Patent Publication Number: US-2017370438-A1

Title: Device for damping vibrations

Description:
The present invention relates to a device for damping vibrations, in particular flexural vibrations and/or torsional vibrations. 
     One area for use of such vibration-damping devices is in the field of sliding roofs for motor vehicles, for example. The document DE 10 2008 064 548 A1 discloses a sliding roof arrangement for a motor vehicle. A frame device of the vehicle roof is designed with two longitudinal frame sections spaced a distance apart from one another, longitudinal guides for a movable vehicle part for a sliding roof cover or a roof liner part, for example, being arranged on these longitudinal frame sections. A drive cable for the vehicle component is mounted, so that it is longitudinally displaceable on each of the longitudinal frame sections. The drive cables are guided by the respective longitudinal guide to a drive device arranged between the two longitudinal guides and is movable by it. A cross member of the drive extends between the two longitudinal frame sections and carries the drive device. The cross member of the drive also carries cable guides for the drive cable between the drive device and the longitudinal frame sections. Furthermore, the cross member of the drive is mounted on the frame device so that it is mechanically coupled and/or vibration is reduced. 
     One object of the present invention is to provide a device for damping flexural vibrations, which can be produced easily and inexpensively and can be used in a flexible manner in various applications. 
     This object is achieved with a device for damping flexural vibrations of the type defined in the introduction, having the features of patent claim  1 . 
     Additional embodiments of the invention are defined in the dependent claims. 
     The inventive device for damping flexural vibrations comprises at least one damping device and at least one retaining device for the damping device. The at least one damping device is connected by means of at least one spring element to the at least one retaining device. The at least one damping device comprises at least one damper mass and at least one spring element. The at least one spring element is arranged and preloaded in such a way that the at least one spring element holds the damper mass in a predetermined position on the retaining device in the resting state of the device. 
     The device is designed for damping flexural vibrations. To do so, the damper mass may oscillate and/or vibrate in both vertical and horizontal directions relative to the at least one retaining device, so that any flexural vibrations and oscillations that occur can be reduced reliably by the inventive apparatus. 
     The at least one spring element holds the at least one damper mass in a predetermined position, such that, for example, a relative movement between the at least one damper mass and the at least one retaining device is made possible. Due to the at least one spring element, for example, a predetermined distance may be set between the at least one damper mass and the at least one retaining device, this distance being necessary for a relative vibration-damping movement between the at least one damper mass and the at least one retaining device with preloading of the at least one spring element. Vibrations with a predetermined frequency and/or amplitude can therefore be reduced. 
     The at least one spring element may have a predetermined bias. The predetermined bias with which the at least one spring element is stretched between the at least one damper mass and the at least one retaining device may be, for example, a tensile stress caused by a tensile force. The at least one spring element can thus be stretched between the at least one retaining device and the at least one damper mass at a predetermined tensile force. However, the predetermined preload on the spring element may also be a compressive stress, which is imposed on the at least one spring element, for example, in mounting the at least one damping device on the at least one retaining device. The device can be adjusted by the preload of the at least one spring element to a predetermined frequency range of the vibrations and/or oscillations to be reduced. Furthermore, the maximum allowed amplitude of the at least one damper mass can be determined and defined relative to the at least one retaining device on the basis of the preload. 
     The at least one damping device may be accommodated in the at least one retaining device. The at least one retaining device may be designed in the form of a housing. The at least one retaining device is preferably designed so that the damper mass for damping the flexural vibration sin a predetermined extent can oscillate freely with compression or stretching of the at least one spring element in and/or on the at least one retaining device. The at least one retaining device may also serve as a stop for the at least one damper mass in order to limit the deflection and/or amplitude of the damper mass. In this way the at least one spring element is protected from an overload. 
     According to a further embodiment, the at least one retaining device may be designed of at least two components. However, the retaining device may be comprised of three or more components. The at least one two components of the at least one retaining device may be connectable for receiving the at least one damping device. This forms a closed system which can be used in a flexible manner in various fields of applications without external influences being able to affect the function of the device for damping flexural vibrations. For example, the device may be embedded in a mounting foam or the like without the foam being able to influence the function of the device and/or the mobility of the damper mass. Furthermore, the device is protected from environmental influences and the like by the retaining device. The two components of the at least one retaining device may be connected to one another by means of click connections, catch connections, screw connections or adhesive connections. The at least one spring element may be vulcanized separately from the at least one retaining device. A modular design is achieved in this way, wherein the at least one spring element and the at least one damper mass are connected to one another and are then coupled to the at least one retaining device. The at least one damper mass may also be vulcanized together with the at least one spring element. 
     According to another embodiment, the at least one retaining device has at least one retaining site, which is used for coupling to the at least one spring element. The at least one retaining site of the at least one retaining device may be designed, for example, so that the at least one spring element is secured on the retaining site for coupling to the at least one retaining device. In the case of a retaining device embodied as two or more parts, the at least one retaining site may be formed between two or more components of the at least one retaining device. In this context, the at least one spring element may also be designed with at least one fastening element. The at least one fastening element may be accommodated in the at least one retaining site of the at least one retaining device. Starting from its fastening element and/or the retaining site, the at least one spring element extends in the direction of the at least one damper mass and is connected to it. Accordingly, the at least one spring element may be in contact with the at least one retaining device only in the area of its at least one fastening element and may then extend freely in the direction of the at least one damper mass. In this way, the vibration capability of the at least one damper mass is ensured on the at least one retaining device and/or in the at least one retaining device. 
     According to one embodiment, the at least one fastening element of the at least one spring element may be designed to be complementary to the at least one retaining site on the at least one retaining device. The shape of the at least one fastening element may thus be adapted to the shape of the at least one retaining site. If the at least one retaining device is comprised of two components, then the at least one retaining site is formed by the two components of the retaining device. In its cross section, the retaining site formed by the two components of the retaining device may then be designed to be complementary to the shape of the at least one fastening element. The at least one fastening element may be designed with a triangular round or oval cross section. However, other types of cross-sectional shapes are also conceivable as long as a coupling is achieved between the at least one spring element and the at least one retaining device. 
     The at least one damper mass may be designed in multiple parts. If the at least one damper mass is designed in two parts, then the at least one spring element may be accommodated in at least some sections between the two parts of the at least one damper mass and connected to the damper mass in this way. In this case, the at least one spring element may be designed with a fastening element, which is to designed for accommodation between the two parts of the damper mass. The parts of the at least one damper mass may be provided with recesses, which may form a receptacle for the at least one fastening element of the at least one spring element. The at least one fastening element of the at least one spring element and the receptacle in the damper mass may be designed to be complementary. 
     Accordingly, the at least one spring element may be designed with a fastening element adapted to the retaining site of the retaining device and one additional fastening element adapted to the receptacle of the at least one damper mass. 
     The damper mass may be designed to be cylindrical or rod shaped. The damper mass as well as the entire device may be adapted in their shape to their site of use and/or their area of use and may have a corresponding shape, depending on the area of use. 
