RU2190789C2 - Torsional vibration damper - Google Patents

Abstract

FIELD: mechanical engineering; vibration dampers. SUBSTANCE: torsional vibration damper has two twistable members made for angular displacement relative to each other, coil spring and support shoe. Joint is provided between support shoe and coil spring in direction of longitudinal axis which is made so that shoe cannot be lost. EFFECT: enlarged range of operating conditions. 25 cl, 10 dwg

Description

 The invention relates to a torsional vibration damper with at least two twistable structural elements that overcome the resistance of at least one energy accumulator and have impact areas for compressing the energy accumulator formed by at least one coil spring, which is at least , one of its two ends interacts with a retaining shoe having the possibility of angular contact or scrolling relative to both of the mentioned structural elements, and intended To Propping corresponding spring end.

 From the patent DE-OS 3610127, a torsionally elastic vibration damper coupling is made in the form of a two-mass flywheel, and between the primary flywheel mass connected to the drive motor and the secondary flywheel connected through the clutch to the gearbox, torsionally elastic or vibration damping elements are introduced, giving the possibility of relative scrolling between both fly masses. These torsionally elastic elements are formed by energy accumulators having coil springs. These energy accumulators during relative scrolling of both fly masses are compressed by the impact areas provided for them. At the same time, covering strips are provided between the impact areas and the coil springs, on which the corresponding coil springs are supported. Further, the patent proposes to use long power batteries in the so-called dual-mass flywheel, which are formed by springs inserted one after another into a certain chamber, i.e. arranged in a sequential row. Wedge-shaped intermediate inserts are provided between the springs inserted into the chamber. Other features of the design of these intermediate inserts are not indicated in the patent.

 From patents DE-OS 3721711 and DE-OS 3721712, retaining shoes or inserts for the end sections of the springs are known having a protrusion of such a shape that even when the corresponding spring is extended from the end section, it can penetrate back into this end section. Although such shoes for springs can find application in support cavities having a substantially closed loop or adapted to the outer diameter of the spring, as applied to chambers for accommodating springs that are not adapted to the outer contour of the springs and / or are generally not closed along the contour, such shoes for springs can be twisted or pinched in such a way that their penetration back into the corresponding springs cannot occur, as a result of which the function of the damping device or two-mass flywheel is at least , broken or even the destruction of the shoes and / or the springs themselves.

 The same drawbacks are also inherent in the torsional vibration damper described in DE 4201370, comprising at least two structural elements which are arranged to be angularly displaceable relative to each other in a certain section to overcome the compression resistance of at least one coil spring, and one retaining shoe, designed to interact with the possibility of angular displacement at one end with a coil spring, with each of these structural elements propping up the corresponding end a helical spring and forms a retaining portion for an adjacent end coil of a helical spring.

 The basis of this invention is the task of creating retaining shoes for springs, which provide excellent support for the ends of the springs interacting with these shoes in all encountered operating conditions and can also be used in a variety of cases and types of vibration dampers. Further, it is necessary to ensure the possibility of particularly simple installation, as well as cheap manufacturing of a vibration damper. The design of a torsional vibration damper according to the invention should also enable a large number of options for fitting to a specific form of a graph of torque or torsion resistance, characterizing both mutually twisted structural elements and generated by an energy accumulator or coil springs that counteract the twisting of these structural elements. Therefore, it is necessary to implement very soft, i.e. very gentle torsion resistance characteristics and / or multi-stage torsion resistance characteristics.

 The task in a torsional vibration damper, comprising at least two structural elements that are capable of angular displacement relative to each other in a certain area to overcome the compression resistance of at least one helical spring, as well as one retaining shoe designed for interaction with the possibility of angular displacement at one of its ends with a coil spring, while each of the mentioned structural elements props the corresponding end of the coil spring and t booster section to the adjoining end winding of a helical spring according to the invention is achieved in that the direction of the longitudinal axis between the shoe and said booster coil spring for positioning and / or retaining position provides a compound which is formed without the possibility of loss of the retaining shoe.

 The retaining shoe has a protrusion that crosses the adjacent end portion of the spring in the direction of the longitudinal axis.

 The retaining shoe is connected to the coil spring by means of a geometric closure, eliminating the possibility of losing the retaining shoe.

 Between the retaining shoe and at least the adjacent end of the coil spring there is a geometric short circuit.

