DE8535983U1 - Damped torsional vibration damper - Google Patents

Description

-8th-

The invention relates to a damped torsional vibration damper according to the preamble of claim 1.

Such a torsional vibration damper is described in DE-OS 26 40 752, for example.

For damping the crankshaft torsional vibrations of multi-cylinder Reciprocating internal combustion engines are silicon oil torsional vibrations and damped rubber-silicone oil torsional vibration absorbers used, the latter especially in highly charged 12 and 16-cylinder diesel engines.

Silicone oil torsional vibration damper with a cross section Γ ") according to DE-OS 26 40 752, Fig. 1, the increased Requirements for highly charged 12 and 16 cylinder engines no longer fair because they have a housing encompassing the inertia x'ing for the hub component (10, FIG. 1) belongs, whose moment of inertia is 0.5 to 0.6 times the ring moment of inertia and thus the first rotational frequency the crankshaft so far that low torsional vibration excitation orders like the 2.5th and 1.5th orders to dangerous torsional vibration meSonance phenomena can lead, therefore 25

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Torsional vibration dampers with housings were developed, that resonate with the inertia ring, i.e. a part

of the secondary inertia ring rotating mass. In embodiments according to DE-OS 26 40 752, Fig. 2 to ζ Fig. 9, it is possible to classify the "dead mass" vibrationally, the primary rotating mass J-prim to 20% and less of the secondary mass J-sec, that is 200% of the total rotating mass of the multi-part inertia ring to be pressed down.

The same applies to embodiments according to DE-GH 19 85

/. 175, DE-OS 32 22 258, DE-PS 26 40 751 C2 and the difficult feasible proposal according to DE-OS 32 21 987. In the embodiments according to DE-OSOS 26 18 820 and DE-OS 12 95 287 the above-mentioned favorable ratio of J-prim / J-sec = 0.2 has not yet been achieved.

In the embodiment according to DE-OS 26 40 752 were the lamellae, which are connected to the flange body as part of the primary rotating mass, are executed several times in order to create a multitude of crevices with alternately sheared viscous liquid. But it wasn't notice that in all these columns, the square of the

/ \ According to alternating shear amplitude, vibration energy is dissipated in heat, and that the internally attached fins practically no heat during the rotation can dissipate and the externally attached lamellae at the outer end have a cross section that is only is a fraction of the heat-producing shear area on both sides of a lamella. Even after both Viewed from the middle, sides can only heat through several heat transfer points between viscous liquids and lamellas, i.e. only with appropriate

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"10-

correspondingly high temperature gradient. This forms

§ a build-up of heat in the middle of the package of

I gripping slats. Experience shows that this leads to ; - 'Temperature differences compared to the outer skin of the parts 5 from 40 C and more; this not only sets the damping ; and resilience properties of the viscous liquid

^; significantly down, but also the durability

;. the viscous liquid, e.g. B. a silicone oil. This

\ Heat build-up affects the efficiency of the insulation

! ίο pfers, especially if the use of services and thus the damper temperature at different speeds of the engine fluctuates significantly.

The torsional vibration damper with viscous damping

) 15 medium according to DE-OS 32 21 987 A1 are the waiting

■ driving conditions from the inside of the chambers to the outside

^: even more unfavorable because the chambers are only partially on the side

'.; cooling due to the air streaked during circulation

\ is set, and radially practically no heat over the

i 20 additional mass can be removed.

\ Also in the embodiment of DE-PS 26 40 751 C 1,

ii Fig. 3, are the heat removal ratios from the interior

if \ of the lamella pack is extremely unfavorable: from a shear

J 25 area of 2x slat circumference κ slat width must be the

\ Heat laterally over a lamella cross-section of 1 χ

\, Lamellar circumference κ lamellar thickness, i.e. over the eightieth part of the surface, is dissipated because the heat dissipation

J over the primary part is practically negligible. Even

in the embodiment according to FIG. 4, the heat dissipation

? ratio still unfavorable: a heat-generating shear

\ area of 2κ lamellar circumference χ lamellar width (in the axial direction) there is only one heat-dissipating transverse

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• - »11-

At the outer end of the lamella, 1 χ lamella circumference jc lamella thickness is available, i.e. an area about 1 / 2Ox smaller according to Fig. A.

