CN112443625A

CN112443625A - Torsional vibration damper

Info

Publication number: CN112443625A
Application number: CN202010595603.6A
Authority: CN
Inventors: 斯蒂芬·哈米斯; 周斌
Original assignee: Schaeffler Technologies AG and Co KG
Current assignee: Schaeffler Technologies AG and Co KG
Priority date: 2019-09-05
Filing date: 2020-06-28
Publication date: 2021-03-05
Also published as: DE102020120392A1

Abstract

The invention relates to a torsional vibration damper having an input part which is arranged so as to be rotatable about an axis of rotation and an output part which is rotatable about the axis of rotation in a limited manner relative to the input part against the action of a spring arrangement, the output part having a charging device for charging the spring arrangement on the output side and an output hub which is connected to the charging device by means of rivets, wherein the spring arrangement is mounted in an annular chamber formed by the input part and protects the annular chamber against the ingress of water. In order to protect the annular space from water penetration in a better manner, a friction-free sealing point, which is self-reinforcing to the water pressure, is provided between the input part and the output part radially outside the rivet in the annular space and/or a friction-free steering mechanism is provided radially inside the rivet between a deflection plate arranged radially inside the rivet and a reinforcing ring for the fastening opening of the input part.

Description

Torsional vibration damper

Technical Field

The invention relates to a torsional vibration damper having an input part which is arranged so as to be rotatable about an axis of rotation and an output part which is rotatable about the axis of rotation in a limited manner relative to the input part against the action of a spring arrangement, the output part having a charging device for charging the spring arrangement on the output side and an output hub which is connected to the charging device by means of rivets, wherein the spring arrangement is mounted in an annular chamber formed by the input part and protects the annular chamber against the ingress of water.

Background

A torsional vibration damper of this type is known, for example, from DE 102017119375 a 1. The torsional vibration damper disclosed therein comprises an output part and an output part, the input part forming an annular chamber for accommodating the spring mechanism, the output part having a loading mechanism for loading the spring mechanism on the output side and an output hub connected to the two disk-shaped parts of the loading mechanism by means of rivets. The disk member preloads the flange member of the spring-loaded mechanism to form the torque limiting mechanism.

According to a first embodiment, the annular chamber is pretensioned radially outside the rivet by means of a disk spring diaphragm accommodated in the rivet from the inside against the cover part of the annular chamber with the interposition of a friction ring. In an alternative embodiment, the disk spring diaphragm is fixed radially on the outside to the cover part and is axially preloaded against one of the two disk parts of the output-side loading mechanism with the friction ring disposed axially in between. The annular space is sealed radially inside the rivet by means of a friction ring, which is axially preloaded between a reinforcing ring of a fastening opening for receiving the torsional vibration damper on a crankshaft of the internal combustion engine and the output hub.

Disclosure of Invention

The object of the invention is to improve a torsional vibration damper of this type. The object of the invention is, in particular, to improve the water entry into the annular chamber while reducing the friction between the input part and the output part and while simplifying the production and assembly of the torsional vibration damper.

This object is achieved by a torsional vibration damper. The torsional vibration damper has an input part arranged rotatably about an axis of rotation and an output part which can rotate about the axis of rotation in a limited manner relative to the input part against the action of a spring means, the output part having a charging means for charging the spring means on the output side and an output hub connected to the charging means by means of a rivet, wherein the spring means is mounted in an annular chamber formed by the input part and protects the annular chamber against the ingress of water, wherein a sealing region with friction is provided between the input part and the output part radially outside the rivet at the annular chamber, which region self-intensifies the water pressure.

The torsional vibration damper mentioned serves for torsional vibration isolation of an internal combustion engine having torsional vibrations. The input part is arranged so as to be rotatable about an axis of rotation and has a fastening opening for receiving a torsional vibration damper on a crankshaft of the internal combustion engine by means of a fastening bolt. The input part is preferably provided with a reinforcement ring arranged in the hole circle region of the fastening opening, for example a reinforced sheet metal annular part stamped and deformed from sheet metal. The input part may comprise a disc-shaped part with a fastening opening and a cover part which is tightly connected to the disc-shaped part, for example welded, the disc-shaped part and the cover part forming an annular chamber. The spring mechanism can be installed in the annular chamber, for example, via arc springs arranged distributed over the circumference or an arc spring group having a plurality of arc springs nested one inside the other.

