CN117006198A - Torsional vibration damper with two-part shaft - Google Patents

Torsional vibration damper with two-part shaft Download PDF

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Publication number
CN117006198A
CN117006198A CN202310369641.3A CN202310369641A CN117006198A CN 117006198 A CN117006198 A CN 117006198A CN 202310369641 A CN202310369641 A CN 202310369641A CN 117006198 A CN117006198 A CN 117006198A
Authority
CN
China
Prior art keywords
shaft
torsional vibration
vibration damper
bearing
output part
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202310369641.3A
Other languages
Chinese (zh)
Inventor
安德烈亚斯·斯塔弗尔
梅拉妮·西尔曼
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of CN117006198A publication Critical patent/CN117006198A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/1213—Spiral springs, e.g. lying in one plane, around axis of rotation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/13164—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses characterised by the supporting arrangement of the damper unit
    • F16F15/13171—Bearing arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/131—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses
    • F16F15/133—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
    • F16F15/134—Wound springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2232/00—Nature of movement
    • F16F2232/02—Rotary

Abstract

The invention relates to a torsional vibration damper (1) having an input part (10) and an output part (2) which can be rotated relative to one another about a rotational axis (A) of the torsional vibration damper (1) to a limited extent against the action of spring elements (30, 40). The torsional vibration damper (1) has a first shaft (50) extending coaxially to the rotational axis (A) and connected in a rotationally fixed manner to the input part (10) and a second shaft (51) extending coaxially to the rotational axis (A) and connected in a rotationally fixed manner to the output part (2). In order to rotatably support the torsional vibration damper (1) about the rotational axis (A), a first bearing (60) is arranged between the first shaft (50) and the second shaft (51), by means of which first bearing the first shaft (50) and the second shaft (51) are rotatably supported relative to each other.

