DE102012209767A1 - Torsionally elastic damper or coupling with a flange for connection to a flange of another component - Google Patents

Abstract

A torsionally elastic damper or a coupling with a flange (11) for connection to a flange (21) of another component (20) has on the first mentioned flange (11) hole openings (14) for passing in each case a fastening element (30) for bracing the first-mentioned flange (11) with the flange (21) of the further component (20). The first-mentioned flange (11) and / or the flange of the further component (20) has around the hole openings (14) local recesses (15) or a peripheral recess (115) enclosing the hole openings (114). Either discs (40) in the local recesses (15) or in the circumferential recess (115) or a circumferential ring (140) in the circumferential recess (115) are arranged. The discs (40) and the ring (140) each have a first abutment side (41) for abutment against the first-mentioned flange (11) and a second abutment side (42) for axial abutment against the flange (21) of the further component (20 ) on. For at least one of the first and second abutment sides (41, 42) and the corresponding abutment surface (16, 26) on the first-mentioned flange (11) or flange (21) of the further component (20), the coefficient of friction μ is greater than immediately between the former Flange (11) and the (21) of the further component (20). This allows a quick and cost-effective adaptation to possibly changing boundary conditions without affecting a desired shortest possible delivery time. If it is found during a final torsional vibration calculation that due to the changes, the screw connections for the connection of another component are no longer sufficiently dimensioned, can be carried out by the inventive measure a quick correction without individual components of the torsionally elastic damper or the clutch with great effort new would have to be made.

Description

The invention relates to a torsionally elastic damper or a coupling with a flange for connection to a flange of another component, wherein the first flange has hole openings for passing in each case a fastening element for bracing the first-mentioned flange with the flange of the further component.

The invention is based on torsionally elastic dampers and clutches, which are mainly used in the drive train of large engines.

For example, torsionally flexible dampers and clutches will be used in large, low-speed, or medium-speed two- and four-stroke diesel engines, as well as gas engines, to combat torsional vibrations in the powertrain. In this case, outer diameters of up to three meters are achieved. Examples of corresponding dampers and clutches are among others DE 10 2008 053 632 B3 . EP 1 304 500 B1 and DE 198 39 470 B4 known.

Such dampers and couplings are usually designed and manufactured individually for each application. On the basis of the boundary conditions specified by the customer, a calculation of the individual components of the damper or the clutch takes place, after which the production then follows. In view of a quick reaction to a customer order, production often begins immediately after the calculation. Before delivery of the damper or the clutch, a final torsional vibration calculation is performed. During such a project, there are occasionally minor changes in the customer's terms and conditions between ordering and delivery. It may happen that in the course of the final torsional vibration calculation it is determined that the screw connections for the connection of the torsionally elastic damper or the torsionally flexible coupling to the flange of the further component are no longer sufficiently dimensioned.

The invention is based on the object to provide a simple and inexpensive remedy. This object is achieved by a torsionally elastic damper or a clutch according to claim 1. In particular, a torsionally elastic damper or a coupling with a flange for connection to a flange of another component is proposed, wherein the first flange has hole openings for passing in each case a fastener for bracing the former flange with the flange of the further component, wherein the first-mentioned flange and or the flange of the further component around the hole openings has local recesses or a circumferential recess enclosing the hole openings, and either discs are arranged in the local recesses or in the circumferential recess or a circumferential ring is arranged in the circumferential recess, wherein the discs or the ring in each case has a first abutment side for axial abutment against the first-mentioned flange and a second abutment side for axial abutment against the flange of the further component, and wherein for at least one of the first and second abutment sides un d the corresponding contact surface on the first-mentioned flange or flange of the other component of the friction coefficient μ is greater than between the former flange and the flange of the other component.

The solution according to the invention allows a quick and cost-effective adaptation to possibly changing boundary conditions without affecting a desired shortest possible delivery time.