The torsional vibration damper further comprises an output part which is rotatable relative to the input part about the axis of rotation in a limited manner against the action of the spring mechanism. The output part comprises a loading mechanism of the spring mechanism on the output side and an output part connected by rivets formed by rivets distributed on the circumference.

The input-side biasing means at the input part and the output-side biasing means at the output part respectively bias the end sides of the bow springs at the input side and the output side. The input-side charging means can be formed by a press arranged on the disk element and/or on the cover element, which press engages axially into the spring cross section of the bow spring, and/or a stop connected to the disk element or to the cover element.

The output-side charging means is formed by a flange part having radially expanded arms, wherein the arms preferably engage from the radially inner side into the spring cross section. The flange part can be connected directly to the output hub by means of rivets which are arranged distributed over the circumference. Alternatively, a torque limiting mechanism may be provided between the flange member and the output hub. For example, the torque limiting mechanism can be formed by two disk-shaped parts which are accommodated in the rivet connection, the flange part being prestressed axially between the disk-shaped parts with a predetermined maximum torque.

On the radial inside of the spring means, a centrifugal pendulum may be arranged on the inside of the annular chamber. For example, the pendulum mass carrier can be formed by a flange part, or a separate pendulum mass carrier can be provided, on which the pendulum masses are pivotably mounted along a predetermined pivot path in a circumferentially distributed manner in the centrifugal force range of the output part rotating about the axis of rotation by means of pivot bearings. In this case, the pendulum masses can be arranged on both sides of a pendulum mass carrier, for example in the form of a flange, wherein axially opposite pendulum masses are connected to one another by means of an intermediate part which passes through an opening in the pendulum mass carrier to form a pendulum mass unit. For example, two pendulum masses spaced apart in the circumferential direction can be provided per pendulum mass unit, wherein the pendulum mass units are in an advantageous embodiment each formed between a running rail of the pendulum mass and a running rail of the pendulum mass carrier, wherein a pendulum roller axially straddling the running rails rolls on the running rails. In an alternative embodiment, the pivot bearing can be formed between an intermediate part accommodated in a recess of the pendulum mass carrier and a running track of the pendulum mass carrier arranged radially one above the other in the axial plane, wherein pivot rollers having substantially the same thickness as the pendulum mass carrier roll on the running track and the pendulum masses are radially one above the other in correspondence with the pendulum mass carrier to form the loss prevention means of the pivot rollers. Alternatively, the pendulum mass carrier can be formed by two side parts which form an axial central region, the pendulum mass being accommodated in the central region, and the pendulum bearing being formed by the side parts and the axially opposite running rails of the pendulum mass, on which the pendulum rollers which bridge the running rails roll. Alternatively or in addition to such a centrifugal force pendulum on the output side, at least one centrifugal force pendulum may be provided on the input side or on the outside of the output side of the annular space.

The annular chamber is preferably at least partially filled with a lubricant in order to reduce the friction of the spring means and minimize wear under the effect of centrifugal forces, in particular at high rotational speeds of the torsional vibration damper. The annular space is particularly protected against water ingress. The concept according to the invention achieves a particularly effective protection against water ingress in the case of non-negligible water pressure by: a friction-bearing sealing region, which self-intensifies the water pressure, is arranged between the input part and the output part, radially outside the rivet, in the annular space. By means of the self-reinforcing sealing point at the annular chamber, for example at the cover part, the seal can be arranged relatively far to the outside in the radial direction, so that even in the case of low water pressures, a pressure is generated at the sealing point, as a result of which an increased tightness is achieved in the radially inner region with respect to the sealing point, depending on the water pressure. The annular chamber can be easily implemented by forming a sealing point at the annular chamber, wherein for example the disk spring diaphragm forming the sealing point can be accommodated in a known manner and relative to the disk spring diaphragm fixed to the cover part without further joining processes at the rivet between the output part and the output-side charging means.