Description

Torsional vibration damper with two-part shaft
Technical Field
The invention relates to a torsional vibration damper having a two-part shaft for supporting the torsional vibration damper as well as possible with the smallest possible requirements for installation space.
Background
In reciprocating piston engines, the periodic process of accelerated piston motion and gas forces in the intake, compression, work and exhaust, in combination with the firing order of the individual cylinders, causes rotational non-uniformities in the crankshaft and the flywheel mass connected in the form of a flywheel. Since the torque and stiffness of the rotating components of the drive train are a torsional vibration-capable structure with a characteristic natural frequency, rotational irregularities introduced by the engine can force torsional vibrations that can cause undesired side effects such as acoustic anomalies or increased wear of the components without damping. To reduce the effect, torsional vibration dampers are used.
From the prior art, a torsional vibration damper is known, which is provided for compensating in particular torsional vibrations in the drive train of a motor vehicle in order not to transfer torsional vibrations generated by an internal combustion engine to the transmission, so that the service life of the transmission is increased. Corresponding torsional vibration dampers are known, for example, from US 2020/0032853 A1. In order to compensate for the corresponding torsional vibrations, the rotating flywheel masses are each mounted on both the engine side and the transmission side. The flywheel masses are arranged coaxially and torsionally to one another and are supported torsionally limited relative to one another about the rotational axis of the torsional vibration damper against the action of the spring element. The spring element and the flywheel mass together form the core of a torsional vibration damper designed as a dual-mass flywheel. According to the devices known from the prior art, the flywheel mass is connected in a rotationally fixed manner to a corresponding hollow shaft, which in turn is supported in a rotationally fixed manner on a further shaft passing through it. The further flywheel mass is connected to the gear wheel in a rotationally fixed manner and is mounted on the hollow shaft in a rotationally fixed manner relative to the further flywheel mass against the action of the spring element.
By the two-part arrangement of the two shafts connected to one another in a rotationally fixed manner, radial forces and axial forces occur by the forces introduced into the gear wheel, which forces can cause tilting of the flywheel mass connected to the hollow shaft in a rotationally fixed manner. This in turn leads to an additional load on the shaft supported via the two rolling bearings. Furthermore, the forces can also cause the flywheel mass, which is connected to the hollow shaft in a rotationally fixed manner, to tilt relative to the other flywheel mass.
It is desirable to introduce torque via gears that are supported at two housing-side bearing points, to filter torsional vibrations introduced at the drive side and to introduce the introduced torque outside the housing-side bearing points. Furthermore, the gears on the input side, which are comprised by the torsional vibration damper, should be supported for torque introduction as precisely as possible in order to minimize wear and the accompanying noise formation. For this purpose, the bearing of the gear wheel at the bearing points on both housing sides is necessary. The output torque is output via an output region that is located outside the housing and thus outside the bearing location. Furthermore, the further components of the torsional vibration damper and the gear wheel should be located within, i.e. between, the housing-side bearing points for reasons of installation space. The widest possible support of the assembly thus conflicts with the desire for the smallest possible installation space of the torsional vibration damper.
Disclosure of Invention
The present invention is based on the object of at least partially overcoming the problems known from the prior art.
The object is achieved by means of the features of the torsional vibration damper of the invention. Further advantageous embodiments of the invention are described herein. The features listed individually in the examples can be combined with one another in a technically meaningful way and can define further embodiments of the invention. Furthermore, the features of the invention are explained and illustrated in detail in the description, wherein further preferred embodiments of the invention are shown.
The torsional vibration damper according to the present invention includes: an input part and an output part and at least one spring element, wherein the input part and the output part are supported in a limited manner relative to one another in a rotatable manner about the axis of rotation of the torsional vibration damper against the action of the spring element; a first shaft extending coaxially with the rotational axis and connected in a rotationally fixed manner to the input element, and a second shaft extending coaxially with the rotational axis and connected in a rotationally fixed manner to the output element, wherein at least one first bearing is arranged between the first shaft and the second shaft, with which the first shaft and the second shaft are mounted in a rotationally fixed manner relative to one another.
It is to be noted in advance that the terms used herein ("first", "second") are used to distinguish one or more objects, sizes or procedures of the same type, i.e. in particular not necessarily to define the relatedness and/or order of the objects, sizes or procedures to each other. If correlation and/or order is desired, this is explicitly stated herein or will be apparent to those skilled in the art upon examination of the specifically described designs.