If it is determined during the final torsional vibration calculation that the screw connections for the connection of a further component are no longer sufficiently dimensioned, can be done by the inventive measure a quick correction without individual components of the torsionally elastic damper or the clutch would have to be rebuilt with great effort ,

Rather, only the recesses mentioned are to be mounted and appropriate discs or in the case of a circumferential recess insert a circumferential ring.

Due to the increased coefficient of friction μ, it is possible to transmit greater forces to a screw connection that initially turns out to be insufficiently dimensioned in the final calculation.

Another advantage of the solution according to the invention is that the outer dimensions of the damper or the clutch change axially at most slightly or remain the same.

The depressions can in principle either be attached to the first-mentioned flange, that is to say to the damper or the coupling or to the further component. In addition, it is possible to provide corresponding depressions both on the damper or the coupling and on the further component. At dampers and couplings for the above The aforementioned purposes often workshop only the damper or the clutch is available, so that you will usually attach the wells only on the flange of the damper or the clutch.

Advantageous embodiments of the invention are specified in further claims.

According to a first embodiment variant, the disks are pressed into the recesses of one of the flanges and the increased coefficient of friction μ is provided on the abutment face of the disks facing the other flange. The power transmission from the first flange to the discs via the hole reveal of the recess and from the discs to the other flange on the friction pair with increased coefficient of friction μ. This has the advantage that the discs after their installation in the wells can not fall out and get lost. In addition, large forces can be transmitted via the hole reveal. Furthermore, only one contact side of the disks needs to be subjected to a friction-increasing processing.

According to a second embodiment variant, the ring or the disks have the increased friction coefficient μ both on the first contact side and on the second contact side. The transmission of power from the first flange to the discs or to the ring and of these to the second flange takes place here in each case via a friction pair with increased coefficient of friction μ, so that the pressing into the respective recess and the related manufacturing effort can be omitted in terms of accuracy.

According to a further advantageous embodiment, the ring or the discs are hardened and have a relation to the flanges increased surface roughness. This has the advantage that in the case of maintenance after disassembly of the flange connection, the disks or the ring can be reused in a new assembly, without a drop in the coefficient of friction μ.

According to a further advantageous embodiment, the surface roughness at the contact sides with an increased friction coefficient μ is in the range of Rz = 20 to 100 μm. Such a surface roughness can be achieved for example by sandblasting, shot peening or embossing. Pyramid or tooth profiles are due to the usual tooth heights in terms of reuse after disassembly usually unsuitable because the mating surfaces are too strong squeezed.

According to a further advantageous embodiment, the ring or the discs on a greater hardness than the flanges, whereby a deformation of the ring or the discs is avoided, which would affect re-assembly in case of maintenance.

According to a further advantageous embodiment, the fastening elements each have a head which is supported on one of the flanges. Between the bearing surface of the head and the abutment surface of the associated disc or the ring on the other of the flanges, a pressure cone is formed, which has a cone angle α in the range of 25 degrees to 35 degrees. This allows optimal utilization of the biasing force of the fasteners.

According to a further advantageous embodiment, the first-mentioned flange forms on its side facing the flange of the further component a radial centering surface for centering on the flange of the further component.

The invention will be explained in more detail with reference to embodiments shown in the drawing. The drawing shows in:

1 1 is a partial sectional view of a torsionally elastic damper according to a first embodiment, which is connected with a flange to the flange of another component,

2 a view of the end face of the flange of the torsionally elastic damper after 1 .

3 1 is a partial sectional view of a torsionally elastic damper according to a second embodiment, which is connected with a flange to the flange of another component,

4 a view of the end face of the flange of the torsionally elastic damper after 3 .

5 a partial sectional view of a torsionally elastic damper according to a third embodiment, which is connected with a flange to the flange of another component, and in

6 a view of the end face of the flange of the torsionally elastic damper after 6 ,

That in the 1 and 2 illustrated first embodiment shows a component 10 in the form of a torsionally elastic damper, which, for example, as in DE 10 2008 053 632 B3 . EP 1 304 500 B1 or DE 198 39 470 B4 can be described described. The internal structure of the damper is of minor importance for the invention described below. Essential, however, is the Presence of a flange 11 for connection to the flange 21 another component 20 , which with the former component 10 has a common axis of rotation A.

