a steering device in which the tubular parts according to the present invention be used,

FIG. 12 an enlarged cross-sectional view along the line 12-12 in FIG. 11,

FIG. 13 shows an enlarged partial cross-sectional view the line 13-13 in Figure 12,

FIG. 1h is a view from below of a motor vehicle using a drive shaft which is a second embodiment of the present invention;

FIG. 15 shows an enlarged cross-sectional view along FIG Line 15-15 in Figure 14,

FIG. 16 shows a cross-sectional view along the line 16-16 in FIG.

909833/1166

Figure 17 is a partial cross-sectional view corresponding to Figure i6 and shows a drive shaft which forms a third embodiment of the present invention, and FIG

FIG. 18 shows an enlarged cross-sectional view along the Line 18-18 in Figure 17.

909833/1166

It is known; that when a motor vehicle hits a stationary object, the motor vehicle causes a certain damping of the shock due to the permanent deformation of the bumper _{9 of} the radiator, the chassis and the like, even if the motor vehicle has no special device for absorbing energy. If there is a load at the connection between the steering column and the wheel

ψ is attached schleunigungsmesser that gemeaaene during the surge acceleration expected to describe the shape of a Halsimiswelle which is similar to that shown in Figure 1. "Although it is difficult ₉ accurate" form of SingaiigsbeBchleunigtmg shown describe exactly au _t this type of .scheint Eingangsliosefeletmigimg two Parameters at & fznwelBen »piping are the peak clutches a and - the duration of the acceleration & t. Aue of an analysis & @ r saliireielaeia on the water and on the land results in experiments

. that the Halbsimiswellenfora seems to be the Eingasgst "@ eehi @ wig" iige "> curve due to the destruction of VerauchskSrners during Stoseee. Assuming ₉ da0 the Verformungsiaechanik for cars is similar, it can be a mathematical analysis of the requirements for the Set up the device for the absorption of energy or the damping device in use on the steering column of the motor vehicle.

ORIGINAL 'INSPECTED 909833/1166

In Figure 1, a Besohleunigungekurve Energieabsorbierungsvorrichtung of the half sine wave iat superimposed na three additional parameters to illustrate, dl · was mathematical description of the characteristics of the device are required. These three parameters are as follows. At time t _± , the device is _{actuated with an acceleration value a g} occurring during the initial acceleration of the impact. The device is operated bit of this acceleration until the speed of the device equals Hull, which is the case at the "lateral point t".

On the basis of the acceleration characteristics shown in FIG. 1, a solution for the stroke requirements of the Energy absorbing device as a function of three variable quantities are developed: The ratio of the acceleration of the device to. the top entrance soles u nigung & ₈ / & _o »an extension-free acceleration ratio

^a o Λ t

, where ν is the original velocity of impact

Ir * ο y B

is equivalent to; and a dimensionless Bubparaeter - *

β ' where β is the stroke of the energy absorbing device. The dimensionless stroke parameter · £ · for the device is shown in Figure 2 as a function of the other two parameters. Examination of the results of this figure shows that if the dap-

909833/1166

If advantages are to be derived, a value · _β Α _{0 is} obtained HuQ _{9 will be} equal to or greater than 0.5 1st. Venn also the

a -

Values for less than i, it can be difficult to

T-.

Kutssen ans the result of the deformation of the car "Tenden attenuation occurring defects don, unless the ratio _v a _e / a _@ 1st close to i, which is extremely impractical. Since the

technical significance of the Bnufteter a_ / a _Ä sich τοη seiest a β ο

understands, and the unique parameters that some 13 retell dare to do require the access control parameter and the

Hubparaneter j ■■■ · The first parameter that ans vertinderliehen Sizes, which are based on the ingress fiieeehlwig »*

cart according to Figure 1 can be used, dnreb the etofigeswlndigkeit r _Q and the paraseter be determined, which depends on the product of the peak "g ⁿ -forces, g _o , and the Stred» ^ ₈ , which is a measure of the initial velocity τ »At, which describes the duration of the input obligation The characteristics of the acceleration parasite are in

FIG. 3 is shown as a function of the initial thrust t _q and the product _{parameter g o} .A ₈ . Examination of the results in FIG. 3 shows that with a material velocity of less than about 6 a / sec. and with appropriate values for g_ · _ the values for the shock acceleration parameter

300833/1166

are greater than i.

