DE102015224241A1 - centrifugal pendulum - Google Patents

Abstract

It is a centrifugal pendulum (10) for damping rotational irregularities introduced via a drive shaft of an automobile engine provided with a connectable to the drive shaft support flange (14), a monofilar to the support flange (14) connected first part pendulum mass (18) for generating a rotation non-uniformity Return moments, a monofilar on the support flange (14) connected second part pendulum mass (20) for generating a rotational irregularity opposing return torque and on the first part pendulum mass (18) and the second part pendulum mass (20) engaging coupling spring (22) for moving apart of the centers of mass ( 28, 30) of the sub-pendulum masses (18, 20), under centrifugal force the mass centers of gravity (28, 30) of the sub-pendulum masses (18, 20) against the spring force of the coupling spring (22) are movable towards each other. By means of the coupling spring (22) coupled to each other Teiltriebelmassen (18, 20), the effective theoretical pendulum length (l) of the centrifugal pendulum (10) can be changed centrifugal force to set a suitable Tilgerordnung for the current rated speed, so that a drive train of a motor vehicle with a good damping capacity of torsional vibrations is possible.

Description

The invention relates to a centrifugal pendulum for damping rotational irregularities introduced via a drive shaft of a motor vehicle engine, with the aid of which a restoring torque directed counter to rotational nonuniformity can be generated.

Out WO 2015/043591 A1 is a centrifugal pendulum for damping introduced via a drive shaft of a motor vehicle rotational irregularities known monofilar over only one connection point and bifilar over two connection points on a support flange pendulum connected pendulum masses may have.

There is a constant need to improve the damping capacity of torsional vibrations in a drive train of a motor vehicle.

It is the object of the invention to show measures that allow a drive train of a motor vehicle with a good damping capacity of torsional vibrations.

The object is achieved by a centrifugal pendulum with the features of claim 1. Preferred embodiments of the invention are set forth in the dependent claims and the description below, each of which individually or in combination may constitute an aspect of the invention.

According to the invention, a centrifugal pendulum for damping rotational irregularities introduced via a drive shaft of a motor vehicle engine is provided with a carrier flange which can be connected to the drive shaft, a monofilar first partial pendulum mass connected to the carrier flange for producing a restoring torque directed against rotational nonuniformity, a monofilar second pendulum mass connected to the carrier flange for generating one of the rotational irregularity opposing return torque and acting on the first part pendulum mass and the second part pendulum mass coupling spring for moving apart the centers of mass of the pendulum masses, under centrifugal force, the centers of mass of the pendulum masses against the spring force of the coupling spring are movable towards each other.

A total mass center of gravity of a theoretical pendulum mass of the centrifugal pendulum pendulum is composed by the position of the center of mass of the pendulum masses coupled to one another via the coupling spring. A change in position of the centers of gravity of the pendulum masses, in particular by pivoting the sub-pendulum masses about a pendulum axis set to the assigned center of gravity, can lead to a change in position of the total mass center of gravity of the centrifugal pendulum. When the sub-pendulum masses are moved away from each other by the coupling spring, the sub-pendulum masses can be pivoted to a position in which the center of gravity of the sub-pendulum masses are positioned closer to a pivot axis of the support flange. As a result, the total mass center of gravity of the centrifugal pendulum on a lower theoretical pendulum length to a theoretical pivot point of the composite of the part pendulum masses and the coupling spring acting as a theoretical pendulum mass overall system. If at a rising nominal speed of the support flange greater centrifugal forces act on the sub-pendulum masses, at least a part of the force acting on the sub-pendulum mass spring force of the coupling spring can be overcome, so that the Teilpendelmassen can move towards each other. As a result, the center of gravity of the sub-pendulum masses can be positioned further away from the axis of rotation of the carrier flange, whereby the total mass center of gravity of the centrifugal pendulum has a larger theoretical pendulum length to the theoretical pivot point of the theoretical pendulum mass. An absorber order Q of the centrifugal pendulum results in the theoretical pendulum length l and the distance L of the theoretical pivot point to the axis of rotation of the carrier flange to Q = √ (L / l). This means that, with an increasing rotational speed and the spring force of the coupling spring compensating centrifugal force acting on the partial pendulum masses, the absorber arrangement of the centrifugal pendulum mass is reduced.