The component 10 may also be a clutch, such as a torsionally flexible coupling or a displacement clutch.

The former flange 11 forms at its to the flange 21 of the further component 20 pointing page 12 a radial centering surface 13 for centering on the flange 21 of the further component 20 out. The flange 21 of the further component 20 has a corresponding centering surface 23 on that with the centering surface 13 of the former flange 11 interacts with both components 10 and 20 with respect to the axis of rotation A center each other.

The former flange 11 further has a plurality of hole openings 14 on which are arranged on a bolt circle concentric to the rotation axis A with preferably the same distance from each other. At the flange 21 of the further component 20 there are corresponding hole openings 24 , which with the hole openings 14 of the former flange 11 aligned. The hole openings 14 and 24 serve to accommodate fasteners 30 passing through the holes 14 and 24 extend to the two flanges 11 and 21 axially to clamp together.

In the illustrated first embodiment, the hole openings 24 on the other component 20 designed as threaded openings in the formed as a threaded bolt fasteners 30 are screwed in. The fasteners 30 each rely on one head 31 on the former flange 11 from whose hole openings 14 in this case are designed as through holes without thread. In a modification of the illustrated embodiment, the fasteners 30 be screwed in the opposite direction, in which case the thread at the hole openings 14 of the former flange 11 is to be provided. Alternatively, the fasteners 30 be tightened with separate nuts.

The former flange 11 forms at its to the flange 21 of the further component 20 pointing page 12 a variety of local pits 15 out, which in each case in the area of the hole openings 14 are arranged. In a preferred embodiment, these are round and concentric with the respective hole opening 14 , However, these may also have a different shape than shown.

In the wells 15 is each a disc 40 arranged, which in turn has a hole opening 43 for the implementation of the fastener 30 having.

Each of the discs 40 has a first attachment page 41 for axial abutment against the former flange 11 and a second investment page 42 for axial abutment against the flange 21 of the further component 20 on.

In the first embodiment according to the 1 and 2 are the discs 40 into the wells 15 of the former flange 11 pressed in, so that the power transmission between the former flange 11 and the discs 40 over the outer circumference 44 the discs 40 he follows.

In the assembled state of the flanges 11 and 21 lies second investment site 42 against a corresponding contact surface 26 of the flange 21 of the further component 20 axially. The first investment page 41 located in 1 also against a corresponding contact surface 16 within the associated recess 15 of the former flange 11 but may also be somewhat spaced therefrom.

The power transmission from the first mentioned flange 11 to the other flange 21 via hole reveal, that is over the outer circumference 44 to the disc 40 and from this over the surface pair 42 / 26 to the other flange 21 , Because the discs 40 preferably over the depressions 15 protrude, that is to the flange 21 of the further component 20 pointing page 12 of the former flange 11 through a gap axially from the other flange 21 spaced, wherein the dimension of the gap may also go to zero.

According to the invention, the pair of surfaces on the second plant side 42 and the corresponding contact surface 26 on the flange 21 of the further component 20 a coefficient of friction μ which is greater than between an immediate pairing of the former flange 11 and the other flange 21 or a pairing of the corresponding contact surfaces 16 and 26 the flanges 11 and 21 ,

This will be without a change in the fasteners 30 or the hole openings 14 achieves an increase in the power transmission capacity of the flange, which in particular in flanges with large diameters cost without great effort on the already finished flange 11 can be realized.

In view of a high power transmission capacity and a good utilization of the biasing force of the fasteners 30 is the diameter of the discs 40 so on the Bearing surface of the head 31 of the respective fastening element 30 matched that between the bearing surface of the head 31 and the contact surface 42 the associated disc 40 on the other flange 21 a pressure cone is formed, which has a cone angle α in the range of 25 degrees to 35 degrees.