The well-known, viscous relaxing, damped torsional vibration damper are also constructed in such a way that the components are welded together so that these Torsional vibration absorbers, for example for maintenance purposes, can no longer be taken apart. The known Torsional vibration absorbers also have components that, due to their design, have increased manufacturing

/ ■> and cause assembly costs.

The object of the invention is to provide a damped To create torsional vibration damper, the assembly of which can be carried out more easily and cheaply Lifetime can be increased by a lower thermal load and in which the ratio of the moment of inertia of the inertia ring and thus the active mass to the moment of inertia of the dead mass, which is caused by Hub components is formed, can be optimally adapted to the space available.

/ The structure of two identically designed assemblies ₂ r enables the production of the components with simple and thus inexpensive shapes. The fact that in each of the assemblies when the sleeve springs are vulcanized, these are accessible from the outside for molding tools, the bond between the hub ring, sleeve spring and end ring section is significantly improved and its manufacture is simplified. This torsional vibration damper can, if desired, be taken apart in a simple manner for maintenance or repair purposes. The arrangement and

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Formation of the shear surface support rings enables one good heat dissipation, especially in the corners on the periphery of the external cooling that are particularly easy to access Torsional vibration damper. Every dissipation heat generates

The low shear surface is therefore located on the outer circumference Part of the cooling surface of approximately the same size without heat transfer interruption at contact surfaces and without cross-section restriction on the heat-dissipating away available. The cooling surface on the circumference can nor through grooves on the circumference of the Utnfangsringes or in the End faces of the end ring sections are improved.

/ ₎ The cooling fins do not extend from the end faces. This enables better air guidance while at the same time avoiding interfering noises. Optimal air guidance is possible when the groove base of the grooves is curved, in particular curved in a circular manner. The arcuate curvature has manufacturing advantages, which are achieved by machining by means of a disk-shaped tool, and the advantage that the air flow is such that an optimal heat dissipation excludes undesirable thermal stress.

The inventive provided circumferential ring has a considerable mass. By this mass of the circumferential ring In addition, the moment of inertia of the inertia ring is increased, so that the ratio of the moments of inertia between the active and dead masses is further improved. Since the dimensioning of the circumferential ring only in axial Direction limits are set and the thickness dimension in the radial direction only by the available Space is limited, an optimal adaptation to this space can be made. Through this training it is

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m

• *

possible, viscous relaxing, damped torsional vibration absorbers different repayment or damping characteristics with itn essentially the same components to manufacture. The same end ring sections and hub components can always be used. It is just required, circumferential rings of different designs to be made available for adaptation to space and performance. The ütnfangsring a see between the front ring sections of the inertia ring wear radially inwardly extending annular flange, the center plane of this circumference ring and its ring flange coincides with the center plane of the torsional vibration damper. This results in again a symmetrical design of the circumferential ring and of the entire torsional vibration damper.

With this embodiment, the surface areas enlarged, between which the viscose fluid is effective is. At the same time, the heat dissipation is also reduced outside through the mass of the inertia ring and the circumferential ring so improved that the enlargement areas where heat is generated does not cause thermal problems.

A favorable symmetrical construction of the torsional vibration damper is made possible by the fact that the hub has a hub ring from which a flange extends radially extends outward between the end ring sections of the inertia ring, and that the center plane of this Flange coincides with the center plane of the torsional vibration damper. On the two front sides of this flange two shear surface support rings can be attached, for example flanged. This shear plane carrier

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rings extend between the two end faces
Ring flange of the circumferential ring and the two inwardly facing end faces of the end ring sections of the inertia ring. The circumference of the hub ring can be widened by a sleeve so that the axial spacing of the shear surface carrier rings can be adjusted by determining the length of the sleeve.