     According to one embodiment, the at least one spring element may have at least one reinforcement. The at least one reinforcement may be a textile reinforcement and/or thread reinforcement in particular. The spring element can absorb higher tensile forces in particular due to the reinforcement. The at least one spring element may preferably be made of rubber or an elastomer. The tensile load on the at least one spring element may be relieved by the at least one reinforcement, which thus contributes to the lifetime of the spring element. The at least one reinforcement may be provided at the surface of the at least one spring element. The at least one reinforcement may also extend through a central region of the spring element. The at least one reinforcement may be provided on individual surfaces or all surfaces of the at least one spring element. The at least one reinforcement may preferably be provided on opposing surfaces of the at least one spring element. 
     According to one embodiment, the at least one retaining device may have ribs. The ribs may serve to secure the damper mass in the event of failure of the at least one spring element. The ribs may extend in the retaining device in such a way that the cross section of the retaining device is reduced in a certain area. The ribs may extend in an interior and/or receiving section for the damper mass formed by the retaining device and thereby reduce its cross section. In the event of failure and breakage, for example, of the at least one spring element during use, then the damper mass can be secured by the ribs in the retaining device. Therefore, the noise generated by an uncontrollable damper mass in this state can be prevented. 
     The at least one damping device may be connected to the at least one retaining device in a pivotably movable manner. For example, a type of hinge may be provided, connecting the at least one damper mass of the at least one damping device pivotably to the at least one retaining device. The at least one spring element in this case serves to reduce the pivoting movements of the at least one damper mass. The at least one damping device may also be connected to the at least one retaining device by means of the at least one spring element in addition to the pivotably movable connection. 
     The at least one retaining device may also have a fluid for damping the movements of the at least one damper mass. The at least one retaining device may thus be filled with a damping fluid, which can reduce the movements of the at least one damper mass required for the vibration damping effect. The damping of the moving damper mass can be influenced in a targeted manner by the damping fluid. For example, the vibration damper and/or the damper mass together with the apring element assigned to it can be adapted to predetermined excitation amplitudes or excitation frequencies by means of a damping fluid. 
     The at least one retaining device may have at least one throttle element. The at least one throttle element can throttle a fluid flow occurring due to movement of the at least one damper mass. In one simple embodiment, the at least one retaining device may have throttle gaps predetermined for this purpose, reducing the rate of the fluid flow occurring due to the movement of the at least one damper mass. Therefore, the movement of the damper mass is in turn reduced to a predetermined extent and thus the damping behavior of the damper mass is influenced in a targeted manner. 
     The at least one retaining device may be designed in the form of a ring. The at least one retaining device may be designed with a rectangular cross section. The at least one annular retaining device may have at least one inside circumferential wall according to one embodiment and at least one outside circumferential wall. The at least one retaining device may be designed in two or more parts. A first component may be designed, for example, with a U-shaped cross section. The first component may thus have two longitudinal legs in cross section and a transverse leg connecting the longitudinal legs. In this case, the second component may be a closure element. The closure element may be designed to be disk-shaped, for example. 
     The at least one damping device may be connected to the at least one inside circumferential wall. The at least one damping device may extend around an exterior radial surface of the at least one inside circumferential wall, for example. The at least one damping device may also be in contact with the radial outer surface of the at least one inside circumferential wall in at least some sections. 
     According to one embodiment, the at least one spring element of the at least one damping device may extend between the at least one inside circumferential wall and the at least one damper mass. The at least one spring element may also establish a connection between the at least one inside circumferential wall and the at least one damper mass. 
     According to one embodiment, the at least one spring element may be fixedly connected to the at least one damper mass before being mounted on the at least one retaining device. Following the connection of at least one spring element to the at least one damper mass, the damping device formed by the spring element and the damper mass may be connected to the retaining device. Due to the connection of the damping device to the at least one retaining device and/or to its at least one inside circumferential wall, the at least one spring element may be acted upon with a predetermined bias. 
     According to one embodiment of the invention, the at least one retaining device may be designed in such a way that a predetermined gap is established between the at least one damper mass and the at least one retaining device. The predetermined gap may be formed, for example, between a side surface of the at least one damper mass and a surface of the at least one retaining device which is opposite this side surface of the at least one damper mass. The at least one retaining device may be designed so that the predetermined gap has a predetermined shape in the cross section of the retaining device. In particular, the shape of the predetermined gap is based on the interaction with the at least one damper mass. The damping of the device can be adjusted, based on the predetermined gap. A variable damping, in particular a progressive damping of the device can be adjusted by means of the predetermined gap. The predetermined gap may be designed so that the at least one damper mass in the at least one retaining device can be decelerated by fluid cushions, for example, air cushions. The at least one damper mass may be in contact with a surface of the at least one retaining device at its side surfaces. The receiving section may therefore be subdivided into two chambers. The air cushions in the chambers may serve to decelerate the damper mass and limit the amplitude of the vibrations. The at least one damper mass may be in contact with the at least one retaining device on its side surface opposite the gap. The at least one damper mass may be in contact with at least one surface of the retaining device and guided there. Therefore, a guided sliding movement between the at least one damper mass and the retaining device can be achieved. The at least one damper mass may be guided by means of at least one guide web on the at least one retaining device. 
     The at least one retaining device may be designed so that the predetermined gap changes with the deflection of the at least one damper mass relative to the at least one retaining device. In other words, the predetermined air gap, which is established between the at least one retaining device and the at least one damper mass, can change, i.e., increase or decrease, as a function of the deflection of the at least one damper mass. For example, the dimension of the predetermined gap may change, i.e., increase or decrease, in a transverse direction relative to the direction of vibration of the at least one damper mass. 
     The predetermined gap may be the largest in at least one location in the resting state of the device. The at least one retaining device may be designed so that the predetermined gap decreases with an increase in the vibration amplitude of the at least one damper mass. The dimension of the predetermined gap can be reduced with an increase in the amplitude of the damper mass. The damper mass can be decelerated in this way by the fluid cushions, for example, air cushions, formed in the at least one retaining device. A progressive damping of the damper mass can therefore be supplied, and striking of the damper mass against the at least one retaining device can be effectively prevented. In other words, if the damper mass is in contact at one of its side surfaces with the at least one retaining device, and if the gap decreases in the direction of vibration of the damper mass, then with an increase in the vibration amplitude, less air can flow out of one chamber into the other chamber in the at least one retaining device. The damper mass may thus be decelerated by the air cushion in the chamber, so that a variable damping and in particular a progressive damping can be achieved. 
     The at least one spring element may extend between at least two retaining sites. 
     The at least one spring element may extend through an opening in the at least one damper mass. The at least one spring element may also be connected to the at least one damper mass. The at least one spring element may be connected by at least one spring web to the at least one damper mass. The at least one spring web may be situated in the at least one opening in the resting state of the device. 