Furthermore, the discs 40 hardened and have at the relevant for the power transmission plant sides one opposite the flanges 11 and 21 increased surface roughness. In the first embodiment, the second plant side 42 with increased coefficient of friction μ a surface roughness with an Rz value (see. DIN 4768 ) in the range of 20 to 100 microns. The other surfaces of the disc 40 may have a lower surface roughness. Furthermore, the discs have 40 a greater hardness than the flanges 11 and 21 on. The friction-enhanced plant sides 42 the discs 40 can be generated, for example, by sandblasting, shot peening or embossing, the resulting microrelief of the surface being fixed by subsequent hardening. However, other manufacturing methods are also used to produce an increase in the coefficient of friction μ and in particular the surface roughness on the disks 40 used.

In the embodiment explained above, the depressions 15 on the former flange 11 , that is on the torsionally elastic damper or on the clutch 10 appropriate. This is particularly advantageous if, due to the dimensions, only the damper or the clutch 10 Workshop available. In a modification of the first embodiment, however, the recesses may also be on the further flange 21 be provided, in which case the slices 40 in the wells of the other flange 21 be pressed. Furthermore, it is possible on both flanges 11 and 21 Wells with pressed-in washers 40 provided.

The 3 and 4 show on the basis of a second embodiment, a further modification of the above-described embodiment, so that below only the differences from the first embodiment, and reference is otherwise made to the first embodiment. The same elements are accordingly provided with the same reference numerals.

In contrast to the first embodiment, the power transmission between the disc takes place 40 ' and both flanges 11 and 21 over surface pairings with increased coefficient of friction μ.

Each of the discs 40 ' has a first attachment page 41 ' for axial abutment against the former flange 11 and a second investment page 42 ' for axial abutment against the flange 21 of the further component 20 on. In the assembled state of the flanges 11 and 21 lies the first investment page 41 ' against a corresponding contact surface 16 within the associated recess 15 of the former flange 11 and the second investment page 42 ' against a corresponding contact surface 26 of the flange 21 of the further component 20 axially, so that the power flow between the flanges 11 and 21 over the pairs of areas 41 ' / 16 and 42 ' / 26 runs. Because the discs 40 ' over the wells 15 preferably protrude slightly, which is to the flange 21 of the further component 20 pointing page 12 of the former flange 11 through a gap axially from the other flange 21 spaced. The measure of the gap can also go to zero here. The disks 40 ' are each with a clearance in the wells 15 used and can be secured against falling out by gluing.

In a modification of the second embodiment may alternatively in the wells on the other flange 21 be provided. Furthermore, it is possible on both flanges 11 and 21 Provide corresponding recesses, which each together a disc 40 ' take up. This may be interesting, for example, if the wall thickness of the former flange 11 should not be reduced too much.

As in the first embodiment, the discs 40 ' hardened and point to the relevant for power transmission bearing surfaces, namely both on the first investment side 41 ' as well as on the second investment page 42 ' one opposite the flanges 11 and 21 increased surface roughness, with suitable Rz values ranging from 20 to 100 microns. The disks 40 ' of the second embodiment are therefore subjected to both sides of the surface roughness increasing processing.

The 5 and 6 show on the basis of a third embodiment, a further modification of the above-described embodiments. As already stated at the outset, the internal structure of the torsionally elastic damper or the coupling is of secondary importance for the invention. However, what is essential is the presence of a flange 111 on the damper or the clutch 110 for connection to the flange 121 another component 120 , which with the former component 110 has a common axis of rotation A.

The former flange 111 indicates at its to the other flange 121 pointing page 112 a radial centering surface 113 for centering on the flange 121 of the further component 120 out. The flange 121 of the further component 120 has one corresponding centering surface 123 on that with the centering surface 113 of the former flange 111 interacts with both components 110 and 120 with respect to the axis of rotation A center each other.

The former flange 111 again has a plurality of hole openings 114 on which are arranged on a bolt circle concentric to the rotation axis A with preferably the same distance from each other. At the flange 121 of the further component 120 there are corresponding hole openings 124 that with the hole openings 114 of the former flange 111 aligned. The hole openings 114 and 124 serve to accommodate fasteners 130 passing through the hole openings 114 and 124 extend to the two flanges 111 and 121 axially to clamp together. The fasteners 130 are in the hole openings 124 on the other component 120 screwed. However, a modification of the attachment of the fasteners is also 130 as described in connection with the first embodiment possible.

