DE102013212272B4 - centrifugal pendulum - Google Patents

Abstract

Centrifugal pendulum (12) with a pair of pendulum masses (38) and a pendulum flange (34), in which an arcuate cut-out (44) with a cut-out contour (46) is provided, - the pendulum masses (38) of the pair of pendulum masses being arranged on both sides of the pendulum flange and supported by at least a spacer bolt (40; 80; 84; 102; 126) guided through the cutout (44), - the spacer bolt (40; 80; 84; 102; 126) having a damping arrangement (63; 81; 85; 103; 127) with a spring (70; 82; 86; 104; 128), the damping arrangement (63; 81; 85; 103; 127) being designed to prevent the spacer bolt (40; 80; 84; 102; 126) from striking on the cutout contour (46) of the cutout (44), characterized in that the spring (70; 82; 86; 104; 128) has a first and a second spring section (72, 74, 76; 96, 98; 106, 108; 130 to 140) which are arranged overlapping one another, - wherein when the spacer bolt (40; 80; 84; 102; 12 6) the first spring section is displaced relative to the second spring section on the cut-out contour (46) of the pendulum flange (34), characterized in that the spring (70; 82; 86; 104) of the damping arrangement (63; 81; 85; 103;) is arranged circumferentially on a stop area (62) of the spacer bolt (40; 80; 84; 102; 126) and spirally radially from a longitudinal axis (58) of the spacer bolt (40; 80; 84; 102; 126) is wound outwards.

Description

The invention relates to a centrifugal pendulum according to the preamble of claim 1. In particular, the invention relates to a centrifugal pendulum with a pair of pendulum masses and a pendulum flange, in which an arcuate cutout with a cutout contour is provided, the pendulum masses of the pair of pendulum masses being arranged on both sides of the pendulum flange and supported by at least one are connected to one another by spacer bolts guided through the cutout, the spacer bolt having a damping arrangement with a spring, the damping arrangement being designed to dampen the spacer bolt hitting the cutout contour of the cutout.

From the DE 10 2011 013 232 A1 discloses a centrifugal pendulum with a pendulum flange and a pendulum mass fixed on both sides of the pendulum flange by means of a spacer bolt accommodated in an arcuate cutout of the pendulum flange, with a movement of the pair of pendulum masses being limited by a stop. In this case, the spacer bolt has a composite element which has a damping element and a ring which surrounds the damping element on the peripheral side. The ring is designed to abut against a cutout contour of the cutout. Due to the hard material combination of ring and pendulum flange, this can lead to increased wear. The damping element is usually made of rubber-like materials. These tend to become brittle in the long term, so that the damping properties of a damping element decrease. Furthermore, if the damping element is destroyed/damaged, the impact of the spacer bolt on the cutout contour can no longer be reliably damped.

As a further prior art on the DE 10 2007 029 609 A1 and the DE 10 2011 013 232 A1 referred.

The object of the invention is to reliably dampen the impact of the spacer bolt of a centrifugal pendulum on a cutout contour of a cutout and to increase the locking strength of the spacer bolt.

According to the invention, this object is achieved by a centrifugal pendulum with the features of claim 1. Advantageous embodiments are specified in the dependent claims.

This object is achieved by a centrifugal pendulum with a pair of pendulum masses and a pendulum flange in which an arcuate cutout with a cutout contour is provided, the pendulum masses of the pair of pendulum masses being arranged on both sides of the pendulum flange. These are connected to one another by at least one spacer bolt guided through the cutout. The standoff has a damping arrangement that includes a spring. The damping arrangement is designed in such a way that the spacer bolt striking the cutout contour of the cutout is cushioned. The spring comprises a first spring section and a second spring section, which are arranged at least partially overlapping, with the first spring section being displaced relative to the second spring section when the spacer bolt strikes the cutout contour of the pendulum flange.

This has the advantage that even after the first spring section has been destroyed or damaged, a damping function is still maintained by the second spring section. Furthermore, noise emissions from the centrifugal pendulum can be reliably dampened as a result. Furthermore, the production of a spring compared to a sleeve is cheaper and more reliable.

