DE2818295A1 - Diesel engine viscous-hydraulic angular oscillation damper - incorporates heavy ring supported by leaf springs mounted in annular space - Google Patents

Abstract

The damping arrangement for the drive with a small to medium sized high speed diesel engine consists of a housing (3) with an annular hollow space along its circumference. The space is filled with a heavy ring (2) leaving a narrow clearance between housing and ring, which is filled with a viscous fluid. The ring is attached to the hub of the housing by radial leaf springs (5), shaped so that the ring will not touch the housing when the springs are bent. Angular oscillations are dissipated by the viscous friction of the fluid, by inertia and by the leaf springs.

Description

Visco-hydraulic torsional vibration damper with leaf spring

Supported swing ring Description of the invention: To reduce the Torsional vibration amplitudes of the engine system of small and medium-sized diesel engines, especially of high-speed high-performance motors and also in other drive systems Torsional vibration dampers and torsional vibration dampers have been used for decades. In the case of visco-hydraulic torsional vibration dampers, i. H. at damping with the help of a highly viscous damping medium in the gap between a flywheel and one of these enclosing housing leads to sliding bearings of the flywheel in the housing as a result alternating sliding to wear and tear in the bearing and thus to it becoming unusable of the damping medium, such as a highly viscous silicone oil, partly through catalytic Decomposition. There are therefore elastic flywheel guides in the housing with radial Leaf springs and other resilient elements have been tried. These are in the so far known designs are not highly resilient, or they do not guarantee sufficient Security against friction under small relative movements and therefore no security from abrasion; Relative movement between the contacting parts occurs in particular when forces are transmitted to springs that are not firmly clamped on both sides. The lack of resilience leads to the fact that known spring supports of the flywheel in the resonance passage of a torsional vibration system to be damped, such as. B. a crankshaft with flywheel and connected drive train, no more can be designed to be durable. Only radial leaf springs can be used permanently relatively small sheet thickness or sufficient length can be designed on both sides are firmly clamped or firmly connected. Inside of the swing ring In the assumed space in the neck, such leaf springs can be placed in recesses in the ring be accommodated. So far, however, this has led to extremely complex constructions, as far as the manufacturing costs for the recesses and the necessary clamping parts are concerned, because the clamping parts must hold the leaf springs immovably in their clamps, so that no abrasion under alternating gliding damages the damping medium (e.g. silicone oil).

In Figure 1 is an embodiment of the invention to overcome the gesckYilderfen Difficulties shown. Sufficient for leaf springs Length, the space inside the damper ring (1) is used, by dividing it into chambers, which on the one hand are filled with, for example, silicone oil Interior are in connection and on the other hand with the opposite of the interior sealed exterior.

In the design according to Figure 1, the last-mentioned chambers generated in that hollow bolts (4) in the housing base (2) and in this case welded-on cover (3). The one remaining between the hollow bolts Space can then be used to accommodate leaf springs (5) and (6). the are mutually according to the invention with cutouts penetrating leaf springs in this embodiment according to Figure 1 according to the invention cohesively at its outer end connected with butted grooves in the damper ring, e.g. B., as shown, by soldering or by welding. The leaf springs are used to compensate for the clamping notch effect according to the invention kept narrower in terms of width in their free length than in the clamping area, where along the radius the width decreases approximately proportionally to the alternating bending moment, which acts in the case of ring vibrations in the housing. The leaf springs are in theirs middle not narrowed part in right-angled intersecting slots in the Housing clamped.

In order to reduce the pressures between the deflected ones at the reversal point of an oscillation Leaf springs and the material remaining between the crossed slots in the housing lower, are about as hard on both sides of the spring-hard leaf springs Enclosures (7), (8), (9) and (10) are also clamped. These side dishes can be in the middle Area that is about the strength of the perpendicular leaf springs increased by the strength of the two right-angled supplements corresponds, according to any one Movement tolerance, e.g. B. I T 5 to be graded by selecting suitable supplements the round flywheel (1) on an evenly wide gap (11) on the circumference in the round Aligning the housing The gap on both sides of the flywheel, the gap (12) on the side of the housing (2) or the gap (13) on the side of the cover (3) should taper inwards as the radius decreases, roughly as shown. The holes in the hollow bolts (4) take place during operational assembly of the damper the fastening screws.