At impact speeds of 12 to 30 m / sec. must however Values for g_ Jl _ reached «earth that are greater than 100, otherwise the stroke reduction shown in FIG. 2 is derived on the basis of the intake acceleration parameter Benefits not realized. In more physical terms, it must be upon the occurrence of an input peak acceleration of 100 g during an impact, the entire remaining weight. formed by the bumper, the radiator, the chassis of the motor vehicle and the Leitpmnke and the like. Exceed at least about 30 cm and possibly be greater than 1.5 η at high speeds. The results in FIG. 3 clearly show that when there are impacts at high speeds (in the range between 12 and 30 m / sec.) the damping of the shock for the driver through the steering column through additional damping devices, such as an energy-absorbing bumper or guardrail can be supported to keep the amount of load and the impact distances of the driver · as low as possible to keep.

In order to determine the actual stroke length required for the steering column from the parameter s according to FIG. 2, the stroke parameter ν o / 2a _{e is shown} in FIG. 4 as a function of the impact velocity vo and various prescribed g values

909833/1166

of the arranged in the steering column annular damping member shown. After it has been bestinoit 1. A value for the dimensions loosely Hübet recke from Figure 2, the time required for the attenuator actual travel distance is obtained by the value of h obtained from figure for ν o / 2a_ one, the

a function of the impact velocity vo and the operating g-

1, the device's force is _ΰ g _ß9 , multiplied by 's.

It is assumed that by developing the Motor vehicle and / or the crash barriers dor value s "" ~ 0.5 Figure 2 can be obtained. For a shock speed of 24 m / eec, which corresponds to a speed of 86.4 km / h, and with a g-value of the energy absorbing device or damping device of 30, which can without harm to the driver according to the established criteria for human endurance If it is acceptable (in forwards and backwards direction), a stroke requirement of 3 x 0.5 == i »5 FuO (0.45 ■) is required for the damping device of the steering column. If the value of s "" 0.5 are not obtained by appropriate design of the vehicle and / or the guardrail, a value of s " ⁼ 0.9 would be realized and, as a result, the damping device of the steering column would have a stroke of almost zero .91 m for the same impact conditions It is evident that if a stroke distance of 0.45 ■ is practically feasible in the steering column and values of 0.9 η

909833/1166

or more are practically impracticable, preventing injury to a driver at relatively high speed, namely at 24 ra / sec. or 86.4 km / h for no steering column damping system is feasible unless the shock absorption is supported by other sources of absorption.

One such source of steam is the highway guardrail, in a further proposal by the applicant (patent application Ref .: P 15 75 076.2 of June 16, 1967) 10 is shown. This guardrail itfo is a periodic one Energy absorbing device 12 and an energy transfer device 14, as shown in Figures 5 to 10 of the present application.

The energy transmission device 14 comprises a shock absorption device 16, an inner tubular member 18, a first connecting means 20 and a bracket 22, the bracket 22 comprises a fixed support 24 and an outer tubular Part 34, which is the periodic energy absorbing device 12 holds in operational assignment on the inner tubular part 18 and the orientation of the part 18 on the periodically acting energy absorbing device 12 maintains. The holder 22 also has a «wide

909833/1166

-Ik-

binding device 36, with which the aus8ere tubular Part 34 connected to the support 24 is the outer tubular part 18, the outer tubular part 34 and the periodic Acting energy absorption device 12 form a damping arrangement 42.