In an embodiment according to the invention, the spring of the damping arrangement is arranged circumferentially on a stop area of the spacer bolt and spirals radially outwards from a longitudinal axis of the spacer bolt. In this way, the impact of the spacer bolt on the contour of the cutout can be reliably cushioned and dampened.

In a further embodiment, the spring is arranged circumferentially on a stop area of the spacer bolt and winds parallel to a longitudinal axis of the spacer bolt body. This configuration has the advantage that the peripheral surface of a damping element arranged underneath is reliably protected by the spring.

It is particularly advantageous here if the spring has a square cross section. As a result, the spring can be provided with numerous windings and at the same time a slim design of the spring can be guaranteed.

In a further embodiment, the spring comprises a first and a second spring element, the first spring element comprising the first spring section and the second spring element comprising the second spring section, the damping arrangement comprising a damping element which is encompassed by the spring elements on the peripheral side. This allows improved damping of the impact while protecting the damp ing element of the spacer bolt can be guaranteed.

In a further embodiment, the first spring element has a bulge and the second spring element has a recess formed corresponding to the bulge, the bulge of the first spring element being designed to engage in the recess of the second spring element. This has the advantage that the spring elements of the spring are arranged in an optimal alignment with one another on the damping element.

In a further embodiment, the spring sections of the spring are arranged relative to one another in such a way that the spring sections essentially cover a peripheral surface of the spacer bolt, in particular the damping element. In this way, direct contact of the spacer bolt or a spacer bolt body or the damping element with the cut-out contour of the pendulum flange is reliably avoided.

In a further embodiment, the standoff has a standoff body, with the damping arrangement comprising a damping element which is arranged between the standoff body and the spring. In this way, the impact of the spacer bolt on the contour of the cutout is particularly well cushioned

In a further embodiment, the spring has a material whose strength is higher than the strength of the damping element. In this way, reliable protection of the damping element by the spring when the spacer bolt hits the contour of the cutout is ensured.

• 1 einen Längsschnitt durch einen Torsionsschwingungsdämpfer mit angeordnetem Fliehkraftpendel;
• 2 eine perspektivische Ansicht des Fliehkraftpendels;
• 3 einen Ausschnitt des in 2 gezeigten Fliehkraftpendels;
• 4 eine Draufsicht auf ein Fliehkraftpendel;
• 5 einen Ausschnitt des in 4 gezeigten Fliehkraftpendels;
• 6 eine Seitenansicht einer ersten Ausführungsform eines Abstandsbolzens des in 1 bis 5 gezeigten Fliehkraftpendels;
• 7 einen Längsschnitt durch den in 6 gezeigten Abstandsbolzen;
• 8 eine Seitenansicht einer zweiten Ausführungsform eines in 1 bis 5 gezeigten Abstandsbolzens;
• 9 eine Seitenansicht einer dritten Ausführungsform eines Abstandsbolzens;
• 10 eine Seitenansicht einer vierten Ausführungsform eines Abstandsbolzens; und
• 11 einen Längsschnitt durch den in 10 gezeigten Abstandsbolzen.

The invention is explained in more detail below with reference to figures. They show:

• 1 a longitudinal section through a torsional vibration damper with arranged centrifugal pendulum;
• 2 a perspective view of the centrifugal pendulum;
• 3 a section of the in 2 shown centrifugal pendulum;
• 4 a plan view of a centrifugal pendulum;
• 5 a section of the in 4 shown centrifugal pendulum;
• 6 a side view of a first embodiment of a spacer bolt in 1 until 5 shown centrifugal pendulum;
• 7 a longitudinal section through the in 6 standoffs shown;
• 8th a side view of a second embodiment of an in 1 until 5 standoff shown;
• 9 a side view of a third embodiment of a standoff;
• 10 a side view of a fourth embodiment of a standoff; and
• 11 a longitudinal section through the in 10 shown standoffs.

