A dynamic vibration absorber with a clamped elastomeric spring

Abstract

The present invention relates to a dynamic vibration absorber having a vibration absorbing mass block having a through-hole extending in a virtual dynamic vibration absorber main axis direction and having a height in the virtual dynamic vibration absorber main axis direction, a vibration damping base having a fastening bolt embedded in the through-hole in the virtual dynamic vibration absorber main axis direction, and an elastomer spring supported at an inner surface of the vibration absorbing mass block defining the through-hole and at an outer surface of the fastening bolt of the vibration damping base. The elastomer spring is composed of an integrally formed molding body made of an elastomer material; and the fastening bolt is fitted into the molding body which has been plugged into the through-hole. The inner surface of the vibration absorbing mass block has a region of a cylindrical peripheral surface segment shape extending in the virtual dynamic vibration absorber main axis direction with a length of at least 40% of the height of the vibration absorbing mass block; and the molding body has a guide region which linearly guides the region of the cylindrical peripheral surface segment shape with respect to the fastening bolt in the virtual dynamic vibration absorber main axis direction.

Description

Technical Field

[0001] This invention relates to a dynamic vibration absorber comprising: a vibration-absorbing mass having a through hole; a damping base having a fastening bolt embedded in the through hole; and an elastic spring that elastically supports the vibration-absorbing mass on the damping base. More specifically, this invention relates to a dynamic vibration absorber having the features described in the preamble of independent claim 1.

[0002] Dynamic vibration dampers are passive components used to reduce vibrations. Many dynamic vibration dampers are used in the automotive manufacturing industry to reduce vibrations in various structures, which are not only disruptive but can also damage the integrity of the structure if resonance occurs.

[0003] The natural frequency of a dynamic vibration absorber is the frequency at which it operates. In the case of a dynamic vibration absorber with an elastomer spring—that is, a dynamic vibration absorber with damping effect produced by the elastomeric material of the spring—this frequency constitutes a frequency band. The natural frequency depends on the stiffness of the elastomer spring and the physical mass of the absorbing mass. The lower the desired natural frequency of the dynamic vibration absorber, the softer the elastomer spring must be, and the greater the physical mass of the absorbing mass must be. Background Technology

[0004] In various dynamic vibration dampers with elastomeric springs, the elastomeric springs are directly vulcanized onto the damping mass block. However, this requires heating the damping mass block to the temperature required for the vulcanization process. This not only increases the heat energy demand but also prolongs the process time. Therefore, various dynamic vibration dampers with elastomeric springs have been developed, in which the elastomeric springs are manufactured separately from the damping mass block in the vulcanization tool before being attached to the damping mass block.

[0005] The dynamic vibration absorber known from DE102017110598A1 comprises: a rigid absorbing mass extending annularly around the main axis of the dynamic vibration absorber; a shape-stabilized damping base having a central fastening hole on the main axis of the dynamic vibration absorber; an elastomeric spring elastically coupling the absorbing mass to the damping base and having a central notch in the region of the main axis of the dynamic vibration absorber; and a fastening element extending through the absorbing mass, the elastomeric spring, and the damping base on the main axis of the dynamic vibration absorber, having a radial clearance relative to the absorbing mass and the elastomeric spring, and supported at the edge of the fastening hole by its radial flange. Here, the elastomeric spring is material-locked to the damping base and shape-locked to the absorbing mass, wherein the elastomeric spring and the absorbing mass engage with each other transversely to the main axis of the dynamic vibration absorber. The engagement of the elastomeric spring and the absorbing mass is ensured by the fastening element extending through the elastomeric spring. The damping base, to which the elastomeric spring is material-locked, is a perforated retaining plate partially embedded in the molding die of the elastomeric material forming the elastomeric spring. During the vulcanization of the elastomeric spring, at least this retaining plate must be fixed in the vulcanization mold used at this time and heated together. This known dynamic vibration absorber has only soft support for the damping base relative to the damping base in the direction transverse to the main axis of the dynamic vibration absorber and around the inclined axis extending transverse to the main axis of the dynamic vibration absorber. Therefore, it does not have selective soft support in the direction of the main axis of the dynamic vibration absorber and a correspondingly low natural frequency of the dynamic vibration absorber.