 A snap-type connection is provided between the retaining shoe and the coil spring, creating a geometric circuit.

 There is a connection between the coil spring and the protrusion of the retaining shoe, eliminating the possibility of losing the retaining shoe.

 The retaining shoe has an annular portion intended to support the adjacent end of the coil spring, from which a protrusion extends into the inner cavity of the coil spring, limited by turns so that the retaining shoe can be held in relation to the coil spring, eliminating the possibility of losing the retaining shoe.

 The free end segment of the spring coil adjacent to the retaining shoe is designed to hold the retaining shoe with respect to the coil spring.

 The retaining shoe has a radial groove designed to enter it with a geometrical closure, like a latch, of at least one coil of a spring.

 The free end section of the end coil of the spring radially enters the groove of the retaining shoe adjacent to this end section of the spring.

 When unclenched, the end coil of the coil spring is adjacent to the retaining shoe, with the exception of the end portion included in the groove of the retaining shoe, and has the same elevation angle as the coils between the end coils.

 The end portion of the corresponding end coil, at least in the unclamped state of the coil spring, is parallel to the retaining pad of the retaining shoe for a given coil spring.

 The end portion of the end coil of the coil spring adjacent to the retaining shoe is offset relative to the other coils radially in the direction to the longitudinal axis of the coil spring.

 The energy accumulator is formed by at least one outer coil spring and at least one inner coil spring inserted into a cavity bounded by turns of the outer coil spring, said at least one supporting shoe being installed on at least one end of the energy accumulator, which with an external coil spring for positioning and / or maintaining a position forms a connection that is made without the possibility of losing the retaining shoe.

 The energy accumulator is formed by at least one outer coil spring and at least one inner coil spring inserted into a cavity bounded by turns of the outer coil spring, said at least one supporting shoe being installed on at least one end of the energy accumulator, which with an internal coil spring for positioning and / or maintaining a position forms a connection that is made without the possibility of losing the retaining shoe.

 The energy accumulator is formed by at least one outer coil spring and at least one inner coil spring inserted into a cavity bounded by turns of the outer coil spring, said at least one supporting shoe being installed on at least one end of the energy accumulator, which with both an external and an internal coil spring for positioning and / or maintaining a position forms a connection that is made without the possibility of losing the retaining shoe.

 The energy accumulator is formed of at least two helical springs arranged in series between the interaction areas of the twisted structural elements, and said supporting shoe is installed between the opposite end sections of the coil springs for positioning and / or maintaining the position of at least one of the screw springs without the possibility of losing said retaining shoe.

 At least one of the two coil springs forms an outer spring into which an inner spring is inserted, the length of which is at least part of the length of the outer spring.

 In at least one pair of coil springs, which include the outer and inner springs, the inner spring is shorter than the outer spring.

 In at least one pair of coil springs, which include the outer and inner springs, both springs have the same length.

 At least one of the coil springs forming the energy of the coil in the open state has a predetermined shape.

 The energy accumulator formed by helical springs has a large ratio of length to outer diameter.

 Between mutually twisted structural elements, no more than three energy accumulators are provided located on the same diametric section.

 Energy accumulators are provided between mutually twisted structural elements and are arranged to scroll in both directions by an angle of at least 30 degrees.

 The torsional vibration damper according to the invention is an integral part of a flywheel consisting of several masses or forms such an integral part.

 Below the invention is considered in more detail with reference to the drawings.

Figure 1 is a section through a vibration damper according to the invention,
figure 2 is a partial section along the line II-II according to figure 1,
figure 3 - retaining shoe in section,
FIG. 4 - end of the spring adjacent to the retaining shoe of figure 3, front view,
5 is a view along arrow V according to figure 4,
FIG. 6-9 - other embodiments of retaining shoes and resp. coil springs interacting with the corresponding shoes,
figure 10 - energy accumulator, consisting of several coil springs.