In 1 a side view of a torsion guide damper 10 with centrifugal pendulums 12 arranged thereon is shown. A disk carrier 16 acting as a clutch output of a clutch device is arranged on a damper input part 14 of the torsional vibration damper 10 designed as a series damper. The clutch device can be designed, for example, as a converter lockup clutch or as a wet clutch. The torsional vibration damper 10 is effectively connected between the clutch output and an output hub 18, the output hub 18 being connectable via a gearing 20 to a transmission input shaft of a transmission in a drive train of a motor vehicle.

The damper input part 14 is centered radially on the inside of the output hub 18 and accommodated in an axially secured manner and encircles first energy storage elements 22 radially on the outside, for example arc springs, which effectively connect the damper input part 14 to an intermediate damper part 24, with the intermediate damper part 24 being rotatable to a limited extent relative to the damper input part 14. The intermediate damper part 24 can in turn be rotated to a limited extent relative to a damper output part 28 by the action of second energy storage elements 26 located radially further inwards, for example compression springs. The damper output part 28 is non-rotatably connected to the output hub 18, for example via a welded connection.

The intermediate damper part 24 consists of two axially spaced disk parts 30, 32 which enclose the damper part 28 axially. One disk part 32 is extended radially outwards to form a pendulum flange 34 . The pendulum flange 34 is integrated into the disk part 32, but can also be fastened to it as a separate component. The pendulum flange 34 is a component of the centrifugal pendulum 12. The disk part 32 is connected in a rotationally fixed manner radially on the inside to a turbine hub 36, which is designed to connect a turbine wheel of a hydrodynamic torque converter. The turbine hub 36 is centered on the output hub 18 and is rotatable relative thereto.

In a radially outer section, the pendulum flange 34 of the centrifugal pendulum 12 accommodates two axially oppositely arranged pendulum masses 38 which are connected to one another via a spacer bolt 40 , the spacer bolt 40 passing through the pendulum flange 34 through an arcuate cutout 42 .

2 shows a perspective view of the centrifugal pendulum 12 and 3 shows an in 2 marked and marked with C (shown in broken lines) of the centrifugal pendulum 12. 4 shows a plan view of the in 2 and 3 shown centrifugal pendulum and 5 shows a section of the in 4 Marked and marked with D section (shown in phantom) of the centrifugal pendulum 12. For clarity, not all pendulum masses are in the 2 until 5 shown.

As already explained above, the spacer bolt 40 extends through the arcuate cutout 44 and thus connects the pendulum masses 38 arranged on both sides of the pendulum flange 34. The in 3 The cutout 44 shown has an arcuate cutout contour 46 which limits the clearance of the spacer bolt 40 by striking the cutout contour 46 with an outer peripheral surface 50 of the spacer bolt 40 . The outer peripheral surface 50 of the spacer bolt 40 is associated with the cutout contour 46 . The pendulum masses 38 are guided by pendulum rollers 52, which pass through kidney-shaped recesses 54 in the pendulum flange 38 and define a path of movement of the pendulum masses 38.

6 shows a side view of an in 1 until 5 illustrated standoff 40 according to a first embodiment. The spacer bolt 40 comprises a spacer bolt body 56 which is rotationally symmetrical to a longitudinal axis 58 of the spacer bolt body 56 . Depending on how the spacer bolt 40 is fastened to the pendulum masses 38 , the longitudinal axis 58 can also be the axis of rotation of the spacer bolt 40 . The spacer bolt body 56 comprises two fastening areas 60 with which the spacer bolt body 56 is coupled to the pendulum masses 38 . The spacer bolt body 56 can be connected to the pendulum masses 38 in the fastening area 60 by means of a rivet connection or a press connection, for example. The stop area 62 is arranged between the two fastening areas 56 . The stop area 62 has a larger diameter than the fastening areas 56 . A damping arrangement 63 with a damping element 64 is provided radially on the outside of the stop area 62 and has a substantially rectangular cross-section which is beveled by bevels 66 in the area of the edges. The damping element 64 is arranged by means of a loose fit on the stop area 62 of the stop body 56, the axial position of the damping arrangement being fixed by the pendulum masses 38 attached to the stop pin 40 in the installed state of the centrifugal pendulum 12. Radially on the outside, the damping arrangement 63 comprises a spring 70 on an outer circumferential surface 68 of the first damping element 64, which spring comprises three spring sections 72, 74, 76, which are arranged on the damping element 64 in an overlapping manner. Furthermore, the formation of cracks in the damping element 64 and the breaking out of material from the damping arrangement 63 are avoided.