The input and output components relate to a flywheel mass on the drive side and a flywheel mass on the driven side, which can be twisted to a limited extent relative to one another about a common axis of rotation against the spring force of the spring element. The output part and/or the input part is preferably formed as a sheet metal element, alternatively preferably as a cast part or a forged part. Further preferably, the manufacturing of the output member and the input member is not limited to the manufacturing method. The input element and the output element can also preferably be produced by different production methods.
The gear wheel is preferably fastened coaxially and rotationally fixed to the first shaft, wherein the gear wheel has a toothless region formed toward the second shaft on a circumferential section of its outer circumferential surface. The first shaft has a flange section on the circumferential side, which is designed to achieve a rotationally fixed connection between the input element, which extends radially and disk-like from the first shaft, and the gear wheel. For this purpose, the flange section is formed with a bore in the direction of the rotational axis, through which the gear wheel and the input part are connected to the flange section and thus to the first shaft in a rotationally fixed manner by means of a threaded connection. The gear is designed to absorb a corresponding torque and to introduce said torque into the torsional vibration damper or to withdraw said torque from the torsional vibration damper.
The second shaft also has a corresponding further flange section on its end facing the first shaft, which further flange section has a bore formed in the direction of the rotation axis a. The output element is formed coaxially with the second shaft with a radial and disk-shaped extension from the second shaft. The further Kong Zaici of the flange section of the second shaft is also designed to provide a rotationally fixed connection between the output part and the second shaft by means of rivets. However, other types of positive, friction-fit and/or material-fit connections between the input member and the first shaft and the output member and the second shaft are preferably also possible.
In order to achieve a space-saving support of the first shaft relative to the second shaft, the second shaft preferably has a longitudinal bore in the direction of the rotation axis on the side pointing toward the first shaft, wherein the first shaft is rotatably supported in the longitudinal bore by means of a first bearing. Furthermore, the first shaft is preferably supported radially relative to the second shaft by a first bearing and in the axial direction by a second bearing. Thus, the first shaft and the second shaft are supported to each other not only in the radial direction but also in the axial direction. The first bearing and the second bearing are preferably implemented separately, wherein the first bearing and the second bearing are implemented as needle bearings or as a combination of sliding bearings and rolling bearings. However, the first bearing and the second bearing may also be formed in combination, preferably for example in the form of a plastic bushing having a flange geometry.
Preferably, the first rolling bearing is arranged radially on the first bearing and coaxially with the second shaft on the outer circumferential surface of the second shaft, wherein the axial positions of the first bearing and the first rolling bearing are preferably identical to each other. In contrast, it is preferable if the second rolling bearing is arranged coaxially with the first shaft and on the outer circumferential surface of the first shaft, wherein the second rolling bearing is arranged on the side of the input part facing away from the output part. The described arrangement of the first and second bearings and the first and second rolling bearings relative to each other achieves an optimal radial runout of the first and second shafts and makes possible tilting of the first shaft relative to the second shaft mechanically difficult. Thus, in addition, the installation space is saved.
Preferably, the output part has a cylindrical section extending radially relative to the axis of rotation and is formed on the circumferential side and coaxially with the axis of rotation with a cylindrical section oriented toward the spring element, wherein a cover extending radially outwards relative to the axis of rotation is furthermore preferred, which has a complementary mating shape to the cylindrical section on the circumferential side and is connected in a rotationally fixed manner to the cylindrical section of the output part or of the input part. Furthermore, it is preferred that the output part and the cover form a channel therebetween which surrounds the axis of rotation, wherein the channel surrounds the spring element at least partially both in the radial direction and in the axial direction with respect to the axis of rotation.
The complementary connection between the cylindrical section of the output member and the end of the cap radially outside with respect to the axis of rotation is understood to be a form-and/or friction-fitting connection between the two elements. For example, the cover can preferably likewise have a cylindrical section on its radially outwardly directed side, which cylindrical section is positively engaged with the cylindrical section of the output part, with which section the cover rests at least partially on the circumferential side against the inner or outer circumference of the cylindrical section of the output part. But alternatively other embodiments of the connection between the output member and the cylindrical section of the cap are also preferred. The cover is preferably formed as a sheet metal element, alternatively preferably as a cast part or a forged part. Further preferably, the manufacture of the cover is not limited to the manufacturing method. The cover may also preferably be manufactured by different manufacturing methods.
