CN117006196A - Torsional vibration damper - Google Patents

Abstract

The invention relates to a torsional vibration damper (1) having an input part (10) and an output part (2) which are rotatable against the action of a spring element (30, 40). The axes (A) are limitedly twisted relative to each other. The torsional vibration damper (1) has an oil drain opening (130), which is formed axially with respect to the axis of rotation (A) and through which the torsional vibration damper (130) can be removed from the torsional vibration damper (130) during operation. 1) Lead away the oil. This makes it possible to achieve a defined flow of oil, in particular in the area of the spring elements (30, 40), and to prevent oil from accumulating in the torsional vibration damper (1) and causing torsional vibrations in the damper (1) Damaging, undesired forces act on components of the torsional vibration damper (1).

Description

torsional vibration absorber

Technical field

The invention relates to a torsional vibration damper, in particular for use in a drive train of a motor vehicle, in particular a drive train which includes not only an internal combustion engine or a reciprocating piston engine but also at least one electric motor as a torque converter. used in hybrid powertrains.

Background technique

In a reciprocating piston engine, the accelerated piston motion and cyclic processes of gas forces during intake, compression, power generation and exhaust, combined with the firing sequence of the individual cylinders, cause non-uniform rotation of the crankshaft and the connected flywheel mass in the form of a flywheel sex. Because the powertrain is a torsionally vibrating structure with characteristic natural frequencies due to the moment of inertia and stiffness of the rotating components, the rotational inhomogeneities introduced by the engine forcefully cause torsional vibrations that would otherwise be unmitigated. Vibrations can cause undesirable side effects, such as abnormal sound or increased wear of components. To reduce these effects, torsional vibration dampers are used.

A torsional vibration damper is known from the prior art, which is provided for compensating in particular torsional vibrations in the powertrain of a motor vehicle in order not to transmit torsional vibrations generated by the internal combustion engine to transmission, thereby increasing the service life of the transmission. Corresponding torsional vibration dampers are known, for example, from US 2020/0032853 A1. In order to compensate for the corresponding torsional vibrations, a rotating flywheel mass is installed both on the engine side and on the transmission side. The flywheel masses are arranged coaxially and torsionably with respect to one another and are mounted so as to be torsionably limited relative to one another about the axis of rotation of the torsional vibration damper against the action of the spring element. The spring element and the flywheel mass together form a torsional vibration damper designed as a dual-mass flywheel. In this case, the spring element is mounted so as to be guided in a channel region of the first or second flywheel mass, wherein a cover complementary to the channel region prevents the spring element from sliding axially out of the channel region. In order to ensure a fixed fit of the cover on the flywheel mass, the cover and the flywheel mass are pressed against each other and together form a channel coaxially surrounding the axis of rotation.

The spring elements must be lubricated within the channels in order to minimize wear. Use oil lubrication for system lubrication. Correspondingly, during operation, the lubricating oil is continuously delivered into the torsional vibration absorber through one or more oil inlet parts, and is accordingly delivered into the channel.

In the torsional vibration damper between the starter generator and the engine, due to the oil transfer into the channel, hydrostatic pressure occurs on said channel, since the channel of the flywheel mass and cover must surround the spring as well as possible . Correspondingly, the channel is thus coordinated with the spring element such that the gap between the spring element and the channel is kept as small as possible in order to ensure good guidance of the spring element. Due to centrifugal forces, the oil located in the channel generates forces in the radial and axial direction on the channel area and the cover forming the channel. This can cause the press fit of the cover and the flywheel mass to be pushed apart in an impermissible manner, causing bending of the component. In addition, after the engine is stopped, a sufficient amount of lubricant should remain in the shock absorber until oil flow is reestablished when starting.

Contents of the invention

For this reason, the invention is based on the object of at least partially overcoming the problems known from the prior art.

Said 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. Features listed individually in the exemplary embodiments can be combined with one another in technically meaningful ways and can define further embodiments of the invention. Furthermore, the characteristics of the invention are explained and explained in detail in the description, which shows further preferred embodiments of the invention.