In the version according to Figure 2, the flywheel (1) has the cross-slotted one Pin im in the housing part (2), the leaf springs (5) and (ó) and their enclosures (7) to (10) the same shape as after the design according to Figure 1. The housing (2 ') has a circumferential Bund (13 *) around the enlarged cover (3 ') with To be able to fasten screws (14) on the circumference. The bolts (4 ') are opposite the Bolts (4) in Fig. 1 are welded into countersinks in the bottom of the housing, they have grooves for sealing rings (15) to the space in the bolt opposite that with the damping medium filled space by the pressing force of the lid generated by the screws (14) to seal. The cover is also surrounded by a circumferential cover opposite the housing Seal (16) sealed in a groove in the housing collar (139). Instead of the bolt (4 ') a flat bar can also be welded to the housing for every 2 bolts. the Holes for attaching the damper must then be welded on a Circle centered on the damper axis by means of a device or gauge or the like be drilled.

The contact pressure of the cover (3 ') for the seals (15) around them Bores can be made by additional screws to be arranged, for example four below i45 in Fig. 2, which are then also enclosed by sealing rings must be.

Figure 3 shows an embodiment in which the one with the damping medium related chambers in the interior of the flywheel (1 ") according to the invention are formed by webs (20) on both sides of the leaf springs (5 ") and (6"); the webs extend from the pin (13 *) on the housing base (2 ") to one with the housing base also cohesively connected slotted ring (21), they are with the housing base welded. After welding the cover (3 ") onto the rim (22) of the housing the edges of cutouts (23) in the cover are welded to the webs.

The flywheel (1 ") has wider slots than the flywheel (1) in picture 1, - so that enclosures can also be used. As an axial position security A snap ring is used between the flywheel (1 ") and the ends of the springs (5") and (6 ") in the manner of a Seeger ring (24), which in turn by a pin (25) or on other way is positively prevented from changing in the circumferential direction.

If the snap ring is arranged in the center of the flywheel, then the Springs (5 ") and (6") can be punched with the same tool and by corresponding According to the invention, the flywheel can also tolerate its dimensions without axial play held between two crossed opposing two-armed leaf springs will.

In the design according to Figure 4, the radial support springs are adjusted according to a further feature of the invention during the torsional oscillation of the flywheel alternately upright bent; they are multiplying in groups the flexibility connected in series in the circumferential direction (such as the group (3) + (4) with group (5) + (6) and group (7) + (8) and others accordingly by 600 staggered groups each time); at the same time they are used to increase the rigidity connected in parallel in the radial direction (e.g. groups (1) to (4), (5) + (6), (7) to (10) and (11) + (12) and further groups offset by 1200 each.) Due to the parallel connection, the radial rigidity is correspondingly opposite known designs with S-shaped in the manner of two hairpin curves lined up next to one another Formed flat springs increased because the edgewise bending hindered under radial forces will. The individual spring groups are each at their two ends by circular ring sections (the inner sections (11) and (13) and the outer sections (12) and (14)) connected, with the radius of curvature and the web widths of the individual springs with regard to the available space and an even distribution of the bending edge stress are designed to be optimizing.

The circular ring section (11) and others in Fig. 4 around 120 seated Circular ring sections are centered in the housing and braced with the housing, the Circular ring section (14) and further circular ring sections offset by 1200 in Figure 4 are centrally connected with a flywheel in the housing. The remaining spring parts and circular ring sections have play with respect to this flywheel and the housing.

In one embodiment in picture 5 are in a two-part Flywheel (2 a) and (2 b) the membrane-like combined springs (15 a) and (15 b) arranged. A single spring membrane would have little stiffness in the axial direction Direction and only suffice in individual cases. To increase the rigidity According to Figure 5, two spring diaphragms are so flat cone-shaped according to the sectional view in Fig. 4 preformed that they can be with the help of shims (31) and (32) outside (for example between outer ring sections of groups (7) to (10) and others offset by 1200 Attachments) and rivets can be attached to the flywheel. The circular ring sections for the summary of the leaf springs (1) to (6) and (11) + (12) are also summarized with enclosures (34) + (35) and rivets (36). In a corresponding way are the circular ring sections for the spring groups (1) to (4) and for others around 1200 offset spring groups using shims (36), (37) and (38) and screws (39) connected to the housing (2 "'). The circular ring sections for the spring groups (5) up to (12) and for further spring groups offset by 1200 are provided with enclosures (41), (42) and (43) are combined. The lid (3 "') is in similar Form, as it was described in the design according to Figure 2, attached, however outside and inside, and outside and inside sealed. In picture 5 there are still the fin filler nozzles (44) indicated for the damping medium and the threaded pins (45) closing them.

In the design according to Figure 6, the radial leaf springs (51) according to a feature of the invention thereby increased in their effective length that the clamping ends inside (51 ') and outside (51 ") bent by 900 and designed in this way be that they are inside in circumferential grooves in the housing (54) and grooves between the housing and cover (53) can be fitted and on the outside in circumferential grooves in two parts designed swing ring with halves (51 a) and (51 b). This invention Execution saves manufacturing and assembly costs because only for clamping another clamping of the two flywheel parts (by not shown in the picture Means) is necessary.