Each damping arrangement 42 has a stroke of about 609 »6 W from its fully extended position to its fully compressed position in which the inner tubular part 18 is almost entirely within the outer tubular part 34. The cushioning assemblies 42 absorb the energy in a manner to be described below in that they are compressed when the shock absorbing device 16 receives a shock from a motor vehicle or the like. special damper starts without the driver or anyone substantial damage would be caused to other occupants of the vehicle.

Each connector 36, 20 includes an eyebolt 44 with an externally threaded end 46 and a socket end 48 on. The socket end 48 has a socket 50 in which a ball member 52 is secured by a screw and nut assembly 54 (Figure 10) is hingedly attached to the connection with

909833/1166

an associated support 24 or an associated shock absorption device 16 is used. When the shock absorber 16 assumes the position in which it is located before the impact, the damping devices 42 form an angle of approximately 45 ° with the shock absorbing device 16. The flexibility of the connecting means 20, 36 and the position of the shock absorbing device 16 ensure before the impact that the stroke of the shock absorbing device 16 is almost only restricted by the distance associated with the diameter of the dampers 42, rather than their compressed length. Furthermore, this arrangement ensures that the damping devices 42 and the connecting means 20, 36 remain intact regardless of the joint angle.

With particular reference now to Figure 5, if optimal energy absorption is to be achieved, the Force F of the shock during the entire stroke length of the cushioning .42 be a constant. For this purpose the force F des

Damper necessarily with the stroke with the change of

1 cos O increase, with Q possibly increasing during d «s Stroke would change between 45 ° and 75 °. This force, which increases with the stroke, is included in the description below the manufacture of the damping device * n 42 is provided. There the shock absorbing device 16 is designed so that it during the stroke of the damping device 42 not for

9098 3371166

permanently verfortat, and since the damping devices both with Both pull and push strokes work, each damper is operational regardless of the angle of the impact force. In order to the impact force is over the largest possible area of the impact » recording device i6 distributed, and it results from it a low probability that any of the attenuators gets destroyed.

The diameter of the outer tubular part 34 is sufficiently larger than the outer diameter of the inner tubular part 18 so that an annular space or chamber 70 is formed between the parts 34 and 1Θ. The periodically acting vif energy absorption device 12 is arranged in the hemmer 70 in a drive-related assignment to the outer tubular part 34 ναι ', the inner tubular part 18, by periodic plastic deformation and the reversal of this deformation on the mechanical transmitted to it by the energy transmission device Ik Energy to absorb energy. The periodically acting energy absorbing device 12 comprises a working cage 72 and a storage cage 73 and a solid, non-elastomeric, in the radial direction uncompressed curved body in the form of a spiral coil 74 with a plurality of turns - 76. Each turn 76 represents a curved body, the a periodic plastic tensile deformation and compression deformation by the

909833/1166

Rotation of each turn 76 about its inner axis can be subjected. The periodically acting energy absorbing device 12 is prevented by a retaining cap 80 from becoming Move beyond the end 78 of the tubular member 18. Ilaltekappe 80 has a side wall 81 that forms the end 78 of the tubular part 18 surrounds and is attached to this by suitable welds 82, as well as a bottom wall 84, the function of which is described below. The side wall 81 has an upper edge 86 on which the Arbeltskäage 72 can engage to prevent it from being on the End 78 is moved past.

The working cage 72 and the storage cage 73 each have a inner tubular part 18 surrounding band 88 and middle curved bodies 90 which are arranged in elongated openings 92 which are provided in an associated band 88 are.