[0006] A damping device for eliminating and / or mitigating vibrations of vehicle components is known from DE102019125701A1, having the features described in the preamble of independent claim 1. This known damping device comprises a mass element, a fastening element for fastening to the vehicle component, and a spring device that allows the mass element to be vibratoryly connected to the fastening element. The mass element or fastening element has a fastening mechanism for fastening the spring device, and the fastening element or mass element has at least two support mechanisms for supporting the spring device, wherein the spring device has at least one fastening device fixed to the fastening mechanism and at least two support segments supported at the support mechanisms in opposite axial directions. Here, the fastening mechanism and the support mechanisms are spaced apart from each other in the axial direction such that the spring device is pre-tensioned when the support segments abut against the support mechanisms. The spring device may be integrally constructed of an elastomeric material and is inserted into a through-hole of the mass element extending in the main direction of the damper. The fastening element is inserted into the through-hole of the spring device. All embodiments of this known damping device have two spring device regions made of an elastomeric material, with oppositely oriented frustoconical circumferential shapes, which are free between the fastening mechanism and the support mechanism. This known damping device also has a vibration-absorbing mass with only soft support at the damping base in the direction transverse to the damper's main axis and around a transverse axis extending transverse to the damper's main axis; therefore, it lacks selective soft support in the direction of the damper's main axis and a correspondingly low damper natural frequency. Summary of the Invention

[0007] The object of the present invention is to clarify a dynamic vibration absorber having the features described in the preamble of independent claim 1, the dynamic vibration absorber having selective soft support of its absorbing mass block at the damping base in the direction of the main axis of the dynamic vibration absorber and a correspondingly low natural frequency of the dynamic vibration absorber, and the dynamic vibration absorber having significantly more rigid support in the direction transverse to the main axis of the dynamic vibration absorber and around an inclined axis extending transverse to the main axis of the dynamic vibration absorber.

[0008] The object of the present invention is achieved by a dynamic vibration absorber having the features described in independent claim 1. A preferred design of the dynamic vibration absorber according to the present invention is given in the dependent claims.

[0009] The dynamic vibration absorber according to the invention comprises: a vibration-absorbing mass having a through hole extending along the virtual main axis of the dynamic vibration absorber and having a height along the virtual main axis of the dynamic vibration absorber; a damping base having a fastening bolt embedded in the through hole along the virtual main axis of the dynamic vibration absorber; and an elastomeric spring supported on the inner surface of the vibration-absorbing mass defining the through hole and the outer surface of the fastening bolt of the damping base. An integral molded body made of elastomeric material constitutes the elastomeric spring; and the fastening bolt is inserted into the molded body already inserted into the through hole. The inner surface of the vibration-absorbing mass has a region in the shape of a cylindrical circumferential segment, the length of which extends along the virtual main axis of the dynamic vibration absorber is at least 40% of the height of the vibration-absorbing mass; and the molded body has a guiding region that linearly guides the cylindrical circumferential segment-shaped region relative to the fastening bolt along the virtual main axis of the dynamic vibration absorber.

[0010] The molding body is composed of an elastomeric material, meaning that the molding body forms an elastomeric spring without having regions that cannot be elastically deformed. Typically, the molding body is composed entirely of an elastomeric material and has a uniform material composition.

[0011] The molding die is secured in the through hole by means of its support on the outer surface of the bolt, by inserting a fastening bolt into the molding die. The vibration-absorbing mass is elastically supported only at the damping base, and typically by only one elastomeric spring consisting of exactly one molding die.

[0012] Typically, the vibration-absorbing mass is constructed to be axisymmetric or even rotationally symmetric with respect to a virtual dynamic vibration absorber main axis, which thus passes centrally through a through-hole in the vibration-absorbing mass. The virtual dynamic vibration absorber main axis means it is not a concrete component of the dynamic vibration absorber.