These two shear surface support rings can be axially Ψ
Β have extending peripheral edges. This will

10 surface area exhibiting shear is significantly increased.

A hub rim is advantageously mounted on each end face of the hub ring. Each of these hub rims has peripheral surfaces to form the conical surfaces. The conical spring sleeves are on these conical surfaces attached, the outside with the conical Innenutnfangsflächen of the end ring sections of the inertia ring are connected.

^N i ^e hub rings can have conical wedge surfaces and the hub rims can be keyed onto these conical surfaces.

To keep the gap widths of the rooms with

25 viscous liquid can be filled between the

Centering pins surrounded by the end ring sections of the sleeves

U are arranged.

A screw connection is required to assemble the components agrees

jf The arrangement and design of Y-shaped in cross-section

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forked shear surface support rings enables a good
Heat dissipation into the corners on the circumference of the torsional vibration damper, which are particularly easily accessible for external cooling.

Embodiments of the invention will be explained with reference to the figures of the drawing.

Show it:

Fig. 1 + 2 sectional views of exemplary embodiments

of a torsional vibration damper with plane \

CSear support rings |

and I.

yy

Fig. 3 is a sectional view of embodiment £

play a torsional vibration damper whose %

Shear surface carrier a Y-shape I

have a moderate cross-section. |

The torsional vibration damper is attached to |

a rotating component, for example a shaft, f

fixed, overall the rotary or Torsionsschwingungunen \

Γ should be erased or optimally steamed. I.

The hub has, according to FIG. 1, a hub ring 1 which [: on the inner circumference for mounting on the rotating component ί

Has holes.

On this hub ring 1, two prefabricated components'

to be assembled. Each of these B ^ ♦ i'ile has an end ring section 3a, 3b. The two end ring sections |

I 3a, 3b are identical and in the illustrated, built-in

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• ·

• · ■

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th position mirror images of each other and symmetrical to Central plane H-H of the torsional vibration damper arranged.

These end ring sections 3a, 3b are each connected to an elastomer sleeve spring 2 by vulcanization, which in turn is then connected to one of the hub rims 8a, 8b. The building blocks, one of which is the Parts 8a, 2 and 3a, the other consisting of parts 8b, 2 and 3b, can be prefabricated, i.e. H. a connection by vulcanization can be carried out. This is beneficial because, as can be easily seen,

/ thereby the axial ends of the elastromeric sleeve spring 2 are exposed so that molding tool parts have free access during vulcanization. This can a tight connection between the elastromer elements and the metal components can be achieved.

It can be seen that the two hub rims 8a and 8b are fastened to the hub ring 1 by means of screw bolts. The hub rim 8a has on the circumference a conical circumferential surface 9a which converges towards the center plane MM of the torsional vibration damper. The hub rim 8b f \ has a conical peripheral surface 9b, which also converges towards the central plane MM. The sleeve springs 2 are conical and the inner circumferences of the end ring sections 3a, 3b are correspondingly conical.

Ring seals 16 are arranged between the hub ring 1 and the hub rims 8a and 8b. From the hub ring 1 a flange 1a extends radially outwards, the center plane of which with the center plane M-M of the torsional vibration

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tilgers coincides. The two shear surface carrier rings 4a, 4b are flanged onto this flange 1a and extend into the space between the end faces of the end ring sections 3a, 3b facing one another. On the outer circumference, these flanged shear surface carrier rings 4a, Ah have circumferential edges 7a, 7b. These circumferential edges 7a, 7b extend over shoulders which are formed on the circumference of the end ring sections 3a, 3b in the end faces facing one another.

On the outer circumference of the end ring sections 3a, 3b is a

/, Circumferential ring 6 screwed on by means of screw bolts. This circumferential ring 6 has a radially inwardly extending annular flange 5 which extends between the

■ jr shear surface support rings 4a, 4b extends. The outer circumference the UE / f at ^^ edges 7a, 7b of these Scherf smile carrier rings 4a, 4b are the inner peripheral portions of the Circumferential ring 6 opposite. Between this circumferential ring 6 and the inwardly facing end faces of the end ring sections 3a, 3b are provided with ring seals 17.

