Vibration damper

Abstract

Vibration absorbers (10, 10') with the following features: - a base section (12) for attachment to a vibration source (50), in particular a vehicle body; - at least one spring section (14) with two end regions (16a, 16b) which is fixed to the base section (12) via at least one holder (18, 18a, 18b); and - at least one absorber mass (20) for absorbing vibration energy from the vibration source (50); - characterized in that the damper mass (20) has at least one through-opening (22) through which the spring section (14) extends, wherein - the spring section (14) is pressed into the through opening (22) in the damper mass (20).

Description

[0001] The invention relates to a vibration damper or a damping device according to the preamble of claim 1, which is intended for attachment to a vibration source, in particular a vehicle body, in order to dampen oscillations or vibrations that can arise from the movement of the vibration source, for example, on a road, or from activities of the vibration source itself, such as engine vibrations. Such a vibration damper comprises a base section for attachment to the vibration source, a spring section, and an absorber mass for absorbing vibration energy from the vibration source.

[0002] A prior art vibration damper is known, for example, from US 11 193 552 B2. In this vibration damper, a damper mass, referred to therein as a vibration body, is secured to a base section with respective holding geometries designed as springs at its ends. The base section is to be secured to the vibration source, such as the vehicle body. The springs engage the ends of the damper mass and extend in the same direction as the main direction of extension of the damper mass. This prior art vibration damper requires various assembly steps and more complex individual parts. Furthermore, the problem can arise that the springs holding the damper mass break. The damper mass can then move freely and become a hazard.

[0003] It is the object of the present invention to provide a vibration damper which is simple in design, can be installed cost-effectively and can, in principle, also be used in difficult space conditions.

[0004] According to the invention, a vibration damper has the features listed in claim 1 and thus also a base section for attachment to a vibration source, in particular a vehicle body. At least one spring section with two ends is provided, which is held on the base section by at least one holder. At least one damper or flywheel mass for absorbing vibration energy from the vibration source is arranged on the base section. The damper mass has at least one through-opening through which the spring section extends. The spring section preferably extends transversely to the main direction of extension of the damper mass. According to the invention, the spring section is pressed into the through-opening in the damper mass.

[0005] Furthermore, the damper mass can be formed with a recess at one, preferably at two or both end regions of the damper mass. These recesses can also be continuous, like the through openings, or can also be formed only to the extent that they allow the installation of a spring section.

[0006] In this way, the spring section can be held at both ends via the holder, whereby the spring section passes through the through opening or the recess in the absorber mass, so that the absorber mass can oscillate freely, dampened by the spring section, in order to absorb vibration energy and thus defuse disturbing vibrations.

[0007] The spring section preferably has a cylindrical or, in particular, oval to elliptical shape, the end regions of which have respective receiving contours into which the holder engages, wherein the spring section is preferably made of a permanently elastic material.

[0008] The end areas of the spring section feature the receiving contours or engagement geometries into which the retaining geometries of the bracket engage. The connection can be achieved by compression, whereby the spring section can be pressed into the continuous opening of the damper mass.

[0009] In this case, the holding geometries of the holder, which is provided on the base section, are preferably designed in the manner of a pair of pliers, so that the end regions of the spring section can be pressed into the preferably pliers-like holding geometries.

[0010] The base section can have two or more mounts for holding respective spring sections. The number of mounts and the number of spring sections can be coordinated with the number of through-holes in the damper mass. Multiple damper masses can also be provided, each with separate spring sections, whereby the spring sections and the damper masses can be designed to dampen different vibration ranges. This means, for example, that two or three damper masses of different masses can be provided on one base section, which are attached to the base section by means of adapted spring sections in order to be optimized for different vibrations in different frequency ranges, thus achieving improved damping.

[0011] The base section can have at least one mounting geometry that penetrates the damper mass without contact and is preferably at least partially provided with a permanently elastic surface layer. Thus, in the event of extreme deflections of the damper mass, which could lead to contact with the mounting geometry or the base section, the permanently elastic surface layer can prevent hard contact, which could cause an unpleasant impact noise.

