Vibration damper with a series of lateral spring elements

Abstract

A vibration damper (1) for reducing vibrations of a functional component comprises a damper base (2), which is fixed to or formed on the functional component and has at least three identically designed support configurations (9), a one-piece damper mass (3) having at least three identically designed, parallel through-holes (14), each of which is opposite one of the at least three support configurations (9) at a distance (13), and several shaped bodies (11) manufactured separately from the damper mass (3) and the damper base (2), each of which in turn comprises an elastomer spring (4) that elastically supports the damper mass (3) on the damper base (2). The shaped bodies (11) are each fixed on one side to one of the support configurations (9) of the damper base (2) and on the other side in the respective opposite through-hole (14) of the damper mass (3).The damping mass (3) is elongated along a virtual main mass axis (16) and all of the at least three through holes (14) run perpendicular to the main axis.

Description

TECHNICAL AREA OF INVENTION

[0001] The invention relates to a vibration damper for reducing vibrations of a functional component, such as the tailgate of a motor vehicle. In particular, the invention relates to a vibration damper with the feature of the preamble of independent claim 1. STATE OF THE ART

[0002] A vibration damper for the tailgate of a motor vehicle typically has a damper mass elongated between its ends in the direction of a virtual main axis. This mass is elastically supported at both ends by axially aligned elastomer springs against a damper base. When the vibration damper is mounted, its main axis is aligned parallel to the main plane of the tailgate and perpendicular to the direction of travel of the motor vehicle. When the tailgate is closed, excessive deflection of the damper mass relative to the damper base, which could damage the elastomer springs, must be prevented.

[0003] Known vibration dampers for tailgates of motor vehicles, corresponding to the design outlined here, are known, for example, from DE 10 2016 115 782 B4 and DE 2017 127 840 B4.

[0004] A vibration damper with the features of the preamble of independent claim 1 is known from WO 2001 / 092752 A1. Here, both the damper base and the damper mass have a rectangular shape, and the shaped elements, each formed in one piece from an elastomeric material, are engaged at the corners of the rectangular shapes in closed through-holes in the damper mass and in mounting lugs of the damper base. For this purpose, the shaped elements each have, at both ends, forming gripping elements that cooperate on both sides. In one base surface, each shaped element has an inwardly facing cavity with two cylindrical sections of different diameters. The cavity extends over the entire length of the respective shaped element between the forming gripping elements at its two ends, so that the elastomeric spring formed between them is tubular.

[0005] From WO 2013 / 167524 A1, a shaped body made of elastomer material for a vibration damper is known, having the features of the preamble of independent claim 1, which has a non-circular cross-section in order to realize different damper natural frequencies for the vibration of the damper mass relative to the damper base in different transverse directions.

[0006] From EP 3 524 845 A1, a vibration damper with a cylindrical damping mass is known. Plastic formwork elements are mounted on the ends of this formwork element, each element having a cup-shaped region facing the end of the damping mass and a cup-shaped region facing away from the damping mass. The cup-shaped region facing the damping mass receives the respective end of the damping mass by means of a frictional connection, with press-fit ribs formed on a cylindrical inner circumferential surface of the cup-shaped region. A central deflection limiting pin of the formwork element projects into the cup-shaped region facing away from the damping mass, and a disc-shaped elastomer spring, vulcanized to a perforated disc, is supported against an inner circumference of this cup-shaped region. The deflection limiting pin projects radially into the central hole of the perforated disc.The perforated disc is secured at its outer circumference in one of two detent recesses on the damper base, which are positioned opposite each other across the damper mass. This well-known vibration damper has a complex, multi-part construction and requires considerable effort to assemble from its components.

