DE102009039989B4 - Pulley with spring damper device - Google Patents

Abstract

Belt pulley (1) for branching off mechanical energy of an internal combustion engine (3) by means of a belt, comprising: - an input part (9) which can be assigned to a crankshaft of the internal combustion engine (3) in a rotationally fixed manner, - coaxially and rotatable by a rotation angle (± δ) Input part (9) mounted and the belt assignable output part (25), - between the input part (9) and the output part (25) connected spring damper means (31) with at least one bow spring (33) for damping torsional vibrations, characterized in that the angle of rotation (± δ) from a spring angle ± φ, in which the input part (9) and the output part (25) against a spring force of the at least one bow spring (33) of the spring damper (31) are rotatable relative to each other, and a clearance angle (± α), with an amount α of at least 5 degrees, at which the input part (9) and the output part (25) are substantially free of the spring force of the at least one bow spring (33). the spring damper device (31) are rotatable relative to each other, composed.

Description

The invention relates to a pulley for branching mechanical energy of an internal combustion engine by means of a belt, with a crankshaft of the internal combustion engine rotatably assignable input part, a coaxial and rotatable about a rotational angle relative to the input part mounted and the belt assignable output part and between the input part and the output part switched spring damper device with at least one bow spring for damping torsional vibrations.

Pulleys can be used to drive aggregates by means of the internal combustion engine. For this purpose, the pulley and the unit can be assigned to each other by means of the belt. The unit may be, for example, a starter generator, wherein mechanical energy from the starter generator to the internal combustion engine, for example, for starting, can be transmitted. The not yet published application of the same applicant with the file number DE 10 2007 058 018 A1 envisages a concept for reducing vibration energy during start-stop operations and at low speeds with so-called trailed friction. Another not yet published German application of the same applicant with the file number DE 10 2009 004 713 A1 shows another possibility, which consists in the upstream of a thrust-side freewheel. The DE 10 2005 043 563 B3 relates to a pulley, characterized in that a clearance is provided, which makes it possible to rotate the first and the second component relative to each other over a limited angular range, without the spring being deformed. The DE 41 03 213 A1 relates to a pulley, in particular for motor vehicles, which can be fastened to an output shaft of an internal combustion engine, such as the crankshaft, in which a circumferentially elastic damping device is provided between an input part fixedly connected to the output shaft and an output part designed as a belt pulley.

The object of the invention is to provide a comparison with the prior art improved and / or alternative pulley.

The object is in a pulley for branching mechanical energy of an internal combustion engine by means of a belt, with a crankshaft of the internal combustion engine rotatably assignable input part, a coaxial and rotatable about a rotation angle rotatably mounted to the input part and the belt assignable output part and between the input part and the Output part connected spring damper device with at least one bow spring for damping torsional vibrations, achieved in that the angle of rotation from a spring travel angle, wherein the input part and the output part against a spring force of the at least one bow spring of the spring damper device are rotatable relative to each other, and a clearance angle, with a Amount of at least 5 degrees, in which the input part and the output part are substantially free of the spring force of the at least one bow spring of the spring damper device rotatable relative to each other, composed. The internal combustion engine, the input part and the output part of the pulley and / or the pulley driven aggregate form a vibratory system that can advantageously be detuned by means of the clearance angle so that building up of resonance can be prevented or at least reduced to a minimum, in particular Events such as start-stop, low speeds and / or load changes. Advantageously, the clearance angle ± act like a thrust-side freewheel, wherein advantageously in a coasting operation after consumption of the clearance angle ± a torque transmission is still possible. This can be utilized, for example, for starting the internal combustion engine or for recuperation in a coasting phase.

In one embodiment, it is provided that the clearance angle is at least 10 degrees, in particular at least 15 degrees, preferably between 15 degrees and 55 degrees, in particular between 25 degrees and 45 degrees. The clearance angle can be advantageously adapted to the requirements or the resonance events to be avoided.

In a further embodiment of the pulley is provided that the input part and the output part are mounted by means of a sliding bearing relative to each other rotatable. Advantageously, a plain bearing can be realized in a simple manner, for example by means of a simple sliding ring.