According to a further alternative embodiment, alternatively or in addition to the self-reinforcing sealing solution radially outside the rivet, a friction-free deflection mechanism can be provided radially inside the rivet between a deflector plate arranged radially inside the rivet and a reinforcing ring of the fastening opening for the input part. The friction torque which is formed between the input part and the output part can be limited to the sealing region by the frictionless steering mechanism, so that the friction hysteresis of the torsional vibration damper can be designed to be correspondingly low.

According to an advantageous embodiment of the proposed torsional vibration damper, the disk spring diaphragms accommodated in the rivet are prestressed axially with respect to the annular chamber from the outside against the cover part of the annular chamber. In contrast to a disk spring diaphragm which is prestressed against the cover part from the inside, the sealing function is self-reinforced in the presence of internal water pressure by prestressing the cover part axially from the outside, since the axial prestress between the disk spring diaphragm and the cover part at the sealing point is increased in dependence on the water pressure present and is not reduced. The pretensioning can therefore be designed to be essentially only dependent on the necessary friction torque of the basic friction between the input part and the output part, which is to be set by means of the pretensioning. In order to provide better friction conditions, a first friction ring, for example made of plastic, can be arranged between the disk spring diaphragm and the cover part.

In particular, in order to space the output hub and the cover part axially apart, a second friction ring may be arranged radially inside the first friction ring between the output hub and the cover part. In addition to this axial spacing, the second friction ring can have a friction torque between the input part and the output part, for example by means of a further seal which is fixed at the output hub between the cover part and the second friction ring and/or from the outside relative to the annular chamber. The first friction ring is accommodated in a rotationally fixed manner at the cover part or at the disk spring diaphragm and forms a frictional engagement with the disk spring diaphragm or the cover part. In this way, the first friction ring with its friction pairing and, if appropriate, the second friction ring with its friction pairing form a first friction mechanism for the basic friction between the input part and the output part.

The disk spring diaphragm can form a sealing point in a prestressed manner, for example as a single-arm lever, for example by being accommodated at a rivet or alternatively only by being supported axially and rotationally fixed at a flange of the output disk hub, at a component of the output-side loading means, for example at a flange part, at a disk part of the torque limiting means, etc. Alternatively, the disk spring diaphragm can be received on the radially inner side at a rivet or supported axially and rotationally fixed at the output part, wherein the disk spring diaphragm is supported axially on the radially inner side at the cover part and is prestressed axially with respect to the cover part with the first friction ring arranged in between on the radially outer side.

In addition to the proposed sealing point radially outside the rivet or in the case of no change in the proposed sealing point radially outside the rivet, a torsional vibration damper is also proposed which has a friction-free steering mechanism which removes the incoming water from the annular gap between the deflector plate arranged radially inside the rivet and the reinforcement ring for the fastening opening of the input part at the crankshaft of the internal combustion engine. The basic friction limitation can be limited by the frictionless steering mechanism to a first friction mechanism located radially outside the rivet. It is to be understood that in a corresponding embodiment of the steering mechanism without play, which is not mentioned, a second friction mechanism and a seal can be arranged radially inside the rivet, by arranging a friction ring, which is axially preloaded, for example by means of a disk spring diaphragm, between the input part (for example a stiffening ring) and the output part (for example a component of the loading mechanism or an output hub).

For example, the deflector plate can be arranged radially outside the stiffening ring and thus inside the annular chamber. In order to prevent water which enters during the rotation of the torsional vibration damper about the axis of rotation or due to gravity from entering the annular space again, a circumferential annular groove can be provided in the axial direction between the deflector plate and the output hub, which annular groove opens into at least one opening of the output hub. The deflector plate is conical and has a diameter that widens towards the annular groove, so that, when the torsional vibration damper rotates about the axis of rotation, water that has entered the annular gap between the reinforcing ring and the deflector plate is guided radially outward into the annular gap due to centrifugal force and is discharged outward via the at least one opening. Preferably, at least two, preferably three or more openings which are connected to the annular groove are arranged distributed over the circumference in the output hub.