A large Tilgerordnung Q is particularly effective at large pivoting angles of the centrifugal pendulum, with smaller pivoting angles less effect is achieved. A low Tilgerordnung Q is particularly effective at small pivoting angles of the centrifugal pendulum, but with large swing angles less effect is achieved. However, it was found that the maximum intended pivoting angle is essentially used only at low speeds and at high speeds only lower tilt angles occur. Due to the deliberate reduction of the absorber order with increasing speeds due to the centrifugal force-induced increase in the theoretical pendulum length, the absorber arrangement can be automatically adapted to the respective rated speed. As a result, both at a low rated speed and at a high rated speed Tilgerordnung for centrifugal pendulum can be achieved for the corresponding speed a good damping result in rotational irregularities, for example in the form of speed fluctuations with the frequency of an integer multiple Engine order, reach. By coupled via the coupling spring each other part pendulum masses, the effective theoretical pendulum length of the centrifugal pendulum pendulum can be changed due to centrifugal force to set a suitable Tilgerordnung for the current rated speed, so that a drive train of a motor vehicle with good damping capacity of torsional vibrations is possible.

Due to the monofilament connection of the sub-pendulum masses, the respective sub-pendulum mass has only exactly one connection to the support flange. In particular, the respective part pendulum mass is rotatably connected to exactly one pivot point about a pendulum axis stationary to the support flange. For example, the respective part pendulum mass is rotatably connected via a bearing pin inserted in a corresponding opening with the support flange. The monofilar connection of the sub-pendulum masses leads to a comparatively simple movement profile of the respective sub-pendulum mass relative to the support flange, which consists in particular in a pure about an eccentric to the axis of rotation of the Trägerflanschs arranged pendulum axis pivoting movement along which the pendulum mass pendulum back and forth can oscillate in both circumferential directions. If the first part pendulum mass and the second part pendulum mass are rotatably mounted about a common pendulum axis, the common pendulum axis represents the theoretical pivot point of the compound pendulum masses and the coupling spring theoretical pendulum mass of the centrifugal pendulum. If the first part pendulum mass and the second part pendulum mass to different staggered pendulum axes are rotatably mounted, the theoretical pivot point of the theoretical pendulum mass of the centrifugal pendulum as the center of the movement curve of the total center of gravity of the considered pendulum mass of the centrifugal pendulum. The sub-pendulum masses are in particular symmetrical, preferably mirror-image, configured so that the same inertial mass and the same mass moment of inertia result for the part pendulum masses. Preferably, the first part pendulum mass and the second part pendulum mass are designed as equal parts, wherein the second part pendulum mass is rotated around a radially extending axis by 180 ° compared to the first part pendulum mass.

The pendulum masses of the centrifugal pendulum under the influence of centrifugal force endeavor to assume a position as far as possible from the center of rotation. The "zero position" is thus the radially furthest from the center of rotation remote position, which can take the pendulum mass in the radially outer position. At a constant input speed and constant drive torque, the center of gravity of the pendulum mass will occupy this radially outer position. With speed fluctuations, the pendulum mass deflects due to their inertia. The center of gravity of the pendulum mass can be moved in the direction of the center of rotation. The centrifugal force acting on the pendulum mass is thereby divided into one component tangentially and another component normal to the pendulum track. The tangential force component provides the restoring force which the pendulum mass wants to return to its "zero position" while the normal force component acts on a force introduction element introducing the rotational speed fluctuations, in particular a flywheel connected to the drive shaft of the motor vehicle engine and generates a counter moment there, that of the rotational speed fluctuation counteracts and dampens the introduced speed fluctuations. For particularly strong speed fluctuations, the center of mass of the pendulum mass can therefore be maximally swung and assume the radially innermost position. In particular, several pendulum masses can be distributed uniformly in the circumferential direction. The inert mass of the pendulum mass and / or the relative movement of the pendulum mass to the support flange is designed in particular for damping a specific frequency range of rotational irregularities, in particular an engine order of the motor vehicle engine. In particular, more than one pendulum mass and / or more than one support flange is provided. For example, the support flange is arranged between two pendulum masses. Alternatively, the pendulum mass can be accommodated between two flange parts of the support flange, wherein the flange parts are connected to each other in a Y-shape, for example.