In a further embodiment of the pulley is provided that the input part and the output part are mounted by means of a rolling bearing relative to each other rotatable. Advantageously, by means of the rolling bearing a precise and relatively low-friction mounting of the input part and the output part possible.

In a further exemplary embodiment of the belt pulley, it is provided that the input part has an input damper cage and the output part has an output damper cage, in each case for wrapping around and supporting the at least one bow spring in at least one spring space. The input damper cage and the output damper cage are in common with the input part and the Output part also arranged relatively rotatable to each other. The input damper cage and the output damper cage can be arranged axially adjacent to each other and enclose the at least one bow spring by means of the spring space formed thereby. Advantageously, spring forces for damping torsional vibrations can be transmitted via the bow spring during relative rotation of the input part and of the output part. It is also possible, by means of friction of the at least one bow spring on the at least one spring chamber of the input damper cage and the output damper cage to allow a further damping of the relative rotational movement of the input part to the output part.

In a further embodiment of the pulley is provided that the at least one spring space by means of rotation of the input part and the output part is variable in length. Advantageously, the at least one bow spring can be compressed and the spring forces transmitted to the input part and the output part. Respective ends of the variable-length spring space can corresponding spring stops on which the at least one bow spring can strike form.

In a further embodiment of the pulley is provided that the at least one spring chamber is arcuate and has a maximum radian measure, which has a free space in forceless bow spring whose radian measure corresponds to the clearance angle. Advantageously, the spring chamber is longer than the arc spring enclosed therein, wherein the excess length, ie the free space, allows the clearance angle, which can be passed through or shortened without transmitting the spring forces of the at least one bow spring in the positive and negative directions. Regardless of this, it is possible, when reducing the free space, to transfer further frictional forces between the input part and the output part, for example by means of an additional further friction device, in particular the sliding bearing and / or by friction of the at least one bow spring on the input damper cage and / or the output damper cage.

In a further exemplary embodiment of the belt pulley, it is provided that the input part has a hub which can be assigned to the internal combustion engine and a hub flange which is fixedly connected therewith, wherein the hub flange is assigned to the input damper cage in a form-locking, frictionally engaged and / or rotationally fixed manner by means of input driving pins. Advantageously, a torque can be transmitted from the internal combustion engine to the input damper cage and from there, after the free angle has been consumed, to the at least one bow spring.

In a further exemplary embodiment of the belt pulley, it is provided that the output part has a belt running ring that can be assigned to the belt, wherein the belt running ring is assigned to the output damper cage in a form-locking, frictionally engaged and / or rotationally fixed manner by means of output driving pins. Advantageously, a torque can be transmitted to the at least one bow spring of the belt on the belt race after consumption of the clearance angle ± a.

In a further exemplary embodiment of the belt pulley, it is provided that the input part has a crankshaft vibration damper with a drive disk associated with the remaining input part and a mass ring oscillatably associated with the drive disk by means of an elastomer spring. Advantageously, by means of the crankshaft vibration damper vibrations occurring during operation of the internal combustion engine can be damped, in particular by means of eradication. Advantageously, the crankshaft vibration damper can be tuned to critical natural frequencies.

• 1 einen Längsschnitt einer Riemenscheibe mit einem mittels eines Gleitlagers relativ verdrehbar zueinander gelagerten Eingangsteil und Ausgangsteil;
• 2 einen Querschnitt der in 1 gezeigten Riemenscheibe mit Sicht auf einen Ausgangsdämpferkäfig;
• 3 einen detaillierteren Halbschnitt des in 1 gezeigten Längsschnitts der Riemenscheibe mit einer Federdämpfereinrichtung;
• 4 der in 2 gezeigte Querschnitt der Riemenscheibe, wobei im Vergleich drei Bogenfedern einseitig an dem sichtbaren Eingangsdämpferkäfig anschlagen;
• 5 eine dreidimensionale Explosionsansicht von schräg vorne der in den 1 bis 4 gezeigten Riemenscheibe;
• 6 einen Längsschnitt einer weiteren Riemenscheibe, wobei im Unterschied das Eingangsteil und das Ausgangsteil mittels eines Wälzlagers relativ verdrehbar zueinander gelagert sind;
• 7 einen detaillierteren Halbschnitt der in 6 gezeigten Riemenscheibe mit einer Federdämpfereinrichtung;
• 8 eine dreidimensionale Explosionsansicht von schräg vorne der in den 6 und 7 gezeigten Riemenscheibe und
• 9 ein Schaubild einer Torsionskennlinie der in den 1 bis 5 beziehungsweise 6 bis 8 gezeigten Riemenscheibe.