The spring 70 is designed as a coil spring. Here is in 7 a coil spring having three sections, each corresponding to a layer of spring 70, is shown. However, a spring 70 with four to ten, in particular eight layers, that is to say with eight spring sections, is also preferred, with each spring section corresponding to one winding of the spring 70 around the spacer bolt body. The spring sections 72, 74, 76 overlap circumferentially. In the 6 and 7 The spring sections 72, 74, 76 shown are designed in such a way that the mutually opposite peripheral surfaces of the spring sections 72, 74, 76 rest against and touch one another, so that when the spacer bolt 40 strikes the cutout contour 46 of the cutout 44, the spring 70 deflects and while impact energy is converted into a deformation of the spring sections 72, 74, 76. During the deformation, the spring sections 72, 74, 76 move relative to one another and consequently rub against the peripheral surfaces of the corresponding next spring section 72, 74, 76, so that part of the impact energy introduced is dissipated by friction work between the peripheral surfaces of the spring elements 72, 74 , 76 is dismantled. This impact energy, which is not converted into friction work, is introduced by the spring 70 into the damping element 64, which is deformed as a result and is pressed radially inward. The damping element 64 and the spring 70 are designed to spring back into an initial position after they have been relieved.

Due to the spring 70, which winds around the longitudinal axis 58 through the spring sections 72, 74, 76, the damping element 64 is completely covered by the spring 70 on the peripheral side. This has the advantage that the damping element 64 is protected.

In 6 and 7 the spring 70 is a coil spring, which has a particularly low ratio of a height h, which corresponds to the material thickness of the spring 70, to a width b, which is the axial Extension is parallel to the longitudinal axis 58 of the spring 70 having. The width b of the spring 70 is essentially identical to the width of the damping element 64 and a width of the stop area 62 of the spacer bolt body 56. Advantageously, the spring 70 has a height of 0.1 to 0.3 mm. The spring 70 has a width b of 4 to 6 mm, in particular 5 mm. Due to the flat design of the respective individual spring section 72, 74, 76, the damping element 64 is not damaged in the initial region, i.e. at a radially inner end 78 of the spring 70, even when the spring 70 compresses, because the end 78 moves during compression drilled into the damping element 64.

8th shows a side view of a second embodiment of a spacer bolt 80 with a damping arrangement 81 with a spring 82, the peripheral side to the already to 6 and 7 explained stop area 62 of the spacer bolt body 56 is arranged. The spring 82, like the one in 6 and 7 shown spring 70, a plurality of spring sections 72, 74, 76 which, starting from a first end 78 of the spring 82, spirally extend radially outwards from the longitudinal axis 58. The spring sections 72, 74, 76 adjoin one another and overlap on the circumferential side. The spring elements 72, 74, 76, however, are circumferentially opposite to each other 6 and 7 , spaced from each other so that the peripheral surfaces of the spring portions 72, 74, 76 do not touch each other. The spring 82 is designed in such a way that the first spring section 72 lying radially on the inside encompasses the stop region 62 of the spacer bolt body 56 . When spring 82 strikes cutout contour 46 of cutout 44 of pendulum flange 34, spring 82 compresses, spring elements 72, 74, 76 move relative to one another, but the impact energy is essentially converted into spring tension of spring 82. If the impact force decreases, the spring 82 springs out again and pushes the spacer bolt 80 away from the cutout contour 46 . After rebounding, the spring 82 reversibly assumes its original shape.

This embodiment has the advantage that the damping element 64, which is usually made of rubber or another flexible plastic, can be dispensed with, so that the damping element 64 cannot break open due to cracking or other signs of aging and a reliable and soft striking of the spacer bolt 80 on the cutout contour 46 is ensured. Of course, however, the spring 82 can also be used as in 6 and 7 shown on the damping element 64 are arranged radially on the outside.