As already described, the output part and the cover form a channel therebetween that surrounds the axis of rotation, wherein the channel surrounds the spring element at least partially both in the radial direction and in the axial direction with respect to the axis of rotation. The sections of the output part and of the cover, which extend radially from the axis of rotation, are designed to prevent the spring element from sliding axially in the direction of the axis of rotation and to fix the spring element axially. In contrast, the cylindrical section of the output part and the complementary part of the cover serve to provide guidance for the spring element in the radial direction, wherein the region is designed as a friction surface for the spring element displaced in the channel. The further stop is preferably also formed at the cover for supporting the spring element. Preferably, instead of one spring element, a plurality of spring elements are distributed over the circumference.
Preferably, the cover is arranged coaxially to the toothless area of the gear on its side radially inside with respect to the axis of rotation and is rotatably supported on the toothless area by means of a third bearing. If the spring element of the torsional vibration damper is compressed, it presses not only against the stop of the output part and of the cover but also against the stop of the input part. Since the stops of the cover and the output member are not exactly in the same position in the axial direction as the attachment of the output member and the second shaft, but are axially offset with respect thereto, a moment acts on the attachment area between the output member and the second shaft. This may cause tilting of the cover and the output member relative to the second shaft. The additional support between the cover and the toothless area of the gear ensures an additional guidance of the output element extending to the cover and a corresponding counter moment. The third bearing is preferably designed for radial support between the cover and the toothless region of the gearwheel and/or for axial support between the cover and the toothless region of the gearwheel. As with the first bearing and the second bearing, the third bearing is preferably embodied as a needle bearing or as a combination of a plain bearing and a rolling bearing. However, the third bearing may also be formed in combination, for example in the form of a plastic bush having a flange geometry.
Drawings
The invention and the technical field are described in detail below with reference to the accompanying drawings. It should be noted that the invention should not be limited by the illustrated embodiments. In particular, if not explicitly stated otherwise, it is also possible to extract some aspects of the facts set forth in the figures and to combine them with other components and knowledge in the present description and/or in the figures. It should be noted in particular that the figures and the dimensional relationships particularly shown are merely schematic. Like reference numerals refer to like objects so that the description from other figures may be used in addition as necessary. The drawings show:
fig. 1 shows a very abstract representation of the input element of a torsional vibration damper according to the invention;
fig. 2 shows a very abstract representation of the output element of a torsional vibration damper according to the invention;
FIG. 3 shows a very abstract view of a torsional vibration damper according to the invention;
fig. 4 shows a schematic longitudinal section of a torsional vibration damper according to the invention.
Detailed Description
Fig. 1 shows a very abstract representation of an input element 10 of a torsional vibration damper according to the invention. The input part 10 is a flywheel mass and is preferably constructed as a sheet metal element, alternatively preferably as a cast part or forging. The input part 10 is designed as a wing flange 20, wherein the wing flange 20 has two wing parts 22 which are designed symmetrically to one another and extend radially away from a wing flange body 21. The input member 10 is in principle not limited to the embodiment of the wing flange 20. The wing flange body 21 has a hollow 24 formed coaxially with the rotation axis a with respect to the outer circumferential surface thereof. The wing flange 20 is formed point-symmetrically with respect to the axis of rotation a. Therefore, the wing portions 22 are configured to face each other. The terms radial or radial direction, axial or axial direction and circumferential direction as used herein are understood to always relate to the rotation axis a unless explicitly stated otherwise.
Fig. 2 shows a very abstract representation of the output part 2 of a torsional vibration damper according to the invention. The output member 2 is configured as a disk-shaped flywheel mass having a hollow portion 3 configured coaxially with the circumferential side. Also as with the wing flange 20, the output part 2 is preferably formed as a sheet metal element, alternatively preferably as a cast part or forging. The output part 2 has a first channel region 4 and a second channel region 5 on the circumferential side and opposite one another, which extend over a part of the circumference of the output part 2. Furthermore, the output part 2 has a first stop 6 and a second stop 8 on the radial outer side, which are likewise formed point-symmetrically to one another, which likewise extend over a part of the circumference of the output part 2 and separate the first and second channel regions 4, 5 from one another. The first stop 6 has a first stop surface 7 which faces the first channel region 4 in the circumferential direction. A second stop surface 18, which is formed opposite the first stop surface 7 in the circumferential direction at the first stop 6, faces the second channel region 5. The second stop 8 has a first stop surface 17 which faces the first channel region 4 in the circumferential direction, while the opposite second stop surface 9 faces the second channel region 5.