The bent ends are, as can be seen in Figure 6, a view from the outside lets designed so that they according to a basic feature of the invention the leaf springs next to each other only touch in one area, which is not alternately deformed (because the bent end of a spring in the clamping area the next tongue is in the groove). This means that there are no changes Relative displacements at the point of contact.

In the execution according to Fig. 7 it is assumed that to achieve larger Oscillation angle of the flywheel a thinner leaf thickness for the radial leaf springs must be chosen. The clamping with the clamping ends bent by 900 (51 ') and (51 ") according to Fig. 6 would then no longer be sufficient Another feature of the invention bilateral wings (55 a) and (55 b) according to picture 7b at the clamping ends of the leaf springs before the mentioned turning of the same on their part be bent by 900, so that the spring element has the shape shown in Figure 7c receives.

After turning the clamping ends by 900 compared to the free length the leaf spring then the wings (55 a) and (55 b) are widened accordingly Grooves in the two flywheel halves (52 a) and (52 b) fitted, as shown in Figure 7a shows. The same applies to the inner clamping end of the leaf springs. The grooves are for this purpose on the one hand in the housing (54) and on the other hand between the housing and cover (53) arranged.

When using spring leaf diaphragms (15 b) as shown in Figure 4, finally every single spring element in its free length by 90 in one pre-deformed axial plane are like this picture 8 for springs (60 '), (60 "), etc. In this case, the compliance in the circumferential direction is such high that all leaf springs that are now alternately flat to be bent are cohesive can merge into an outer ring (61) and an inner ring (62) and individual springs no longer have to be lined up one behind the other as in Figure 4. If several spring membranes are used arranged next to each other, then these are expediently reduced by a fraction of the distance between two leaf springs offset from one another at an angle.

With the design according to Fig. 9, a firm clamping is achieved on the outside end of a leaf spring (71) this in a round piece with a cleared Longitudinal slot pressed and through a transverse pin (73) in the round piece in a radial Direction positioned.

The leaf spring, however, must first with its narrow end from the inside and are inserted through the bore of the flywheel (74) on the outside. Will she after pressing into the round piece p2) and inserting the transverse pin (73) radially inwards into a corresponding countersink p5), then the inner The clamping end of the leaf spring is inserted into a radial slot in the clamping ring (76 b) so that the leaf spring between the hatched part of the clamping ring in Figure 9a p6 b) and the housing (77) is positioned radially. The cross pin p3) is then axially secured by the countersink p5). The lid p8) is in a way with screwed to the housing (77) and seals the inner ring, for example with round rubber in a circumferential groove, as was previously shown in other designs. With layers (79 a) and (79 b) it is achieved once that the surface pressures between the spring and the tension rings in the alternating bending is mitigated, on the other hand they can be tolerated and selected in such a way that the desired freedom of play is guaranteed in the restraint even with alternating bending of the spring and finally in the design according to Fig. 9 c, they bring about a desirable increase in the free length of the leaf spring in the area of the radial slots of the clamping rings (76 a) and (76 b), without the clamping of the spring in the area of its outer long sides is affected. When forming the width dimensions of the leaf spring is according to the invention an optimization in the sense of a uniform bending edge tension aimed at the free spring length and a compensation of the clamping notch effect, by placing the spring on both sides at the beginning of the clamping areas between the shims (79 a) and p9 b) on the one hand and the round piece (72) on the other hand about twice as much is wide, as at the end of the radius of curvature of the free spring length. Before hanging up and screwing on the cover (78) is another clamping ring p6a), the also at the point of a leaf spring to be clamped, for example by pushing is radially slotted to reinforce the clamping effect and the radial positioning inserted.

Claims (17)

