EP3516260A1

EP3516260A1 - Shaft bearing

Info

Publication number: EP3516260A1
Application number: EP17755155.3A
Authority: EP
Inventors: Markus Dürre; Christian Paul
Original assignee: Vibracoustic SE
Current assignee: Vibracoustic SE
Priority date: 2016-09-26
Filing date: 2017-08-16
Publication date: 2019-07-31
Also published as: KR102373696B1; KR20190053860A; WO2018054620A1; DE102016118157A1; DE102016118157B4; CN109790893A; US20190264739A1; US10876574B2

Abstract

The present invention relates to a shaft bearing (10), comprising an inner body (16), an outer body (12) surrounding the inner body (16) at a distance, and an elastomer body (20) which elastically connects the inner body (16) to the outer body (12). The invention is characterized in that the elastomer body (20) has a damping device (28).

Description

Welienlager

The present invention relates to a Welienlager having an inner body, a surrounding the inner body at a distance outer body and an elastomeric body, which connects the inner body and the outer body elastically with each other.

Shaft bearings of the type mentioned are used for supporting a propeller shaft of a motor vehicle. The shaft bearing serves to keep the Kardanwelte exactly in position during the ferry operation and to compensate for axial displacements during start-up and braking. In addition, the Welien bearing isolates noise and dampens the resonance frequencies and wobble of the cardan shaft.

For this purpose, the shaft bearing is coupled via the inner body to the propeller shaft, so that vibrations of the propeller shaft are introduced into the shaft bearing.

As a result, the elastomer body begins to vibrate and dampens and / or isolates the vibrations introduced into the Welienlager. About the outer body, the fixing of the shaft bearing takes place on a motor vehicle part, in particular the motor vehicle body.

EP 2 690 305 B1 discloses a shaft bearing which has an outer body and an inner body arranged concentrically with the outer body, wherein the outer body and the inner body are connected to one another by means of an annular, elastic spring element.

Furthermore, DE 101 26 016 A1 discloses a shaft bearing which has a rolling bearing with an outer body, which is enclosed on the outer peripheral side by a retaining ring with a radial distance, wherein in the gap formed by the gap at least one in the axial and radial direction elastically yielding spring - body is arranged. The outer body is relatively unverd rehbar with a

Vibration damper connected.

The dynamic stiffness of a shaft bearing increases significantly as soon as the elastomeric body vibrates in a flexible eigenmode containing larger mass motions in the relevant direction. This increased stiffness can adversely affect the decoupling function of the bearings in the high-frequency range.

The invention has for its object to provide a shaft bearing having an improved rigidity.

To solve the problem, a shaft bearing with the features of claim 1 is proposed.

Advantageous embodiments of the shaft bearing are the subject of the dependent claims.

According to a first aspect of the invention, the shaft bearing comprises an inner body, an outer body surrounding the inner body at a distance, and an elastomer body elastically connecting the inner body and the outer body with each other, wherein the elastomer body has an eradicator.

When the elastomeric body is excited to vibrate, the eradicator acts as a damper and reduces mass movement in the elastomeric body while the eradicator vibrates strongly. As a result, the rigidity, in particular the dynamic rigidity, of the shaft bearing in the target frequency range, which corresponds to the resonance frequency of the eradicator, can be reduced. Thus, the shaft bearing also has a sufficient decoupling function in the high-frequency range. In addition, the mass and the frequency of the erosion device can be easily adjusted to the problem area of the elastomeric body of the shaft bearing by means of the finite element method. In addition, with a large mass of the repayment device, the dynamic stiffness can be deliberately lowered in a desired frequency range below the natural level, so that an approximately "bathtub shape" of the dynamic Sieifigkestskurve arises. The shaft bearing can also be referred to as a propeller shaft bearing.

The inner body may be an inner ring or an outer ring of a rolling bearing which rotatably supports a propeller shaft. A formed as Snnenring inner body is preferably vulcanized into the elastomeric body. About the inner ring of the elastomeric body on a rolling bearing, which supports a propeller shaft rotatably, be set. The inner ring causes a uniform surface pressure on the roller bearing and thus a uniform force transmission from the rolling bearing to the shaft bearing. If the inner body is an outer ring of a roller bearing, the elastomeric body is preferably bonded to the inner body in a materially bonded manner.

The outer body may be an outer ring or a bearing carrier. About the bearing carrier, the attachment of the shaft bearing takes place on a motor vehicle part. A trained as an outer ring outer body is advantageously vulcanized into the elastomeric body. About the outer ring of the elastomeric body can be fixed to a bearing carrier. If the outer body is a bearing carrier, the elastomeric body is preferably fixed non-positively to the bearing carrier. For this purpose, the elastomeric body may be fixed by means of a securing ring on the bearing carrier.