Further advantages, features and details emerge from the following description in which an exemplary embodiment is described with reference to the drawing. The same, similar and / or functionally identical parts are provided with the same reference numerals. Show it:

• 1 a longitudinal section of a pulley with a relative to one another by means of a sliding bearing rotatably mounted to each other input part and output part;
• 2 a cross section of in 1 shown pulley with view of an output damper cage;
• 3 a more detailed half-section of the in 1 shown longitudinal section of the pulley with a spring damper device;
• 4 the in 2 shown cross-section of the pulley, in comparison, three bow springs abut one-sided on the visible input damper cage;
• 5 a three - dimensional exploded view obliquely from the front of the 1 to 4 shown pulley;
• 6 a longitudinal section of another pulley, wherein in contrast the input part and the output part are mounted by means of a rolling bearing relative to each other rotatable;
• 7 a more detailed half-section of the in 6 shown pulley with a spring damper device;
• 8th a three - dimensional exploded view obliquely from the front of the 6 and 7 shown pulley and
• 9 a graph of a torsional characteristic in the 1 to 5 respectively 6 to 8th shown pulley.

1 shows a longitudinal section of a pulley 1 for branching off mechanical energy of an in 1 only by reference 3 indicated internal combustion engine by means of a in 1 not shown belt. The pulley 1 For example, a crankshaft of the engine 3 be assigned rotationally fixed and mechanical energy from the crankshaft to a belt pulley 5 the pulley 1 transfer. On the belt race 5 may run a belt, for example, a starter generator of the internal combustion engine 3 can drive.

The pulley 1 has a combustion engine 3 assignable hub 7 on, the crankshaft of the internal combustion engine 3 rotatable is assignable. The hub 7 is another component of the pulley 1 rotatably assigned, which is an input part 9 the pulley 1 form. The entrance part 9 the pulley 1 has a hub flange 11 , a crankshaft vibration damper 13 as well as an input damper cage 15 on. Alternatively, the entrance part 9 even without the crankshaft vibration damper 13 be executed. The crankshaft vibration damper 13 has a hub flange 11 rotatably associated drive plate 17 on, by means of an elastomeric spring 19 capable of swinging a mass ring 21 assigned. The crankshaft vibration damper 13 can according to the absorber principle in the internal combustion engine 3 reduce or dampen occurring vibrations. The entrance part 9 is by means of a sliding bearing 23 an output part 25 the pulley 1 assigned. The starting part 25 is by means of the sliding bearing 23 relatively rotatable to the entrance part 9 arranged. The entrance part 9 and the starting part 25 are coaxial with a rotation axis 27 the pulley 1 arranged. In this case, the input part can be used to transmit the mechanical energy 9 and the starting part 25 around the axis of rotation 27 rotate and can thereby be additionally rotated by these relative to each other. The starting part 25 points next to the belt race 5 an output damper cage 29 on.

2 shows a cross section of in 1 shown pulley 1 , wherein the output damper cage 29 is visible in a plan view.

3 shows a half-section of the in 1 illustrated longitudinal section of the pulley 1 , wherein a spring damper device 31 is shown in detail.

4 shows the in 2 illustrated cross section of the pulley 1 , where three bow springs 33 the spring damper device 31 are shown in a stop position. In 2 are the bow springs 33 in a central position within one of the input damper cage 15 and the output damper cage 29 each formed spring chamber 35 ,

5 shows a three-dimensional exploded view obliquely from the front of the crankshaft vibration damper 13 in the 1 to 4 shown pulley 1 , The following is on the 1 to 5 Referenced.