According to a first aspect of the invention, a torsional vibration damper according to the invention comprises an input part and an output part and at least one spring element, wherein the input part and the output part are about an axis of rotation of the torsional vibration damper against the action of the spring element Mounted so as to be rotationally limited relative to one another, wherein the output part has a radial extension 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 towards the spring element; relative to rotation Cover with an axis extending radially outwards, which cover has a peripherally adapted shape complementary to the cylindrical section and is connected in a rotationally fixed manner to the cylindrical section of the output part, with the output part and the cover being therebetween A circumferential channel is formed, wherein the channel at least partially surrounds the spring element both in the radial direction and in the axial direction relative to the axis of rotation, wherein the channel forms a friction surface for the spring element that extends coaxially with the axis of rotation, wherein the output The component and/or the cover has an oil drain opening in the region of the section extending in the radial direction toward the axis of rotation, wherein the oil drain opening is formed radially inside with respect to the friction surface.

It is presupposedly noted that the numerals ("first", "second"...) used here are used preferentially (only) to distinguish between several objects, entities or processes of the same type, In particular, the relative dependence and/or sequence of the objects, dimensions or processes described are not mandatory. If correlation and/or sequence is required, this is explicitly stated herein or will be apparent to a person skilled in the art upon examination of the specifically described design.

The input part and the output part are the drive-side flywheel mass and the output-side flywheel mass, which can be limitedly twisted 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 and/or the cover are preferably designed as sheet metal elements, alternatively preferably as cast or forged parts. Furthermore preferably, the production of the output part, the input part and the cover is not limited to the manufacturing method described. The input part, the output part and the cover can also preferably each be produced by different production methods.

In order to transmit the torque to the torsional vibration damper, the drive-side input part is preferably connected to the ring gear in a rotationally fixed manner by means of a screw connection. The teeth of the ring gear mesh with, for example, the teeth of the other drive side of the gear, via which a corresponding torque is exerted.

In order to prevent the spring element from moving in the axial direction, ie in the direction of the axis of rotation and thus out of the guide channel, the edge of the spring element facing away from the output part or the channel area is held in the channel area by a cover. In order to connect the output part and the cover in a rotationally fixed manner, the cylindrical section of the output part and the complementary part of the cover are pressed against each other and together form a circumferential channel. The cylindrical section of the output part and the complementary part of the cover can preferably be welded or screwed to one another. Other connection types that achieve a rotationally fixed connection between the cylindrical section of the output part and the complementary part of the cover are also preferred.

A complementary connection between the cylindrical section of the output part and the radially outer end of the cover with respect to the axis of rotation is to be understood as a form-fitting and/or friction-fitting connection between the two elements. For example, the cover can preferably also have on its radially outwardly directed side a cylindrical section that is form-fitting with the cylindrical section of the output part, with which section the cover rests at least partially on the circumferential side. At the inner or outer circumference of the cylindrical section of the output member. Alternatively, however, other embodiments of the connection between the output part and the cylindrical section of the cover are also preferred.

The output part and the cover form between them a channel surrounding the axis of rotation, wherein the channel at least partially surrounds the spring element relative to the axis of rotation both in the radial direction and in the axial direction. In this case, the output part and the section of the cover extending radially from the axis of rotation are designed to prevent axial slippage of the spring element in the direction of the axis of rotation and to axially secure said spring element. 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, with said area forming a friction surface for the spring element displaced within the channel. Preferably, instead of one spring element, a plurality of spring elements are formed distributed over the circumference.

Excess lubricant can flow out through correspondingly positioned oil outlets in the radial height of the channels. Only a small amount of oil remains in the channel, so that even when the torsional vibration damper is stopped, a certain oil reserve is already maintained in the torsional vibration damper for a subsequent start-up. The reduced oil quantity ensures, in particular, that the forces generated by the oil located in the channels at rotational speed are limited to the components forming the channels. For this purpose, the oil drain hole is arranged radially further inwards with respect to the friction surface. Preferably, the oil drain openings have a spacing in the radial direction relative to the friction surface that corresponds to the diameter of the spring element's cross section, wherein it is particularly preferred that the oil drain openings have a cross section relative to the friction surface that corresponds to the diameter of the spring element. The radius of the spacing. As a result, a good outflow of oil from the channel can advantageously be achieved. Furthermore, it is preferred that the oil outlet opening has a distance relative to the friction surface that corresponds to at most half the diameter of the cross-section of the spring element, provided the spring element does not have a circular cross-section.