     The at least one spring element may have a section, which forms at least one stop buffer. The at least one stop buffer may reduce the impact of the at least one damper mass on the at least one retaining device if adequate damping cannot be achieved by means of the fluid cushion in one of the chambers. The at least one stop buffer may be facing at least one of the retaining sites of the at least one spring element. The at least one stop buffer may be provided on an end area of the at least one opening in the at least one damper mass. If the at least one spring element is connected by at least one bushing to the at least one damper mass then the at least one stop buffer may be provided on at least one of the end faces of the at least one bushing. 
    
    
     
       Exemplary embodiments of the invention are described below with reference to the accompanying figures, in which: 
         FIGS. 1 and 2  show perspective views of the device according to a first embodiment of the invention; 
         FIG. 3  shows a top view of the device according to the first embodiment of the invention; 
         FIG. 4  shows a side view along the sectional line III-III in  FIG. 3 ; 
         FIG. 5  shows a side view of the device according to the first embodiment of the invention; 
         FIG. 6  shows a sectional view along the sectional line V-V in  FIG. 5 ; 
         FIGS. 7 and 8  show perspective views of the device according to a second embodiment of the invention; 
         FIG. 9  shows a top view of the device according to the second embodiment of the invention; 
         FIG. 10  shows a sectional view along the sectional line IX-IX in  FIG. 9 ; 
         FIG. 11  shows a detail view of the detail X in  FIG. 10 ; 
         FIG. 12  shows a side view of the device according to the second embodiment of the invention; 
         FIG. 13  shows a sectional view along the sectional line XII-XII in  FIG. 12 ; 
         FIGS. 14 and 15  show perspective views of the device according to a third embodiment of the invention; 
         FIG. 16  shows a top view of the device according to the third embodiment of the invention; 
         FIG. 17  shows a sectional view along the sectional line XVI-XVI in  FIG. 16 ; 
         FIG. 18  shows a side view of the device according to the third embodiment of the invention; 
         FIG. 19  shows a sectional view along the sectional line XVIII-XVIII in  FIG. 18 ; 
         FIGS. 20 and 21  show perspective views of the device according to a fourth embodiment of the invention; 
         FIG. 22  shows a top view of the device according to the fourth embodiment of the invention; 
         FIG. 23  shows a sectional view along the sectional line XXIIa-XXIIa in  FIG. 22 ; 
         FIG. 24  shows a sectional view along the sectional line XXIVb-XXIVb in  FIG. 22 ; 
         FIG. 25  shows a side view of the device according to the fourth embodiment of the invention; 
         FIG. 26  shows a sectional view along the sectional line XXV-XXV in  FIG. 25 ; 
         FIGS. 27 and 28  show perspective views of the device according to a fifth embodiment of the invention; 
         FIG. 29  shows a top view of the device according to the fifth embodiment of the invention; 
         FIG. 30  shows a sectional view along the sectional line XXIX-XXIX in  FIG. 29 ; 
         FIG. 31  shows a side view of the device according to a fifth embodiment of the invention; 
         FIG. 32  shows a sectional view along the sectional line XXXI-XXXI in  FIG. 31 ; 
         FIG. 33  show a perspective view of the device according to a sixth embodiment of the invention; 
         FIGS. 34 to 36  show additional views of the device according to the sixth embodiment of the invention; 
         FIG. 37  show a perspective view of the device according to a seventh embodiment of the invention; 
         FIGS. 38 to 40  show additional views of the device according to the seventh embodiment of the invention; 
         FIG. 41  show a perspective view of the device according to an eighth embodiment of the invention; 
         FIGS. 42 to 44  show additional views of the device according to the eighth embodiment of the invention; 
         FIG. 45  show a perspective view of the device according to a ninth embodiment of the invention; 
         FIGS. 46 to 48  show additional views of the device according to the ninth embodiment of the invention; 
         FIG. 49  show a perspective view of the device according to a tenth embodiment of the invention; 
         FIGS. 50 to 52  show additional views of the device according to the tenth embodiment of the invention; 
         FIGS. 53 and 54  show perspective views of the device according to an eleventh embodiment of the invention; 
         FIGS. 55 and 56  show additional views of the device according to the eleventh embodiment of the invention; 
         FIGS. 57 to 59  show views of the device according to a twelfth embodiment of the invention; and 
         FIGS. 60 to 62  show views of the device according to a thirteenth embodiment of the invention. 
     
    
    
       FIG. 1  shows a perspective view of the device for damping flexural vibrations labeled with  10  in general. 
     The device  10  comprises a retaining device  12  which is designed in the form of a housing. The retaining device, i.e., the housing  12  is comprised of two components  14  and  16 . The retaining device  12 , i.e., the housing has two retaining sites  18  and  20  which serve to connect with a spring element ( FIG. 2 ) which is not shown in  FIG. 1 . The two halves, i.e., parts  14  and  16  of the housing  12  may be connected to one another by means of a snap connection, a screw connection or an adhesive connection. The device  10  is elongated and is desired to accommodate a damping device (not shown in  FIG. 1 ). Between the retaining sites  18  to  20  and the receiving section  22  for the damping device ( FIG. 2 ) reinforcing ribs  24  can be seen, serving to reinforce the housing components, i.e., the housing halves  14  and  16 . 
       FIG. 2  shows a perspective view of the device  10  without the housing halves  14 . 
     The damping device DE of the device  10  comprises a damper mass  26  and spring  2   o  elements  28  and  30 . The damper mass  26  is accommodated in the receiving section  22  of the housing component  16 . The damper mass  26  is connected to the housing component  16  and/or to the retaining sites  18  and  20  of the housing component  16  by means of the spring elements  28  and  30 . The spring elements each have a spring section  32  and  34  which develops into a fastening section  36 ,  38  and also serves to connect to the damper mass  26 . The fastening sections  36 ,  38  and/or the fastening elements  36 ,  38  are accommodated in the retaining sites  18 ,  20  and serve to couple the spring elements  28 ,  30  to the retaining sites  18 ,  20  of the housing halves  16 . 
     The fastening elements  36  and  38  are designed to be complementary to the retaining sites  18  and  20 . 
       FIG. 3  shows a top view of the device  10  in which the housing halves  14  can be seen. The housing halves  14  and/or the housing  12  is/are provided with retaining sites  18 ,  20 . The reinforcing ribs  24  for reinforcing the housing  12  extend between the receiving section  22  and the retaining sites  18  and  20 . 
       FIG. 4  shows a sectional view along the sectional line IV-IV in  FIG. 4 . 
     In the assembled state, the housing halves  14  and  16  form the receiving section  22  for the damper mass  26  between them. The damper mass  26  is coupled to the housing  12  by means of the spring elements  28  and  30 . To do so, the spring elements  28  and  30  have fastening elements  36  and  38  which are accommodated in the retaining sites  18  and  20  in the housing  12 . The retaining sites  18  and  20  and the fastening elements  36  and  38  are designed to be complementary to one another. 