[0007] From EP 3 524 845 A1, a vibration damper with an elongated damping mass extending along a virtual principal axis is known. The damping mass is formed in multiple parts along the principal axis. At its ends, it has plastic form elements with axial press fits into which elongated, plate-shaped mass elements of the damping mass, arranged parallel to each other, are pressed. Each of the form elements also has a through-hole oriented orthogonally to the principal axis. Through opposing through-holes in a damper base, one-piece spring elements made of elastomer material engage in the through-holes in the form elements to elastically support the damping mass at both ends against the damper base. The one-piece spring elements made of elastomer material are constructed exactly as known from WO 2001 / 092752.This well-known vibration damper has a damping mass with a complex, multi-part structure and also requires considerable effort to assemble from its components. TASK OF INVENTION

[0008] The invention is based on the objective of demonstrating a vibration damper with the features of the preamble of independent claim 1, which has a particularly simple construction, whose damper natural frequencies can be tuned to significantly different values ​​in a particularly simple manner, and which is particularly well suited for reducing vibrations of a tailgate of a motor vehicle. SOLUTION

[0009] The object of the invention is achieved by a vibration damper having the features of independent claim 1. The dependent claims relate to preferred embodiments of the vibration damper according to the invention. DESCRIPTION OF THE INVENTION

[0010] A vibration damper according to the invention for reducing vibrations of a functional component, which may be a tailgate of a motor vehicle, has a damper base that is either fixed to the functional component or formed on the functional component and which has at least three identically designed support configurations. A one-piece damper mass of the vibration damper has at least three identically designed, parallel through-holes, each of which is located opposite one of the at least three support configurations at a distance. Several molded parts of the vibration damper according to the invention, manufactured separately from the damper mass and the damper base, each comprise an elastomer spring that elastically supports the damper mass on the damper base.The shaped elements are each fixed on one side to one of the support configurations of the damper base and on the other side in the respective opposite through-hole of the damper mass. In the vibration damper according to the invention, the damper mass is elongated along a virtual main mass axis, with all of the at least three through-holes running perpendicular to the main mass axis.

[0011] The at least three identically designed section configurations of the damper base and the at least three identically designed through-holes in the damper mass, despite the fundamentally simple design of the vibration damper according to the invention, offer considerable possibilities for varying the damper natural frequencies for the different vibration modes of the vibration damper according to the invention, and thus the possibility of setting very different damper natural frequencies for different vibration directions. One of the possible variations is to not fill all support configurations and opposing through-holes with the shaped elements, i.e., not to support the damper mass with the maximum possible number of elastomer springs.If one or more pairs of a support configuration and an opposing through-hole are left unused, a further variation is possible by choosing the location of the unused pairs along the main axis of the mass. The variations described so far exist without any changes to the damper base, the damper mass, or the individual components.

[0012] Since all of the at least three through-holes in the vibration damper according to the invention are perpendicular to the main axis and the damper mass is always supported at the damper base by at least two elastomer springs, the exact number of elastomer springs supporting the damper mass has no fundamental influence on the vibration modes in which the damper mass can oscillate relative to the damper base. This is quite different from, for example, when a damper mass with a rectangular base is elastically supported at the damper base by only two or three elastomer springs arranged parallel to each other, instead of by four elastomer springs arranged parallel to each other at all four corners of the rectangle.The number of elastomer springs for the elastic support of the damper mass at the damper base, which is at least optionally greater than two, is therefore fundamentally not an option for limiting the number of possible vibration modes in the vibration damper according to the invention, but rather for adjusting the damper natural frequencies of the existing vibration modes.

[0013] The fact that the damping mass of the vibration damper according to the invention is a single piece means that it consists, at least substantially, of a single body with a typically constant composition that is materially cohesive over its entire extent, for example, a metal body produced by casting and / or rolling and subsequently machined by a material removal process. Alternatively, the damping mass can also consist, for example, of a plastic matrix loaded with heavy particles, such as metal particles or mineral particles.

[0014] The fact that the damping mass of the vibration damper according to the invention is elongated along the main axis of the mass means that the damping mass has an extent along the main axis that is a multiple of its maximum diameter perpendicular to the main axis of the mass. Specifically, the extent of the damping mass along the main axis of the mass can be between three and one hundred times or between five and twenty times its maximum diameter.

[0015] In the vibration damper according to the invention, the at least three through-holes are preferably arranged at equal intervals along the main axis of the mass. It is further preferred if at least four through-holes are arranged along the main axis of the mass. The number of through-holes arranged along the main axis of the mass can also be greater than four and may be, for example, five, six, seven, or eight. In principle, their number can be even greater and may, for example, be a maximum of twelve.