[0012] The design of the base section, combined with the damper mass and the bolted connection to the vehicle, creates a captive connection. This means that even in the event of elastomer failure (spring tears), the damper mass is held in place and cannot fall off. This means that even if one or more (all) spring sections break, the base section's mounting geometry holds the damper mass firmly to the vibration source or the vehicle, preventing the damper mass from becoming a source of danger.

[0013] The spring section, which is pressed into the opening in the damper mass, is advantageously equipped with a constriction area, for example, centrally located on the outer circumference of the cylindrical spring section. After the press-in process, the damper mass rests securely on the spring section, and even strong impacts or vibrations that can occur when a vehicle drives over a road with potholes cannot impair the connection between the spring section and the damper mass.

[0014] Advantageously, the spring section is preferably provided with a hollow space at each of its two ends, which facilitates the deformation of the spring section, i.e., its reversible deformation, during the compression process. The hollow space can be cylindrical and can extend approximately to just before the constriction of the spring section. The spring section can be provided with reinforcement areas at its ends, which can provide the advantage that the holding geometries of the bracket enable a stronger fixation of the spring section and thus of the damper mass.

[0015] The present invention will be explained in more detail below using preferred embodiments with reference to the accompanying figures. The same reference numerals are used for functionally identical parts throughout the embodiments, so that a repeated description of identical components of the vibration damper according to the invention is unnecessary. The figures show: Fig. 1 a perspective view of an embodiment of a vibration damper according to the invention, Fig. 2 a spring section in a perspective view, Fig. 3 a further embodiment in a perspective view, Fig. 4 a longitudinal section through the Fig. 3 shown embodiment, which is held on a vibration source, Fig. 5 a base section of the further embodiment according to the Fig. 3 and Fig. 4 in a perspective top view, Fig. 6 the absorber mass of the further embodiment according to Fig. 3 and following in a perspective view, Fig. 7 a mounting arrangement of the embodiment according to Fig. 3 and following in a partly sectioned, partly perspective view, Fig. 8 a sectional perspective view of a spring section in its mounting position with respect to the damper mass and with respect to the mounting on the base section, and Fig. 9 is a perspective top view of an additional embodiment according to the invention.

[0016] The Fig. 1 shows an embodiment according to the invention, in which a vibration damper 10 according to the invention is shown in a perspective view.

[0017] The vibration damper 10 has a base section 12, which can be secured to a vibration source, such as a vehicle body, via fastening devices 24a, 24b, such as screw bolts. Reference to a vibration source or vehicle body can also refer to a part of the vehicle body, such as a tailgate, a door, a vehicle headliner, or the like.

[0018] A holder 18 is provided on the base section 12, which holder has two holding geometries 18a, 18b, by means of which a spring section 14 is held at its two ends 16a, 16b. The spring section 14 has respective engagement geometries 32 at its two end regions 16a, 16b, which are preferably cylindrically symmetrical and into which the holding geometries 18a, 18b of the holder 18 can engage. The holding geometries 18a, 18b are preferably designed in a pincer-like manner, with opposing wings provided on the holding geometries 18a, 18b, which engage in a pincer-like manner into the engagement geometries 32 of the spring section 14.During assembly of the spring section 14 on the holding geometries 18a, 18b, the end regions 16a, 16b of the spring section 14 are pressed into the pincer-like wings, whereby the preferably cylindrical cavities 26 at the two end regions 16a, 16b of the spring section 14 support a reversible deformation of the end regions 16a, 16b.

[0019] It should be noted that the spring section 14 extends substantially perpendicular to the main extension direction of the damper mass 20. The spring properties of the spring section 14 are utilized perpendicular to the main extension direction of the spring section 14. The spring section 14 is preferably used as a type of plate spring.