In particular, a pivotable in the printing direction of the coupling spring pivot angle of the first part pendulum mass and the second part pendulum mass is limited by a limit stop. As a result, it can be prevented that the center of mass of the respective pendulum pendulum mass gets into a radius lying within its pendulum axis and thus does not dampen but rather amplifies speed fluctuations.

Preferably, a first pendulum volume which can be painted over by the first part pendulum mass is spaced apart from a second pendulum volume which can be passed over by the second part pendulum mass. As a result, it can be safely avoided that the sub-pendulum masses can block each other when moving towards each other. The pendulum masses can instead be moved past each other. Optionally, the pendulum masses in a relative position, in which the center of mass of the respective part pendulum mass are positioned at most far radially outward, abut each other to block swinging the center of mass to a smaller radius.

Particularly preferably, the first part pendulum mass is arranged offset from one another to the second part pendulum mass in the axial direction. As a result, depending on the oscillation angle in the axial direction, the part pendulum masses can at least partially overlap without striking each other, so that installation space in the circumferential direction can be saved. As a result, it is possible to provide a particularly large number of pendulum masses in the circumferential direction one behind the other, in particular in pairs, by coupled-together partial pendulum masses. The damping effect can be correspondingly high.

In particular, the first part pendulum mass are rotatable about a first pendulum axis and the second part pendulum mass about a second pendulum axis, wherein the first pendulum axis and the second pendulum axis have a substantially equal distance from a rotation axis of the support flange. The arrangement of the pendulum axes on a common radius to the axis of rotation of the support flange can result in substantially symmetrical, in particular mirror-image, motion profiles for the sub-pendulum masses. This results in a similar motion profile in both pivot directions for the trained by the coupled part pendulum masses theoretical pendulum mass. The total mass center of gravity can thereby move on a circular path about a pivot point, which lies centrally on an imaginary connecting line between the pendulum axes of the sub-pendulum masses.

Preferably, the first part pendulum mass and the second part pendulum mass about a common pendulum axis, in particular via a common bearing pin, rotatable. A first pendulum axis of the first part pendulum mass and a second pendulum axis of the second part pendulum mass can thereby coincide to form a common pendulum axis, which can simultaneously represent the pivot point for the total mass center of the combined pendulum mass by the coupled part pendulum masses. This makes it possible to store both the first part pendulum mass and the second part pendulum mass by a common bearing pin monofilar to the support flange, resulting in a low-cost and simple construction with few components.

Particularly preferably, the coupling spring is designed as a tensile or compressive loaded coil spring, torsion spring, leg spring, bow spring or bow spring. Depending on the arrangement, storage and design of the sub-pendulum masses, a suitable coupling spring can be selected. It is possible that the coupling spring acts radially outward to the pendulum axis of the part pendulum masses as a compression spring or radially within the pendulum axis of the pendulum masses as a tension spring on the part pendulum masses.

In particular, the coupling spring is guided on the support flange or a component connected to the support flange, in particular a bearing bolt for mounting the first part pendulum mass and / or the second part pendulum mass. Even with a sudden impact of torque ("Impact"), the correct relative position of the coupling spring can be maintained. For example, the coupling spring can be wound as a torsion spring or leg spring around a part of the bearing pin.