9 shows a third embodiment of a spacer bolt 84 with a damping arrangement 85 having the damping element 64 and a spring 86, which is formed in two parts and comprises a first spring element 88 lying radially on the inside and a second spring element 90 lying radially on the outside and enclosing the first spring element 88. The spring 86 or the spring elements 88, 90 surround the damping element 64 on the peripheral side. The damping element 64 is as in 6 and 7 explained formed and arranged on the standoff body 56. The first spring element 88 is arranged on the peripheral surface 68 of the damping element 64 and essentially completely encloses the peripheral surface 68 of the damping element 64 . The first spring element 88 is partially ring-shaped and has a recess 92 which is arranged parallel to the longitudinal axis 58 of the spacer bolt 84 . Furthermore, the first spring element 88 has a bulge 94 which is arranged opposite the recess 92 in the embodiment. However, another arrangement is also conceivable. The bulge 94 extends radially outwards from the longitudinal axis 58 , the bulge 94 running parallel to the longitudinal axis 58 in the axial direction. A selective design of the bulge 94 is also possible. The bulge 94 is delimited in the circumferential direction by two spring sections 96, 98 which abut on their inner circumferential surface 95 against the outer circumferential surface 68 of the damping element 64. The second spring element 90 is designed as a sleeve and encompasses the first spring element 88 in the region of the spring sections 96, 98 and itself forms a spring section. The second spring element 90 has a recess 100 which is designed to correspond to the bulge 94 of the first spring element 88 and in which the bulge 94 of the first spring element 88 engages when the spacer bolt 84 is in the installed state. As a result, twisting of the second spring element 90 relative to the first spring element 88 can be avoided, so that the peripheral surface 68 of the damping element 64 is completely surrounded by the spring 86 . As a result, the second spring element 90 also completely overlaps the spring elements 96, 98 of the first spring element 88, so that when the spacer bolt 84 strikes the cutout contour 46 of the cutout 44 between the first spring element 88 and the second spring element 90, the spring elements 88, 90 move relatively move towards one another and friction work is performed on the contacting surfaces of the spring elements 88, 90, and the impact energy is thus damped by the spring 86 in addition to the damping element 64.

Due to the design of the spring 86, the two spring elements 88, 90 can be easily combined in a stamping and subsequent bending process getting produced. The mounting on the spacer bolt takes place in that the two spring elements 88 , 90 are pushed onto the damping element 64 parallel to the longitudinal axis 58 onto the damping element 64 . Due to the spring force of the spring elements 88, 90, they are automatically held on the damping element 64.

10 shows a fourth embodiment of a spacer bolt 102 with a damping arrangement 103 with the damping element 64 and a spring 104 which surrounds the damping element 64 on the peripheral surface 68 on the peripheral side. The standoff body 56 and the damping element 64 are in 6 and 7 explained in more detail. Spring 104 is designed as a wrap spring and comprises a first spring section 106 arranged radially on the inside and a second spring section 108 arranged radially on the outside first spring section 106 is applied. The consequence of this is that the impact energy due to the relative movement of the two spring sections 106, 108 to one another is also partially dissipated in friction work between the inner peripheral surface 110 and the outer peripheral surface 112, and thus the impact of the spacer bolt 102 on the cutout contour 46 of the cutout 44 in addition to the damping element 64 is damped.

The spring 102 has opposite the in 6 and 7 shown spring a greater height of the spring sections 106, 108 in the range of 0.3 to 0.5 mm at a width b of 4 to 6 mm, so that to avoid damage to the damping element 64 by a radially inner first end 114 of the Spring 102, the first end 114 is provided with a chamfer 116 on the side facing the damping element 64. As a result, when the spacer bolt 102 of the first end 114 strikes, the first end 114 of the first spring section 116 penetrates the spring into the damping element 64 due to a reduction in diameter. Furthermore, in the region of the first end 114 of the first spring section 106 there is a relief element 118 which is arranged between the first end 114 and a second end 120 of the spring 102 . The relief element 118 has an expansion 122, which is designed in such a way that in the transition between the first spring section 106 and the second spring section 108, the inner diameter of the second spring section 108 in the circumferential direction (clockwise in 10 ) before the first end 114 of the spring 102 is reached, so that a cavity 124 is formed between the second spring section 108 and the damping element 64 in the radial direction and in the circumferential direction between the widening 122 and the first end of the spring 102, which cavity is designed to receive the first end 114 when the spring 102 strikes the cutout contour 46 of the cutout 44 . This has the advantage that the first end 114 slides along the circumferential side 68 of the damping element 64 in the circumferential direction, and damage to the damping element 64 is thus additionally avoided.