The input damper cage 15 and the output damper cage 29 each have three curved recesses 37 with a substantially semicircular cross section. The recesses 37 are circularly curved and are arranged adjacent to each other, that this total the three spring chambers 35 for receiving the three bow springs 33 form. Every spring chamber 35 has a substantially circular cross-section which is adjacent to an outer contour or a diameter of the bow springs 33 is adjusted. The spring chambers 35 or the associated recesses 37 have a radian which corresponds to an angle γ. If the input damper cage 15 and the output damper cage 29 are arranged opposite to the recesses 37 are flush with each other, so there is a spring chamber 35 , which makes the maximum circumferential extent the angle γ. The recesses 37 the output damper cage 29 and the input damper cage 15 are limited by stops at which the bow springs 33 can strike. In 2 are the bow springs 33 in the center of the spring chambers 35 arranged, so do not hit the attacks 39 on. In 4 beat the bow feathers 33 by way of example at one of the stops 39 on. It can be seen that, as in 4 shown between one of the stops 39 and the bow spring 33 depending on the rotational position of the input part 9 relative to the starting part 25 a free space 41 can remain. With correspondingly arranged recesses 37 shows this freedom 41 a maximum circumferential extent or a radian measure, the one clearance angle α equivalent. At a relative rotation of the output part 25 to the entrance part 9 Advantageously, the free space 41 , starting from the in 4 shown position, be reduced in positive or negative direction of rotation, before the bow springs 33 between the attacks 39 the recesses 37 be clamped. Advantageously, in the positive direction of rotation and in the negative direction of rotation, starting from the in 4 shown position, first the clearance angle ± a are swept over, wherein the rotational movement no spring force of bow springs 33 counteracts. In a further relative rotation, this can be against the spring force of the bow springs 33 respectively. This can be done as long as the bow springs 33 moved to block, whereby depending on the direction of rotation a spring angle ± φ can be swept over. The remaining spring chamber then 35 corresponds to a block angle β the bow feathers 33 , The angles α . β . γ . δ such as φ are in 4 located. The following applies: a rotation angle ± δ of the pulley 1 is composed of the maximum spring angle ± φ plus the clearance angle ± a, thus corresponds to the addition of twice the in 4 drawn spring angle φ the bow feathers 33 plus twice the in 4 drawn clearance angle α of the open space 41 ,

In addition to the spring force of the bow springs 33 can at a relative rotational movement of the output part 25 to the entrance section 9 still frictional forces occur. These can, for example, between the bow springs 33 and that of the output damper cage 29 and the input damper cage 15 formed spring chambers 35 go out, with the bow springs 33 in a rubbing contact with the spring chambers 35 can stand. To a possible wear-free sliding of the bow springs 33 To allow the damper cages 15 . 29 be made of plastic or have corresponding friction shells. For setting a corresponding frictional force and for axially guiding the damper cages 15 . 29 or the input part 9 and the starting part 25 can be thrust washers 43 . 47 be provided. The thrust washers 43 . 47 For example, they can have elastic properties in order to provide a contact pressure on the bow springs 33 adjust. A first thrust washer 43 is between the hub flange 11 and one end of a covenant 45 of the belt pulley 5 arranged. A second thrust washer 47 is between a circumferential lead 49 the hub 7 and another end of the covenant 45 of the belt pulley 5 arranged. Advantageously, the belt race 5 and thus the starting part 25 axially between the thrust washers 43 and 47 be guided.

As in 5 can be seen, the input damper cage 15 as well as the output damper cage 29 each a plurality of circumferentially arranged pimples 51 on, the form-fitting each in corresponding holes 53 of the hub flange 11 or the belt raceway 5 can intervene. Advantageously, the output damper cage 29 by means of the pimples 51 and the holes 53 positive fit the belt pulley 5 be assigned rotatably. Similarly, the input damper cage 15 by means of the pimples 51 the holes 53 of the hub flange 11 be associated with positive locking rotation.

Additionally and / or alternatively, the output damper cage 29 by means of three output driving pins 55 the belt race 5 be assigned rotatably. Analogously, alternatively, the input damper cage 15 by means of three input driving pins 57 non-rotatably the hub flange 11 be assigned. The driving bolts 55 . 57 can do this in appropriate holes 59 the damper cages 29 . 15 and in each case three of the holes 53 of the hub flange 11 or the belt raceway 5 be introduced.