[0013] In the dynamic vibration absorber according to the invention, the absorbing mass block is guided by its guidance at the guide region of the molding die, the stiffness of which is much higher than the stiffness resisting the offset of the absorbing mass block relative to the fastening bolts along the virtual main axis of the dynamic vibration absorber. Typically, this stiffness ratio is at least 1:4, and usually at least 1:9. However, it should be understood that, in terms of the absolute dimensional value of the linear guidance, the linear guidance stiffness provided by the guide region of the molding die to the cylindrical circumferential segment shape region is not large, because the guide region is part of the molding die made of an elastomeric material.

[0014] The linear guidance provided by the cylindrical circumferential segment-shaped region extending along the virtual main axis of the dynamic vibration absorber on the inner surface, at a length of at least 40% of the height of the absorbing mass block, resists not only the linear radial displacement of the absorbing mass block relative to the fastening bolt in the direction transverse to the virtual main axis of the dynamic vibration absorber, but also the overturning of the absorbing mass block relative to the fastening bolt around an inclined axis extending transverse to the main axis of the dynamic vibration absorber. This long linear guidance effect of the cylindrical circumferential segment-shaped region on the inner surface of the absorbing mass block at the mold guide area increases with the length of the cylindrical circumferential segment-shaped region along the virtual main axis of the dynamic vibration absorber. Therefore, preferably, the length of the cylindrical circumferential segment-shaped region extending along the virtual main axis of the dynamic vibration absorber is at least 50% of the height of the absorbing mass block, and more preferably, at least 60% of the height of the absorbing mass block. Also beneficial to the high linear guidance stiffness relative to overturning achieved by the mold guide area is that the length of the cylindrical circumferential segment-shaped region is at least equal to its diameter, and preferably at least 1.2 times its diameter.

[0015] Specifically, the guiding area of ​​the molding body can have guide rings spaced apart along the main axis of the virtual dynamic vibration absorber. These guide rings each abut against a cylindrical circumferential segment of the inner surface along the entire inner circumferential surface of the through-hole, or only abut against the inner surface of the vibration-absorbing mass block when it displaces relative to the fastening bolts in the radial direction along the main axis of the virtual dynamic vibration absorber. Guide rings that only abut against the inner surface of the vibration-absorbing mass block when it displaces relative to the fastening bolts in the radial direction along the main axis of the virtual dynamic vibration absorber ideally do not exert any force on the vibration-absorbing mass block vibrating along the main axis of the dynamic vibration absorber. While these guide rings cannot prevent minute radial displacement of the vibration-absorbing mass block relative to the fastening bolts across the virtual main axis of the dynamic vibration absorber, they can limit it to a negligible amplitude range. However, the guide ring abuts against the inner surface of the vibration-absorbing mass block with low pressure in the region of the cylindrical circumferential segment, which only introduces low frictional damping for the vibration of the vibration-absorbing mass block relative to the fastening bolts in the direction of the main axis of the dynamic vibration absorber. Thus, the desired function of the dynamic vibration absorber according to the invention is not affected. It can also be demonstrated that achieving the guide ring abutting against the inner surface of the vibration-absorbing mass block with low contact pressure is simpler than achieving a very small free gap between the surface of the guide region and the surface of the region of the cylindrical circumferential segment.

[0016] The stiffness of the cylindrical circumferential segment region on the inner surface of the vibration-absorbing mass block, guided linearly by the guide region, can be improved by pre-tightening the molding body in the guide region. However, for the aforementioned reasons, applying pre-tightening as pressure pre-tightening between the outer surface of the fastening bolt and the inner surface of the through hole is not necessarily beneficial. Therefore, it is advantageous to apply pre-tightening to the molding body in the guide region by expanding the molding body around the fastening bolt, i.e., by inserting the fastening bolt into the annular molding body, or by clamping the molding body along the direction of the virtual dynamic vibration absorber's main axis.