The amount of energy absorbed by each damper 42 depends in part on the number of turns 76 that are rotated about their inner axes during a particular tube. The number of turns 76 that are rotated depends on whether or not they are brought into working engagement with the inner tubular portion and the outer tubular portion 34 during a particular working stroke

909833/1 166

not. The windings 76 are brought äuseeren 18 and the tubular Toil Vi during a working stroke in Arbeitooingriff with the inner tubular member in order to generate the to your old Arbeitehub increasing force, as is provided in the preparation of each damping device k2. This is achieved in that the inner tubular part 18 is designed to be conically tapered by a certain amount from its end 78 to its other end Sk. Such a conical tapering of the inner tubular part 18 forms a variable chamber 70 which results in an increase in the force during the working stroke. The hatred of the conical taper depends on the length of the inner tubular member 18, its diameter and the diameter of the coils 76, as will be described in detail below.

During a particular working stroke, the working cage 72 not only absorbs energy due to the rotation of the curved body $ 0 about its inner axis, but it also moves the windings 76 of the spiral-shaped body lh in a working position with the outer tubular part 34 by shifting the windings 76 on the inner tubular Part 18 along in the direction of arrow 96. A certain number of turns 76 is from the beginning in working engagement with the inner tubular part 18 and the outer tubular part 34, so that the periodically acting energy absorption.

909833/1166

device 12 a certain amount of energy at the beginning of the impact Uei absorbs the turns 76 in working engagement with the inner tubular part 18 and the outer tubular To bring part 34, the inner wall 98 of the outer tubular 'Feiles 34 and the outer wall 100 of the inner tubular Part 18 a sufficient exercise force on the windings 76 exercise in order to turn them around their Innon axes. At the The periodic energy absorbing device can end the stroke 12 can be brought back to the end 78 of the inner tubular part 18 by the extension movement of the associated damping device 42. During this extension movement the storage cage 73 ensures that the turns 76 remain properly lined up.

When a special damping device 42 vol constantly extended is, the periodically acting energy from, orbierungseinrichtung 12 prevented by a nut 104 from exiting the open end 102 of the tubular part 34. the Nut 104 sits on an externally threaded ring 106 which is attached to the end 102 of the tubular part 34 by suitable Welds 108 is attached.

Although for the various individual parts of each damping device 42 a number of different parameters

909833/1166

To apply, the following values can be used as illustrative Example are given:

The inner tubular member 18 may be a hollow cylindrical body of heat treated stainless steel 17-7 PH. This body came through a wall thickness of O ₉ 6J5 ram “as ee

Arrows IiO in Figure 8 is indicated, an effective position to »P 30%, 8 ma and an outside diameter, tier an aem lsi © 9 ¹ * 69j (0% mm and is at a rate of change v & a 0.5 wo. Per Meters in the direction of the end 78 sn tapers a shorter diameter.

The outer tubular ^f £, n \ "5k can be the hollow cylindrical body made of heat-treated stainless steel 17-7PH with a wall thickness of 0.635 mm and an outer diameter of 72.21 ms.

The annular chamber 70 has between the outer tubular

Part 34 and the inner tubular part 18 at the end 9h of the inner tubular part 18 have a clearance of about 0.94 mm with a corresponding increase with a rate of change of 0.5 mm per meter towards the end 78 to a highest increase of 0.381 mm.

909833/1166

The curved bodies 90 in the cages 72 and 73 exist made of a stainless steel wire 302 and each have a diameter of about 1.18 mn and a length of 22.098 ma. In each of the cages 72, 73 there are six such bodies and a force of about 81.646 kg is required to move each cage necessary"

The spiral coil 74 is made of a stainless steel Steel wire 302 approximately 1.143 mm in diameter, and has about 80 turns 76. It takes about 90.718 kg to rotate each turn about its inner axis. There the clear width of the annular chamber 70 has a maximum increase of 0.038 mm and the curved body 90 by 0.038 mm have a larger diameter than the turns 76, the Cages 72, 73 always in working engagement with the tubular parts 18 and 34. This ensures that the cages 72, 73 always exert a moving force on the windings 76 during the working stroke of the damping device 42.