The mass of the inertia ring is formed by the circumferential ring 6 and the end ring sections 3a, 3b. The space f ~% between the annular seals 16 and 17 is filled with viscous liquid ₂ r in a known manner.

For centering, centering pins 12, which are surrounded by spacer sleeves 11, are provided between the mutually facing end faces of the end ring sections 3 a, 3 b.
30th

In Fig. 3, M-M denotes the center plane of a damped torsional vibration damper.

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-18-

Each torsional vibration damper consists of two identical

trained assemblies. Each of these assemblies has &

I a hub ring 1, a sleeve spring 2 and a face

f. ring section 3a, 3b. In one embodiment

f 5, the same assembly is arranged again on the other side of the central plane MM in a mirror image of the illustrated.

I To manufacture a torsional vibration damper, η '. "* ¹ must be a

1 jo only such Paugi ^{1 unit} are made. This j means that for the metal-made parts, ^{namely: i} \ lent of the hub ring 1 and the Stirrringabschnitt 3a, 3b,

2 only two forms are required.

In the illustrated embodiment, the hub ring 1 has a ring part which has a flat end face 1b ] and a frustoconical beveled end face Ic j . A recess is provided on the outer edge

I 20 N ^ benringes 1 a truncated cone-I-shaped sleeve spring 2 is placed, which extends radially 5 inward from the inner edge of the end ring portion 3a, 3b so that, as shown, in, i ~ \ axial direction a Sandwich assembly results, which __ includes parts 1, 2 and 3a, 3b. This sandwich assembly is assembled to form a unitary component by vulcanizing the sleeve spring 2 onto the parts 1 and 3a, 3b. It can be seen that the two edge sections of the sleeve spring 2 are freely accessible from the outside for passing tools during the vulcanization of this assembly, so that the vulcanization process can be controlled in the desired manner and the required connection characteristics are achieved. In

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the recesses on the circumferential edge of the hub ring 1 is a two-part shell ring-shaped, Y-shaped forked shear surface support ring Aa, Ab . The fork ends Ac extend to the end edges on the circumference of the torsional vibration damper and run at an angle of approximately AB with respect to the central plane MM, ie they

ι run in the bisector of the edge angle at j

As shown, the fork ends 4c of the shear surface support 4a, Ab are bent over in such a way that these fork ends 4c run perpendicular to the axis of the torsional vibration damper. _{A / t} circumferential ring 6a, 6b is fixed in the Y-shaped fork space, which ring is fastened by means of screws in the exemplary embodiment shown on the left. Between the shear surface support ring 4a, 4b, the end ring sections 3a, 3b and the circumferential ring 6a, 6b

j- is a gap formed with a viscous Shear fluid is filled.

A sealing ring can be provided at 18 if desired.

At the periphery, the peripheral ring 6a, 6b grooves, so that f are formed sealing ribs here. Grooves 15, between which cooling fins 14 are left, can also be cut into the end faces of the end ring sections 3a, 3b.

As shown, sets, the two-part primary side hub ring 1 in two thin-walled, shell-shaped shear surface support rings 4a, 4b to the outside continuously, which in cross-section on the periphery as far as possible towards the outer cooling easily accessible corners on both sides

• · · fl ti Μ ι *) * ·

4 4 4 i 4 44 * .- *

-20-

extend and with their surface lines in the conical Part approximately in the respective bisector, which start from the corners, lie.

The version shown on the right differs differs from the one shown on the left in that the circumferential ring 6b has ring shoulders 6c which, as shown, around the ßirnringabschnitt 3b are each pressed around, around the torsional vibration damper on the outer edge

Holding and sealing IQ together.

s \ As with 19 illustrated, the two mirror-image hub rings 1 may be bolted or screwed together.