11 and 12 show a fifth embodiment of a standoff 126, wherein 11 a side view of the standoff 126 and 12 a cross section through the in 11 standoffs 126 shown.

The spacer bolt 126 comprises the spacer bolt body 62 and a damping arrangement 127 with the damping element 64 and a spring 128. The spring 128 is arranged on the peripheral side of the peripheral surface 68 of the damping element 64, which is designed as a spiral spring and extends parallel to the longitudinal axis 58 around the peripheral surface 68 of the Damping element 64 winds. In this case, the spring 128 has a multiplicity of spring sections 130 to 140 , each spring section 130 to 140 corresponding to a winding around the damping element 64 . As a result, the spring sections 130 to 140 are in the side view ( 11 ) i.e. overlap in the longitudinal direction. The spring sections 130 to 140 have a square cross section, so that an arrangement of a large number of spring sections 130 to 140 on the damping element 64 is possible. If the spacer bolt 126 strikes the cutout contour 46 of the cutout 44 of the pendulum flange 38 , the damping element 64 is protected by the spring 128 . When it hits, the cutout contour 46 contacts at least one of the spring sections 130 to 140 on the outer peripheral surface 50 of the spring 128 . In the embodiment, the spring 128 is designed such that the end faces, i.e. the side faces of the spring sections 130 to 140 which are arranged perpendicularly to the longitudinal axis 58, are in contact with the respective end face of the next spring section 130 to 140. If the spring 128 strikes the outer contour 46 , friction work is performed between the two end faces and the impact energy when the spacer bolt 126 strikes is thus at least partially dissipated in the spring 128 .

The spring 128 can be used up with an enlarged diameter on the damping element 64, the spring 128 after the widening being automatically reversible into a basic position stood returns and thus attaches itself to the peripheral surface 68 of the damping element 64 and surrounds the damping element 64 . As a result, the spring 128 can be easily attached. In the same way, those in the 6 until 8th and 10 shown springs 70, 82, 104 are mounted.

The damping element 64 of the spacer bolt 40, 84, 102, 126 can be fastened to the fastening section 62 of the spacer bolt body 56 by means of a loose fit, so that the damping element 64 together with the spring 70, 86, 104, 128 is mounted so that it can rotate easily about the longitudinal axis 58 . This has the advantage that the spring 70, 86, 104, 128 or the damping element 64 is rotated when it hits the contour of the cutout, so that the impact load is distributed evenly around the circumference over the lifetime of the spacer bolt 40, 84, 102, 126 and the Spacer bolts 40, 84, 102, 126 have a longer life expectancy. The damping element 64 and the spring 70, 86, 104, 128 are fastened in the axial direction by the pendulum masses 38, which are arranged in the fastening section 60 of the spacer bolt body 56.

Advantageously, the spring 70, 82, 86, 104, 128 is made of high-strength steel, in particular stainless steel or spring steel. Alternatively, it is also conceivable for the spring 70, 82, 86, 104, 128 to have a plastic, in particular a high-strength plastic, which may also be fiber-reinforced, as the material.

All embodiments of the damping arrangement 63, 81, 85, 103, 127 have in common that they have a spring 70, 82, 104, 128, which protects the spacer bolt body 61 from a hard impact on the cutout contour 46 of the cutout 44 of the pendulum flange 34, wherein the spring 70, 82, 86, 104, 128 has at least two spring sections 72, 74, 76, 88, 90, 96, 98, 106, 108, 130 to 140, each of which overlaps. The spring sections 72, 74, 76, 88, 90, 96, 98, 106, 108, 130 preferably completely enclose the spacer bolt body 56 in the stop area 62 on the circumferential side, so that a damping element 64 that may be arranged underneath or the spacer bolt body 61 can be pushed out before it hits the Cutout contour 46 of the cutout 44 of the pendulum flange 34 is protected.