The connecting part 20 is attached to the end 94 of an associated damping device 42 by means of a pin 112, which is fastened in the open end 94 of the inner tubular part by suitable welds 114 and one old Has internally threaded bore 116 which receives the externally threaded end 46 of the eyebolt * 44,

909833/1166

The connecting part 36 is with the end 118 of the outer tubular part 34 connected by an end cap 120, which is in the open end 118 by suitable weldings 122 is attached and an internally threaded bore 124 comprising the externally threaded end 46 of the eyebolt 44 records. An air inlet valve 126 is in the end cap 120 attached and is used to introduce compressed air into the interior of the outer tubular part 34 to exercise a against the closed bottom wall 84 of the end cap 80 directed force, which serves to do so, the damping device 42 to extend again if it was previously compressed

909833/1166

A first exemplary embodiment of an energy-absorbing tubular telescopic part with the ability to transmit of three moments will now be described in connection with FIGS. ii to 13, in which a steering device 146a comprises a shock absorbing device l6d in the form of a steering wheel, which rotatably with an inner tubular part 18d is connected, which is telescopic in an outer tubular Part 34d is seated which has a sliding shaft 216 attached to end 218 of the outer tubular member. The sliding shaft 216 is the usual steering gears (not shown) operatively associated with housed in a housing indicated by dashed lines 220 is shown.

The steering device 146a further comprises a periodic acting energy absorption device 12d, that of the periodically acting energy absorption device described above 12 can be the same, with the difference that a certain Number of turns 76d can be provided with spherical parts 222 which are arranged in groove-shaped chambers 224, around the inner tubular part 18d with the outer tubular To connect part 14d rotatably while allowing the relative reciprocating movement between these two parts. the Groove-shaped chambers 224 can be formed by running in the axial direction curved channels 226 are formed in the

9 0 9 8 3 3/1166 original INSPECTED

outer tubular part 34d are formed, as well as by corresponding formed in the inner tubular part ISd · » de channels 228.

A second embodiment for an energy-absorbing tubular telescopic part with the ability to transmit torques is now shown in connection with FIGS 16 to 16, in which a motor vehicle 230 comprises a chassis 232 with a frame 234, a rear axle housing 238, a diffemtial 240 and a transmission 242. A driveshaft assembly 244 connects the transmission 242 to the differential 240 and includes an inner tubular member ISe ₉ that telescopes into one of our tubular members 34e.

The drive shaft 244 also includes a periodically Energy absorbing device 12d, that of the above in connection with the figures il to 13 described periodically acting energy absorption device can be the same. The periodically acting energy absorbing device 12d has at least one turn 76d, which is provided with spherical parts 222, which are in groove-shaped chambers 246 are arranged to rotate around the inner tubular member ISe to connect with the outer tubular part 34e and at the same time the relative movement in the axial direction or the re-

909833/1166

relative back and forth motion between these two parts to allow. The groove-shaped chambers 246 know by in Krttnnte channels 248 extending in the axial direction are formed formed in the outer tubular part 34e are, as well as through corresponding channels 250, which in the inner tubular part 18e are formed.

As shown in Figures 17 and 18, a drive shaft 244a can be identical to the drive shaft 44, bit the deviation that the spherical parts 222 and the groove-shaped chambers 246 by a plurality of shearable parts 222a or slots 246a extending in the circumferential direction can be replaced. -

The drive shaft 244a has a periodically acting energy absorption device 12f, which can be the same as the periodically acting energy absorption device 12d the difference that the spherical elements 222 are omitted, whereby the turns 76f are the same as the turns 76 described in connection with old FIGS. 7-8.