[0016] In the vibration damper according to the invention, the damping mass typically has a constant outer circumference along its extension along the main axis of the mass. It is understood that the through-holes of the damping mass are not taken into account in this consideration. While the outer circumference of the damping mass can, in principle, vary along its extension along the main axis of the mass, this generally entails considerably greater effort in the manufacture of the damping mass. Preferably, the damping mass has a simple cuboid shape. Specifically, a rectangular outer circumference of the damping mass around the main axis of the mass can have a side-length ratio between 1:1.5 and 1.5:1, or preferably between 1:1.2 and 1.2:1, and most preferably approximately 1:1. This means that the damping mass preferably has a square cross-section transverse to its main axis of mass.The through holes are regularly inserted into the damping mass perpendicular to one side and in the middle between and along the other sides.

[0017] In the vibration damper according to the invention, all shaped bodies and their elastomer springs are typically identical. However, different shaped bodies and elastomer springs can also be used in the vibration damper according to the invention. In this case, it is preferred if the different shaped bodies and elastomer springs are arranged in a mirror-symmetrical arrangement with respect to a virtual transverse median plane of the vibration damper according to the invention, which extends transversely to the main axis of mass. However, this is not absolutely necessary.

[0018] In a preferred embodiment of the vibration damper according to the invention, one of several shaped elements is fixed to each of the at least three support configurations and in each of the at least through-holes. This is intended to mean, at a minimum, that the damper mass is supported at the damper base by at least three elastomer springs, and, in the case of an even number of support configurations and through-holes, by at least four elastomer springs. Furthermore, it can mean that all support configurations and through-holes are actually occupied by shaped elements, and that none of the pairs consisting of a support configuration and an opposing through-hole remains unoccupied.There are still possibilities for variation regarding the damper natural frequencies through different shaped bodies with different elastomer springs and / or through different orientations of the shaped bodies with their elastomer springs around the distance between the support configurations and the through holes.

[0019] The through-holes in the damping compound of the vibration damper according to the invention are preferably closed at the edges. The through-holes can be created during the first step of manufacturing the damping compound, for example by mold casting, or they can be completely formed. Typically, however, at least their final contour is formed by removing material, specifically usually by removing material.

[0020] Preferably, the through-holes have a stepped progression through the damping compound, which allows for easy fixing of the respective shaped body by interlocking.

[0021] In the vibration damper according to the invention, the through holes can have a non-circular cross-section. This makes it possible to fix the shaped bodies and thus their springs in a fixed orientation in the direction of rotation about the distance of the respective through hole to the associated support configuration.

[0022] The support configurations of the damper base of the vibration damper according to the invention can have simple mounting lugs into which the shaped elements can also be attached. The mounting lugs can also have a non-circular cross-section in order to fix the shaped elements in a specific orientation in the direction of rotation by the distance between the respective support configuration and the opposite through-hole. Adapted to the non-circular through-holes and support configurations, at least one of the shaped elements can have a non-circular base-side connection configuration and / or a non-circular mass-side connection configuration. This non-circular connection configuration can be formed on a rigid plastic component of the respective shaped element, to which its elastomer spring is bonded, in particular by a material bond.

[0023] In a specific embodiment of the vibration damper according to the invention, at least one of the molded bodies has an elastomer spring with a non-circular cross-section. The mass of the elastomer material of the elastomer spring can be at least 25% and preferably at least 50% greater from its center of mass in a first direction transverse to the distance of the respective through-hole to the respective support configuration than in a second direction transverse to the main axis. Specifically, the non-circular cross-section of the elastomer spring of the at least one molded body can, for example, have a solid rectangular, oval, or elliptical shape.For a solid rectangular cross-section with short sides of length a and long sides b = 1.25 x a, the mass of the elastomeric material of the elastomeric spring has a mean distance to its center of mass that is exactly 25% greater in the first direction transverse to the distance and along the long sides than in the second direction transverse to the distance and along the short sides. At b = 1.5 x a, the mean distance in the first direction is exactly 50% greater than the mean distance in the second direction, and at b = 2 x a, the mean distance in the first direction is 100% greater than the mean distance in the second direction.