     The fastening elements  36 ,  38  are designed to be essentially triangular in cross section and can be accommodated in the suitably designed retaining sites  18  and  20 . The fastening elements  36  and  38  can be secured between the housing parts  14  and  16 . The retaining sites  18  and  20  in the assembled state of the housing  12  form a receptacle for the fastening elements  36  and  38 , the receptacle being designed with a triangular cross section in the assembled state of the housing  12 . Starting from the fastening elements  36  and  38 , the spring elements  28 ,  30  extend with their elongated spring sections  32  and  34  in the direction of the damper mass  26 . The spring elements  28  and  30  are produced from an elastomer, in which the damper mass  26  can be embedded in at least some sections or completely. 
     The damper mass  26  can oscillate in the receiving section  22  for damping vibrations and oscillations in the vertical and horizontal directions, i.e., in the X and Y directions. The housing and/or the housing parts  14  and  16  become(s) narrower in the direction of the retaining sites  18  and  20 . Accordingly, the damper mass  26  can oscillate in the X direction until the damper mass  26  comes to a stop on the tapering sections  40  and  42  against one or, alternately, both of the walls of the housing  12 . In the Y direction, the damper mass  26  can oscillate until it comes to a stop on one of the walls  44  and  46  of the housing parts  14  and  16 , which run parallel to the longitudinal axis of the housing  12 . Thus a maximum allowed amplitude of the damper mass  26  is secured by means of the housing  12 . In this way, overloading of the spring elements  28 ,  30  can be prevented. Depending on the field of use, the housing  12  may be made of aluminum, plastic or steel. 
     By assembling the housing parts  14  and  16 , the fastening elements  36 ,  38  of the spring elements  28 ,  30  are secured in the retaining sites  18  and  20  and are coupled to the housing  12  in this way. 
       FIG. 5  shows a side view of the device  10 . 
     The housing  12  of the device  10  is comprised of the housing parts  14  and  16 , which, in the assembled state, form a receiving area  22  and retaining sites  18  and  20  for the spring elements. The spring elements  28  and  30  as well as the damper mass  26  are accommodated completely in the housing  12 . 
       FIG. 6  shows a sectional view along the sectional line V-V in  FIG. 5 . 
     The damper mass  26  is embedded in the elastomer used to produce the spring elements  28  and  30 . The fastening elements  36 ,  38  couple the spring elements  28  and  30  to the housing  12  and/or to the housing part  16  in  FIG. 6 . The elongated spring section  32 ,  34  of the spring elements  28 ,  30  extends between the fastening elements  36  and  38  and the damper mass  26 . The damper mass may also oscillate in Z direction to a limited extent until its deflection is limited by one of the side walls  48 ,  50  of the housing part  16 . The fastening elements  36 ,  38  extend in the Z direction over the entire cross section of the housing part  16  and reduce their cross section in the direction of the spring section  32 ,  34 . 
     Additional embodiments of the invention are described below. The same reference numerals are used for similar features or those having the same effect but with an additional number added in front. 
       FIG. 7  shows a perspective view of the device  110 . 
     The device  110  corresponds in its design largely to the device  10  described with reference to  FIGS. 1 to 6  according to the first embodiment of the invention. 
     To avoid repetition, in this context reference is made only to the differences between the embodiments described in detail with reference to  FIGS. 1 to 6  and the embodiment according to  FIG. 7 through 13 . 
       FIG. 8  shows a perspective view of the device  110  without the housing part  114 . 
       FIG. 9  shows a top view of the device  110 . 
       FIG. 10  shows a sectional view along the sectional line IX-IX in  FIG. 9 . 
       FIG. 10  shows the housing  112  with its housing halves  114  and  116 . The housing halves  114  and  116  form the retaining sites  118  and  120  for the fastening elements  136  and  138  of the spring elements  128  and  130  between them. The elongated spring sections  132  and  134  connect the fastening elements  136 ,  138  to the damper mass  126 . The spring elements  128  and  130  are in turn made of an elastomer in which the elongated or rod-shaped damper mass  126  is also embedded. Furthermore, a reinforcement  152  and  154  is embedded in the elastomer. The reinforcement  152  and  154  extends in sections in the area of the fastening elements  136 ,  138  and the spring sections  132  and  134  and forms a surface of the spring elements  128  and  130 . The reinforcement  152  and  154  serves to absorb tensile forces acting on the spring elements  128  and  130  during operation of the device  110 . The reinforcement  152 ,  154  should accordingly relieve the load on the spring elements  128  and  130  during tensile loading, which contributes to the lifetime of the spring elements  128  and  130 . If the damper mass  126  oscillates relative to the housing  112 , the spring elements  128 ,  130  are loaded by tension and pressure in alternation. Under tensile loads on the spring elements  128  or  130 , the load of the elastomer of the spring elements  128  and  130  can be reduced by the reinforcement  152  and/or  154 . 
       FIG. 11  shows a detail view of the detail X in  FIG. 10 . 
       FIG. 11  shows the reinforcement  154  which extends in sections to the outside surfaces of the spring section  134  and of the fastening element  138 . The reinforcement  154  runs further in the direction of the damper mass  126  until the elastomer develops into the section running parallel to the housing wall  144  on the damper mass  126 . Accordingly, the reinforcement  154  runs in the shape of a trough along the elastomer of the spring element  130  in the area of the fastening element  138  and the spring section  134 . The reinforcement may be in particular a thread reinforcement and/or textile reinforcement. 
       FIG. 12  shows a side view of the device  110 . 
       FIG. 13  shows a sectional view of the device  110  along the sectional line XII-XII in  FIG. 12 . 
       FIG. 14  shows a perspective view of the device  210  according to a third embodiment of the invention. 
     The housing  212  of the device  210  is designed to be identical to the housings of the two embodiments described above. 
       FIG. 15  shows the device  210  in a perspective view without the housing part  214 . 
     The damper mass  226  according to this embodiment is designed in two parts. The parts  226   1  and  226   2  are connected to one another by means of screws  256 . The parts  226   1  and  226   2  of the damper mass  226  form receptacles  258  and  260  between them for the spring elements  228  and  230 . For accommodation in the receptacles  258 ,  260 , the spring elements  228 ,  230  are provided with fastening elements  262  and  264  which are designed to be complementary to the cross section of the receptacles  258 ,  260 . The receptacles  258  and  260  are designed with a cross section in the form of a 90° rotated T. The fastening elements  262  and  264  are designed accordingly in the form of a 90° rotated T and are secured in the receptacles  258 ,  260  by means of the screws  256 . 
       FIG. 16  shows a top view of the device  210 . 
       FIG. 17  shows a sectional view along the sectional line XVI-XVI in  FIG. 16 . 
       FIG. 16  shows the screws  256 , which are used for connecting the damper mass parts  2261  and  2262  to one another. 
     Between them, the damper mass parts  226   1  and  226   2  form receptacles  258 ,  260  for the fastening elements  262  and  264  of the spring elements  228  and  230 . 