As in 5 can be seen, for mounting, securing and / or Zentrierungszwecke two bolts 61 for assigning the hub flange 11 to the crankshaft vibration damper 13 be provided. In final assembled condition of the pulley 11 are the crankshaft vibration damper 13 , the hub flange 11 and the hub 7 Assigned to each other by means of screws not shown rotatably.

6 shows a longitudinal section of another pulley 1 , 7 shows a more detailed half-section of the in 6 shown pulley 1 , 8th shows an exploded view of in 6 and 7 shown pulley 1 , In the following, only the differences to the representation according to the 1 to 5 received.

In difference are the entrance part 9 and the starting part 25 by means of a rolling bearing 63 relatively rotatable associated with each other. The rolling bearing 63 takes over the functions of the 1 to 5 shown plain bearing 23 and the thrust washers 43 and 47 Therefore, according to the representations of the 6 to 8th can be omitted. Another difference is the belt pulley 5 plate-shaped in the direction of the crankshaft of the internal combustion engine, not shown 3 opened, where seen in the axial direction, the positions of the input damper cage 15 and the output damper cage 29 are reversed. Also, the pulley 1 according to the representation of 6 to 8th the functions of the hub 7 and the hub flange 11 in a hub entrance section 65 united. The hub entrance part 65 can the crankshaft of the engine 3 be assigned rotatably. In addition, the hub input part 65 the input damper cage 15 be assigned rotatably. Another difference is the input damper cage 15 as well as the output damper cage 29 each circularly curved ribs 67 on, each opposite the spring chambers 35 forming recesses 37 are arranged. Ribs 67 the input damper cage 15 can form-fit in circular arc-shaped slots 69 of the hub entrance part 65 of the entrance part 9 intervention. Ribs 67 the output damper cage 29 can form-fit in circular arc-shaped slots 69 of the belt pulley 5 of the starting part 25 intervention.

For receiving the rolling bearing 63 has the hub input part 65 a projection forming an inner bearing receiver 71 on, on which the rolling bearing 63 can be applied accurately. The lead 71 can in the belt raceway 5 centrically intervene, the angled collar 73 comprising, an outer bearing support of the rolling bearing 63 forms. When assembled, the rolling bearing is 63 perfectly fitting between the projection 71 of the hub entrance part 65 and the federal government 73 of the belt pulley 5 arranged.

9 shows a graph 75 a torsion characteristic 77 in the 1 to 5 or 6 to 8 illustrated pulley damper 1 , On an x-axis 79 of the graph 75 is a twist angle of the input part 9 relative to the starting part 25 applied. On a y-axis 81 of the chart 75 is a twisting motion counteracting torsional moment, that of the bow springs 33 is applied, applied. It can be seen that when sweeping the clearance angle ± a of the relative rotational movement of the input part 9 to the starting part 25 no force counteracts. The representation according to 9 can be idealized, with additionally occurring frictional forces that lead to a hysteresis-shaped formation of the torsion characteristic 77 would be neglected. Next is the torsion curve 77 it can be seen that on one, in 9 left side shown thrust side 83 , the torsional moment increases linearly. During the linear increase of the thrust torsional moment, the angle -φ is swept over. Once the angle -φ is used up, so the input part 9 and the starting part 25 on a not shown optional stop abut each other or the bow springs 33 have driven to block, the torsional moment increases almost infinitely. On one, in 9 right hand side of the train 85 results in a rotationally symmetric course of the torsion 77 , wherein also during a linear increase of the torsional moment the spring angle + φ is swept over until the torsional moment increases almost infinitely.

Additionally is in 9 by means of a downward pointing time axis 87 a time course 89 possibly occurring torsional vibrations of the input part 9 relative to the starting part 25 located. It can be seen that the vibration is partly in the spring angle + φ against the spring forces of the bow springs 33 and it oscillates to the clearance angle ± a. The passage of time 89 can, what in 9 not shown in detail, against the spring forces of the bow springs 33 and at the exhaustion of the clearance angle ± a different gradients, in particular gradients and / or amplitudes have. This can advantageously the oscillatory system of the pulley 1 be so upset that resonance catastrophes are avoidable. Further, the passage of time 89 can be seen that during the oscillation of the clearance angle ± a is not completely used up. Advantageously, this can be designed so that a mutual striking of the bow springs is avoidable.