 Torsional vibration damper, partially shown in FIGS. 1 and 2, is a flywheel 1 divided into two parts, which consists of a first or primary flywheel mass 2, fixed to a driven shaft of an internal combustion engine, not shown, and a second or secondary flywheel mass 3. On the second flywheel mass 3, it is possible to fix the friction clutch by laying a clutch disc between them, by means of which the gearbox input shaft not shown in the drawing can be turned on and off. The flywheel masses 2 and 3 are mounted with the possibility of mutual rotation on the bearing 4, which in the illustrated embodiment is located radially outward with respect to the holes 5 for passing screws fastening the first flywheel 2 to the driven shaft of the internal combustion engine during assembly. Between both fly masses 2 and 3, there is a damping device 6, consisting of energy accumulators 7, of which at least one is formed by compression coil springs 8, 9, 10. As can be seen especially from FIG. 2, the compression coil spring 9 is inserted into the space formed by the turns 8a of the spring 8 or, in other words, both coil springs 8 and 9 are inserted one into the other in the direction of their length. In the illustrated embodiment, the angular extent or length of the arc 11 of the inner coil spring 9 is less than the length 12 of the outer coil spring 8. In this case, it is advisable to make the inner spring 9 shorter than the outer spring 8 by a distance of 13, which is about 1-5 angular degrees. However, the length or angle of difference 13 may be greater. Springs 8, 9 can have the same length or the same angular extent. With both parallel acting coil springs 0, 9, the coil spring 10 forms a series connection in a row. Although an internal spring is not provided in the illustrated embodiment according to FIG. 2, in many applications such an internal spring would be appropriate. Then it is installed in the spring 10 in the same way as the inner spring 9 in the outer spring 8. For some applications, it may be appropriate to use only the outer spring 3, i.e. inner spring 9 drops out.

 Both fly masses 2 and 3 have impact areas 14, 15 or 16 for energy accumulators 7. In the illustrated embodiment, impact areas 14, 15 are formed by protrusions extruded in these places from stamped sheet parts 17, 18, forming fly mass 2. Impact sections 16, provided axially between sections 14, 15, are formed by at least one flange-like part 20 connected to the secondary flywheel 3, for example by rivets 19. This part 20 serves as a torque transmission element and from the energy accumulator 7 to the fly mass 3. The impact sections 16 are formed in the form of radial protrusions 16 on the outer contour of the flange-like impact means 20. The part 13 obtained by cold stamping of sheet material serves to fix the first fly mass 2 or the whole divided into two parts flywheel 1 on the driven shaft of an internal combustion engine. On the outer contour, part 17 is connected to part 18, also made of sheet material. Both parts 17 and 18 form an annular space 21 having a toroidal section 22. The annular space 21 or toroidal section 22 is at least partially filled with a viscous medium, for example thick oil. In the circumferential direction between the protrusions or the impact areas 14, l5, the parts 17,18 form protrusions 23, 24, which define the toroidal portion 22 and serve to accommodate the energy accumulators 7, fixing them in the radial and axial directions. But at least, when the device 1 is rotated, the coils of the springs 8 and 10 are supported in parts 17 and / or 18 that define a toroidal portion 22 around the outer perimeter. In the illustrated embodiment, a casing 25 is provided for protection against wear, made in the form of at least one hardened sheet insert or sheet gasket. It is advisable to arrange the casing 25 in a circumferential direction, at least along the entire length or angular extent of the expanded energy accumulator 7. Under the influence of the centrifugal force of the support of the wicks of the springs 8 and 10, friction damping depending on the rotational speed is created between them and the frictional interaction with them fluctuations in the lengthening or compression of the energy accumulators 7 or power accumulators 8 and 10.

 On its inner contour, part 17 carries an intermediate sleeve 20 in which the inner ring of the ball bearing 4 is placed. The outer ring of the ball bearing 4 carries a flywheel mass 3.

 As can be seen especially from FIG. 2, the impact areas 16 are angularly shorter than the impact areas 14,15, as a result of which, judging by the theoretical resting position shown in FIG. 2 or the initial position, a slight scrolling in both directions of rotation of the fly masses is possible 2 and 3 relative to each other without spring action.

 Between facing each other, i.e. adjacent end coils 27, 28, on the one hand, and coils 29, on the other hand, springs 8, 9 and 10, as can be seen from FIG. 2, an intermediate element 30 is provided, which can be called a retaining shoe or a spring seat and which serves to support the end turns 27, 28, 29, i.e. the end sections of the springs 3, 9 and 10. In the embodiment shown in FIG. 2, the intermediate insert or retaining shoe of the spring 30 has an annular section 31 on which the springs 8, 9 and 10 rest in the circumferential direction, as well as extending at right angles to the section 31, the protrusion 32, which enters the cavity between the turns 10a, i.e. in the end portion of the spring 10. In the illustrated embodiment, the retaining shoe 30 is hollow, that is, has a cavity 33. As can be seen in figure 2, the energy accumulators 7 or the coil springs 8, 9, 10 that form them do not have end sections facing the impact areas 14, 15, 16, no retaining inserts or shoes. However, at least one of the ends of the energy accumulators 7 could provide a spring shoe or retaining insert.