Reference List

10

torsional vibration damper

12

centrifugal pendulum

14

damper input part

16

slat carrier

18

output hub

20

gearing

22

first energy storage elements

24

intermediate damper part

26

second energy storage elements

28

damper output part

30

disk part

32

disk part

34

pendulum flange

36

turbine hub

38

pendulum mass

40

Standoffs (first embodiment)

44

arched cutout

46

cutting contour

50

outer peripheral surface of the standoff

51

standoff body

52

pendulum roller

54

kidney-shaped recess

56

standoff body

58

longitudinal axis

60

mounting area

62

stop area

63

damping arrangement

64

damping element

66

bevel

68

Peripheral surface of the first damping element

70

Feather

72

spring section

74

spring section

76

spring section

78

radially inner end of the spring

80

Standoffs (second embodiment)

81

damping arrangement

82

Feather

84

Standoffs (Third Embodiment)

85

damping arrangement

86

Feather

88

first spring element

90

second spring element

92

recess

94

bulge

95

peripheral surface

96

spring section

98

spring section

100

recess

102

Standoffs (fourth embodiment)

103

damper assembly

104

Feather

106

first spring section

108

second spring section

110

inner peripheral surface of the second spring portion

112

outer peripheral surface of the first spring portion

114

first end of the pen

116

chamfer

118

relief element

120

second end of the spring

122

widening

124

cavity

126

Standoffs (Fifth Embodiment)

127

damping arrangement

128

Feather

130 140

spring section

Claims (4)

Centrifugal pendulum (12) with a pair of pendulum masses (38) and a pendulum flange (34), in which an arcuate cutout (44) with a cutout contour (46) is provided, - the pendulum masses (38) of the pair of pendulum masses being arranged on both sides of the pendulum flange and being supported by at least a spacer bolt (40; 80; 84; 102; 126) guided through the cutout (44), - the spacer bolt (40; 80; 84; 102; 126) having a damping arrangement (63; 81; 85; 103; 127) with a spring (70; 82; 86; 104; 128), wherein the damping arrangement (63; 81; 85; 103; 127) is designed to prevent the spacer bolt (40; 80; 84; 102; 126) from striking on the cutout contour (46) of the cutout (44), characterized in that - the spring (70; 82; 86; 104; 128) has a first and a second spring section (72, 74, 76; 96, 98; 106, 108; 130 to 140) which are arranged overlapping one another, - whereby when the spacer bolt (40; 80; 84; 10 2; 126) on the cut-out contour (46) of the pendulum flange (34), the first spring section is displaced relative to the second spring section, characterized in that the spring (70; 82; 86; 104) of the damping arrangement (63; 81; 85; 103;) is arranged circumferentially on a stop area (62) of the spacer bolt (40; 80; 84; 102; 126) and is spirally wound radially outwards from a longitudinal axis (58) of the spacer bolt (40; 80; 84; 102; 126). Centrifugal pendulum (12) after claim 1 , characterized in that the spring sections (72, 74, 76; 96, 98; 106, 108; 130 to 140) are arranged relative to one another in such a way that the spring sections (72, 74, 76; 96, 98; 106, 108; 130 to 140) substantially cover a peripheral surface (95) of the spacer bolt (40; 80; 84; 102; 126). Centrifugal pendulum (12) according to one of the preceding claims, characterized in that the spacer bolt (40; 80; 84; 102; 126) comprises a spacer bolt body (56), the damping arrangement (63; 81; 85; 103; 127) a damping element (64) disposed between the standoff body (56) and the spring (70; 82; 86; 104; 128). Centrifugal pendulum (12) after claim 3 , characterized in that the spring (70; 82; 86; 104; 128) comprises a material whose strength is higher than the strength of the damping element (64).

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