The two end ring sections 3a and 3b can have finely machined reference surfaces 20, 20a or 21, 21a, on which the end ring sections 3a, 3b, the hub rings 1 and the sleeve spring 2 after the vulcanization of the sealing and resilient elastomers with the circumferential ring 6a or 6b through the screws 22 without the shear surface support rings 4a or 4b connected, for fine machining on mating surfaces 23, can be received. After a demolition

Γ) days, the mating surfaces 24 can be reworked in accordance with the precision-machined reference surfaces 20, 20a. the

₂ r mating surfaces 25 in accordance with the finely machined reference surfaces 21, 21a. In this way it is ensured that the gaps between the end ring section 3a and the shear surface carrier ring 4a, the circumferential ring 6a and the shear surface carrier ring 4a or the circumferential ring 6b and the shear surface carrier ring 4b, the shear surface carrier 4b and the end ring section 3b maintain their nominal dimensions, even if according to the Vulcanization of the sealing

- 2 1 -

the resilient elastomers locally different shrinkage of the elastomers leads to displacements.

The embodiment marked b allows one Assembly of the torsional vibration damper without screwing

Claims (1)

• · Dipl.-Ing. Dr. MXCHAEL. Mf = IXKOUSKI patent attorney European Patent Representative European Patent Attorney Handataire en brevets europeens Dr.H. HaikoBski patent attorney Xantener Str. 10 D-IOOO Berlin 15 German Patent Office 8000 Munich 2 Your! Eichen: Tour ref. laniener Sirsie B-IQQO Berlin 15 Telephone 030/881 81 81 * 882 68 6k Telex 1 85 366 Datui: Office tmchen Date: tfyipneniurger Strasse 6 / 18.1 D-80Q0 Bünchen 11 Phone 089/18 08 18 Telex 5 22 263 Our lei: Hy ref. P 312/85 VI / R / 5Ch 2.1985 Regards; Applicant; Prof. Dr.-Ing. Klaus Federn, Berlin 1. Damped torsional vibration damper with a multi-part Hub and one, two end ring sections and a circumferential ring having inertia ring with at least one flange section of the hub, at least one gap space filled with viscous liquid forms and its end ring sections, respectively 312/8 & / 1 _{4 pa5} -2 • 4 α are connected to one of the hub parts by means of a sleeve spring, characterized in that two identical assemblies, each of which has a hub section (1, 1a, 1e), a sleeve spring (2) and a front ring section (3a, 3b> has, mirror images of each other and symmetrical to the mid-life (M-M) of the torsional vibration damper are mounted that from the circumference dtfs hub section (1, 1a, le) two Shear surface support rings (4a, 4b) extend outward between the end ring sections (3a, 3b), the outer edges are axially spaced from each other, and that one, in the, of the two Shear surface support rings (4a, 4b) limited annular space, circumferential ring (6, 6a, 6b) extending into it is mounted on the circumference of the end ring sections (3a, 3b). 2. Damped torsional vibration damper according to claim 1,
characterized in that the circumferential ring (6, 6a, 6b) merges inward between the two shear surface support rings (4a, 4b) having extending annular flange (5). 3. Damped torsional vibration damper according to claim 2, characterized in that 312/85 / 1.pa5 • * · n a a · a a · a I • a »· · · β» ι • · ft · · * the central planes of the circumferential ring (6, 6a, whether) and of the Ririgflanschs (5) with the center plane <M-M) des Torsional vibration damper coincide. 4. Damped torsional vibration damper according to one of claims 1 - 3, characterized in that i. i a flange (1aj 1e) from a hub ring (1)! radially outward between the end ring sections / ₍ (3a, 3b> of the inertia ring and that the central plane (MM) of this flange (1a, Ie) coincides with the central plane (MM) of the torsional vibration damper. 5. Damped torsional vibration damper according to one of claims 1 - A, characterized in that two shear surface support rings (4a, 4b) f are attached to the two end faces of the flange da) of the hub ring (1), which are located between the two end faces surfaces of the annular flange (5) of the peripheral ring (6, 6a, 6b) and the two inwardly facing end faces of the end ring sections (3a, 3b) of the inertia ring extend. 