In an advantageous embodiment, the repayment device is designed as a one-shot oscillator. As a result, the eradication device acts as an additional mass on the elastomeric body and reduces its mass movements during a swing of the elastomer body, while the one-shot oscillates strongly.

In an advantageous embodiment, the repayment device is materially connected to the elastomeric body. As a result, the attachment of the eradication device can be carried out almost cost-neutral, since the preferred material content of the eradication device at the product sales price is very low. Preferably, the repayment device is of the same material and connected in one piece with the elastomeric body. In an advantageous embodiment, the elastomeric body has at least one circumferential fold, wherein the eradication device is connected to the at least one fold. The at least one fold can accommodate an axial and / or radial deflection of the inner body relative to the outer body. In addition, a fold is easily deformable and thus forms an expansion or crumple zone of the spring element, which can absorb tensile or compressive stresses. The at least one fold can be rotationally symmetrical or not rotationally symmetrical. The elastomeric body may furthermore have two folds, which preferably form a circumferential cavity. In addition, a stop buffer may be arranged in the cavity. About the stop buffer, a roller bearing can be supported elastically on the bearing bracket. When the elastomeric body has two folds, each of the folds may have an eradicator. Furthermore, only one of the wrinkles can have an eradication device.

In an advantageous embodiment, the repayment device is connected to the elastomer body such that it is arranged outside the force flow occurring in the elastomeric body. In particular, the repayment device is arranged parallel to the force flow. Since the eradicator is outside the power flow, the vibrated elastomer body is calmed by the eradicator vibrating. The force flow occurring in the elastomeric body extends from the inner body via the elastomer body, in particular the at least one fold, to the outer body. Preferably, the repayment device is connected to the fold such that it is arranged outside the force flow occurring in the fold.

In an advantageous embodiment, the repayment device is formed from an elastomer. Since the eradication device is made of the same material as the elastomer body, the eradication device can be produced virtually free of cost since its material content to the elastomer body is low. Furthermore, the eradication device can be formed from a metal or plastic.

In an advantageous embodiment, the repayment device has an annular structure which is connected to the elastomeric body. In particular, the annular structure is preferably a closed ring structure. The annular structure is preferably connected to the fold, wherein a central axis of the annular structure extends concentrically to a central axis of the shaft bearing.

In an advantageous embodiment, the eradication device has tabs which are connected to the elastomer body. The lobes can be tuned differently, so that different frequencies or directions can be eradicated. When tuning as a tuning set, which corresponds to an incremental increase, the tabs can increase the broadband of the absorber. Advantageously, the tabs, in particular perpendicular, protrude from the elastomeric body. The flaps are preferably arranged at equidistant distances from one another on the elastomer body.

In an advantageous embodiment, the elastomeric body has at least two radial webs, wherein the eradication device is connected to the radial webs. At least one tab is advantageously connected to each of the radial webs. The radial webs connect a radially inner elastomeric section with a radially outer elastomeric section.

In an advantageous embodiment, at least one mass element is embedded in the eradication device. By embedding a mass element, which can also be referred to as an insert, the effective mass of the eradication device can be significantly increased without thereby increasing the production costs disproportionately. The mass element may be made of plastic or metal. The mass element may be formed as a ring. Preferably, a mass element designed as a ring is used in an erosion device designed as an annular structure. If the eradication device is formed from a plurality of lobes protruding from the elastomeric body, at least one mass element may be embedded in each of the lobes or, for example, only in every second lobe or only in one lobe.

In an advantageous embodiment of the elastomeric body is cohesively and / or non-positively connected to the inner body and / or the outer body. Thus, the elastomeric body may be pressed into the gap formed between the inner body and the outer body. Furthermore, the elastomeric body radially externally on the inner body and radially inwardly on the outer body cohesively connected, in particular vulcanized be. The inner sleeve and / or the outer sleeve can furthermore be vulcanized into the elastomeric body. In a cohesive connection, the inner sleeve and / or the outer sleeve is preferably provided with openings, which are penetrated by the elastomer of the elastomeric body.

Hereinafter, the shaft bearing and other features and advantages will be explained with reference to exemplary embodiments, which are shown schematically in the figures. Hereby show:

Fig. 1 is a perspective view of a world camp according to a first

Embodiment with a partial cutout;

FIG. 2 shows a perspective view of a cross section through the elastomer body shown in FIG. 1 with the eradication device according to a first embodiment; FIG.

Fig. 3 is a front view of the cross section shown in Fig. 2;

4 shows a cross section through an elastomer body with a repayment device according to a second embodiment;

5 is a perspective view of an elastomer body with a eradicator according to a third embodiment;

6 is a graph showing the variation of dynamic stiffness versus frequency in a conventional journal bearing, a journal bearing with a TiJgungseinrichtung according to a first embodiment and a shaft bearing with a repayment device according to the second embodiment.