Fig. 3 shows a very abstract representation of the torsional vibration damper 1 according to the invention, in which the previously described output part 2 and input part 10 are arranged on top of one another or coaxially to the axis of rotation a, so that the recesses 3, 24 of the output part 2 and of the input part 10 are aligned with one another. According to fig. 3, in addition to the input part 10 and the output part 2, the torsional vibration damper 1 further comprises a first spring element 30 and a second spring element 40, which are each designed as a compression spring. The input part 10 in the form of a wing flange 20 is configured to be rotatable relative to the output part 2. The first spring element 30 is mounted in the first channel region 4 of the output part 2 so as to be movable in the circumferential direction, and the second spring element 40 is mounted in the second channel region 5 so as to be movable in the circumferential direction, wherein the first and second channel regions 4, 5 serve as guides for the spring elements 30, 40. The spring elements 30, 40 have an extension in the uncompressed state, which corresponds to the extension of the channel regions 4, 5 over the circumference of the output part 2. The first stop surface 7 of the first stop 6 forms a support for the first end 31 of the first spring element 30, wherein the second stop surface 9 of the second stop 8 forms a support for the first end 41 of the second spring element 40. The second stop 8 has a first stop surface 17 for supporting the first spring element 30. Furthermore, the first stop 6 has a second stop surface 18 for supporting the second spring element 40. The stop surfaces 17, 18 of the first and second stop portions 6, 8 opposite the stop surfaces 7, 9 are designed to delimit the respective other spring element 30, 40 on the circumferential side, but can likewise absorb forces as long as angular momentum is produced in the opposite direction. Opposite the stop surfaces 7, 9, 17, 18 of the first and second stop elements 6, 8, the wing flange 20 likewise has a stop surface 23, which forms a support for the second end 32, 42 of the first or second spring element 30, 40.
The input element 10 in the form of a wing flange 20 is the driven primary side of the torsional vibration damper 1 and is directly acted upon with an external torque and twisted about the axis of rotation a. The output part 2 which is operatively connected to the wing flange 20 indirectly via the spring elements 30, 40 is referred to hereinafter as the secondary side of the torsional vibration damper 1 which is driven via the primary side. Although not shown, the primary side can preferably be driven by an internal combustion engine, wherein the secondary side preferably transmits torque to a transmission fastened thereto, in particular to a transmission input shaft, not shown.
If the input member 10 is twisted relative to the output member 2, the first and second spring elements 30, 40 are compressed or exert opposing moments against the twist. If the drive-side torque acting on the input element 10 decreases or the applied torque is not subject to fluctuations but is applied identically, the spring elements 30, 40 can at least partially relax and release their stored energy in order to swivel the input element 10 back in torsion relative to the output element 2.
Fig. 4 shows a schematic longitudinal section of a torsional vibration damper 1 according to the invention for illustrating further components of the torsional vibration damper 1. The torsional vibration damper 1 comprises a first shaft 50 arranged coaxially with the axis of rotation a and a second shaft 51 also arranged coaxially with the axis of rotation a. The first shaft 50 is rotatably supported in the longitudinal bore 52 of the second shaft 51 via a first bearing 60 with respect to the second shaft 51. Further, a second bearing 61, which is configured as a spacer between the first shaft 50 and the second shaft 51 and supports the first shaft 50 and the second shaft 51 to each other in the axial direction, i.e., in the direction of the rotation axis a, is provided between the first shaft 50 and the second shaft 51.
Starting from the rotation axis a, the second shaft 51 with the first bearing seat 71 is rotatably supported in the radial direction by a first rolling bearing 70 at a housing, not shown. Correspondingly, the first shaft 50 having the second bearing seat 81 is rotatably supported on a housing, not shown, by means of a second rolling bearing 80 at its end facing away from the second shaft 51, offset along the rotational axis a.
On the circumferential side, the first shaft 50 has a flange section 53 which is designed to provide a rotationally fixed connection between the input part 10, which extends radially and disk-shaped from the first shaft 50, and the gear 110 by means of the screw connection 54. For this purpose, the flange section 53 is formed with a bore 55 extending in the direction of the rotational axis a, through which the gear 110 and the input part 10 are connected to the flange section 53 and thus to the first shaft 50 in a rotationally fixed manner by means of the screw connection 54. The gear 110 is designed to absorb a corresponding torque and to introduce it into the torsional vibration damper 1 or to withdraw it from the torsional vibration damper 1. The torsional vibration damper 1 is preferably used in a drive train of a motor vehicle, which preferably has at least one internal combustion engine as a torque source. The torsional vibration damper 1 is preferably connected directly or indirectly to the crankshaft of the internal combustion engine via a gear 110. The torsional vibration damper 1 is preferably connected to a starter generator which combines the functions of the starter and of the vehicle generator with one another.