The shearable parts 222a connect an inner tubular part 18f in a rotationally fixed manner with an outer tubular part Part 34f, but can easily be sheared off to allow relative axial movement or reciprocating movement between

909833/1166

to allow these two parts. Each shearable part 222a can be held in place in the slot 246a assigned to it by a weld 108a which also attaches an externally threaded part 106a to the outer tubular part 3ht . Four shearable parts 222a can be used, and each part can consist of a 5O ₈ 8 ram χ 0.0503 mm large UiSsingheilageblech or the like. The measurement of 50.8 mm is arranged in the radial direction so that each part 222a is subjected to normal torque loads which occur during the rotation of the drive shaft 2kka. occur * is not sheared. The dimension of O _s 0508 mm allows the shearing without undue increase d®r Mrapfungskiaft, when the drive shaft is subjected to an axial load of 2kh & sufficient greetings, to trigger the periodic effect of the energy-absorbing means acting periodically 12f.

While those shown and described in detail here special tubular parts are capable of the above To achieve goals and to offer advantages, it should be noted that they are only illustrative of the present preferred embodiments of the invention, and that the details of the training or construction shown here are only limited by the scope of the attached parts which form part of the present disclosure *

909833/1166

Claims (1)

Munich, the II. October 1968 AlU, IXiC. ! feet Covina, California
West Garvey Avenue 2017
V. St. A. Patent application; "Energy-absorbing, telescopic tubular © parts with the ability to transmit torque." PATENT CLAIMS Iv Energy-absorbing telescopic part with the ability to Transmission of torques, characterized by an inner part (l8), which is telescopic in an outer part (34) with sufficient space to form an annular chamber (70) sits between the two parts, a periodically acting Energy absorbing device (12) located in the chamber is to absorb energy that is applied to the periodically acting energy absorbing device by a relative 9 0 9 8 3 3/1166 axial movement of the two parts (i8, 34) is transmitted, whereby the periodically acting energy absorption unit has means for absorbing energy through a plastic deformation and the reversal of the plastic deformation of the same parts, the plastic deformation by the transfer of mechanical energy from the parts ( i8, Jk) is caused on the energy absorbing device, and means (222, 246) which connect the parts (18, 34) to one another to prevent the relative rotation between them without significantly hindering the relative axial movement between the two parts. 2. Energy-absorbing part according to claim 1, characterized in that that further parts of the periodically acting energy absorbing device are determined in one direction effective operation of the parts (i8, 34) of a periodic deformation subjected, gradually changing the force required to move the parts, until it reaches a prescribed value, after which it is constant as the parts continue to move. 3 · Energy-absorbing part according to claim i, characterized in, that one part (l8d) is an upper part of the steering column and the other part (34d) is a lower steering column part. 9 09833/1166 4. Energy-absorbing file according to claim I _9, characterized in that one part (l8e) is connected to the transmission of a motor vehicle and the other part (34e) is connected to the differential of the motor vehicle. 5 energy-absorbing part according to claim i, characterized in that the periodically acting energy-absorbing device consists of a solid, non-elastomeric, curved body which is not compressed in the radial direction and which can be rotated around its inner axis in order to by alternating "de plastic tensile deformation and plastic compression deformation equal parts to absorb energy that is transferred to them during each cycle ¹ through the parts (18, 3h) . 6. Energy-absorbing part according to claim i, characterized in that the periodically acting energy-absorbing device comprises a working cage (72), a spiral-shaped body (74) and a storage cage (73) 7. Energy-absorbing part according to claim I _9, characterized in that the annular chamber (70) has a variable width, and that the periodically acting energy absorbing device is subjected to mechanical energy in a hatred that is controlled by the variable width of the chamber. 90983 3/1166 β. Energy-absorbing part according to claim 1 _9, characterized in that the connecting means (222-, 246, 25 ©) »at least one each in the axial direction-extending Kasaer {2% 6 or 250) on each part (jhe or iSe) and an ils substantially spherical member (222) which is inserted into the eammra. is arranged. 9. Energy-absorbing part according to claim I ₉ dadiareli characterized t that the connecting means comprise at least one alssclbaren part (223 $, which connects the inner part * (l8f) bit üma outer part (34f). 909833/1166 uv Blank page