[0024] The non-circular cross-section of the elastomer spring of the at least one molded body allows for additional variations in the damper's natural frequencies in the vibration damper according to the invention. The at least one of the molded bodies can be oriented relative to the damper mass and the damper base such that the first direction of its elastomer spring runs along the main axis of the mass. In this case, the non-circular elastomer spring supports the damper mass less rigidly transversely to the main axis than along it. Accordingly, the damper's natural frequency for vibrations of the damper mass transversely to the main axis is lower, and the damper's natural frequency for vibrations of the damper mass along the main axis is higher, than when the first direction of the elastomer spring of the at least one of the molded bodies runs transversely to the main axis.

[0025] In a specific embodiment of the vibration damper according to the invention, all shaped bodies have an elastomer spring with a non-circular cross-section, as defined above. The first directions of all elastomer springs can then run parallel to each other, and in particular, all along the main axis of mass or all transverse to the main axis of mass. In principle, the first directions can also run obliquely at an acute angle to the main axis of mass. In this case, however, a mirror-symmetrical arrangement of the non-circular cross-sections with respect to the virtual transverse center plane of the vibration damper, which runs transversely to the main axis of mass, is preferred.

[0026] The damper base of the vibration damper according to the invention can have a hat-shaped support in a longitudinal section along the main axis of the mass, which encloses the damper mass on three sides with its hat profile. If the vibration damper according to the invention is designed as a vibration damper for a rear panel of a motor vehicle, it is preferably provided for mounting on the tailgate in such a way that the support of the damper base is located in front of the damper mass in the closing direction of the tailgate and thus supports the inertial forces that become effective when the tailgate closes or when the tailgate decelerates rapidly at the end of its closing action without overloading the elastomer springs.

[0027] Advantageous further developments of the invention result from the patent claims, the description and the drawings.

[0028] The advantages of features and combinations of features mentioned in the description are merely exemplary and can have an effect alternatively or cumulatively, without the advantages necessarily having to be achieved by embodiments according to the invention.

[0029] Regarding the disclosure content—not the scope of protection—of the original application documents and the patent, the following applies: Further features can be derived from the drawings—in particular, the geometries depicted and the relative dimensions of several components to one another, as well as their relative arrangement and functional connection. The combination of features from different embodiments of the invention or from features of different claims is also possible, deviating from the chosen cross-references of the claims, and is hereby encouraged. This also applies to features that are illustrated in separate drawings or mentioned in their description. These features can also be combined with features from different claims.Likewise, features listed in the patent claims may be omitted for further embodiments of the invention, but this does not apply to the independent patent claims of the granted patent.

[0030] The features mentioned in the claims and the description are to be understood, with regard to their number, as meaning that exactly that number or a greater number than the stated number is present, without the need for the explicit use of the adverb "at least". Thus, for example, if a single-piece damping mass is mentioned, this is to be understood as meaning that exactly one single-piece damping mass, two (at least not rigidly coupled) single-piece damping masses, or more (at least not rigidly coupled) single-piece damping masses are present. The features listed in the claims may be supplemented by further features or may be the only features that the subject matter of the respective claim possesses.

[0031] The reference numerals contained in the patent claims do not constitute a limitation of the scope of the subject matter protected by the patent claims. They merely serve the purpose of making the patent claims easier to understand. BRIEF DESCRIPTION OF THE FIGURES