In an alternative embodiment, the deflector plate can have a radially inwardly inclined flange which spans the axial flange of the stiffening ring radially inwardly with a radial gap in the axial direction, i.e. is configured conically, wherein the free end of the flange has the smallest diameter. Water which may possibly accumulate between the deflector plate and the output hub can be displaced into the through-opening of the output hub for screwing the torsional vibration damper on the crankshaft.

The deflector plate of the slack-free steering gear can be fixedly received at the rivet between the reinforcing gear and the output hub. It has been found to be advantageous if the deflector plate is inserted radially inside the rivet into an axial gap defined radially inside the rivet between the loading mechanism and the output hub. This means that the rotationally connected mounting of the deflector plate on the output part is eliminated and only a centering arrangement of the axial play between the loading mechanism and the output hub is provided.

Drawings

The invention is explained in detail on the basis of the exemplary embodiments shown in fig. 1 to 3. In which is shown:

figure 1 shows in section the upper part of a torsional vibration damper arranged rotatably about an axis of rotation,

FIG. 2 shows the upper part of the torsional vibration damper of FIG. 1 in a further section, an

Fig. 3 shows the upper part of the torsional vibration damper in section, which has a further steering mechanism in relation to the torsional vibration damper of fig. 1 and 2.

Detailed Description

Fig. 1 and 2 show the upper part of the torsional vibration damper 1 arranged about the axis of rotation d in sections along two different sectional lines. The torsional vibration damper 1 has an input part 2 and an output part 3 which are rotatable relative to one another and in a limited manner about an axis of rotation d against the action of a spring mechanism 4 and thus serve to damp torsional vibrations.

The input part 2 comprises a disk-shaped part 5 and a cover part 6, which are connected to one another radially on the outside, are welded in a sealing manner here and thus form an annular chamber 7, in which the spring means 4 is mounted. The disk-shaped part 5 has fastening openings 8 distributed over the circumference on the radial inside for fastening the torsional vibration damper 1 to a crankshaft of an internal combustion engine by means of screws, not shown, belonging to the torsional vibration damper 1, which screws are accommodated in the torsional vibration damper 1, for example, so as to be secured against loss. The reinforcing ring 9 serves to reinforce the fastening opening 8 and is made, for example, of sheet metal and, if appropriate, hardened. The reinforcing ring 9 is U-shaped in cross section and is configured with a radially outer flange 10.

A starter ring gear 11 is accommodated radially on the outside of the disc-shaped part 5.

The output part 3 comprises an output-side loading mechanism 12 and an output hub 14 which is fixed to the loading mechanism by means of rivets 13. The loading mechanism 12 is configured as a flange part 15 with arms 18 and is riveted directly to the output hub 14, the arms 18 engaging from the radially inner side between circumferentially adjacent end faces of arc springs 16, 17 of the spring mechanism 4 nested one inside the other. Alternatively, a torque limiting mechanism may be provided between the flange member 15 and the output member 3.

The arc springs 16, 17 are loaded on the input side by means of axial press-on

portions

19, 20, between which the arms 18 pass in the axial direction.

Pendulum masses

21, 22 are suspended in a manner known per se on both sides of the flange part 15 in the centrifugal force region of the flange part 15 rotating about the axis of rotation d so as to be able to pivot by means of pivot bearings, not shown, in order to form a centrifugal pendulum 23 arranged in the annular chamber 7.

The annular chamber 7 is sealed radially outside the rivet 13 between the input part 2 and the output part 3 under the influence of water in a self-reinforcing manner at a sealing point 24. For this purpose, the disk spring diaphragm 25 is fastened to the rivet 13 and is axially prestressed radially on the outside against the cover part 6 outside the annular chamber 7. In this case, a friction ring 26 made of plastic is accommodated in a rotationally fixed and centered manner in the cover part 6, the friction ring 26 being prestressed axially by means of a disk spring diaphragm 25, so that a friction torque of the steel-plastic friction pair is formed when the input part 2 and the output part 3 rotate relative to one another.