     According this embodiment, the damper mass  226  is not enclosed completely in an elastomer. 
     The fastening elements  262  and  264  are designed in the form of a 90° rotated T and are accommodated in the receptacles  258  and  260 . However, the fastening elements  262  and  264  may also have other shapes, as long as they are accommodated in their shape in the receptacles  258  and  260  in the damper mass  226  and can ensure a secure connection to the damper mass  226 . The spring elements  228 ,  230  can be produced separately and/or vulcanized separately and then connected to the damper mass  226 . The damper mass  226  may be inserted together with the spring elements  228  and  230  into one of the housing halves  214 ,  216 . The fastening elements  236 ,  238  are secured in the holding sites  218 ,  220  of the housing  212  and are thus coupled to the housing  212 . 
       FIG. 18  shows a side view of the device  210 . 
       FIG. 19  shows a sectional view along the sectional line XVIII-XVIII in  FIG. 18 . 
       FIG. 19  shows that the damper mass  226  is not embedded completely in the elastomer used to produce the spring elements  228 ,  230 . Instead the spring elements  228 ,  230  and/or their fastening elements  262 ,  264  are accommodated in the receptacles  258 ,  260  in the damper mass  226 . 
       FIGS. 20 and 21  show perspective views of a device  310  according to a fourth embodiment of the invention. 
     The fourth embodiment according to  FIGS. 20 to 26  corresponds mostly to the embodiment described with reference to  FIGS. 1 to 6 . 
       FIG. 22  shows a top view of the device  310 . 
       FIG. 23  shows a sectional view along the sectional line XXIIa-XXIIa in  FIG. 22 . 
       FIG. 23  shows the housing  312 , the damper mass  326  and the spring elements  328  and  330 . The spring elements  328  and  330  couple the damper mass  326  to the housing  312  by means of their fastening elements  336  and  338 . 
     Ribs  366  which serve to secure the damper mass in the event of failure of the one or both spring elements  328  and  330  can be seen in the housing half  316 . For example, if one of the spring elements  328 ,  330  happens to fail, the damper mass can be secured in the housing  312  by means of the ribs  366 . This method of securing the damper mass  326  in the housing  316  prevents the damper mass from being able to move freely, i.e., uncontrollably, in the housing  312  and thereby possibly resulting in an increased noise emission. 
       FIG. 24  chows a sectional view along the sectional line XXIIb-XXIIb in  FIG. 22 . 
       FIG. 24  shows the ribs  366 , which taper on both side walls  348  and  350  of the housing  316 , narrowing the cross section of the receiving section  322  in the direction of the bottom  367  of the housing part  316 . The ribs  366  extend obliquely in the direction of the bottom  367 . The ribs  366  can secure the damper mass  326  in the housing  312  if the damper mass  326  is freely movable in the housing  312  after failure of one of the spring elements  328 ,  330 . The ribs  366  may also be designed in a conical shape. 
       FIG. 25  shows a side view of the device  310 . 
       FIG. 26  shows a sectional view along the sectional line XXV-XXV in  FIG. 25 . 
       FIG. 26  shows the ribs  366  on the side walls  348  and  350 , the ribs being capable of securing the damper mass  326  in the housing  312  and/or in the housing part  316 . 
       FIG. 27  shows a perspective view of a device  410  according to a fifth embodiment of the invention. 
     The device  410  is designed to be designed to be round, i.e., circular in contrast with the embodiments described above. 
     The housing  412  is comprised of two housing parts  414  and  416 . The housing  412  in turn has a retaining site  318  which extends around the receiving section  422  for the damper mass (not shown in  FIG. 27 ) in the form of a ring. Reinforcing ribs  424  for the housing  412  are provided between the retaining site  418  and the retaining section  422 . 
       FIG. 28  shows a perspective view of the device  410  without the housing part  416 . The device  410  has three spring elements  428 ,  430  and  468 . The spring elements  428 ,  430  and  468  serve to couple the damper mass  426  to the housing  412 . The retaining site  418  extends in a circular arrangement around the receiving section  422 . The retaining site  418  receives the fastening elements  430 ,  432  and  470  of the spring elements  428 ,  430  and  468 . The damper mass  426  is designed in a cylindrical shape. The spring elements  428 ,  430 ,  468  are offset by 120° from one another on the circumference of the damper mass  426 . The fastening elements  436 ,  438  and  470  according to this embodiment are again designed with a triangular cross section. 
     The spring elements  428 ,  430  and  468  each have a spring section  432 ,  434  and  472 , connecting the fastening elements  432 ,  434  and  470  to the damper mass  426 . 
       FIG. 29  shows a top view of the device  410  showing its round, i.e., circular shape. 
       FIG. 30  shows a sectional view along the sectional line XXIX-XXIX in  FIG. 29 . 
     The housing  412  is composed of two housing parts  414  and  416 . The damper mass  426  is coupled to the housing  412  by the spring elements  428 ,  430  and  468 . To do so, the spring elements, i.e., the spring element  430  in  FIG. 30  have fastening elements  434 . The housing parts  414  and  416  form a retaining site  418  in the assembled state, designed with a rectangular cross section and extending in a ring shape around the damper mass  426 . The retaining site  418  is designed to be complementary to the triangular cross section of the fastening elements  432 ,  434  and  470 . The damper mass  426  is completely embedded in the elastomer used to produce the spring elements  428 ,  430  and  468 . 
       FIG. 31  shows a side view of the device  410  showing the two housing halves  414 ,  416  of the housing  412 . 
       FIG. 32  shows a sectional view along the sectional line XXXI-XXXI in  FIG. 31 . 
     The spring elements are offset by 120° from one another on the circumference of the cylindrical damper mass  426 . Starting from the damper mass  426 , the spring elements  428 ,  430  and  468  extend with their spring sections  432 ,  434  and  472  in the direction of the retaining site  418 . The fastening elements  436 ,  438  and  470  of the spring elements  428 ,  430  and  468  are accommodated in the retaining site  418 . 
       FIG. 33  shows a perspective view of a device  510  according to a sixth embodiment of the invention. 
     The device  510  comprises a retaining device  512 , which is designed in the form of a housing. The retaining device  512  is comprised of two housing parts  514  (see  FIG. 34 ) and  516 . The retaining device  512  comprises four retaining sites  518 ,  520 ,  574  and  576 . The retaining sites  518 ,  520 ,  574 ,  576  serve to connect with a spring element; of those shown in  FIG. 33 , only the spring elements  528  and  578  can be discerned. The spring elements  528  and  578  each have a spring section  532  and  580 , which develops into a fastening section  536  and  582 . The spring sections  532  and  580  also serve to connect with the damper mass  526 . The fastening sections and/or fastening elements  536  and  582  are accommodated in the retaining sites  518  and  574 , coupling the spring elements  528 ,  578  to the retaining sites  518 ,  574  of the housing halves  516 . The spring elements  528  and  578  are put under tensile load and/or shearing according to this embodiment. 