[0032] The invention will now be further explained and described with reference to preferred embodiments shown in the figures. Fig. Figure 1 shows a vibration damper according to the invention in a perspective view. Fig. 2 shows from the same perspective as Fig. 1 a damper base of the vibration damper according to Fig. 1. Fig. 3 shows from the same perspective as Fig. 1 a damping mass of the vibration damper according to Fig. 1. Fig. Figure 4 shows two shaped bodies made of elastomer material of the vibration damper according to Fig. 1 in two different perspective views and one opposite the Fig. 1 to 3 scales increased. Fig. 5 shows the two shaped bodies according to Fig. 4 in two side views rotated 90° to each other. Fig. 6 is a cross-section through one of the shaped bodies according to the Fig. 4 and Fig. 5 lengthwise in a in Fig. 5. Section line VI-VI shown at a further enlarged scale. Fig. 7 is a top view of the vibration damper according to Fig. 1 with a view to its retarder base according to Fig. 2 in one opposite the Fig. 1 to 3 reduced scale; and Fig. 8 is a cross-section through the vibration damper according to the Fig. 1 and Fig. 7 along a in Fig. 7 drawn section line VIII-VIII in a opposite Fig. 7 enlarged scale. FIGURE DESCRIPTION

[0033] The in Fig. 1 and Fig. The vibration damper 1 shown in Figure 7 comprises a damper base 2, a damper mass 3, and several elastomer springs 4 that elastically support the damper mass 3 on the damper base 2. The damper base 2 is designed for attachment to a functional component (not shown) whose vibrations are to be dampened by the vibration damper 1 and which could, for example, be the tailgate of a motor vehicle. For attachment to the functional component, the damper base has a mounting hook 5 and mounting holes 6 and 7. Between these mounting holes 6 and 7, the damper base 2 includes a hat-shaped support 8 that encloses the damper mass on three sides in one plane. The entire damper base 2 can be formed by a simple sheet metal part. Stops for the damper mass 3 (not shown in the figures) can project from the support 8, limiting its deflection relative to the damper base 2 from the plane defined by the support 8.

[0034] In the middle section of carrier 8, the Fig. 2 separately shown damper base 2 four support configurations 9 in the form of mounting eyes 10 into which according to Fig. 1. Each of four shaped bodies 11 made of elastomer material 12 is attached at its base. Four parallel through holes 14 are located opposite the four support configurations 9 at a distance 13. Fig. The damper mass 3 is formed by means of three separately shown components. The edge-closed through-holes 14 have a stepped profile through the damper base 3 with a radially inwardly directed offset 15, see [reference]. Fig. 8. The shaped bodies 11 are connected to the through holes 14 on the mass side and are inclined at the offsets 15 in the direction of the distance 13. The through holes 14 are aligned parallel to each other and run in a longitudinal median plane of the damper mass 3 orthogonally to a main mass axis 16. Along the main mass axis 16, the damper mass 3 is elongated such that its length along the main mass axis 16 is more than ten times the side length of its square cross-section. The sides of the cross-section of the damper mass 3, which runs transversely to the main mass axis 16, run in pairs parallel to the distance 13 and perpendicular to it. The damper mass 3 is a single, continuous shaped body 17 made of metal with a uniform composition throughout its entire volume. The four through holes 14 in the damper mass 3 are identical, as are the connection configurations 9 of the damper base 9 opposite them.

[0035] In the present case, all four shaped bodies 11 with their elastomer springs 4 are also included, of which in Fig. 4 and Fig. 5, where two are shown from different angles, are identically designed. However, this is no more necessary than the requirement that all four pairs of through holes 14 and connection configurations 9 are fitted with shaped bodies 11. Furthermore, in the preferred embodiment of the vibration damper 1 according to the invention shown, the elastomer springs 4 are not round in cross-section transverse to the distance 13, see Fig. 7, with its greatest extent perpendicular to the distance 13, which in Fig.7 runs from left to right, preferably either along the main axis of the mass 16 or transversely to it, in order to set different damping natural frequencies in the vibration directions of the damping mass 3 relative to the damping base 2, both along and transversely to the main axis of the mass 16. In particular, the spread of these two damping natural frequencies, i.e., the distance between these two damping natural frequencies, can also be varied by the orientation of the non-circular cross-sections of the elastomer springs 4. REFERENCE MARK LIST 1 vibration damper 2. Rebate base 3. Tuning mass 4 elastomer springs 5 mounting hooks 6 mounting holes 7 mounting holes 8 carriers 9 Support configuration 10 Mounting eye 11 Molded parts 12 Elastomer material 13 distance 14 Through hole 15 Jump 16 Main mass axis 17 metal molded bodies QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] DE 10 2016 115 782 B4