Preferably, the first part pendulum mass and the second part pendulum mass is arranged in the axial direction between the support flange and a cover connected to the support flange, wherein the support flange and the cover substantially completely cover the first part pendulum mass and the second part pendulum mass viewed in the axial direction. The sub-pendulum masses can thereby be received protected in a formed between the support flange and the Teckel receiving space. Preferably, the support flange covers the part pendulum masses radially outward and can additionally serve as bursting protection.

Particularly preferably, the first part pendulum mass and / or the second part pendulum mass under a centrifugal force, in particular against a spring force of a retaining spring, with a proportion displaceable radially outward mass body for centrifugally induced displacement of the center of mass of the pendulum mass. By means of the mass body which can be displaced relative to the partial pendulum mass, the center of mass of the pendulum mass can be changed as a function of the centrifugal force acting on the mass body. At a high speed and high attacking centrifugal forces, the center of mass of the pendulum mass shifts to a larger radius. The relevant for the Tilgerordnung pendulum length can be influenced not only by the pivot angle of the first part pendulum mass and the second part pendulum mass but also by the change of the center of mass within the respective part pendulum mass by the centrifugal force displacement of the mass body. This makes it possible via the spring characteristic of the coupling spring and the spring characteristic of the retaining spring to adjust the course of Tilgerordnung depending on the current speed suitable and to provide different gradients of Tilgerordnung in different speed ranges.

The invention will be explained by way of example with reference to the accompanying drawings based on preferred embodiments, wherein the features shown below both individually and in combination may constitute an aspect of the invention. Show it:

1 FIG. 2 is a schematic diagram of a first embodiment of a centrifugal pendulum, FIG.

2 : a simplified schematic diagram of the centrifugal pendulum from 1 at a low speed,

3 : a simplified schematic diagram of the centrifugal pendulum from 1 at a medium speed,

4 : a simplified schematic diagram of the centrifugal pendulum from 1 at a high speed,

5 : A schematic sectional view of an embodiment of the centrifugal pendulum 4 .

6 FIG. 2 is a simplified schematic diagram of a second embodiment of a centrifugal pendulum at a low speed. FIG.

7 : a simplified schematic diagram of the centrifugal pendulum from 6 at a medium speed and

8th : a simplified schematic diagram of the centrifugal pendulum from 6 at a high speed.

This in 1 shown centrifugal pendulum 10 has one about a rotation axis 12 rotatable support flange 14 on, with the several circumferentially successively arranged pendulum masses 16 pendelbar are connected. The pendulum masses 16 Here are each by a first part pendulum mass 18 and a second partial pendulum mass 20 composed of a, designed for example as a helical compression spring, coupling spring 22 connected to each other. The first part pendulum mass 18 is a first swing axle 24 rotatable with the support flange 14 coupled while the second part pendulum mass 20 around a second swing axle 26 rotatable with the support flange 14 is coupled. In the illustrated embodiment fall the first pendulum axis 24 and the second pendulum axis 26 to a common pendulum axis together, where it is also possible that the pendulum axes 24 . 26 are provided spaced apart on a common radius in the circumferential direction. In one in the support flange, for example, from a drive shaft of an automotive engine in a drive train of a motor vehicle, initiated rotational nonuniformity from the part pendulum masses 18 . 20 and the coupling spring 22 composite pendulum mass 16 due to their inertia deflect and thereby a rotational nonuniformity opposite restoring moment in the support flange 14 initiate.

The first part pendulum mass 18 has a first center of mass 28 and the second part pendulum mass 20 a second center of mass 30 on. In regular operation, when the support flange rotates at a certain rated speed, it engages at the center of mass 28 . 30 the partial pendulum masses 18 . 20 a centrifugal force 32 on, due to the deflected from the radial direction relative position of the Teilpendelmassen 18 . 20 has a proportion in the tangential direction. Due to the tangential part of the centrifugal force 32 become the center of gravity 28 . 30 the partial pendulum masses 18 . 20 pressed against each other. The coupling spring 22 however, attacks with a spring force 34 at the partial pendulum masses 18 . 20 to the sub-pendulum masses 18 . 20 move apart so that the tangential part of the centrifugal force 32 the spring force 34 the coupling spring 22 directed against. The partial pendulum masses 18 . 20 occupy thereby a relative position to each other, which is due to the balance of forces between the tangential part of the centrifugal force 32 and the spring force 34 the coupling spring 22 results.