 The retaining shoe 30 is connected about a compression screw spring 10 in a manner that reliably eliminates the possibility of its loss. To do this, between the shoe 30 and the spring 10, a geometric closure is provided, which in the illustrated embodiment is latched, as will be explained in more detail when considering FIGS. 3 and 4.

 As can be seen from figure 3, the spring shoe or retaining insert 30 has an annular groove 34 formed in the form of a recess, which is provided in the axial protrusion 32, directly adjacent to the annular section 31. The outer portion 35 of the protrusion 32 corresponds to at least approximately the inner diameter 36 turns 10a of spring 10 (FIG. 4). It is advisable to make the outer diameter 35 slightly smaller than the inner diameter 36, which takes place at least in the portion of the end of the spring facing the shoe 30.

 As can be seen from figure 4, the free end segment 37 of the end coil 29 adjacent to the retaining shoe 30, in the radial direction to the axis of the spring 38 is bent or shifted relative to the other zones of the end turns of the spring 29 or relative to the turns of the spring 10a. This results in a light width 39, which is less than the inner diameter 36 of the end turn 29 and the inner diameter 36 of the end turn 29 and the turns 10a or the outer diameter 35 of the protrusion 32. When assembling the spring 10 and the retaining shoe 30, the protrusion 32 is pushed into the corresponding end portion of the spring 10 so that the end turn 29 is first extended, so that the distance 29 first increases. Therefore, the end portion 37 is radially pushed out.

 As soon as the end portion 37 of the turn 29 reaches the level of the groove or recess 34, the end turn 29 can spring back, as a result of which the distance 29 decreases again and thereby the end portion 37 radially penetrates the groove 34, snap into it, so that the retaining shoe 30 held in the spring 10 without the possibility of loss. The protrusion 32 has at its free end a narrowing or chamfer 39, which facilitates the penetration or pressing of this protrusion 32 into the end portion of the spring 10 facing it. Through the constriction 39, the end portion 37 can be extended radially outward.

 As can be seen from Fig. 5, the end turn 29 has everywhere, except for the end portion 37 radially entering the groove 34, the same step, i.e. the same angle of elevation as in the end turns 10a of the spring 10. The end segment 37 of the spring 10, at least in the open state of the spring 10, runs parallel to the supporting surface 31a (Fig. 3) of the annular portion 31 of the retaining shoe 30. For this end section 37, as can be seen from FIG. 5, is bent from the dotted position 37a to the position of the end portion 37 shown in solid lines in the direction of the longitudinal axis 38 of the spring 10.

 At the end 39 of the spring 10, adjacent to the impact areas 14, 15, 16, the last turn is in a known way pressed to the last but one turn due to deformation in the direction of the axis of the spring 38 and sanded, as a result of which it at least approximately forms an abutment area located perpendicular to the axis of the spring 33. Such a shape of the final coil is proposed, for example, in the patent DE-OS 4229416. Both coil springs 8 and 9 have also flattened end coils at their end portions corresponding to them, which ensures a flawless rileganie these portions of the springs 14, 15, 16 as well as the excellent Propping these springs 8, 9, the end portion 31 of the interposer 30 or retaining shoe.

 Coil springs 8 and 10 may have the same stiffness or different stiffnesses. You can also adapt the ratio of the lengths of the springs 8 or 9 and the spring 10 to a particular application, and this ratio of lengths can be in the range from 0.5: 1 to 3: 1, preferably in the range from 1: 1 to 2: 1.

 The use of retaining shoe 30 provides the following advantages.

 - It is possible to connect in a series row springs with a different ratio between the length and diameter of the spring, and it is always ensured that the end sections of these springs face each other flawlessly and, in addition, slipping or loss of retaining shoes 30 from the corresponding springs is eliminated. Thus, the intermediate insert always acts flawlessly and cannot be destroyed by the springs 8, 10 due to the skew between the corresponding end sections of these springs.