[0020] Since the spring portion 14 is made of a flexible material, such as rubber, latex, a softer plastic material or the like, such as by injection molding or the like, the spring portion 14 will return to its original shape after deformation in order to achieve a firm mechanical connection between the spring portion 14 and the holder 18.

[0021] The spring section 14 can be designed to be non-rotationally symmetrical, resulting in different damping properties in different spatial directions. This allows combinations of damper properties to be set in the three spatial directions X, Y, Z and / or mode ratios. For example, one damper mode can vary to one or more additional damper modes (1st mode = X: 20 Hz, 2nd mode = Z: 30 Hz). By structurally modifying the spring section 14, it is possible to design the vibration system so that the vibration displacements in the plus and minus directions are equal. To achieve this, the weight of the damper mass in conjunction with the stiffness of the spring section 14 must be appropriately maintained within the spring section.

[0022] Before the spring section 14 is secured to the bracket 18, a damper mass 20 is connected to the spring section 14. The damper mass 20 has a through-opening 22 into which the spring section 14 is pressed. After assembly of the illustrated vibration damper 10, the damper mass 20 is mounted on the spring section 14 at a distance from the base section 12 and can oscillate freely, for example, to dampen vibrations. The retaining geometries 18a, 18b hold the spring section 14 at its end regions 16a, 16b at a sufficient distance from the base section 12.

[0023] In the Fig. 2 shows a perspective view of the advantageously cylindrical spring section 14, as it is in the embodiment according to Fig. 1, but also in the further embodiment. The spring section 14 has engagement geometries 32 at its ends, which are intended to serve as receiving contours for the holding geometries 18a, 18b according to Fig. 1. Corresponding engagement geometries 32 are provided at both end regions 16a, 16b of the spring section 14. A cavity 26, also provided at both end regions 16a, 16b of the spring section 14, facilitates the pressing of the spring section 14 during the assembly of both the damper mass 20 to the spring section 14 and the end regions 16a, 16b of the spring section 14 to the holding geometries 18a, 18b of the embodiment according to Fig. 1 and the further embodiments according to the following Fig. 3 and following. A constriction region 14a in the center of the cylindrically symmetrical spring section 14 serves to secure the damper mass 20 in a predetermined position on the spring section 14. The cavities 26 at both end regions 16a, 16b of the spring section 14 are also useful for the necessary compression of the spring section 14. After all compression processes, the reversibly deformed regions of the spring section 14 return to their original shape, thus enabling a firm, albeit not irreversible, mechanical connection between the individual components of the vibration damper 10 according to the invention.

[0024] A further embodiment of a vibration damper 10' according to the invention is shown in Fig. 3 in a perspective view. In principle, the components that correspond to the first embodiment according to Fig. 1 correspond to the components shown here.

[0025] In the vibration damper 10', only two spring sections 14 are provided, and between these spring sections 14 extends an elongated damper mass 20, wherein the base section 12 is also longitudinally extended in the same way. In the two through openings 22 provided at the respective ends of the damper mass 20, respective spring sections 14 are provided, which can be of similar or identical design, as shown in Fig. 2 shown.

[0026] The damper mass 20 has two mounting recesses 30 through which mounting cups 28 extend, which are components of the base section 12.

[0027] The mounting pots 28 have mounting openings 29 through which fastening devices 24a, 24b according to Fig. 1 to connect the entire assembly of the vibration damper 10' to a vibration source. A gap is naturally provided between the mounting recess 30 of the damper mass 20 and the mounting cup 28 so as not to impair the free vibration of the damper mass 20.

[0028] In Fig. 4, an assembly situation of the vibration damper 10' in relation to a vibration source 50, such as a vehicle body, can be considered. Here, fastening devices 24a, 24b are schematically shown above the mounting pots 28, such that they hold the damping device 10' to the vibration source 50. The sectional view shows how the spring section 14 is oriented in the through opening 22 in the damper mass 20 without any spacing. As can be seen, the spring section 14 does not necessarily have to be round in cross-section, but can also be oval in shape. The seat of the spring section 14 within the through opening 22 of the recess 23 is at the constriction area 14a of the spring section 14 according to Fig. 2 located.