As in 2 is shown at a low speed, the centrifugal force 32 small, so the sub-pendulum masses 18 . 20 from the spring force 34 the coupling spring 22 are pushed far apart. The centers of mass 28 . 30 the partial pendulum masses 18 . 20 As a result, they are located at a smaller radius to the axis of rotation 12 , This is also an overall mass focus 36 the from the Teilpendelmassen 18 . 20 and the coupling spring 22 composite pendulum mass 16 at a smaller radius to the axis of rotation 12 arranged. A pendulum length l of the total mass center of gravity 36 the pendulum mass 16 to one by the pendulum axles 24 . 26 defined pivot point, in the illustrated embodiment, with the common pendulum axis of the pendulum masses 18 . 20 coincides, is comparatively short. At a rising speed, as in 3 represented the centrifugal force 32 a part of the spring force 34 the coupling spring 22 overcome, so that the sub-pendulum masses 18 . 20 approach. As a result, mass centers of gravity shift 28 . 30 the partial pendulum masses 18 . 20 and thus also the overall mass center of gravity 36 the pendulum mass 16 to a larger radius. Because the pivot point of the pendulum mass 16 not shifted but the overall mass 36 moves radially outward, the pendulum length l increases. Due to the non-changing pivot point of the pendulum mass 16 remains a distance L of the pivot point of the pendulum mass 16 to the axis of rotation 12 constant. The order of correction Q = √ (L / l) is thereby reduced. As in 4 can be shown at a maximum speed the Teilpendelmassen 18 . 20 have approached so far that in extreme cases, the main centers of gravity 28 . 30 and, if appropriate, essentially also the overall mass center of gravity 36 are arranged one behind the other in the axial direction. The pendulum length l is maximum in this case and the absorber order Q minimal.

As in 5 shown, the sub-pendulum masses 18 . 20 be arranged in the axial direction one behind the other, so that they can not strike against each other when pivoting. This also allows both partial pendulum masses 18 . 20 with the help of a common bearing bolt 38 rotatably store. The bearing bolt 38 can do this at one of the support flange 14 pointing away axial side in one with the support flange 14 connected lid 40 be held. The pendulum mass 16 can thereby between the lid 40 and the carrier flange 14 be taken captive and covered in the axial direction and protected against environmental influences. In the illustrated embodiment, the support flange surrounds 14 with the help of a starter ring 42 the pendulum mass 16 radially outside, leaving the pendulum mass 16 in a closed reception room 44 protected may be included. In addition, the carrier flange acts 14 with his starter ring 42 as burst protection for the pendulum mass 16 ,

At the in 6 . 7 and 8th illustrated embodiment of the centrifugal pendulum 10 is compared to the in 1 to 5 shown embodiment of the centrifugal pendulum 10 the coupling spring 22 designed as a torsion spring with protruding legs. The coupling spring 22 can characterized on the sides facing away from the parts pendulum masses 18 . 20 attack. This facilitates the coupling spring 22 so far as to compress that the mass centers of gravity 28 . 30 are arranged at maximum speed in the axial direction one behind the other, without the material of the coupling spring 22 such a close approximation of the partial pendulum masses 18 . 20 blocked. The coupling spring 22 can on the bearing pin 38 be plugged so that the coupling spring on the support flange 14 is guided.