 - When using at least one inner spring, it can be made shorter, since for its compression it should not occupy more than at least part of the total length of the spring 10.

 - Further, the intermediate insert 30 allows the use of internal springs of different lengths and / or stiffnesses. Therefore, it is also possible to provide at least one inner spring inside the spring 10, which may be the same length as the spring 10, or be shorter or longer. For many applications, it may also be advisable that, as shown in FIG. 6, the intermediate insert 130 has an annular support portion 131 from which protrusions 132, 132a extend in both axial or circumferential directions of the device 1. With this embodiment of the intermediate insert 130, the axial connection of the energy accumulator 7 in the axial direction of the solid connection with the intermediate insert 7 can be not only a spring 10, but also a spring 8, so that both springs 8 and 10 in the circumferential direction of the device 1 are firmly connected to each other. With this design, in contrast to the embodiment shown in FIG. 2, the inner spring 9 should be made shorter by at least the length of the protrusion 132a.

 Further, the protrusion 132a according to Fig.6 can be made in such a way that it is consistent with the internal spring 9, so that then at least the spring 9 is connected to the spring 10.

 Further, as shown in Fig. 7, the intermediate insert 230 can also be made in such a way that the eye has a stepped protrusion 232a, with each step having a groove 233, 234a, into which, at least in its partial section, the corresponding end coil of the spring enters 208, 209. With this design, it is further achieved that the inner spring 209 is practically unable to slip relative to the outer spring 208, i.e. the inner spring 209 does not pop out of the outer spring 208. The intermediate insert 230 may, as shown in FIG. 7 by the dotted line, also have a protrusion 232 for the spring 10 of FIG. 2, which is connected to the spring 10 in a manner that reliably eliminates the possibility of loss. When using an inner spring inserted inside the outer spring, the protrusion 232 can also be made in the form of 232a, whereby a second inner spring can be connected to the intermediate insert 230.

 In the embodiment shown in FIG. 8, in which two outer springs 308, 310 with a retaining insert 330 between them are connected in series, each time an inner spring 309, 309a inserted inside the springs 303, 310 is provided, the intermediate insert 330 is suspended only in the inner spring 309, i.e. connected to the inner spring in a manner that reliably eliminates the possibility of loss.

 Thus, a large number of options are possible in relation to the suspension or fixing of the intermediate insert 30, 130, 230, 330 on the springs adjacent to these inserts, and the intermediate insert is connected in a way that eliminates the possibility of loss of at least one of these springs. However, the corresponding intermediate insert may enter a connection with several springs or even with all adjacent springs.

 In the embodiment of FIG. 9, a support shoe 430 connected to a spring 409 has a protrusion 432 with a threaded groove 434 located on its outer surface. The end coils 409a of the spring 409 are wound in such a way that they can be screwed onto the threaded groove 434, and it is advisable to make the end coils 409 with respect to their inner diameter so that they abut against the protrusion 432 with a radial interference, thereby eliminating the unscrewing of the retaining shoe or inserts from the end portion of the spring 409.

 In the illustrated embodiment according to FIG. 2, only two springs or two sets of springs are installed in a series row. However, three or more springs or sets of springs can also be connected in series, and each time, between the adjacent ends of the springs or sets of springs, a support shoe according to the invention can be provided.

 The retaining shoes provided according to the invention with the reliable elimination of the possibility of loss at least at one end of the spring can also be provided at the end sections of the respective springs facing the impact sections 14, 15, 16. So, for example, in figure 2 of the spring 8 and 10 could be performed in one piece, i.e. they would form one spring, and a retaining shoe 30 would be provided at the end 39 of the spring 10. When the springs 8 and 10 were made, it would be entirely possible to provide a retaining shoe according to FIGS. 7, 8 or 9 in the end section 39a of the spring 8. When the springs 8 or 10 are executed, the whole, i.e. when using a through outer spring between the impact areas 14, 15, 16 on these springs, there is no need for retaining shoes or inserts shown in Fig. 30.

 At least one end coil of a coil spring coupled to the support shoe may be longitudinally attached to the penultimate coil by deformation in the direction of the length of the spring 38 and ground. In this regard, reference has already been made to patent DE-OS 4229416. In a preferred embodiment, the end turn made in this way has a smaller inner diameter with respect to the rest of the turns, due to which it can snap into the groove of the corresponding shoe. This embodiment of the end coil of the spring 208a is shown in Fig.7. By means of such a design of the end portion of the spring, it is ensured that when the spring is compressed between it and the retaining shoe, there is a relatively large contact area, so that the force created by compressing the spring can be distributed on the larger bearing surface of the shoe.