The former flange 111 forms at its to the flange 121 of the further component 120 pointing page 112 a single circumferential recess 115 out, which is about the hole openings 114 extends. In the surrounding depression 115 can slices 40 ' as described in the second embodiment each of the hole openings 114 be arranged assigned.

As 6 can be removed, however, in the third embodiment, a circumferential ring 140 into the surrounding depression 115 used the hole openings 114 and 124 assigned hole openings 143 for the implementation of the fasteners 130 having.

The ring 140 has a first attachment page 141 for axial abutment against the former flange 111 and a second investment page 142 for axial abutment against the flange 121 of the further component 120 on.

In the assembled state of the flanges 111 and 121 lies the first investment page 141 against a corresponding contact surface 116 within the surrounding depression 115 of the former flange 111 and the second investment page 142 against a corresponding contact surface 126 of the flange 121 of the further component 120 axially, so that the power flow between the flanges 111 and 121 over the pairs of areas 141 / 116 and 142 / 126 runs. Because the ring 140 axially over the circumferential recess 115 preferably protrudes slightly, which is to the flange 121 of the further component 120 pointing page 112 of the former flange 111 through a gap axially from the flange 121 spaced. The gap may also go to zero here. The encircling ring 140 is with a clearance in the circumferential recess 115 used and optionally secured by gluing against falling out.

In a modification of the third embodiment, the circumferential recess 115 alternatively also on the other flange 121 be provided. Furthermore, it is possible on both flanges 111 and 121 to provide corresponding circumferential recesses, which in each case together the ring 140 take up.

As a result, an increase in the power transmission capacity of the flange is achieved, especially at flanges with large diameters cost without great effort on the already finished flange 111 can be realized.

In view of a high power transmission capacity and a good utilization of the biasing force of the fasteners 130 is the radial width of the ring 140 such on the support surface of the head 131 of the respective fastening element 130 matched that between the bearing surface of the head 131 and the radial width of the second abutment surface 142 on the other flange 121 a pressure cone is formed, which has a cone angle α in the range of 25 degrees to 35 degrees.

The ring 140 is in turn hardened and points to the relevant for power transmission contact surfaces 141 and 142 one opposite the flanges 111 and 121 increased surface roughness, wherein Rz values according to DIN 4768 are provided in the range of 20 to 100 microns. The ring 140 is subjected on both sides of a surface roughness increasing processing. The friction-enhanced plant sides 141 and 142 of the ring 140 can be generated, for example, by sandblasting, shot peening or embossing, the resulting microrelief of the surface being fixed by subsequent hardening. However, other manufacturing methods are also used to produce an increase in the coefficient of friction μ and in particular the surface roughness on the ring 140 used. The ring 140 also has a greater hardness than the flanges 111 and 121 on.

The above-described torsionally elastic dampers and clutches allow rapid and cost-effective adaptation, if it should turn out after the manufacture of the damper or the clutch in a final torsional vibration calculation due to slightly changed boundary conditions that the original design of the screw connections on the flange is no longer sufficient. This procedure enables compliance with short delivery times Order placement and avoids the new production of individual components of the damper or the clutch.

Another advantage of the torsionally elastic dampers and couplings according to the invention is that the outer dimensions change axially at most slightly or remain the same.