       FIG. 34  shows a top view of the device  510 . 
     The retaining device  512  has a receiving section  522  for the damper mass  526  in which the damper mass can oscillate in vertical and horizontal directions, i.e., in the X and Y directions for damping vibrations and oscillations. 
       FIG. 34  shows a top view of the device  510 , illustrating the housing parts  514  and  516  of the retaining device  512 . The housing parts  514  and  516  have the retaining sites  518  and  574 . 
       FIG. 35  shows a sectional view along the sectional line XXXV-XXXV in  FIG. 34 . 
     The retaining device  512  has the receiving section  522  in which the damper mass  526  and also in some sections the spring elements  578  and  584  are accommodated. 
     The spring elements  578  and  584  each have a spring section  580 ,  586  and a fastening element  582 ,  588  which are accommodated in the retaining sites  574  and  576 . The damper mass  526  is surrounded completely by the material used for the spring elements  578  and  584 , for example, an elastomer. 
       FIG. 36  shows a sectional view along the sectional line XXXVI-XXXVI in  FIG. 34 . 
       FIG. 36  shows the four spring elements  528 ,  530 ,  578  and  584 . The spring elements  528 ,  530 ,  578  and  584  each have a spring section  532 ,  534 ,  580 ,  586  and a fastening section  536 ,  538 ,  582  and  588 , which are accommodated in the retaining sites  518 ,  520 ,  574  and  576  of the housing part  514 . 
     The spring elements  528 ,  530 ,  578  and  584  each extend between the walls  544  and  546  and the surfaces  590  and  592  of the damper mass  526  that are opposite these walls  544 ,  546 . The walls  544  and  546  extend essentially parallel to the surfaces  590 ,  592  of the damper mass  526  in the resting state of the device  510 . The walls  544 ,  546  and the surfaces  590 ,  592  run essentially in the X direction in the resting state of the device  510  whereas the spring elements  528 ,  530 ,  578  and  584  extend in the Z direction. 
       FIG. 37  shows a perspective view of a device  610  according to a seventh embodiment. 
     The device  610  comprises a retaining device  612 , only the housing part  616  of which is discernible in  FIG. 37 . The damper mass  626  is connected by the spring elements  628  and  630  to the retaining sites  618 ,  620  of the housing part  616 . To do so, the fastening elements  636  and  638  of the spring elements  626  and  630  are accommodated in the retaining sites  618 ,  620 . Between the damper mass  626  and the fastening elements  636  and  638 , the spring sections  632  and  634  of the spring elements  628 ,  630  extend. 
       FIG. 38  shows a front view of the device  610 . 
     The retaining device  612  comprises two housing parts  614  which have the retaining sites  618 ,  620 . 
       FIG. 39  shows a sectional view along the sectional line XXXIX-XXXIX in  FIG. 38 . 
     The spring elements  630  and  678  are accommodated in the retaining sites  620  and  674  of the housing parts  614  and  616 . The retaining sites  614  and  616  form a receiving section  622  between them for the damper mass  626 . The spring elements  630 ,  678  connect the damper mass  626  to the housing parts  614 ,  616 . The spring elements  630 ,  678  are subjected to a tensile load during the operation of the device  610 . 
       FIG. 40  shows a sectional view along the sectional line XL-XL in  FIG. 38 . 
       FIG. 40  shows the four spring elements  628 ,  630 ,  678  and  684 , which connect the housing parts  614 ,  616  to the damper mass  626 . 
     The spring elements  628 ,  630 ,  678  and  684  are accommodated with their fastening sections  636 ,  638 ,  682  and  688  in the retaining sites  618 ,  620 ,  674  and  676 . 
     The spring elements  628 ,  630 ,  678  and  684  according to this embodiment extend in the Y direction. The areas  690 ,  692  of the damper mass are opposite the surfaces  648 ,  650  of the housing parts  614 ,  616 . The walls  648  and the surfaces  690 ,  692  are run in the X direction. 
       FIG. 41  shows a perspective view of the device  710  according to an eighth embodiment of the invention. 
     The device  710  comprises a retaining device  712  of which only the housing half  716  is shown. 
     The damper mass  726  is accommodated in the retaining device  712 . The spring elements  728  and  730  extend between the retaining device  712  and/or the housing part  716  and the damper mass  726 . The device  710  also comprises a type of hinge S by means of which the damper mass  726  is connected to the retaining device  712 . The hinges S are formed by a bearing journal  794  and a bearing section  796  on the damper mass  726 . The bearing journal  794  is accommodated in an opening O in the bearing section  796  and is supported on a bearing  798  of the housing part  716 . 
       FIG. 42  shows a front view of the device  710 , showing the housing parts  714 ,  716  of the retaining device  712  with their retaining sites  718 ,  720 . 
       FIG. 43  shows a sectional view along the sectional line XLIII-XLIII in  FIG. 42 . 
       FIG. 43  shows the hinge S which is formed by the bearing journal  794  and a bearing section  796  of the damper mass  726 . The bearing journal  794  is accommodated in an opening O of the bearing section  796 . The housing parts  714 ,  716  in turn form a receiving section  722  for the damper mass  726 . The damper mass  726  is mounted on the retaining device  712  and/or the housing parts  714 ,  716  by means of the hinge S in a pivoting movable mount. 
       FIG. 44  shows a sectional view along the sectional line XLIV-XLIV in  FIG. 42 . 
     The spring elements  728 ,  730  connect the damper mass  726  to the housing part  714  and extend in the X direction. The damper mass  726  is also mounted in a pivotably movable manner on the housing parts  714 ,  716  by means of the hinges S. The housing part  714  therefore has a bearing site  798 , which supports the bearing journal  794  on the housing part  714 . The bearing  794  is accommodated in an opening O in a bearing section  796  of the damper mass  726 . With a movement of the damper mass  726 , the damper mass  726  can pivot about the bearing journal  794 . In doing so, the spring elements  728 ,  730  are subjected to a tensile load. Vibrations and oscillations can be reduced by the pivoting movement of the damper mass  726 . 
       FIG. 45  shows a perspective view of a device  810  according to a ninth embodiment of the invention. 
     The damper mass  826  has hinges S, which mount the damper mass  826  on the retaining device  812 . The bearing sections  896  also have the spring elements  828  and  830  according to this embodiment extending between the bearing sections  896  of the damper mass  726  and the retaining device  812 . The retaining device  812  according to this embodiment is comprised of three parts, of which only the parts  816  and  899  are shown in  FIG. 45 . 
       FIG. 46  shows a front view of the device  810  in which the three housing parts  814 ,  816  and  899  are shown. The housing parts  814 ,  816  and  899  together form the retaining sites  818 ,  820 ,  874  and  876 . 
       FIG. 47  shows a sectional view along the sectional line XLVII-XLVII in  FIG. 46 . 