According to the 1 to 5 the centering of the pulley takes place 1 over the plain bearing 23 , The pulley 1 , which is a vibration damper, consists of two parts, one by means of the spring damper device 31 shown torsional vibration damper and the optional crankshaft vibration damper 13 , Both are over the hub 7 centered, which is attachable to the crankshaft, not shown, by means not shown in detail axial screws.

The crankshaft vibration damper 13 has the drive plate 17 with the hub 7 is connected via the axial screws, not shown, and the mass ring 21 on. The massing 21 is about the elastomer spring 19 with the drive plate 17 coupled. A mass moment of inertia of the mass ring 21 and a spring stiffness of the elastomeric spring 19 can be advantageously adapted to Torsionseigenfrequenzen the crankshaft.

A belt drive torque can be via the hub flange 11 on the entrance damper cage 15 be directed. This entrance damper cage 15 can via positive connection with the hub flange 11 be connected.

In addition, for further stabilization, the input cam bolts 57 in the hub flange 11 riveted over the holes 59 in the input damper cage 15 can transmit a part of the belt drive torque form-fitting.

The input damper cage 15 includes the bow springs on one side 33 that absorb the belt drive torque and onto the output damper cage 29 , the bow feathers 33 also included on one side, forward.

This is form-fitting with the belt race 5 connected, which passes the belt drive torque on the belt, not shown.

Again, for stabilization the Ausgangsmitnehmerbolzen 55 in the belt raceway 5 to be riveted, which has holes 59 in the output damper cage 29 a part of the belt drive torque transmitted positively. The belt race 5 is by means of the sliding bearing 23 on the hub 7 centered and rotatable in the circumferential direction.

Laterally, the belt pulley 5 through the thrust washers 43 and 47 who are at the hub 7 or the hub flange 11 support, held axially.

A radial and centrifugal support of the bow springs 33 can by a diameter centering of the damper cages 15 . 29 in the hub flange 11 or the belt raceway 5 respectively.

The bow springs 33 For example, they can be shown running dry in plastic damper cages. However, it is also possible to realize by means of additional sealing elements running in the fat. This can, for example, as in the German application of the same applicant with the file number DE 10 2006 053 766.1 respectively. This application is incorporated by reference into the subject of the present application.

In the illustration according to the 2 and 4 you can clearly see that the bow springs 33 in the circumferential direction the advantageous clearance angle ± a to the damper cages 15 and 29 which, as shown in FIG 2 in the central position of the bow springs 33 in twice half the value a / 2 of the free space 41 corresponding clearance angle ± a divides. In a no-load operation, there may be a random location of the bow springs 33 to adjust.

As in 9 to recognize, has the torsion characteristic 77 the significant clearance angle with the amount α ≥ 5 degrees, preferably between 15 degrees and 55 degrees. While passing through this clearance angle ± α, the bow springs become 33 essentially load-free, with the exception of form or centrifugal force induced external friction, through the channels or spring chambers 35 the damper cages 15 . 29 pushed. After exhausting the clearance angle ± a, the bow springs become 33 loaded and compressed by the zug- or thrust-side angle + φ or -φ.

An end stop can either via appropriate, in the 1 to 8th Not shown stop elements between the belt race 5 and the hub flange 11 or by blocking the bow springs 33 respectively. By means of the time axis 87 is stylized a damper vibration angle at events, such as start-stop and load changes, for example, consumers switching shown.

By the illustrated zugseitige swinging in the rebound, see reference numerals 85 in 9 , within the angle + φ with a defined spring rate and in the empty stage within the clearance angle ± a, which advantageously acts as a thrust-side freewheel, with a spring rate 0 , the vibration system is detuned so that the building of resonance at one of the above-mentioned conditions can be effectively prevented.

The angles ± α and ± φ and the spring rates of the bow springs 33 can be structurally tuned or defined so that over all states an impact on the train-side or thrust-side stop or blocking the bow springs 33 safely preventable. Preferably, a design can be made so that the damper or the pulley 1 only within the angular range -φ of the thrust side 83 or + φ of the train side 85 swings. Advantageously disturbing impact noise can be avoided, resulting in a total cost-effective solution without additional components.