[0017] In the dynamic vibration absorber according to the invention, the elastic support of the vibration-absorbing mass block in the direction of the main axis of the dynamic vibration absorber can be achieved by the following method: the molding body constitutes two flanges, each of which is arranged at one end of the guiding area of ​​the molding body and protrudes outward from the guiding area in the radial direction relative to the virtual main axis of the dynamic vibration absorber. These two flanges, under elastic preload, abut against the end faces of a cylindrical circumferential segment-shaped region on the inner surface. The end faces of the cylindrical circumferential segment-shaped region on the inner surface are stepped portions extending annularly around the virtual main axis of the dynamic vibration absorber on the inner surface of the vibration-absorbing mass block, radially opposite to the main axis of the dynamic vibration absorber, at which the cylindrical circumferential segment-shaped region on the inner surface terminates. The flanges of the molding body are supported at these end faces under preload; therefore, the cylindrical circumferential segment-shaped region on the inner surface of the vibration-absorbing mass block elastically separates these flanges from each other. This occurs during the process of the elastomeric spring engaging with the through-hole of the vibration-absorbing mass block.

[0018] The vibration-absorbing mass block achieves particularly flexible axial support along the main axis of the dynamic vibration absorber via the flanges of the molding body in the following manner: the molding body has an annular axial recess surrounding the fastening bolts in the flange end faces of the two flanges facing away from each other. In the molding body that has been engaged in the through hole, these recesses can close by the elastic bending of the flanges away from each other. These recesses not only reduce the axial support stiffness of the vibration-absorbing mass block at the fastening bolts, but also reduce the stress of the elastomeric material of the molding body when the molding body is engaged in the through hole and when the vibration-absorbing mass block is axially offset relative to the fastening bolts and the molding body deforms. In other words, the axial recesses are preferably formed in the flange end faces such that the molding body forms an annular solid joint around the fastening bolts, so that the flanges bend away from each other like disc springs.

[0019] When the molded mold body protrudes from the flange at its two axial ends along the direction of the virtual dynamic vibration absorber main axis, the flange has space in which it can deform without colliding with other parts of the damping base.

[0020] The molded body can be held on the fastening bolt by a retaining element, which is fixed at the free end of the fastening bolt and protrudes outward from the outer surface of the fastening bolt in the radial direction relative to the main axis of the virtual dynamic vibration absorber. Specifically, the retaining element can be screwed onto the free end of the fastening bolt. For this purpose, the retaining element can be screwed onto the fastening bolt at its free end using a self-locking screw. When the diameter of the retaining element is larger than the inner diameter of the cylindrical circumferential section of the inner surface of the vibration-absorbing mass block, the retaining element functions as an anti-dislodgement device for the vibration-absorbing mass block arranged on the fastening bolt, even in the event of elastomeric spring failure.

[0021] As the outer circumferential surface of the fastening bolt decreases along its length toward its free end, the molding die can be supported in the opposite direction to the retaining element at the outer surface of the resulting frustoconical circumferential shape of the fastening bolt. However, to achieve this support, the full opening angle of the outer circumferential surface of the fastening bolt needs to be at least approximately 10°. However, this is not necessarily optimal for the desired linear guidance of the region at the fastening bolt where the molding die achieves the cylindrical circumferential segment shape of the inner surface of the vibration-absorbing mass block. More suitable for this is that the outer circumferential surface of the fastening bolt remains constant along its length, or decreases toward its free end only by a small full opening angle of less than 5°, optionally 1° to 3°. Such a small opening angle may be necessary to allow the fastening bolt to be demolded from the injection mold, thus enabling the fastening bolt to be manufactured using an injection molding process in a cost-effective manner.

[0022] In one embodiment of the dynamic vibration absorber according to the invention, the molding body abuts against the outer surface of the fastening bolt along its entire length, between the base of the vibration-absorbing mass block where the fastening bolt is fixed and which protrudes radially outward from the outer surface of the fastening bolt, and the retaining element at the free end of the fastening bolt. Here, this abutment is preferably achieved on the entire outer circumferential surface of the fastening bolt, and it can also be achieved entirely on the entire outer surface of the fastening bolt.