The spring element is preferably designed as a compression spring, wherein the compression spring has a first side and a second side with which it is supported against stops of the input part and the output part. Furthermore, the spring element is preferably arranged in such a way that the torsional vibration damper does not have an imbalance during operation when the input part is torsion relative to the output part and the spring element is compressed therewith. In order to prevent imbalances caused by oil flowing out unevenly, oil drain holes are provided on the circumference of the output part and the cover respectively in such a way that a uniform outflow over the circumference of the torsional vibration damper is possible. For example, if the torsional vibration damper has a pair of spring elements opposite each other, the oil drain openings are preferably formed mirror-image of each other with respect to the longitudinal axis, also on the output part but also on the cover. Furthermore, it is preferred that in order to improve the cooling of the spring element in particular and thereby further increase its expected service life, the oil drain opening is preferably formed only in the area of the spring element. This causes the oil accelerated outwards by centrifugal force to flow towards the oil drain holes in the area of the spring element, so that the oil drain hole is less dense than when the oil drain holes are arranged evenly distributed over the circumference of the output part and cover. The hole is subjected to a greater volume flow of oil.

The output part is preferably connected in a rotationally fixed manner to the shaft, wherein the input part is also preferably mounted rotatably on the shaft by means of a plain bearing. The connection of the output part to the shaft may preferably be a material-fitting connection or a friction-fitting connection, wherein a material-fitting connection may be understood to mean a welded connection of two components or a one-piece production. Furthermore, the shaft preferably has a central bore and a feed bore for the oil supply pointing radially outwards from the central bore, wherein the output part and/or the input part has further feed bores which are partially radial. Align outwards with the surrounding channels. The term "radially outwardly directed" is understood to mean an orientation of the supply opening with a radial portion or radial orientation.

In order to enable lubrication of the torsional vibration damper, the shaft has a central bore along the axis of rotation, which is continuously filled with oil. Starting from the central hole, supply holes are provided radially to the outer circumference of the shaft. The first supply opening opens into the area of the sliding bearing in order to provide this area with lubricant. The second supply opening opens into a surrounding gap, which is formed on the one hand by the shaft and the output part connected in one piece with the shaft, and on the other hand by the input part. For this reason, the third supply opening is guided through the input part and/or through the output part in order to discharge the oil out of the gap. Owing to the centrifugal force, the oil is conveyed from there into the region of the surrounding channel, so that one or more spring elements are continuously moistened.

According to a second aspect, a preferred embodiment is proposed in which at least a first spring element and a second spring element are included, the second spring element being shortened relative to the first spring element.

It is presupposedly noted that the use of numerical terms such as “first” and “second” here is only used to distinguish between multiple objects, entities or processes of the same type, i.e. in particular it is not mandatory to define the object in question. , size or correlation of processes to each other and/or sequence. If correlation and/or sequence is required, this is explicitly stated herein or will be apparent to a person skilled in the art upon examination of the specifically described design.

As is known from the prior art, the input part and the output part involve an input-side flywheel mass via which the rotational motion is introduced and a driven-side flywheel mass which is driven by the drive The flywheel mass drives the flywheel and then outputs rotational energy again on the driven side. The output part and/or the input part is preferably designed as a sheet metal element, wherein the output part and the input part are alternatively preferably designed as a cast or forged part. Furthermore preferably, the production of the output part and the input part is not limited to the production method described.

The second spring element is shortened relative to the first spring element, shortening here meaning a smaller extension of the second spring element relative to the first spring element, in particular in the circumferential direction.

In principle, the torsional vibration damper is not limited to the arrangement between the internal combustion engine and the transmission. A torsional vibration damper can also preferably be used in conjunction with a pulley decoupler. Preferably, general use for damping torsional vibrations is also possible on various machine elements, in particular in gear dampers.

Preferably, when the input part is twisted relative to the output part, the first spring element first resists twisting, wherein the second spring element resists twisting only after a further twisting of the input part relative to the output part. In this case, the angular positions of the input part and the output part are set to one another such that sequential actuation of the spring elements is possible. Through different switching of the spring elements, at least two levels of torque-dependent damping characteristics are obtained with respect to the torsion angle. Since initially only the first spring element resists torsion, the resistance square of the first spring element forms the first stage of the resistance characteristic curve.

Preferably, the second spring element resists twisting only when the input part is twisted by a transition angle relative to the output part. Therefore, the first spring element and the second spring element only exert a common resistance torque against further rotation of the input part relative to the output part when they have rotated the transition angle, so that together they form the second stage of the resistance characteristic curve.