The second shaft 51 also has a corresponding further flange section 56 at its end facing the first shaft 50, which further flange section has a further bore 57 formed in the direction of the rotational axis a. Coaxial to the second shaft 51, the output part 2 is formed with a radial and disk-shaped extension starting from the second shaft 51. The further bore 57 of the further flange section 56 of the second shaft 51 is also designed here to provide a rotationally fixed connection between the output part 2 and the second shaft 451, for example by means of rivets 58.
The output part 2 has a first channel region 4 and a second channel region 5 which are opposite one another about the axis of rotation a and extend over a part of the circumference of the output part 2, wherein the outer circumferential region of the output part 2 is folded in a pot shape in the direction of the axis of rotation a and forms a cylindrical section 100 coaxial with the axis of rotation a. Furthermore, the output part 2 has a first stop 6 and a second stop 8 on the radial outer side, which likewise extend over a part of the circumference of the output part 2 and separate the first and second channel regions 4, 5 from one another.
The input member 10 has stop portions 23 opposed to the stop portions 6, 8 of the output member 2, respectively. The spring elements 30, 40 are each supported in the circumferential direction in the channel regions 4, 5 and between the stops 6, 8, 23, wherein the channel regions 4, 5 serve as guides for the spring elements 30, 40. Since the spring elements 30, 40 are supported with their first ends 31, 41 on the stops 6, 8 of the output part 2 and with their second ends 32, 42 on the stop 23 of the input part 10 according to fig. 3, the spring elements 30, 40 resist a torsion of the input part 10 relative to the output part 2.
In order to prevent the spring elements 30, 40 from moving out of the guide channels 4, 5 in the axial direction, i.e. in the direction of the axis of rotation a, the edges of the spring elements 30, 40 facing away from the output part 2 or the channel regions 4, 5 are held in the channel regions 4, 5 by the cover 90. The cover 90 is arranged coaxially to the output part 2 and the input part 10 and is likewise formed disk-shaped in the radial direction starting from the axis of rotation a. In order to ensure a uniform loading of the spring elements 30, 40 in their extension direction and to avoid possible torsion, the first stop 91 and the second stop 92 are likewise formed at the cover 90 in such a way that they act in the same direction in order to support the stops 6, 8 of the output part 2.
Furthermore, the cover 90 likewise has, on its radially outwardly directed side, a crimped and cylindrical section 101 which is complementary to the cylindrical section 100 of the output part 2, with which section the cover 90 rests on the inner circumference of the cylindrical section 100 of the output part 2 on the circumferential side. In order to connect the output part 2 and the cover 90 to one another in a rotationally fixed manner, the cylindrical sections 100, 101 of the output part 2 and the cover 90 are pressed against one another and form a circumferential channel 120 therebetween. The spring elements 30, 40 are thus held not only by the inner side of the cylindrical section 101 of the cover in the radial direction, but also by the channel regions 4, 5 and the radially outwardly directed side of the cover 90 in the axial direction.
The cover 90 is formed on its radially inwardly directed side with a further flanged and cylindrical section 102, which is formed opposite to the radially outer cylindrical section 101. In the radial direction, the toothless area 111 of the gearwheel 110 and the further cylindrical section 102 overlap, wherein a third bearing 62 is arranged between the cylindrical section 102 and the toothless area 111 of the gearwheel 110, which third bearing supports the further cylindrical section 102 with respect to the toothless area 111 of the gearwheel 110 both in the radial direction and in the axial direction, i.e. in the direction of the axis of rotation a.
The invention relates to a torsional vibration damper 1 having an input part 10 and an output part 2 which can be twisted about a rotational axis a in a limited manner relative to one another against the action of spring elements 30, 40. The torsional vibration damper 1 has a first shaft 50 extending coaxially with the rotational axis a and connected in a rotationally fixed manner to the input part 10, and a second shaft 51 extending coaxially with the rotational axis a and connected in a rotationally fixed manner to the output part 2. In order to rotatably support the torsional vibration damper 1 about the rotational axis a, a first bearing 60 is provided between the first shaft 50 and the second shaft 51, with which first bearing the first shaft 50 and the second shaft 51 are rotatably supported relative to one another.
List of reference numerals
1. Torsional vibration damper
2. Output part
3. Blank part
4. A first channel region
5. Second channel region
6. First stop part
7. A first stop surface
8. Second stop part
9. A first stop surface
10. Input member
17. A first stop surface
18. Second stop surface
20. Wing flange
21. Wing flange body
22. Wing part
23. Stop block
24. Blank part
30. First spring element
31. First end portion
32. Second end portion
40. Second spring element
41. First end portion
42. Second end portion
50. First shaft
51. Second shaft
52. Longitudinal hole
53. Flange section
54. Threaded connection
55. Hole(s)
56. Additional flange section
57. Additional holes
58. Rivet
60. First bearing
61. Second bearing
62. Third bearing
70. First rolling bearing
71. First bearing seat
80. Second rolling bearing
81. Second bearing seat
90. Cover for a container
91. First stop part
92. Second stop part
100. Cylindrical section of output part
101. Cylindrical section of cap
102. Additional cylindrical section of the cap
110. Gear wheel
111. Toothless areas
120. Channel
Arotation axis