[0023] The reliable positioning of the molding body on the fastening bolts is achieved by clamping the molding body between the base and the retaining element.

[0024] In one embodiment of the dynamic vibration absorber according to the invention, the fastening bolts and, if present, the damping base constitute the area of ​​the base molding mold, which further has fastening and positioning areas for fixing the damping base to the structure to be damped and for orienting the fastening bolts relative to the structure to be damped. Here, the base molding mold can be a die-cast mold that can be mass-produced at low cost and is composed of a lighter, lighter metal alloy.

[0025] In another embodiment of the dynamic vibration absorber according to the invention, the fastening bolt is screwed into the vibration damping base of the damping base, or is configured to be screwed directly into the structure to be damped. Here, the fastening bolt may be integrally constructed with a retaining element protruding from the outer surface of the fastening bolt. Attached Figure Description

[0026] The present invention will be further explained and illustrated below with reference to the preferred embodiments shown in the accompanying drawings.

[0027] Figure 1 A longitudinal section of the dynamic vibration absorber according to the present invention is shown along its virtual dynamic vibration absorber main axis.

[0028] Figure 2 According to Figure 1 The diagram shows a radial top view of the dynamic vibration absorber relative to its main axis, with the viewing angle relative to... Figure 1 Viewed from the right, as Figure 2 The section line II is shown in the drawing.

[0029] Figure 3 According to Figure 1 and Figure 2 The diagram shows a perspective view of the dynamic vibration absorber according to the present invention. Detailed Implementation

[0030] Figures 1 to 3 The dynamic vibration absorber 1 shown has a vibration-absorbing mass block 2, which is elastically supported at the damping base 4 by an elastomeric spring 3. The damping base 4 has a base molding body 5, which is here a die-cast molding body 6 made of a light metal alloy, such as a zinc die-casting alloy. The base molding body has a fastening region 7 through which the base molding body 5 can be fixed to the structure where the vibration of the dynamic vibration absorber 1 needs to be attenuated. In the fastening region 7, the base molding body 5 has a fastening screw through hole 8 and an anti-rotation protrusion 9 that is laterally offset relative to the fastening screw through hole 8. The anti-rotation protrusion 9 is embedded in a corresponding groove of the corresponding structure, just like the fastening screw (not shown) that passes through the fastening screw through hole 8 and whose screw head is supported on the edge 10 of the fastening screw through hole. A positioning area 11 extends from the fastening area 7 to the base molding mold 5, which positions and orients the fastening bolts 12 of the base molding mold 5 relative to the fastening area 7.

[0031] The fastening bolt 12 extends into the through hole 14 along the direction of the virtual main axis 13 of the dynamic vibration absorber 1. This through hole passes through the vibration-absorbing mass block 2 along the direction of the virtual main axis 13. The vibration-absorbing mass block 2 is rotationally symmetrical with respect to the virtual main axis 13, i.e., it is constructed as a rotating body about the main axis 13 of the dynamic vibration absorber. The vibration-absorbing mass block 2 is supported at the fastening bolt 12 by an elastomeric spring 3. The elastomeric spring 3 is composed of a one-piece molded body 16, which is separately made of elastomeric material 15 before being inserted into the vibration-absorbing mass block 2. A molded mold 16 is fully abutted against the outer surface 17 of the fastening bolt 12, both around the entire circumference of the bolt 12 along the virtual main axis 13 of the dynamic vibration absorber and along the entire length between the damping base 18 and the disc-shaped retaining element 19 in the positioning area 11. The fastening bolt 12 itself is fixed to the damping base, and the retaining element is fixed to the free end 21 of the fastening bolt by a self-locking screw 20 embedded in the bolt 12. In other words, the molded mold 16 is clamped between the base 18 and the retaining element 19 on the fastening bolt 12 along the virtual main axis 13 of the dynamic vibration absorber. The diameter of the retaining element 19 is larger than the minimum inner diameter of the through hole 14, so that the retaining element 19 also functions as an anti-dislodgement device for the vibration-absorbing mass 2 on the fastening bolt 12. The molding body 16 has a guide region 22 facing the vibration-absorbing mass block 2 and a flange 23 adjacent to the guide region 22 along the direction of the virtual dynamic vibration absorber main axis 13 and protruding from the guide region 22 in the radial direction of the virtual dynamic vibration absorber main axis 13.