Preferably, the first spring element resists twisting only when the input part is twisted by a free angle relative to the output part. A slight twisting of the input part relative to the output part is therefore possible without the first spring element or the second spring element already exerting a resistance torque at the onset of the twisting. If the free angle has been selected accordingly, it allows installation without preloaded spring elements and provides good isolation capabilities for pinion starting.

The first spring element and the second spring element are preferably arranged relative to each other in such a way that the torsional vibration damper has no theoretical unbalance during operation when the input part is torsion relative to the output part. As a result of the twisting of the input part relative to the output part, an increased spring compression of the first spring element and the second spring element also occurs, so that a displacement of the center of gravity also occurs. In order that the described process does not create imbalances in the torsional vibration damper that would trigger torsional vibrations, the spring elements are arranged so as to be mass-free and unbalanced relative to each other.

The first spring element and the second spring element are preferably arc-shaped and are guided in the channel region formed on the output part and/or the input part. At least the output part has on the circumferential side and opposite each other a first channel region and a second channel region, which extend over a part of the circumference of the output part. Furthermore, the output part has a first stop on the radially outer side and a second stop which is also designed symmetrically with respect to one another, said first stop and said second stop also being arranged on a partial circumference of the output part. extends upward and separates the first channel area and the second channel area from each other.

The first spring element and the second spring element preferably each comprise at least one compression spring, wherein the compression spring has a first side and a second side, with which the compression spring is supported on the input part and the output on the stop of the component.

The output part or the input part is preferably designed as a wing flange, wherein the wing flange has two wings extending radially away from the body of the wing flange and serving as a first spring element and a second spring. The stop of the component. The wings are preferably designed symmetrically with respect to one another, in particular point-symmetrically with respect to the axis of rotation in a plane perpendicular to the axis of rotation. Alternatively, the wings are symmetrical with respect to an axis extending perpendicularly through the axis of rotation, but are not point symmetrical with respect to the axis of rotation.

Furthermore, it is preferred that the first spring element and/or the second spring element are formed as a spring assembly, wherein the spring assembly is formed from an outer spring and a shortened inner spring arranged coaxially with the outer spring. According to the described configuration of the first spring element and/or the second spring element, the shortened inner spring is coaxially integrated into the corresponding outer spring. The inner spring is shortened relative to the outer spring and is mounted immovably in the outer spring. The formation of the first spring element and the second spring element as a spring group has the advantage that, with respective different lengths of the inner spring and the outer spring, a resistance characteristic curve up to four steps can be produced. Thus, with an increased torsion of the input part relative to the output part, the torque increases approximately in a curve-like manner. This contributes to improved running smoothness and further increases the damping effect of the torsional vibration dampers.

According to a third aspect, a torsional vibration damper according to the invention preferably comprises an input part and an output part and at least one spring element, wherein the input part and the output part oppose the action of the spring element about an axis of rotation of the torsional vibration damper. Mounted so as to be torsionably limited to each other; a shaft extending coaxially with the axis of rotation, wherein the output part or the input part is connected to the shaft in a rotationally fixed manner, wherein the shaft is mounted so as to be rotatable about the axis of rotation, and in rotation A first rolling bearing is arranged in the direction of the axis upstream of the device consisting of the input part and the output part, and a second rolling bearing is arranged downstream of the device consisting of the input part and the output part.

As is known from the prior art, the input part relates to the input-side flywheel mass and the output part relates to the output-side flywheel mass via which the rotational motion is introduced and which is driven by the drive The flywheel mass drives the flywheel on the driven side and then outputs rotational energy again on the driven side. The output part and/or the input part is preferably designed as a sheet metal element, wherein the output part and the input part are alternatively preferably designed as a cast or forged part. The manufacturing of the output part and the input part is not limited to the manufacturing method described.

The input part is the driven primary side of the torsional vibration damper and is directly acted upon by an external torque, wherein the input part or the output part is connected in a rotationally fixed manner, preferably by means of a screw connection, to a gear via which the corresponding torque is introduced into the torsional vibration damper. It should be noted beforehand that the opposite arrangement is also preferred, ie the input part is connected to the shaft in a rotationally fixed manner, with the other parts being arranged accordingly, so that the following is not restricted to the arrangement described. Therefore, the reverse introduction of torque is also possible, in which the torque is introduced into the torsional vibration damper via the flywheel mass connected to the shaft.