The invention has been explained in more detail above with reference to exemplary embodiments and further modifications. However, it is not limited to this. Rather, technical features of the individual embodiments and modifications may also be combined with each other, if not expressly described, as long as technically possible. The invention comprises in particular all embodiments defined by the claims.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102008053632 B3 [0003, 0027]
• EP 1304500 B1 [0003, 0027]
• DE 19839470 B4 [0003, 0027]

Cited non-patent literature

• DIN 4768 [0041]
• DIN 4768 [0058]

Claims (8)

Torsionally elastic damper or clutch ( 10 ; 110 ) with a flange ( 11 ; 111 ) for connection to a flange ( 21 ; 121 ) of another component ( 20 ; 120 ), the former flange ( 11 ; 111 ) Hole openings ( 14 ; 114 ) for carrying out in each case a fastening element ( 30 ; 130 ) for bracing the former flange ( 11 ; 111 ) with the flange ( 21 ; 121 ) of the further component ( 20 ; 120 ), characterized in that the first-mentioned flange ( 11 ; 111 ) and / or the flange of the further component ( 20 ; 120 ) around the hole openings ( 14 ) local wells ( 15 ) or one of the hole openings ( 114 ) enclosing circumferential recess ( 115 ) and that either discs ( 40 ; 40 ' ) in the local recesses ( 15 ) or in the surrounding depression ( 115 ) or a circumferential ring ( 140 ) in the circumferential recess ( 115 ), the discs ( 40 ; 40 ' ) or the ring ( 140 ) each have a first attachment page ( 41 ; 141 ) to rest against the former flange ( 11 ; 111 ) and a second investment site ( 42 . 142 ) for axial abutment against the flange ( 21 ; 121 ) of the further component ( 20 ; 120 ), and wherein for at least one of the first and second plant sides ( 41 . 42 ; 141 ; 142 ) and the corresponding contact surface ( 16 . 26 ; 116 . 126 ) on the first-mentioned flange ( 11 ; 111 ) or flange ( 21 ; 121 ) of the further component ( 20 ; 120 ) the coefficient of friction μ is greater than directly between the first mentioned flange ( 11 ; 111 ) and the ( 21 ; 121 ) of the further component ( 20 ; 120 ). Torsionally elastic damper or clutch ( 10 ; 110 ) according to claim 1, characterized in that the discs ( 40 ) into the depressions ( 15 ) one of the flanges ( 11 . 21 ) are pressed and the increased coefficient of friction μ at the other flange ( 21 . 11 ) facing the plant side of the discs ( 40 ) is provided. Torsionally elastic damper or clutch ( 10 ; 110 ) according to claim 1, characterized in that the ring ( 140 ) or the discs ( 40 ' ) at both the first investment side ( 41 '; 141 ) as well as on the second investment page ( 42 '; 142 ) have the increased coefficient of friction μ. Torsionally elastic damper or clutch ( 10 ; 110 ) according to one of claims 1 to 3, characterized in that the ring ( 140 ) or the discs ( 40 ; 40 ' ) are hardened and at least at the plant sides ( 42 ; 41 ' . 42 '; 141 ; 142 ) with an increased coefficient of friction μ a with respect to the flanges ( 11 . 21 ; 111 . 121 ) have increased surface roughness. Torsionally elastic damper or clutch ( 10 ; 110 ) according to claim 4, characterized in that the surface roughness at the plant sides ( 41 . 42 ; 141 ; 142 ) with an increased coefficient of friction μ in the range of Rz = 20 to 100 microns. Torsionally elastic damper or clutch ( 10 ; 110 ) one of claims 1 to 5, characterized in that the ring ( 140 ) or the discs ( 40 ; 40 ' ) a greater hardness than the flanges ( 11 . 21 ; 111 . 121 ) exhibit. Torsionally elastic damper or clutch ( 10 ; 110 ) according to one of claims 1 to 5, characterized in that the fastening elements ( 30 . 130 ) one head each ( 31 . 131 ) located on one of the flanges ( 11 . 21 ; 111 . 121 ) and between the bearing surface of the head ( 31 . 131 ) and the contact surface of the associated disc ( 40 ' ) or of the ring ( 140 ) on the other of the flanges, a pressure cone is formed, which has a cone angle α in the range of 25 degrees to 35 degrees. Torsionally elastic damper or clutch ( 10 ; 110 ) according to claim 1, characterized in that the first-mentioned flange on its side facing the flange of the further component side forms a radial centering surface for centering on the flange of the further component.

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