[0032] The guiding region 22 guides the cylindrical circumferential segment-shaped region 24 of the inner surface 25 of the defining through hole 14 linearly along the direction of the virtual dynamic vibration absorber main axis 13 relative to the fastening bolt 12. For this purpose, the guiding region 22 has three guide rings 26 spaced apart from each other around the virtual dynamic vibration absorber main axis 13. Each guide ring 26 may be individually abutted against the cylindrical circumferential segment-shaped region around the virtual dynamic vibration absorber main axis 13, or may have a small radial distance from the cylindrical circumferential segment-shaped region, but these distances are bridged when the absorbing mass 2 experiences radial displacement relative to the fastening bolt 12. In either case, an elastic restoring force acts on the cylindrical circumferential segment-shaped region 14 to resist radial displacement of the absorbing mass 2 relative to the fastening bolt 12. The cylindrical circumferential segment-shaped region 14 extends more than 50% of the height of the absorbing mass 2 along the virtual dynamic vibration absorber main axis 13. Furthermore, the length of region 24, which is the circumferential segment of the cylinder, is more than 1.2 times its diameter. These are all measures that help to achieve linear guidance of the vibration-absorbing mass block 2 relative to the fastening bolt 12 through the molding body 16.

[0033] The fastening bolt 12 has a slight taper, meaning its outer circumferential surface tapers slightly from the damping base 18 towards the free end 21, wherein the outer surface 17 has a small, complete open angle in the range of 1° to 3°, as required for demolding the die-cast molded body 6 from the die-casting mold. The slightly tapered outer surface 17 does not detract from the function of the dynamic vibration absorber 1. The damping mass 2 is provided with soft, elastic support at the fastening bolt 12 in the direction of the dynamic vibration absorber's main axis 13 by means of the flange 23 to achieve a low dynamic vibration absorber natural frequency of the dynamic vibration absorber 1 precisely in this direction. The flange 23 abuts against mutually opposing end faces 27 extending radially to the virtual dynamic vibration absorber's main axis 13, these end faces being constructed by the inner surface 25 at the ends of the cylindrical circumferential segment-shaped region 24. Flange 23 rests against end face 27 under elastic preload, which is generated by the flange 23 being supported by a disc spring around a solid joint 28 constructed in the molding body 16 and annularly surrounding the main axis 13 of the virtual dynamic vibration absorber. The position of the solid joint 28 is defined by an axial recess 29 in the opposing flange end faces of the two flanges 23, annularly surrounding the fastening bolt 12 and thus annularly surrounding the main axis 13 of the virtual dynamic vibration absorber. The axial recess 29 is open after the molding body 16 is individually manufactured and before the molding body 16 is engaged with the vibration-absorbing mass block 2, i.e., it has an open free cross-section. During engagement, the axial recess 29 is opened by the mutual support of the flanges 23. Figure 1 The structure is at least substantially closed. When the absorbing mass 2 vibrates along the virtual dynamic vibration absorber main axis 13, the absorbing mass 2 is linearly guided relative to the fastening bolt 12 via the guide region 22 of the molding body 16 through the cylindrical circumferential segment 24 of the inner surface 25 of its through hole 14, and is relatively softly and elastically supported at the fastening bolt 12 via the flange 23 of the molding body 16 in the virtual dynamic vibration absorber main direction 13. In the direction transverse to the dynamic vibration absorber main axis 13 and around the inclined axis extending transverse to the dynamic vibration absorber main axis 13, the absorbing mass 2 is supported at the fastening bolt 12 by the molding body 16 in a relatively much rigid manner, with a spring stiffness typically at least 4 times higher.