Furthermore, a friction ring 27 is arranged between the inner circumferential portion of the cover member 6 and the outer circumferential portion of the output hub 14, the friction ring 27 serving to protect the disc spring diaphragm 25 against high axial forces that occur during mounting of the transmission by engaging the transmission input shaft of the transmission into the inner toothed portion 28 of the output hub 14. The friction ring 27 can be axially prestressed by means of the disk spring diaphragm 25 axially supported on the contact surface 29 of the cover part by means of an axial force built up between the rivet and the contact surface. In this case, the friction ring 26 is prestressed by a further axial force between the contact surface 29 and the outer circumference of the disk spring diaphragm 25.

The two friction rings 26, 27 form a friction mechanism 30 with their friction pair to provide a basic friction over at least a part of the angle of rotation between the input part 2 and the output part 3. The friction means 30 can be extended or stepped in rotation angle by setting the free angle of one or both friction rings 26, 27.

The annular chamber 7 is protected radially inside the rivet 13 against the ingress of water by a friction-free steering mechanism 31. For this purpose, an annular gap 33 is formed between the axial flange 10 of the reinforcing ring 9, which projects slightly radially outward, and the annular deflector plate 32, which bridges this flange in the axial direction. The deflector plate 32 is arranged radially outside the axial flange 10 and is conically configured in such a way that, if necessary, water entering, for example, through the through-opening 34 for fastening the torsional vibration damper 1 is displaced by the free end of the deflector plate 32 in the direction of the output hub 14. The output hub 14 has an annular gap 35 at the deflector plate 32, which opens into openings 36 arranged distributed over the circumference, so that water which is displaced into the annular gap 35, for example under the influence of centrifugal force, is discharged via the openings 36.

The deflector plate 32 is inserted radially inside the rivet 13 into the axial gap 37 between the flange part 15 and the output hub 14 and is arranged centrally.

Fig. 3 shows, in a sectional view, the upper part of a torsional vibration damper 1a arranged about the axis of rotation d, which is modified with respect to the torsional vibration damper 1 of fig. 1 and 2. The torsional vibration damper 1a has a friction-free steering mechanism 31a which is varied with respect to the friction-free steering mechanism 31 of the torsional vibration damper 1.

The steering mechanism 31a comprises a centrally arranged deflector plate 32a accommodated in an axial gap 37a between the flange part 15a and the output hub 14a, the deflector plate 32a axially spanning on the radial inside an axial flange 10a of the reinforcing ring 9a, which extends radially outwards on the end side, so that a first annular gap 33a, which is formed in a labyrinth-like manner between the deflector plate 32a and the axial flange 10a, and a second annular gap 33b, which makes it difficult for water to enter into the annular chamber 7a, between a radially extending portion 38a of the flange 10a and the flange part 15 a. Due to the conical design of the annular deflector plate 32a, the diameter of which increases in the direction of the output hub 14a, the incoming water can be discharged immediately or can be collected first and then discharged through the through-opening 34a, according to the embodiment of the annular gap 35 and the opening 36 of the steering mechanism 31 in fig. 1 and 2. The

annular gaps

33a, 33b are selected to be so narrow that water with a water pressure dependent on the centrifugal force remains in the predetermined rotational speed range of the torsional vibration damper 1a on the basis of its capillary force.