 The energy accumulator 507 shown in FIG. 10 differs from the energy accumulator 7 according to FIG. 2 mainly in that a coil spring 509a is inserted inside the coil spring 510. Spring 509a is firmly connected to retaining shoe 530, at least in the circumferential direction, or in the direction of axis 538 of energy accumulator 507. As in FIG. 2, there is an external spring 508 and an internal spring 509 inserted into it, which are connected in series with springs 510, 509a.

 The inner spring 509a has a much higher stiffness than the outer spring 510. The length of the inner spring 509a in the circumferential direction, or in the direction of the axis 538, is also much less than the length of the outer spring 510.

 The length or angular extent of the unstretched stiff spring 509a is selected in such a way that a sufficient twisting angle is ensured softer, i.e. having lower stiffness of the outer spring 510 before the inner spring 509a is compressed.

 As can be seen from the distance between two adjacent turns shown in FIG. 10, the inner spring 509a has a smaller coil lift in the direction of the axis 538 of the energy accumulator 507 than the outer spring 510. In the illustrated embodiment, the spring 509a is made with respect to the spring 510 so that with the mutual twisting of two flywheel masses 2,3 according to FIG. 1, the turns of the inner spring 509a are compressed to the limit before they can be compressed to the limit of the turns of the outer spring 510, so that the overload of the outer spring 510 can be eliminated.

 However, the inner spring 509a can be made with respect to the spring 510 and in a way that is already due to the high stiffness, i.e. the high slope of the characteristics of the internal spring 509a, the torque that occurs with large amplitudes of oscillations, which may be greater than the nominal torque created by the internal combustion engine, is perceived by the internal spring 509a mainly with a spring, due to which the external spring is more sensitive to heat in compressed to the limit state, should perceive only part of this torque. If the inner spring 509a quenches or absorbs the shock torsion load sufficiently, the loading of the outer spring 510 to its limit state may occur or be tolerated.

 In the embodiment shown in FIG. 10, the inner spring 509a may also have a larger coil lift in the direction of the axis 538 of the energy accumulator 507 than the outer spring 510.

 It is advisable to provide that the rise of the turns of the inner spring 509a be directed against the rise of the turns of the outer spring 51. This means that when viewed along the same circumferential direction, i.e. the direction of the axis of the battery anergy 507, the turns of one spring are wound clockwise with a certain step, and the turns of the other spring are wound counterclockwise with a corresponding step.

The torsion angle of both flywheel masses 2, 3, within which both springs 509a and 510 are connected in parallel, can be from 5 to 20 ^o . However, depending on the application, this angle may be larger, we hide in the extreme case, the inner spring 509a may be only slightly shorter than the outer spring 510, as is the case, for example, in figure 2. with respect to the springs 8, 9. However, it is advisable that the inner spring 509a prevents overloading the turns of the outer spring 510 when compressed to the limit of at least one of the springs 509a, 510. The outer spring 510 can have a slope such that it creates between mutually twisting flywheel masses 2, 3, twisting resistance of the order of 0.5-4 Nm / ^o . The torsional resistance created by the spring 509a can be in the range of 20-80 Nm / ^o . However, these values may also be less and more than indicated. It is advisable to give the internal spring 509a rigidity, which between the fly masses 2, 3 creates a twisting resistance of the order of 20-50 Nm / ^o .

 Connected to the spring 510 in series, the spring 508 can have a stiffness that is equal to, less than, or preferably greater than the stiffness of the spring 510. The stiffness of the spring 509 can in turn equal to, greater than or less than the stiffness of the spring 508.

 In the energy accumulator 507 shown in FIG. 10, the coaxially located springs 509a, 510 are connected in series with the coaxially arranged springs 508, 509. However, the principle of operation described in connection with the springs 509a and 510 can be applied to energy accumulators, which consist only of from two coaxially spaced and inserted into each other springs. This means that in FIG. 10, a coil spring 510 would extend along the entire length of the energy accumulator 507, with the inner spring 509a having to be adapted accordingly with respect to its length and spring properties. Therefore, in such an energy storage device, the outer spring would have an angular extension or length corresponding to the sum of the lengths of the springs 510, springs 508 and intermediate insert 530. In this case, the spring 509a must also be made longer.