[0034] Advantageous improvements of the present invention are derived from the patent claims, the specification, and the drawings.

[0035] The features and advantages of combinations of features mentioned in the specification are merely exemplary and may work alternatively or cumulatively, but these advantages are not necessarily achieved by embodiments of the present invention.

[0036] Regarding the disclosure of the original application documents and patents, but not the scope of protection, the following applies: Other features can be derived with reference to the accompanying drawings, particularly the geometry shown, the relative dimensions of the various components, their relative arrangement, and their functional connections. Features of different embodiments of the invention or combinations of features from different patent claims are permissible, even if they deviate from the reference relationships of the selected patent claims, and are hereby suggested. This also applies to features shown in separate drawings or mentioned in their descriptions. These features may also be combined with features from different patent claims. Similarly, features listed in patent claims may be omitted for other embodiments of the invention, but this does not apply to the independent claims of granted patents.

[0037] The features mentioned in the patent claims and specification should be understood in terms of quantity to mean that there is exactly one or more such a quantity, without the need for the explicit use of the adverb "at least". Therefore, for example, when referring to a screw, it should be understood that there is exactly one screw, two screws, or more screws. A feature listed in a patent claim may be supplemented by other features, or may be the only feature present in the subject matter of the corresponding claim.

[0038] Reference numerals included in the patent claims do not constitute a limitation on the scope of the subject matter protected by the patent claims. They are used only to make the patent claims easier to understand.

[0039] List of reference numerals

[0040] 1. Dynamic vibration absorber

[0041] 2 vibration-absorbing mass blocks

[0042] 3. Elastic spring

[0043] 4 Vibration-damping base

[0044] 5. Base molding mold

[0045] 6 Die-casting mold body

[0046] 7 Fastening Area

[0047] 8 Fastening screw through holes

[0048] 9 Anti-rotation protrusions

[0049] 10 Edges

[0050] 11 Location Areas

[0051] 12 fastening bolts

[0052] 13 Virtual dynamic vibration absorber main axis

[0053] 14 through holes

[0054] 15 Elastomer Materials

[0055] 16 Molding Molds

[0056] 17 Outer Surface

[0057] 18 bases

[0058] 19 Holding elements

[0059] 20 screws

[0060] 21 free ends

[0061] 22 Guiding Area

[0062] 23 flange

[0063] 24 regions with cylindrical circumferential segments

[0064] 25 inner surface

[0065] 26 guide rings

[0066] 27 end face

[0067] 28 solid joints

[0068] 29. Depression.

Claims

1. A dynamic vibration absorber (1), comprising: A vibration-absorbing mass block (2) has a through hole (14) extending along the direction of the virtual main axis (13) of the dynamic vibration absorber and has a height along the direction of the virtual main axis (13) of the dynamic vibration absorber. A vibration damping base (4) having fastening bolts (12) embedded in the through hole (14) along the direction of the virtual dynamic vibration absorber main axis (13), and An elastomeric spring (3) is supported at the inner surface (25) of the vibration-absorbing mass block (2) defining the through hole (14) and at the outer surface (17) of the fastening bolt (12) of the vibration-damping base (4). The elastomeric spring (3) is formed by an integral molded body (16) made of elastomeric material (15) and The fastening bolt (12) is inserted into the molding body (16) which has been inserted into the through hole (14). Its features are, The inner surface (25) of the vibration-absorbing mass block (2) has a region (24) in the shape of a cylindrical circumferential segment, the length of which extends along the direction of the main axis (13) of the virtual dynamic vibration absorber is at least 40% of the height of the vibration-absorbing mass block (2). The molding body (16) has a guiding region (22) that guides the cylindrical circumferential segment shape of the region (24) linearly relative to the fastening bolt (12) along the direction of the virtual dynamic vibration absorber main axis (13).