LIST OF REFERENCE NUMBERS

10

 centrifugal pendulum

12

 axis of rotation

14

 beam flange

16

 pendulum mass

18

 first part pendulum mass

20

 second part pendulum mass

22

 coupling spring

24

 first swing axle

26

 second swing axle

28

 first center of mass

30

 second center of mass

32

 centrifugal

34

 spring force

36

 Total center of gravity

38

 bearing bolt

40

 cover

42

 starter wreath

44

 accommodation space

l

 pendulum length

L

 distance

Q

 Tilgerordnung

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

• WO 2015/043591 A1 [0002]

Claims (10)

Centrifugal pendulum for damping rotational irregularities introduced via a drive shaft of a motor vehicle engine, with a carrier flange which can be connected to the drive shaft (US Pat. 14 ), a monofilar on the support flange ( 14 ) connected first part pendulum mass ( 18 ) for generating a rotational irregularity opposing return torque, a monofilar to the support flange ( 14 ) connected second part pendulum mass ( 20 ) for generating a rotational irregularity opposing return torque and one on the first part pendulum mass ( 18 ) and the second part pendulum mass ( 20 ) engaging coupling spring ( 22 ) for separating the centers of gravity ( 28 . 30 ) of the partial pendulum masses ( 18 . 20 ), whereby under centrifugal influence the centers of mass ( 28 . 30 ) of the partial pendulum masses ( 18 . 20 ) against the spring force of the coupling spring ( 22 ) are movable towards each other. Centrifugal pendulum according to claim 1, characterized in that in the pressure direction of the coupling spring ( 22 ) paintable pivot angle of the first part pendulum mass ( 18 ) and the second part pendulum mass ( 20 ) is limited by a limit stop. Centrifugal pendulum according to claim 1 or 2, characterized in that one of the first part pendulum mass ( 18 ) paintable first pendulum volume to one of the second part pendulum mass ( 20 ) übersteichbaren second pendulum volume is spaced. Centrifugal pendulum according to one of claims 1 to 3, characterized in that the first part pendulum mass ( 18 ) to the second part pendulum mass ( 20 ) is arranged offset in the axial direction to each other. Centrifugal pendulum according to one of claims 1 to 4, characterized in that the first part pendulum mass ( 18 ) about a first pendulum axis ( 24 ) and the second part pendulum mass ( 20 ) about a second pendulum axis ( 26 ) are rotatable, wherein the first pendulum axis ( 24 ) and the second pendulum axis ( 26 ) a substantially equal distance to a rotation axis ( 12 ) of the carrier flange ( 14 ) exhibit. Centrifugal pendulum according to one of claims 1 to 5, characterized in that the first part pendulum mass ( 18 ) and the second part pendulum mass ( 20 ) about a common pendulum axis ( 24 . 26 ), in particular via a common bearing pin ( 38 ), are rotatable. Centrifugal pendulum according to one of claims 1 to 6, characterized in that the coupling spring ( 22 ) is designed as a tensile or compressive loaded coil spring, torsion spring, leg spring, bow spring or bow spring. Centrifugal pendulum according to one of claims 1 to 7, characterized in that the coupling spring ( 22 ) on the support flange ( 14 ) or one with the carrier flange ( 14 ), in particular a bearing pin ( 38 ) for storing the first part pendulum mass ( 18 ) and / or the second part pendulum mass ( 20 ) is guided. Centrifugal pendulum according to one of claims 1 to 8, characterized in that the first part pendulum mass ( 18 ) and the second part pendulum mass ( 20 ) n axial direction between the support flange ( 14 ) and one with the support flange ( 14 ) associated lid ( 40 ), wherein the support flange ( 14 ) and the lid ( 40 ) the first part pendulum mass ( 18 ) and the second part pendulum mass ( 20 ) in the axial direction substantially completely cover. Centrifugal pendulum according to one of claims 1 to 9, characterized in that the first part pendulum mass ( 18 ) and / or the second part pendulum mass ( 20 ) an under centrifugal force, in particular against a spring force of a retaining spring, with a proportion radially outwardly displaceable mass body for centrifugally displaced mass center of gravity ( 28 . 30 ) of the partial pendulum mass ( 18 . 20 ) having.

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