       FIG. 47  shows the three housing parts  814 ,  816  and  899  which form the retaining sites  874 ,  820 . The damper mass  826  is supported via the bearing journal  894 , so that it can pivot on the housing parts  814 ,  816 ,  899 . The spring elements  830  and  878  which extend in the direction of the housing parts  814 ,  816  and  899  starting from the bearing section  896  are provided on the bearing sections  896  of the damper mass  826 . The spring elements  830  and  878  are alternately subjected to tensile loading and compressive loading due to the pivoting movement of the damper mass  826 . 
       FIG. 48  shows a sectional view along the sectional line XLVIII-XLVIII in  FIG. 46 . 
     The damper mass  826  according to this embodiment has the hinges S by means of which the damper mass  826  is mounted on the retaining device  812  so that it is pivotably movable. The retaining site  814 ,  816  (not shown in  FIG. 48 ) and  899  form the bearing sites  898  for the bearing journals  894 . 
     The damper mass  826  is designed in the form of a U as in the embodiment described above. 
       FIG. 49  shows a perspective view of a device  910  according to a tenth embodiment of the invention. 
     The device  910  has a damping device DE which is formed according to this embodiment by two damper masses  926  connected to one another by means of spring elements  928 ,  930 . The damper masses  926  are accommodated in the receiving section  922  in the retaining device  912  and/or in the housing part  914  of the retaining  912 . 
     The damper masses  926  are mounted on the retaining device  912  and/or the housing part  914  in a pivotably movably manner by means of the hinges S. 
     In this embodiment, the hinges S are also formed by the bearing journal  944 , which is accommodated in a bearing section  996  of the damper masses  926  and is supported on a bearing site  998  of the housing part  914 . 
       FIG. 50  shows a front view of the device  910 , illustrating the housing halves  914  and  916  of the retaining device  912 . 
       FIG. 51  shows a sectional view along the sectional line LI-LI in  FIG. 50 . 
       FIG. 51  shows the two damper masses  926 , which are connected by a spring element  930 . Both of the damper masses  926  are mounted on the retaining device  912  and/or the housing halves  914  and  916  by means of the hinges S. 
     When the damper masses  926  are pivoted about the bearing journal  994  because of vibrations or oscillations, the damper masses  926  execute a movement relative to one another, and the spring  930  is subjected to a tensile load. Due to the movements of the damper masses  926  and the associated load on the spring element  930 , vibrations and oscillations can be damped with the device  910 . 
       FIG. 52  shows a sectional view along the sectional line LII-LII in  FIG. 50 . 
       FIG. 52  shows the two damper masses  926  which are connected to one another via the spring elements  928  and  930 . The damper masses  926  are mounted on the housing part  914  by means of the hinges S, so that they are pivotabty movable on the housing part  914 . To accommodate the bearing journals  994 , the housing part  914  has bearing sites  998 . The bearing journals  994  have been accommodated in an opening O in the bearing sections  996  of the damper masses  926 . With pivoting movements of the two damper masses  926 , the spring elements  928  and  930  are subjected to a tensile load. 
     According to an eleventh embodiment of the invention,  FIG. 53  shows a perspective view of a device  1010 , in particular for damping flexural vibrations and/or torsional vibrations, for example, on shafts. 
     The device  1010  comprises a retaining device  1012 . According to this embodiment, the retaining device  1012  is designed to be ring-shaped and has an inside circumferential wall  1100  and an outside circumferential wall  1102 . The retaining device  1012 , i.e., the housing  1012 , is comprised of two components  1014  and  1016 . Component  1014  here forms a closure element or a cover for sealing the component  1016 . 
       FIG. 54  shows a perspective view of the device  1010  in which the component  1014 , i.e., the closure element has been accommodated. 
     The closure element  1014  is designed in the form of a disk. The second component  1016  is designed with a U-shaped cross section, wherein the inside circumferential wall  1100  and the outside circumferential wall  1102  form two legs of the U shape which are connected to one another by means of a transverse leg (not shown in  FIG. 54 ). Between the inside circumferential wall  1100  and the outside circumferential wall  1102 , the damping device DE is accommodated. The damping device DE is comprised of an annular damper mass  1026  which is connected to the component  1016  by means of a spring element  1028 . The spring element  1028  is designed in the form of a ring and extends between an inside circumferential area  1004  of the damper mass  1026  and a radially exterior surface  1106  of the inside circumferential wall  1100  of the retaining device  1012  and/or of the component  1016 . The radial outer surface  1006  of the inside circumferential wall  1100  of the retaining device  1012  and/or of the component  1016 . The outer radial surface  1106  of the inside circumferential wall  1100  forms a retaining site  1018  for the spring element  1028  and/or for the damping device DE. 
       FIG. 55  show a top view of the device  1010  in which the component  1016  can be recognized in particular. 
     In the top view according to  FIG. 55 , the annular shape of the device  1010  can be seen with the inside circumferential wall  1100  and the outside circumferential wall  1102 . 
       FIG. 56  shows a sectional view along the sectional line LVI-LVI in  FIG. 55 . 
     The component  1016  is designed with a U-shaped cross section and can be sealed by the component  1014  to form a sealed receptacle section  1022  with the component  1014 . The component  1014  is designed in the form of a disk. 
     The component  1016 , which is designed with a U-shaped cross section, also has a transverse leg  1108  connecting the two legs  1100  and  1102 , in addition to having the two U legs formed by the inside circumferential wall  110  and the outside circumferential wall  1102 . 
     The damping device DE is accommodated in the receiving section  1022 . The receiving section  1022  is formed by the two components  1014  and  1016 . The damper mass  1026  is designed in a ring shape and has a rectangular cross section. 
     The spring element  1028  extends between the inside circumferential surface  1104  of the damper mass  1026  and the radial outer surface  1106  of the inside circumferential wall  1000 . The spring element  1028  is designed in a ring shape. The spring element  1028  may be in contact with the radial outer surface  1106  of the inside circumferential wall  1100 . The radially outer surface  1106  of the inside circumferential wall  1100  forms a retaining site  1018  for the spring element  1028  and establishes a connection between the retaining device  1012  and the damping device DE. 
     Between the outside circumferential surface  1110  and the side surfaces  1112  and  1114  of the damper mass  1026  and the components  1014  and  1016 , a gap s is formed. The gap s ensures that the damper mass  1026  can oscillate for oscillation damping in the receiving section  1022  of the retaining device  1012 . For oscillation damping the damper mass  1026  can be deflected in the radial direction. It is also possible for the damper mass  1026  to be deflected in the axial direction of the axis M for vibration damping. The respective gap s defines a maximum deflection of the damper mass  1026  relative to the retaining device  1012 , i.e., it limits the deflection of the damper mass  1026  relative to the retaining device  1012 . 