6. Damped torsional vibration damper according to one of claims 1 - 5, characterized in that 312/85 / 1.pa5 the two shear surface carrier rings (4a, 4b) axially between the circumferential sections of the two end ring sections (3a, 3b) and inner circumferential sections of the circumferential ring (6, 6a, 6b) extending circumference ^ - have edges (7a, 7b). 7. Damped torsional vibration damper according to one of claims 1 - 6, characterized in that a hub rim (8a, 8b) is mounted on each end face of a hub ring (1), the peripheral surfaces of which (9a, 9b) are conical outer surfaces on which a conical sleeve spring (2) is mounted, the outer Circumferential surfaces with conical Irinenümfängsflachen the End ring sections (3a, 3b) of the inertia ring are connected. 8- damped torsional vibration damper according to claim 7,
( j characterized in that the hub rings (8a, 8b) have a conical inner bore with which they aui 'an outer cone (10) of the Hub ring (1) are keyed. 9. Damped torsional vibration damper according to one of claims 1 - 8,
30th characterized in that 312/85 / 1.pa5 St «t ·· a · it ft * -δ " between the inwardly facing end faces of the End ring sections (3a, 3b) of the inertia ring Sf of Centering pins (12) surrounded by spacers (11) are* 10i damped * torsional vibration damper according to one of the Claim »1 - 9, characterized _t that
10
/ \ the end ring sections (3a, 3b) have shoulder shoulders on the circumference in the end faces facing one another. 11. Damped torsional vibration damper according to one of claims 1 -10, characterized in that in the outwardly facing end faces (13) at deti End ring sections (3a, 3b), of the inertia ring between them leaving cooling ribs (14), grooves (15) are trained. 12, damped torsional vibration damper according to claim 11,
characterized in that is the groove bottom (15a) of the groove (15) is curved, par- AQ wider arcuately curved. 13. Damped torsional vibration damper according to one of the 312/85 / 1.pa5 t ·· »it · <ι ·" . j 44 4 4 .... <«« 4 * • * * Claims 1 -12, characterized in that c a bowl-shaped shear surface extends from the Chträgerring (4a, 4b) extends, the cross section of which has the shape of a Y-shaped fork and that into the open Y-fork of this shear surface support ring (4a, 4b) the annular flange (5) of the circumferential ring <6, 6a, 6b) extends into it, , \ 14. Damped torsional vibration damper according to claim 13, characterized in that
15th the fork ends <4c) of the bowl-shaped, forked Shear surface support ring (4a, 4b) from the center plane (M-M) of the torsional vibration damper “Whose outer marginal edges extend. 15, damped torsional vibration damper according to claim 13 or 14, \ characterized in that the Y-shaped forked shear surface support ring (4a, 4b) consists of two identical, mirror-inverted, thin-walled shell ring components.
30th 16. Damped torsional vibration damper according to one of claims 1 -15, 312/85 / 1.pa5 -7- 312/85 / 1.pa5 characterized in that the circumferential ring (6, 6a, 6b) to the end ring sections (3a, 3b) is screwed on. 17. Damped torsional vibration damper according to one of the Claims 1 - 16, characterized in that 1 I. the circumferential ring (6, 6a, 6b) around the edges of the forehead f / ■ ring sections (3a, 3b) pressed edge flanges | having. j 18. Damped torsional vibration damper according to one of the | Claims 13-17, j characterized in that I f the hub ring (1) has a circumferential ring with a flat \ End face (Ib) and a conically bevelled \ Has end face (Ic), the edge of which has an Auf- j recess Ud) for the shear surface carrier ring \ ζ (4a, 4b) has. f 1 19. Damped torsional vibration damper according to one of the ■ Claims 1-18, i characterized in that I. the sleeve spring (2) is a cone "trumpet-shaped sleeve. 1