List of reference numerals

1 torsional vibration damper

1a torsional vibration damper

2 input part

3 output part

4 spring mechanism

5 disc-shaped component

6 cover part

7 annular cavity

7a ring cavity

8 fastening opening

9 reinforcing ring

9a reinforcement ring

10 Flange

10a flange

11 starter gear ring

12 loading mechanism

13 riveting piece

14 output hub

14a output hub

15 Flange part

15a flange part

16 arc spring

17 arc spring

18 arm

19 pressing part

20 pressing part

21 pendulum mass

22 pendulum mass

23 centrifugal pendulum

24 sealing part

25 disc spring diaphragm

26 Friction ring

27 Friction ring

28 internal tooth part

29 contact surface

30 friction mechanism

31 steering mechanism

31a steering mechanism

32 deflection plate

32a deflector plate

33 annular gap

33a annular gap

33b annular gap

34 through hole

34a through hole

35 annular gap

36 opening

37 axial clearance

37a axial clearance

38a extension

d axis of rotation

Claims

1. A torsional vibration damper (1, 1a) having an input part (2) which is arranged so as to be rotatable about an axis of rotation (d) and an output part (3) which is rotatable about the axis of rotation (d) in a limited manner relative to the input part (2) against the action of a spring mechanism (4), which output part has a loading mechanism (12) for loading the spring mechanism (4) on the output side and an output hub (14, 14a) which is connected to the loading mechanism by means of a rivet (13), wherein the spring mechanism (4) is mounted in an annular chamber (7, 7a) formed by the input part (2) and protects the annular chamber (7, 7a) against the ingress of water, characterized in that between the input part (2) and the output part (3), radially outside the rivet (13), A friction-bearing sealing point (24) which self-intensifies the water pressure is provided at the annular chamber (7, 7 a).

2. Torsional vibration damper (1, 1a), in particular according to claim 1, having an input part (2) which is arranged rotatably about an axis of rotation (d) and an output part (3) which is rotatable about the axis of rotation (d) in a limited manner relative to the input part (2) against the action of a spring mechanism (4), which output part has a charging mechanism (12) for charging the spring mechanism (4) on the output side and an output hub (14, 14a) which is connected to the charging mechanism by means of a rivet (13), wherein the spring mechanism (4) is mounted in an annular chamber (7, 7a) formed by the input part (2) and protects the annular chamber (7, 7a) from water ingress, characterized in that a deflection plate (32) which is arranged radially inside the rivet (13), 32a) And a friction-free steering mechanism (31, 31a) is arranged between the reinforcing rings (9, 9a) of the fastening opening (8) for the input part (2).

3. The torsional vibration damper (1, 1a) as claimed in claim 1 or 2, characterized in that the disk spring diaphragm (25) accommodated at the rivet (13) is prestressed axially with respect to the annular chamber (7, 7a) from the outside against the cover part (6) of the annular chamber (7, 7 a).

4. A torsional vibration damper (1, 1a) as claimed in claim 3, characterized in that a first friction ring (26) is provided between the belleville spring diaphragm (25) and the cover member (6).

5. Torsional vibration damper (1, 1a) as claimed in claim 4, characterized in that a second friction ring (27) is arranged radially inside the first friction ring (26) between the output hub (14, 14a) and the cover member (6).

6. The torsional vibration damper (1, 1a) as claimed in claim 4 or 5, characterized in that the disk spring diaphragm (25) is supported axially on the radially inner side at the cover part (6) and is prestressed axially on the radially outer side with the first friction ring (26) interposed against the cover part (6).

7. The torsional vibration damper (1) as claimed in any of claims 2 to 6, characterized in that the deflector plate (32) is arranged radially outside the stiffening ring (9) and a surrounding annular gap (35) opening into at least one opening (36) of the output hub (14) is provided axially between the deflector plate (32) and the output hub (14).

8. The torsional vibration damper (1a) as claimed in any of claims 2 to 6, characterized in that the deflection plate (32a) has a radially inwardly inclined flange which spans the axial flange (10a) of the stiffening ring (9a) radially inwardly with a radial gap in the axial direction.

9. The torsional vibration damper (1, 1a) as claimed in any of claims 2 to 8, characterized in that the deflection plate (32, 32a) is inserted radially inside the rivet (13) into an axial gap (37, 37a) defined radially inside the rivet between the loading mechanism (12) and the output hub (14, 14 a).

10. The torsional vibration damper (1, 1a) as claimed in any of claims 1 to 9, characterized in that pendulum mass pieces (21, 22) forming a centrifugal pendulum (23) are arranged at the loading means (12) radially inside the spring means (4) distributed over the circumference.