     The spring element  1028  is connected to the damper mass  1026  before the damping device DE formed by the damper mass  1026  and the spring element  1028  is connected to the retaining device  1012 . The spring element  1028  is connected to the inside circumferential surface  1104  of the damper mass  1026 . Following that, the damping device DE, i.e., the damper mass  1026  on the spring element  1028  is pressed into the component  1016  and/or the spring element  1028  is pressed onto the radial outer surface  1106  of the inside circumferential wall  1100  of the component  1016 . In this way, the spring element  1028  is provided with a predetermined bias. The spring element  1028  holds the damper mass  1026  in a predetermined position on the retaining device  1012 , i.e., on the component  1016  in the resting state of the device  1010 . Following the mounting of the damping device DE, the housing, i.e., the retaining device  1012 , is sealed with the component  1014 . For connecting the two components  1014  and  1016 , for example, catch noses or the like can be provided on the components  1014  and  1016 . 
       FIG. 57  shows a top view of a device  2010  according to a twelfth embodiment of the invention. 
     The device  2010  has a retaining device, i.e., a housing  2012 , of which only the housing half  2014  is shown in  FIG. 57 . Retaining sites  2018  and  2020  for the spring elements  2028  and  2030  are formed on the housing half  2014 . Of the spring elements  2028  and  2030 ,  FIG. 57  shows only the fastening sections  2036  and  2038  which are designed in the form of a thickened area. 
     The device  2010  according to this embodiment is designed in the shape of a rod. 
       FIG. 58  shows a sectional view along the sectional line LVIII-LVIII in  FIG. 57 . 
     The device  2010  has a retaining device  2012  and a damper mass  2026 . The damper mass  2026  is connected to the retaining device  2012 , i.e., the housing halves  2014  and  2016  by the spring element  2030 . Therefore, a retaining site  2020  is formed on the housing half  2014 . A retaining site  2076  is formed on the housing half  2016 . The spring element  2030  extends between the retaining sites  2020  and  2076  through the damper mass  2026 . The spring element  2030  is connected to the retaining sites  2020  and  2076  of the housing halves  2014 ,  2016  by its fastening sections  2036  and  2088 . The fastening sections  2036  and  2088  are designed in the form of thickened areas, in particular in the form of cambered thickened areas and are accommodated in the retaining sites  2020  and  2076 , which are offset toward the inside in the direction of the damper mass  2026 . The spring  2030  comprises a spring web  2116  and is connected to the damper mass  2026  by the spring web  2116 . The spring web  2116  is connected to a bushing  2118 . The bushing  2118  is accommodated in an opening  2120  in the damper mass  2026 . The spring element  2030  extends between its fastening sections  2038  and  2088  through the opening  2120  in the damper mass  2026 . The inside circumferential surface of the bushing  2118  is coated with the material of the spring element  2030 . The spring element  2030  has stop buffers AP which are provided on the end faces of the bushing  2118 . The stop buffers AP can reduce the impact of the damper mass  2026  on the retaining device  2012 . 
     The damper mass  2026  has side faces  2122  and  2124  which extend parallel to the spring sections  2034  and  2086  of the spring element  2030 , i.e., the side surfaces  2122  and  2124  extend in the Y direction. Between the side surfaces  2122  of the damper mass  2026  and the surface  2126  of the retaining device  2012  opposite this side surface, a predetermined gap s is formed. In contrast with that, the side surface  2124  is in contact with the surface  2128  of the retaining device  2012 . Therefore, the receiving sections  2022  formed by the housing halves  2014  and  2016  is subdivided into two chambers  2120  and  2132 . It can be seen in  FIG. 58  that the dimension of the gap s changes in the X direction due to the shape of the surface  2126 . The damper mass  2026  oscillates in the Y direction under the load of the spring element  2030 . In the Y direction, i.e., in the direction of oscillation of the damper mass  2026 , the gap s is reduced when the damper mass  2026  is deflected in the direction of the housing surfaces  2044  and  2046 . The surface  2126  has a kink  2134 , which lies essentially in the area of the connection point of the housing halves  2014  and  2016 . 
       FIG. 59  shows an enlarged view of the detail LIX in  FIG. 58 . 
       FIG. 59  shows the damper mass  2026  and the housing halves  2014  and  2016  in sections. 
     The gap s is inserted between the side face  2122  of the damper mass  2026  and the surface  2126  of the housing halves  2014  and  2016 . The surface  2126  on the housing halves  2014  and  2016  has a kink  2134 , which is situated on the connecting site between the housing halves  2014  and  2016 . In this location  2134 , the gap s is largest in the X direction. The gap s becomes smaller in the direction of the surface  2044 , i.e., continuously in the Y direction. With a deflection of the damper mass  2026  in the Y direction, the gap s between the surface  2122  of the damper mass  2026  and the surface  2126  of the housing halves  2014  and  2016  becomes smaller continuously with an increase in the deflection. Therefore, only a very small amount of air in the chamber  2132  can flow between the damper mass  2026  and the surface  2126 . The air cushion formed in the chamber  2132  brakes the damper mass  2026 , so that a variable damping, in particular progressive damping of the damper mass  2026  is achieved and the damper mass  2026  can be prevented from striking the damper mass  2026  against the housing halves  2014 ,  2016 . If adequate damping cannot be provided by means of the air cushions, the impact of the damper mass  2026  on the retaining device  2012  can be reduced by means of one of the stop buffers AP. 
     The size of the air gap s between the surface  2122  of the damper mass  2026  and the surface  2126  of the housing parts  2014 ,  2016  is reduced, the further the damper mass  2026  is deflected in the Y direction, i.e., the greater the amplitude of the damper mass  2026 . Starting from the surface  2044 , the surface  2126  runs continuously up to the kink  2134 , i.e., the gap s becomes larger continuously. 
     The thirteenth embodiment of the invention illustrated in  FIGS. 60 to 62  corresponds largely to the twelfth embodiment described with reference to  FIGS. 57 to 59 . 
     The only important difference between the two embodiments is that additional kink points are provided on the surface  2126 . The following embodiments relate to the housing part  2016 , a large detail of which is illustrated in  FIG. 62 , but they also apply similarly to the housing part  2016 . 
     In a first section the surface  2126  runs parallel to the Y axis and beyond the kink  2136  the surface  2126  runs at an angle to the Y axis in a second section, so that the gap s between the damper mass  2026  and the surface  2126  becomes larger up to the kink  2134 . The kink  2134  is situated between the two housing halves  2014 ,  2016  at the connection point. Starting from the first kink  2134  the gap s becomes smaller again up to the third kink  2138  because of the angled course of the surface  2126  to the Y axis. 
     Due to the contour, i.e., the shape of the surface  2126 , the amplitude of the damper mass  2026  can be adjusted. In a comparison of the twelfth embodiment ( FIGS. 57 to 59 ) and the thirteenth embodiment ( FIGS. 60 to 62 ), it can be seen that in the thirteenth embodiment its extent in the X direction can be reduced more rapidly than is the case with the twelfth embodiment, so that the maximum allows amplitude of the damper mass  2026  is smaller in the thirteenth embodiment.