[0029] The Fig. Figure 5 shows the base section 12 of the vibration damper 10' according to the further embodiment. Here, the pincer-like design of the mount 18 with its two holding geometries 18a, 18b can be seen separately. A permanently elastic surface layer 28a can be formed on the mounting cups 28, which can prevent hard contact between the damper mass 20 and the base section 12, of which the mounting cup 28 is a part, in the event of heavy impacts, such as when a vehicle drives through a pothole.

[0030] The holder 18 can, of course, also be designed differently. For example, the holder 18 can be designed as an angled sheet metal piece with an eyelet through which an end region 16a or 16b is pressed. Each end region 16a, 16b of the spring section 14 is then assigned a corresponding angled sheet metal wing with an opening or eyelet (not shown).

[0031] Fig. 6 shows a perspective view of a damper mass 20 and in particular the through openings 22 at the two ends of the elongated damper mass 20. The through openings 22 have contours which enable an improved hold of the spring section 14, in particular via its constriction area 14a, on the damper mass 20. Furthermore, according to Fig. 6 the mounting recesses 30 can be seen again separately.

[0032] According to Fig. 7 shows a partial sectional view that between the inner surface of the mounting recess 30 and the outer surface of the mounting pot 28, which is provided here by a permanently elastic surface layer 28a, there is a gap which allows free vibrations of the damper mass 20.

[0033] According to Fig. 8 shows again in detail the position of the spring section 14 relative to the damper mass 20 and relative to the base section 12 and its holders 18 or the holding geometries 18a, 18b.

[0034] The damper mass 20 has a surface such that a firm contact can be provided between the constriction region 14a of the spring section 14 and the damper mass 20. The through opening 22 is provided with a bulge in the region of the constriction region 14a of the spring section 14, so that a good mechanical connection can be achieved between the spring section 14 and the damper mass 20 in the longitudinal direction of the spring section 14, i.e., its main extension direction.

[0035] The spring section 14 can be made of a permanently elastic material, while the base section 12 could be stamped from a sheet steel, for example. The damper mass 20 is preferably made of a heavy material in order to provide a high weight for absorbing vibration energy in the smallest possible space.

[0036] The shape and weight of the damper mass 20 can be modified to any desired shape. Adapting the spring section 14 (stiffness adjustment, shape / Shore hardness) provides a highly advantageous system. The spring section 14 can thus be used as a modular solution, meaning that several different spring sections 14, base sections 12, etc. can be prepared and combined as needed.

[0037] The design frequency and vibration shapes can be set at the typical frequencies of approximately 10 Hz, 15-200 Hz, or 200 Hz. High-frequency natural frequencies up to 1500 Hz can also be at least partially damped in special cases.

[0038] The fact that the spring section 14 is a separate component, which is woven into the damper mass 20 around the base section 12 after vulcanization, results in advantages in processing time. Furthermore, there is no need to heat the relatively heavy damper masses in the vulcanization tool, so the vulcanization time can be significantly shortened. Furthermore, energy (heating the mass) is saved.

[0039] By means of the constriction area 14a on the spring section 14, which serves to tie the spring section 14 into the damper mass 20 using a tie-in tool, a correct position can be ensured so that incorrect installation for the provision can be excluded.