7 shows a perspective view of a shaft bearing according to a second embodiment with a partial cutout;

Fig. 8 is a perspective view of a shaft bearing according to a third

Embodiment with a partial cutout; and 9 is a front view of a shaft bearing according to a fourth embodiment.

In Fig. 1, a shaft bearing 10 is shown according to a first embodiment, which serves for supporting a propeller shaft of a motor vehicle, not shown.

The shaft bearing 10 has an outer body 12, which forms a receiving opening 14 into which an inner body 16 formed as an inner ring is inserted. The outer body 12 and the inner body 16 form an annular gap 18, in which an elastomer body 20 is introduced. The elastomer body 20 thereby elastically connects the inner body 16 to the outer body 12, so that the inner body 16 can move relative to the outer body 12.

The shaft bearing 10 also has a bearing support 22, which surrounds the outer body 12 on the outer peripheral side. About the bearing bracket 22, the attachment of the shaft bearing 10 takes place on a motor vehicle part, not shown, in particular a motor vehicle body. Furthermore, the shaft bearing 10 has a rolling bearing 24 which surrounds the propeller shaft, not shown. In particular, the elastomer body 20 is supported on the roller bearing 24 via the inner body 16.

As can be seen in particular in FIGS. 2 and 3, the elastomeric body 20 has a radially inner portion 26 which is connected to the inner body 16, and a radially outer portion 28 which is connected to the outer body 12, wherein the two portions 26 , 28 are connected to each other via a fold 30. Both the inner body 16 and the outer body 12 are embedded in the elastomer body 20, in particular vulcanized.

The elastomer body 20 also has an erosion device 32, which is materially connected, in particular in the same material and in one piece, to the fold 30. The repayment device 32 is formed as shown in FIGS. 2 and 3 as an annular structure 34 and acts as a one-shot oscillator.

The vibrations acting on the cardan shaft during driving are transmitted from the inner body 16 to the elastomer body 20, with the pleat 26 starting to oscillate. Since the eradication device 28 outside the Force flux is arranged on the elastomer body 20, the repayment device 28 vibrates strongly and thus reduces the mass movements in the fold 26. As a result, the rigidity of the shaft bearing 10 in the target frequency range can be significantly reduced and thus the problem of reduced decoupling function can be solved. Thus, the shaft bearing 10, even in the high frequency range on a sufficient decoupling function. In addition, the mass and frequency of the eradicator 32 can be easily matched to the problem area of the elastomeric body 20 of the shaft bearing 10 by the finite element method. In addition, with a large mass of the repayment device 32, the dynamic stiffness can be deliberately lowered in a desired frequency range below the natural level, so that an approximate "bathtub shape" of the dynamic stiffness curve is produced.

FIG. 4 illustrates a second embodiment of the eradication device 32, which differs from the first embodiment in that a mass element 36 is embedded in the erosion device 32. The mass member 36 is formed as a ring 38 and may be made of metal or plastic. The effective mass of the eradicator 28 can be significantly increased by the mass element 36 without thereby increasing the production costs disproportionately.

FIG. 5 shows a third embodiment of the eradication device 28, which differs from the other two embodiments in that the erosion device 28 has tabs 40 which protrude approximately perpendicularly from the elastomer body 20 and are arranged at equidistant distances from each other. The tabs 40 can be tuned differently so that different frequencies or directions can be eliminated. Furthermore, in a tuning as a tuning set, which corresponds to an incremental increase, the bandwidth of the repayment device 32 can be increased. Each tab 40 may also be embedded with a mass member 40 to increase the operation.

Fig. 6 shows a graph of the course of the dynamic stiffness over the frequency, in particular in the high frequency range at 920 Hz. The with K1 The curve shown by K2 shows the curve in a shaft bearing 10 with a torsion device 32 according to the first embodiment. The curve marked K3 shows the course in a shaft bearing 10 with a torsion device 32 according to the second embodiment. As can be seen from the graph, a shaft bearing 10 provided with a torsion device 32 has a lower dynamic stiffness in the high frequency range, in particular at 920 Hz, compared to a conventional shaft bearing without a torsion device, since the eradicator 32 reduces the mass movement of the elastomer body 20 ,

In the following, further embodiments of the world bearing 10 will be described, for the description of which the previously used reference symbols for identical or functionally identical parts will be used.

In Fig. 7, a second embodiment of a Welienlagers 19 is shown that differs from the first embodiment in the configuration of the elastomeric body 20 and the outer body 12 and in the attachment of the elastomeric body 20 on the outer body 12.

The outer body 12 forms in the embodiment shown in Fig. 7, the bearing support 22 and is formed in two parts. The bearing carrier 22 has a first bearing carrier shell 48 and a second bearing carrier shell 50.