2. The dynamic vibration absorber (1) according to claim 1, characterized in that, The length of the cylindrical circumferential segment region (24) extending along the direction of the virtual dynamic vibration absorber main axis (13) is at least 50% of the height of the vibration-absorbing mass block (2), and preferably at least 60%.

3. The dynamic vibration absorber (1) according to claim 1 or 2, characterized in that, The length of the region (24) of the cylindrical circumferential segment is at least equal to its diameter, and preferably at least 1.2 times its diameter.

4. The dynamic vibration absorber (1) according to claim 1 or 2, characterized in that, The guide region (22) of the molding body (16) has guide rings (26) spaced apart along the direction of the virtual dynamic vibration absorber main axis (13), each guide ring abutting the cylindrical circumferential segment region (24) of the inner surface (25) along the entire inner circumferential surface of the through hole (14), or abutting the inner surface (25) of the vibration-absorbing mass block (2) only when the vibration-absorbing mass block (2) is displaced relative to the fastening bolt (12) in a radial direction relative to the virtual dynamic vibration absorber main axis (13).

5. The dynamic vibration absorber (1) according to claim 1 or 2, characterized in that, The molding body (16) is in a pre-tightened state in the guide area (22).

6. The dynamic vibration absorber (1) according to claim 1, characterized in that, The molding body (16) forms two flanges (23), each of which is located at one end of the guide area (22) of the molding body and protrudes outward from the guide area (22) in the radial direction relative to the main axis (13) of the virtual dynamic vibration absorber. The flanges are elastically preloaded and abut against the end face (27) of the cylindrical circumferential segment region (24) of the inner surface (25).

7. The dynamic vibration absorber (1) according to claim 6, characterized in that, The molding body (16) has an axial recess (29) in the flange end faces of the two flanges (23) facing away from each other, which forms a solid joint (28) for opening the flanges (23) apart in a disc spring manner.

8. The dynamic vibration absorber (1) according to claim 6 or 7, characterized in that, The molded mold (16) protrudes from the flange (23) at its axial end along the direction of the virtual power vibration absorber main axis (13).

9. The dynamic vibration absorber (1) according to claim 1, characterized in that, The molding body (16) is held on the fastening bolt (12) by a retaining element (19) fixed at the free end (21) of the fastening bolt (12), the retaining element protruding outward from the outer surface (17) of the fastening bolt (12) in a radial direction relative to the main axis (13) of the virtual dynamic vibration absorber, wherein the retaining element (19) is optionally tightened at the free end (21) of the fastening bolt (12) by a self-locking screw (20) and / or has a diameter greater than the inner diameter of the cylindrical circumferential segment shape region (24) of the inner surface (25).

10. The dynamic vibration absorber (1) according to claim 9, characterized in that, The outer circumferential surface of the fastening bolt (12) remains constant along its length or gradually decreases toward its free end, wherein the full opening angle of the outer circumferential surface is less than 5° and optionally falls within the angle range of 1° to 3°.

11. The dynamic vibration absorber (1) according to claim 9 or 10, characterized in that, The molding body (16) is located along the entire length of the fastening bolt (12), between the base of the vibration-absorbing mass block (2) where the fastening bolt (12) is fixed and which protrudes radially outward from the outer surface (17) of the fastening bolt (12) and the retaining element (19) at the free end (21) of the fastening bolt (12), and the molding body (16) is located on the outer surface (17) of the fastening bolt (12), wherein the molding body (16) is optionally located on the entire outer circumferential surface of the fastening bolt (12) or on the outer surface (17) of the fastening bolt (12).

12. The dynamic vibration absorber (1) according to claim 11, characterized in that, The molding body (16) is clamped between the base (18) and the retaining element (19).

13. The dynamic vibration absorber (1) according to claim 1 or 2, characterized in that, The fastening bolt (12) and, if present, the damping base (18) are components of a base molding body (5), which also has fastening and positioning areas (7, 11) for fixing the damping base (4) to the structure to be damped and for orienting the fastening bolt (12) relative to the structure to be damped, wherein the base molding body (5) is optionally a die-cast molding body (6) and preferably made of a light metal alloy.

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