[0040] In the Fig. 9 illustrates an additional embodiment of a vibration damper 10" according to the invention. Here, the damper mass 20' is formed by the respective base sections 12, as shown in Fig. 1, via spring sections 14 (see Fig. 2). The damper mass 20' is provided with recesses 23 at both end regions 21 of the damper mass 20'. The recesses 23 are preferably continuous, thus corresponding to the continuous openings 22 according to the above embodiments. However, the recesses 23 may also be non-continuous, so that a pressing in of the spring section 14 and its holder, as for example in Fig. 1. In this case, a clear view of the end region 16a, 16b of the spring section 14, which is accommodated in the recess 23, would be blocked. Of course, in this embodiment, too, the construction with the mounting cup 28 and the mounting recess 30 of the further embodiment according to the Fig. 3 to 8 should be used accordingly, especially to ensure that they are also protected against loss. List of reference symbols 10, 10', 10" vibration absorbers 12 Base section 14 spring section 14a Constriction area 16a, 16b end areas 18 Bracket 18a, 18b Holding geometry 20, 20' absorber mass 21 Final region 22 continuous opening 23 Recess 24a, 24b Fastening device 26 cavity 28 mounting pot 28a permanently elastic surface layer 29 Mounting opening 30 Mounting recess 32 engagement geometries, receiving contours 50 Vibration source, vehicle body

Claims

[1] Vibration absorbers (10, 10') with the following features: - a base section (12) for attachment to a vibration source (50), in particular a vehicle body; - at least one spring section (14) with two end regions (16a, 16b) which is fixed to the base section (12) via at least one holder (18, 18a, 18b); and - at least one absorber mass (20) for absorbing vibration energy from the vibration source (50); - characterized by that the damper mass (20) has at least one through opening (22) through which the spring section (14) extends, wherein - the spring section (14) is pressed into the through opening (22) in the damper mass (20). [2] Vibration damper (10, 10') according to claim 1, characterized byin that the spring section (14) has a preferably cylindrical, or in particular oval to elliptical shape, the end regions (16a, 16b) of which have respective engagement geometries (32) into which the holder engages via holding geometries (18a, 18b), wherein the spring section (14) is preferably made of a permanently elastic material. [3] Vibration damper (10, 10') according to one of claims 1 or 2, characterized by that the holder (18) has holding geometries (18a, 18b) assigned to the respective end regions (16a, 16b) of the spring section (14), which can be brought into engagement with the engagement geometries (32) at the end regions (16a, 16b) of the spring section (14). [4] Vibration damper (10, 10') according to claim 3, characterized by that the holding geometries (18a, 18b) result in a pincer-like formation. [5] Vibration damper (10, 10') according to one of the preceding claims, characterized bythat the base portion (12) has two or more holders (18) for holding respective spring portions (14). [6] Vibration damper (10, 10') according to one of the preceding claims, characterized by that a plurality of spring sections (14) are provided which are held by respective holders (18) and which hold a damper mass (20). [7] Vibration damper (10, 10') according to one of the preceding claims, characterized by that the base section (12) has at least one fastening geometry (28, 28a) which penetrates the absorber mass (20) without contact and is preferably at least partially provided with a permanently elastic layer (28a). [8] Vibration damper (10, 10') according to one of the preceding claims, characterized by that the through opening (22) ends in a recess (23) in the damper mass (20), so that a clear view of an end region (16a, 16b) of the spring section (14) is not obstructed. [9] Vibration damper (10, 10') according to one of the preceding claims, characterized by that the spring section (14) is pressed into the holding geometries (18a, 18b) on the base section (12). [10] Vibration damper (10, 10') according to one of the preceding claims, characterized by that the spring section (14) is provided with a cavity (26) at its two end regions (16a, 16b). [11] Vibration damper (10, 10') according to one of the preceding claims, characterized by that the spring section (14) is formed with reinforcing regions at its end regions (16a, 16b). [12] Vibration damper (10'') according to one of claims 1 to 11, characterized by that the damper mass (20') is formed at end regions (21) with a recess (23) into which respective spring sections (14) extend. [13] Vibration damper (10'') according to claim 12, characterized bythat respective holding geometries (18a, 178b) extend into the preferably continuous recesses (23) in order to hold a respective end region (16a, 16b) of a spring section (14).

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