 In the illustrated examples of execution, only two springs inserted one into another are provided each time. However, for many applications, it may be advisable to have three or even four springs inserted one into the other, which are advisable to fix in the circumferential direction relative to each other, as described previously. Thus, for example, inside the spring 409 of FIG. 9, another spring could be provided that can be mounted on an additional protrusion adjacent to the protrusion 432 of the retaining shoe 430. This additional protrusion can, for example, be made in the same way as the protrusion for the spring 209 according to Fig.7.

 The design according to this invention has the advantage that, as noted earlier, the retaining inserts or shoes of the springs cannot slip out of the ends of the springs on which they are placed, which ensures that the springs interact seamlessly or when the springs are installed in a series row, the springs are perfectly supported against each other . Such slip of the retaining inserts can occur especially when using long springs of a relatively large diameter and with a relatively small slope of the spring characteristics, since, as described in the patents DE-OS 3721711 and DE-OS 372I712. when the rotating device 1, the centrifugal force acting on the springs can become so large that after compression of the springs, for example, under the action of a force shock, they, due to the large friction between the coil of the spring and the sections supporting them, at least can no longer relax on their own, as a result, they have a shorter length compared to a completely relaxed state. Without fixing the retaining shoes according to this invention, they could fall out or slip out of the end portion of the corresponding spring or springs and scroll or turn in the chamber 21 or in the toroidal space 22. Then, when the respective springs are re-compressed or interacted, it will not always be ensured that the protrusion or protrusions intermediate inserts can penetrate into the respective springs or at the respective ends of the springs, as a result of which the destruction of the intermediate inserts can occur.

 The claims set forth in this application are proposals for the wording of which do not claim to receive comprehensive patent protection. The applicant reserves the right to claim patentability of other features disclosed so far only in the description and / or drawings.

 Backlinks given in additional paragraphs of the formula indicate another performance of the subject matter of the main paragraph using the characteristics of this particular paragraph; they should not be understood as a refusal to obtain independent subject protection of additional items with a back link.

 Nevertheless, the subjects of these additional paragraphs also form independent inventions, which are formulated independently of the subjects of the previous additional paragraphs.

 The invention is also not limited to the embodiment as described. Moreover, numerous changes and modifications are possible within the scope of the present invention, especially such variants, elements and combinations and / or materials, which, for example, acquire the character of inventions due to the combination or change of certain features, or elements, or steps of the applied methods described in general an example of execution and in the claims, and due to the combined features lead to a new subject or to a new stage, or a new sequence of the applied method, if they relate to persons manufactured, tested or operated.

Claims (25)