At the pulley 1 as shown in the 6 to 8th is the rolling bearing 63 intended. Furthermore, by means of the hub input part 65 the belt drive torque directly on the input damper cage 15 be transmitted.

LIST OF REFERENCE NUMBERS

1

pulley

3

internal combustion engine

5

Belt race

7

hub

9

introductory

11

hub flange

13

crankshaft vibration dampers

15

Input damper cage

17

driver disc

19

elastomer spring

21

ground ring

23

plain bearing

25

output portion

27

axis of rotation

29

Output damper cage

31

Spring damper device

33

bow spring

35

spring chamber

37

recess

39

attacks

41

free space

43

first thrust washer

45

Federation

47

second thrust washer

49

head Start

51

burl

53

drilling

55

Ausgangsmitnehmerbolzen

57

Eingangsmitnehmerbolzen

59

drilling

61

bolt

63

Rolling

65

Hub front end

67

ribs

69

slots

71

head Start

73

Federation

75

graph

77

torsion characteristic

79

x -Axis

81

y -Axis

83

thrust side

85

tension side

87

timeline

89

timing

Claims (10)

Belt pulley (1) for branching off mechanical energy of an internal combustion engine (3) by means of a belt, comprising: - an input part (9) which can be assigned to a crankshaft of the internal combustion engine (3) in a rotationally fixed manner, - coaxially and rotatable by a rotation angle (± δ) Input part (9) mounted and the belt assignable output part (25), - between the input part (9) and the output part (25) connected spring damper means (31) with at least one bow spring (33) for damping torsional vibrations, characterized in that the angle of rotation (± δ) from a spring angle ± φ, in which the input part (9) and the output part (25) against a spring force of the at least one bow spring (33) of the spring damper (31) are rotatable relative to each other, and a clearance angle (± α), with an amount α of at least 5 degrees, at which the input part (9) and the output part (25) substantially free of the spring force of the at least one bow spring (33) of the spring damper device (31) are rotatable relative to each other, composed. Pulley according to the preceding claim, characterized in that the clearance angle (± α) is at least 10 degrees, in particular at least 15 degrees, preferably between 15 degrees and 55 degrees, in particular between 25 degrees and 45 degrees. Pulley according to one of the preceding claims, characterized in that the input part (9) and the output part (25) by means of a sliding bearing (23) are mounted rotatable relative to each other. Pulley to one of Claims 1 or 2 , characterized in that the input part (9) and the output part (25) by means of a rolling bearing (63) are mounted relative to each other rotatable. Pulley according to one of the preceding claims, characterized in that the input part (9) has an input damper cage (15) and the output part (25) has a Ausgangsdämpferkäfig (29), respectively for enclosing and supporting the at least one bow spring (33) in at least one spring chamber (35). Pulley according to the preceding claim, characterized in that the at least one spring chamber (35) by means of rotation of the input part (9) and the output part (25) is variable in length. Pulley according to one of the preceding two claims, characterized in that the at least one spring chamber (35) is arcuate and has a maximum radian which has a free space in forceless bow spring (33) whose radian measure corresponds to the clearance angle (a). Pulley according to one of the preceding three claims, characterized in that the input part (9) has a hub (7) which can be assigned to the internal combustion engine (3) and a hub flange (11) which is assigned in a rotationally fixed manner, the hub flange (11) being connected to the input damper cage (15). positively, frictionally engaged and / or by means of Eingangsmitnehmerbolzen (57) is assigned rotationally fixed. Pulley according to one of the preceding four claims, characterized in that the output part (25) has a belt ring (5) which can be assigned to the belt, the belt race ring (5) being connected to the output damper cage (29) in a form-fitting manner, frictionally engaged and / or rotatably associated by Ausgangsmitnehmerbolzen (55). Pulley according to one of the preceding claims, characterized in that the input part (9) comprises a crankshaft vibration damper (13) with a drive disc (17) rotatably associated with the rest of the input part and a mass ring (21) vibrationally connected to the drive disc (17) by means of an elastomer spring (19) ) having.

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