[0003] DE 2017 127 840 B4

[0003] WO 2001 / 092752 [0004, 0007] WO 2013 / 167524 A1

[0005] EP 3 524 845 A1 [0006, 0007]

Claims

[1] Vibration damper (1) for reducing vibrations of a functional component with - a damper base (2) which is to be fixed or formed on the functional component and which has at least three identically formed support configurations (9), - a one-piece damping mass (3) having at least three identically designed parallel through holes (14) which are each opposite one of the at least three support configurations (9) at a distance (13), and - several shaped bodies (11) manufactured separately from the damping mass (3) and the damping base (2), each comprising an elastomer spring (4) which elastically supports the damping mass (3) on the damping base (2), - wherein the shaped bodies (11) are each fixed on one side to one of the support configurations (9) of the damper base (2) and on the other side in the respective opposite through hole (14) of the damper mass (3),characterized by , that the damping mass (3) is elongated along a virtual main mass axis (16), wherein all of the at least three through holes (14) are perpendicular to the main mass axis (16). [2] Vibration damper (1) according to claim 1, - wherein the at least three through holes (14) are arranged at equal intervals along the main mass axis (16) and / or - wherein at least four through holes (14) are arranged along the main mass axis (16). [3] Vibration damper (1) according to any one of the preceding claims, - wherein the damping mass (3) has a constant outer circumference around the main mass axis (16) over its extension along the main mass axis (16) and / or - wherein an outer circumference of the damping mass (3) with a rectangular cross-section around the main axis of the mass (16) has a side length ratio between 1:1.5 and 1.5:1 or between 1:1.2 and 1.2:1 and preferably 1:

1. [4] Vibration damper (1) according to any one of the preceding claims, - wherein all shaped bodies (11) are identically formed and / or - wherein one of the several shaped bodies (11) is specified at each of the at least three support configurations (9) and in each of the at least three through holes (14). [5] Vibration damper (1) according to any one of the preceding claims, - wherein each of the at least three through holes (14) is closed at the edges and / or - wherein each of the at least three through holes (14) has a stepped progression through the damping mass (3). [6] Vibration damper (1) according to any one of the preceding claims, - wherein each of the at least three through holes (14) has a non-circular cross-section and / or - wherein each of the at least three support configurations (9) has a mounting eye (10) which optionally has a non-circular cross-section. [7] Vibration damper (1) according to one of the preceding claims, wherein at least one of the molded bodies (11) has a non-circular base-side connection configuration and / or a non-circular mass-side connection configuration, wherein, optionally, at least one of the two connection configurations is formed on a hard plastic part body of the at least one of the molded bodies (11) to which the elastomer spring (4) is attached. [8] Vibration damper (1) according to one of the preceding claims, wherein at least one of the shaped bodies (11) has an elastomer spring (4) with a non-circular cross-section, wherein the mass of an elastomer material (12) of the elastomer spring (4) has a mean distance (13) to its center of mass that is at least 25% and preferably at least 50% greater in a first direction transverse to the distance (13) of the respective through hole (14) to the respective support configuration than in a second direction transverse to the main axis. [9] Vibration damper (1) according to claim 8, - wherein at least one of the shaped bodies (11) is oriented relative to the damper mass (3) and the damper base (2) such that the first direction of its elastomer spring (4) runs longitudinally or transversely to the main mass axis (16) and / or - wherein all shaped bodies (11) have an elastomer spring (4) with a non-circular cross-section, wherein the mass of an elastomer material (12) of the elastomer spring (4) has a distribution in a first direction transverse to the distance (13) of the respective through hole (14) to the respective support configuration that is at least 25% and preferably at least 50% wider than in a second direction transverse to the main axis, wherein, optionally, the first direction of all elastomer springs (4) is parallel to each other. [10] Vibration damper (1) according to one of the preceding claims, wherein the damper base (2) has a hat-shaped support (8) in a longitudinal section along the main axis (16) of the mass, which surrounds the damper mass (3) on at least three sides.

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