Claims (10)

1. A torsional vibration damper (1), comprising: -an input part (10) and an output part (2) and at least one spring element (30, 40), wherein the input part (10) and the output part (2) are supported in a limited rotational manner relative to each other about a rotational axis (a) of the torsional vibration damper (1) against the action of the spring element (30, 40); a first shaft (50) extending coaxially to the rotation axis (A) and connected in a rotationally fixed manner to the input element (10); and a second shaft (51) extending coaxially to the rotation axis (A) and connected to the output part (2) in a rotationally fixed manner, wherein at least one first bearing (60) is arranged between the first shaft (50) and the second shaft (51), by means of which first bearing the first shaft (50) and the second shaft (51) are rotatably mounted relative to each other.
2. Torsional vibration damper (1) according to claim 1,
it is characterized in that the method comprises the steps of,
the second shaft (51) has a longitudinal bore (52) on the side facing the first shaft (50) in the direction of the rotational axis (A), wherein the first shaft (50) is rotatably mounted in the longitudinal bore (52) by means of the first bearing (60).
3. Torsional vibration damper (1) according to claim 1 or 2,
it is characterized in that the method comprises the steps of,
the first shaft (50) is supported radially with respect to the second shaft (51) by the first bearing (60) and in the axial direction by a second bearing (61).
4. Torsional vibration damper (1) according to claim 2,
it is characterized in that the method comprises the steps of,
a first rolling bearing (70) is arranged radially above the first bearing (60) and coaxially with the second shaft (51) on the outer circumferential surface of the second shaft (51).
5. Torsional vibration damper (1) according to one of the preceding claims,
it is characterized in that the method comprises the steps of,
a second rolling bearing (80) is provided coaxially to the first shaft (50) and arranged on the outer circumferential surface of the first shaft (50), wherein the second rolling bearing (80) is arranged on the side of the input part (10) facing away from the output part (2).
6. Torsional vibration damper (1) according to one of the preceding claims,
it is characterized in that the method comprises the steps of,
a gearwheel (110) is provided which is coaxial to the first shaft (50) and is fixed in a rotationally fixed manner to the first shaft (50), wherein the gearwheel (110) has a toothless region (111) formed toward the second shaft (51) on a circumferential section of its outer circumferential surface.
7. Torsional vibration damper (1) according to one of the preceding claims,
it is characterized in that the method comprises the steps of,
the output part (2) has a radial extension with respect to the rotational axis (a), and a cylindrical section (100) oriented toward the spring element (30, 40) is formed on the circumferential side and coaxially with the rotational axis (a).
8. Torsional vibration damper (1) according to claim 7,
it is characterized in that the method comprises the steps of,
a cover (90) is provided which extends radially outwards relative to the axis of rotation (A), has a complementary mating shape to the cylindrical section (100) on the circumferential side and is connected in a rotationally fixed manner to the cylindrical section (100) of the output part (2) or of the input part (10).
9. Torsional vibration damper (1) according to claim 8,
it is characterized in that the method comprises the steps of,
the output part (2) and the cover (90) form a channel (120) therebetween which surrounds the axis of rotation (a), wherein the channel (120) surrounds the spring element (30, 40) at least partially in the radial direction and in the axial direction with respect to the axis of rotation (a).
10. Torsional vibration damper (1) according to claim 8 or 9,
it is characterized in that the method comprises the steps of,
the cover is arranged coaxially to the toothless region (111) of the gear wheel (110) on its radially inner side with respect to the rotational axis (A) and is rotatably mounted on the toothless region (111) by means of a third bearing (62).
CN202310369641.3A 2022-05-05 2023-04-07 Torsional vibration damper with two-part shaft Pending CN117006198A (en)

Applications Claiming Priority (2)

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DE102022111141.5A DE102022111141A1 (en) 2022-05-05 2022-05-05 Torsional vibration damper with two-part shaft
DE102022111141.5 2022-05-05

Publications (1)

Publication Number Publication Date
CN117006198A true CN117006198A (en) 2023-11-07

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DE (1) DE102022111141A1 (en)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4026204A1 (en) 1990-08-18 1992-02-20 Bayerische Motoren Werke Ag Double flywheel for combustion engine crankshaft - consists of bearing with hole in and screws
FR2982231B1 (en) 2011-11-08 2013-11-08 Jtekt Europe Sas ASSISTANCE MODULE FOR VEHICLE ASSISTED STEERING SYSTEM
DE102015208232A1 (en) 2015-05-05 2016-11-10 Schaeffler Technologies AG & Co. KG Torque transfer device
DE102017203459A1 (en) 2017-03-02 2018-09-06 Zf Friedrichshafen Ag Gear arrangement for a transmission of a vehicle or the like
JP6719653B2 (en) 2017-03-29 2020-07-08 本田技研工業株式会社 Power transmission device

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