Claims visco-hydraulic torsional vibration damper with Blottfeder-supported Flywheel torsional vibration damper with spring-loaded flywheel, consisting of a housing with a circular cavity, one the cavity for the most part Part-filling flywheel, one that fills the gap between the housing and the flywheel (with relative movement between the two) energy dissipating viscous medium and elastic connecting elements between the housing and the flywheel, characterized in that that the adhesive, frictional, positive or material fit with the housing on the one hand and flywheel on the other hand connected elastic elements directed essentially radially, subjected to bending in the case of relative oscillating movement between the housing and the flywheel and are designed in such a way that there are no parts with relative movements at any point touch and rub against each other. 2) torsional vibration damper with spring-loaded flywheel according to claim 1, characterized in that the elastic connecting elements in their resilient Length are designed as leaf springs in two or more radial axial planes. 3) torsional vibration damper with spring-loaded flywheel according to claim 1 and 2, characterized in that the leaf springs largely in their resilient length as "bodies of equal strength", d. H. with the most constant edge tension possible are formed in the flat bend. 4) torsional vibration damper with spring-loaded flywheel according to claim 1 and 2, characterized in that the leaf springs are designed as stamped parts are so that they are made by punching from flat spring steel sheet or spring steel strip or Like. Can be produced. 5) torsional vibration damper with spring-loaded flywheel according to claim 1, 2 and 4, and possibly also 3, characterized in that the to the free radial spring length on both sides adjoining clamping ends of the leaf springs after punching are bent (beveled) at right angles and thus curved, that they are on both sides in circumferential grooves on the flywheel or in flywheel parts on the one hand and on the housing or in housing parts on the other. 6) torsional vibration damper with spring-loaded flywheel according to claim 1, 2, 4 and 5 and possibly also 3, characterized in that the direction circumferential grooves folded leaf spring ends are dimensioned so that with of their Alignment aid for individual radial support springs without additional ones Arrange elements in a row on the circumference. 7) torsional vibration damper with spring-loaded flywheel according to claim 1, 2, 4, 5 and 6 and possibly also 3, characterized in that the bent Leaf spring ends in the circumferential grooves around 900 in a plane perpendicular to the axis have beveled U-iron-shaped flanges so that they fit with these flanges Fit without play in grooves whose clear width is greater than the spring steel sheet thickness. 8) torsional vibration damper with spring-loaded flywheel according to claim 1, 2 and optionally further claims, characterized in that the bent Leaf spring ends are designed or recessed in such a way that in the circumferential direction on successive leaf springs only touch in sheet metal areas within the grooves, which are not elastically stressed or stressed to a negligible extent. 9) torsional vibration damper with spring-loaded flywheel according to claim 1, 2 and optionally further claims, characterized in that the Grooves receiving leaf spring ends face one another in the housing and cover on the one hand and in two flywheel halves joined together by screws, rivets or the like be incorporated and tolerated in such a way that they have a fixed clamping of the Ensure leaf spring ends. 10) torsional vibration damper with spring-loaded flywheel according to claim 1, 2 and optionally further claims, characterized in that between the flywheel halves enough space is left out that the free leaf spring parts can bend undisturbed and without risk of contact with the flywheel halves. 11) Torsional vibration damper with spring-loaded flywheel after. claim 1, 2 and optionally further claims, characterized in - that the between the lined up leaf springs in their radial free length remaining space with an elastic or viscoelastic medium, such as. B. rubber is filled. 12) torsional vibration damper with spring-loaded flywheel according to claim 1, 2 and optionally further claims, characterized in that the leaf springs dimensioned and designed in such a way that they are not only subject to operational Conditions occurring maximum relative movements between the flywheel and housing endure long-term, but also ensure that the small-sized split between the housing in the radial direction and in the axial direction in all damper positions be sufficiently preserved. 13) torsional vibration damper with spring-loaded flywheel according to claim 1, characterized in that the space in the housing within the flywheel in Sub-spaces sealed against each other are subdivided, either only to the space outside of the housing are open or only to the space within the housing. 14) Torsional vibration damper with spring-loaded flywheel according to claim 1 and 3, characterized in that within a massive swing ring of preferably approximately rectangular cross-section crossed, penetrating each other in cutouts radial leaf springs are arranged, which at their ends with the inner ring surface or are connected with cutouts in the ring in a form-fitting or butt-fitting manner and the in Radial slots that are perpendicular to each other through a round pin in the housing If necessary with adaptable shims and intermediate sheets the flywheel radially position centrally and axially approximately in the center of the housing in such a way that the radial gap on the outside of the ring and the axial gap on both sides of the flywheel remain the same in the circumferential direction even with different damper positions. 15) torsional vibration damper with spring-loaded flywheel according to claim 1, 13 and 14, characterized in that the axial form fit of the leaf spring fastening in the ring by a snap ring, preferably with an adapted end piece to compensate for unbalance is guaranteed. 16) torsional vibration damper with spring-loaded flywheel according to claim 1, 2, 3 and 4, characterized in that the radial leaf springs when punching of cut-outs remain in a flat lamella and then close on both sides Beginning of its free length between the roundings to the inside and outside remaining Circular ring can be plastically twisted by 900 with its broad side in axial planes. 17) torsional vibration damper with spring-loaded flywheel according to claim 1, 2, 3, 4 and 16, characterized in that two or more such leaf spring constructions offset at an angle to each other with their circular rings between swing ring halves be clamped on the one hand and in the housing on the other hand.