 1. A torsional vibration damper comprising at least two structural elements that are configured to be angularly displaced relative to each other in a certain area to overcome the compression resistance of at least one helical spring, as well as one retaining shoe designed for interaction with the possibility of angular displacement at one of its ends with a coil spring, while each of the mentioned structural elements props up the corresponding end of the coil spring and forms a retaining section for an adjacent end coil of a helical spring, characterized in that in the direction of the longitudinal axis between the retaining shoe and said helical spring for positioning and / or maintaining position, a connection is provided that is made without the possibility of losing the retaining shoe.  2. The torsional vibration damper according to claim 1, characterized in that the retaining shoe has a protrusion that crosses the adjacent end section of the spring in the direction of the longitudinal axis.  3. The torsional vibration damper according to claim 1 or 2, characterized in that the retaining shoe is connected to the coil spring by means of a geometric circuit, eliminating the possibility of losing the retaining shoe.  4. Torsional vibration damper according to one of claims 1 to 3, characterized in that there is a geometric circuit between the retaining shoe and at least the adjacent end of the coil spring.  5. Torsional vibration damper according to one of claims 1 to 4, characterized in that a latch-type connection is provided between the retaining shoe and the coil spring, creating a geometric circuit.  6. Torsional vibration damper according to one of claims 1 to 5, characterized in that there is a connection between the helical spring and the protrusion of the retaining shoe, eliminating the possibility of losing the retaining shoe.  7. The torsional vibration damper according to one of claims 1 to 6, characterized in that the retaining shoe has an annular section designed to support the adjacent end of the coil spring, from which a protrusion extends into the internal cavity of the coil spring, limited by turns so that it is possible holding the retaining shoe in relation to the helical spring, eliminating the possibility of losing the retaining shoe.  8. Torsional vibration damper according to one of claims 1 to 7, characterized in that the free end segment of the spring coil adjacent to the retaining shoe is designed to hold the retaining shoe relative to the coil spring.  9. A torsional vibration damper according to one of claims 5 to 8, characterized in that the retaining shoe has a radial groove designed to enter it with a geometric closure, such as a latch, of at least one coil of a spring.  10. The torsional vibration damper according to claim 9, characterized in that the free end portion of the end coil of the spring radially enters the groove of the retaining shoe adjacent to this end portion of the spring.  11. The torsional vibration damper according to claim 9 or 10, characterized in that, when unclenched, the end coil of the coil spring is adjacent to the retaining shoe, with the exception of the end portion included in the groove of the retaining shoe, and has the same elevation angle as the turns between end turns.  12. A torsional vibration damper according to one of claims 7 to 11, characterized in that the end portion of the corresponding end turn, at least in the unclamped state of the coil spring, is parallel to the retaining pad of the retaining shoe for this coil spring.  13. The torsional vibration damper according to one of claims 7-12, characterized in that the end portion of the end coil of the coil spring adjacent to the retaining shoe is offset relative to the other coils radially in the direction to the longitudinal axis of the coil spring.  14. Torsional vibration damper according to one of claims 1 to 13, characterized in that the energy accumulator is formed by at least one external coil spring and at least one internal coil spring inserted into a cavity bounded by turns of the external coil spring moreover, at least at one end of the energy accumulator, said retaining shoe is mounted, which with an external coil spring for positioning and / or maintaining a position forms a connection that is made without the possibility of losing a retaining shoe.  15. A torsional vibration damper according to one of claims 1 to 13, characterized in that the energy accumulator is formed by at least one external coil spring and at least one internal coil spring inserted into a cavity bounded by turns of the external coil spring moreover, at least at one end of the energy accumulator, said retaining shoe is mounted, which with an internal coil spring for positioning and / or maintaining a position forms a connection that is made without the possibility of loss of retaining of the shoe.  16. The torsional vibration damper according to one of claims 1 to 13, characterized in that the energy accumulator is formed by at least one outer coil spring and at least one inner coil spring inserted into the cavity bounded by the coils of the outer coil spring moreover, at least one end of the energy accumulator has the aforementioned shoe, which with both the outer and the inner coil spring for positioning and / or maintaining the position forms a connection that is made without possible STI loss retaining shoe.  17. Torsional vibration damper according to one of claims 1 to 13, characterized in that the energy accumulator is formed of at least two helical springs placed in series in a row between the interaction areas of the twisted structural elements, and the said end springs are installed between opposite end sections retaining shoe for positioning and / or maintaining a position with respect to at least one of the coil springs without the possibility of losing said retaining shoe.  18. The torsional vibration damper according to claim 17, characterized in that at least one of the two coil springs forms an external spring into which an internal spring is inserted, the length of which is at least part of the length of the external spring.  19. Torsional vibration damper according to one of claims 1 to 18, characterized in that at least one pair of coil springs, which include the outer and inner springs, the inner spring is shorter than the outer spring.  20. Torsional vibration damper according to one of claims 1 to 18, characterized in that at least one pair of coil springs, which include the outer and inner springs, both springs have the same length.  21. The torsional vibration damper according to one of claims 1 to 20, characterized in that at least one of the coil springs forming the energy accumulator in the expanded state has a pre-curved shape.  22. The torsional vibration damper according to one of claims 1 to 21, characterized in that the energy accumulator formed by the coil springs has a large ratio of length to outer diameter.  23. Torsional vibration damper according to one of claims 1 to 22, characterized in that no more than three energy accumulators located on the same diametrical section are provided between mutually twisted structural elements. 24. Torsional vibration damper according to one of claims 1 to 23, characterized in that the energy accumulators are provided between mutually twisted structural elements and are configured to scroll in both directions by an angle of at least 30 ^o .  25. Torsional vibration damper according to one of claims 1 to 23, characterized in that the torsional vibration damper according to the invention is an integral part of a flywheel consisting of several masses or forms such an integral part.

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