The elastomer body 20 shown in FIG. 7 has two folds 42a, 42b which define a cavity 44 with the outer body 12. At each of the folds 42a, 42b formed as an annular structure 34 eradication device 32 is connected. In addition, the elastomer body 20 has a circumferential stop buffer 46, which projects into the cavity 44. The stop buffer 46 limits a radial deflection of the inner body 16 and roller bearing 24 to the bearing carrier 22. Each of the folds 42a, 42b is fixed non-positively on the bearing bracket 22. For this purpose, each of the folds 42a, 42b on the end side a bead portion 43 with a bead core, which einliegen in corresponding recesses 45 of the bearing support 22. 8, a third embodiment of a shaft bearing 10 is shown, which differs from the first embodiment in the configuration of the outer body 12 and the elastomer body 20 and the attachment of the elastomer body 20 to the outer body 12. fn the embodiment shown in Fig. 8, the outer body 12 is formed as a bearing carrier 22 and has a support arm 52 for attachment to a motor vehicle part, not shown.

In the exemplary embodiment shown in FIG. 8, the elastomer body 20 is approximately U-shaped and frictionally fixed to the bearing carrier 22. For this purpose, the radially outer portion 28 endseitlg a mounting portion 54, via which the elastomeric body 20 is fixed to the bearing bracket 22. The attachment portion 54 comprises a circumferential recess 56, into which a projection 60 projecting from the bearing carrier 22 rests, and a collar portion 58, which is designed as a leg 62 projecting in the radial direction and bears against an end face 64 of the bearing carrier 22. In order to secure the elastomeric body 20 from being pulled out of the annular gap 18, a securing ring 66 is clamped on the fastening portion 54.

In addition, the radially outer portion 28 has two radially inwardly projecting lips 68, which limit a radial deflection of the inner body 16 and the rolling bearing 24.

9, a fourth embodiment of a shaft bearing 10 is shown, which differs from the first Ausführungsfonm in the embodiment of the elastomer body 20.

The radially inner and outer portions 26, 28 are connected to each other in the elastomer body 20 shown in Fig. 9 via radial webs 70. Between the radial webs 70 stops 72 are arranged, which limit a radial deflection of the inner body 16 to the bearing bracket 22. Each of the radial webs 70 is provided with an erosion device 32 designed as a flap 40. LIST OF REFERENCE NUMBERS

shaft bearing

outer body

receiving opening

inner body

annular gap

elastomer body

bearing bracket

roller bearing

radially inward section

radially outboard section

wrinkle

repayment facility

annular structure

mass element

ring

cloth

a fold

b fold

bead

cavity

deepening

buffer

first bearing carrier shell

second bearing carrier shell

Beam

attachment section

deepening

collar portion

head Start

leg 64 front side

66 circlip

68 lip

70 radial bar

72 stop

K1 Course of the Dynamic Stiffness of a Conventional Shaft Bearing K2 Course of the Dynamic Stiffness of a Shaft Bearing with a Torsion Device According to a First Embodiment

K3 Course of the dynamic stiffness of a Welieslagers with a torsion device according to a second embodiment

Claims

claims

A shaft bearing (10) comprising an inner body (16), an outer body (12) surrounding the inner body (16) at a distance, and an elastomer body (20) elastically connecting the inner body (16) and the outer body (2) therewith characterized in that the elastomeric body (20) has a repayment device (32).

2. Shaft bearing according to claim 1, characterized in that the repayment device (32) is designed as a one-shot oscillator.

3. Shaft bearing according to claim 1 or 2, characterized in that the repayment device (32) is integrally connected to the elastomeric body (20).

4. Shaft bearing according to one of the preceding claims, characterized in that the elastomeric body (20) has at least one circumferential fold (30, 42 a, 42 b), wherein the eradicating means (32) with the at least one fold (30, 42 a, 42 b) connected is.

5. Shaft bearing according to one of the preceding claims, characterized in that the repayment device (32) is connected to the elastomer body (20) such that it is arranged outside of the force occurring in the elastomeric body (20).

6. Shaft bearing according to one of the preceding claims, characterized in that the repayment device (32) is formed of an elastomer.

7. Shaft bearing according to one of the preceding claims, characterized in that the repayment device (32) has an annular structure (34) which is connected to the elastomer body (20).

8. Shaft bearing according to one of claims 1 to 6, characterized in that the repayment device (32) has tabs (40) which are connected to the elastomer body (20).

9. Shaft bearing according to one of the preceding claims, characterized in that at least one mass element (36) in the erasure means (32) is embedded.

10. Shaft bearing according to one of the preceding claims, characterized in that the elastomeric body (20) is materially and / or non-positively connected to the inner body (16) and / or the outer body (12).