Furthermore preferably, the input part or the output part is rotatably mounted on the shaft by means of a sliding bearing. The plain bearing is designed to reduce the frictional resistance between the input part and the shaft and to prevent or at least reduce wear of the components when the input part lies directly against the shaft.

Preferably, the shaft is in one piece with the output or input part. One-piece production is here defined, for example, as the production of the shaft and the output part by milling from one piece of material, so that subsequent connections between the shaft and the output part do not have to be produced, for example, in the form of screw connections, press connections or welded connections. .

The two-piece embodiment of the shaft and the output part, which are then connected to each other in a rotationally fixed manner, proves to be disadvantageous in this regard: ie, by the forces introduced into the gear wheel, radial forces as well as axial forces act on the torsional vibration damper. . These forces cause the torsional vibration damper to tilt relative to the shaft, which causes additional loading of the two rolling bearings, but also causes the output part to tilt relative to the input part, which causes the stops of the input part and the output part. The changed spacing. Torsional vibration dampers are preferably used in powertrains of motor vehicles. Due to the at least sometimes high rotational speeds and the installation space conditions prevailing there, there are no moments or component loads in the associated components that would cause problems with shearing of the elements relative to each other, as would be the case between a shaft and an output or input part. Subsequent connections between them are potentially possible. In addition, a space-saving geometry is achieved through one-piece production.

In order to cope with the corresponding thermal expansion of the torsional vibration damper and compensate for this, the first rolling bearing and/or the second rolling bearing are preferably designed as fixed bearings or floating bearings.

Alternatively, the shaft and the output part and/or the input part are preferably multi-piece. According to an alternative embodiment of the torsional vibration damper, the output part is then connected in a form-locking, friction-locking and/or material-fitting manner to a corresponding receiving point on the shaft in a rotationally fixed manner. The advantage of the two-part embodiment over the one-piece embodiment is that the shaft, the output part and the input part can preferably be composed of different materials individually or in pairs, wherein the materials can be adapted to the respective conditions. . Thus, for example, a gear may advantageously have increased rigidity relative to a more flexible shaft. By producing the individual components separately, other processing techniques adapted to the respective functions of the components can also be used.

Furthermore, the production costs for a one-piece component increase compared to the production costs for a two-part component. The connection of the output part to the shaft is preferably carried out by riveting, screwing, welding, soldering and/or clamping after machining of the corresponding component.

Preferably, the output part or the input part has a radial extension 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 towards the spring element, wherein it furthermore preferably has a radial extension relative to the axis of rotation. Cover with an axis extending radially outwards, which cover has a circumferential shape complementary to a cylindrical section of the output part or the input part and is connected in a rotationally fixed manner to the cylindrical section of the output part or the input part . In order to prevent the spring element from moving in the axial direction, ie in the direction of the axis of rotation and thus out of the guide channel, the edge of the spring element facing away from the output part or the channel area is held in the channel area by a cover. In order to connect the output part and the cover to one another in a rotationally fixed manner, the cylindrical section of the output part and the complementary part of the cover are pressed against each other. The cylindrical section of the output part and the complementary part of the cover can preferably be welded or screwed to one another. Other connection types that achieve a rotationally fixed connection between the cylindrical section of the output part and the complementary part of the cover are also preferred.

A complementary connection between the cylindrical section of the output part and the radially outer end of the cover with respect to the axis of rotation is to be understood as a form-fitting and/or friction-fitting connection between the two elements. For example, the cover can preferably also have on its radially outwardly directed side a cylindrical section that is form-fitting with the cylindrical section of the output part, with which section the cover rests at least partially on the circumferential side. At the inner or outer circumference of the cylindrical section of the output member. Alternatively, however, other embodiments of the connection between the output part and the cylindrical section of the cover are also preferred.

The output part or input part and the cover preferably form between them a circumferential channel relative to the axis of rotation, wherein the channel at least partially surrounds the spring element both in the radial direction and in the axial direction relative to the axis of rotation. The portions of the output part and of the cover extending radially from the axis of rotation are here designed to prevent axial sliding of the spring element in the direction of the axis of rotation and to axially secure said spring element. In contrast, the cylindrical section of the output part and the complementary part of the cover serve to guide the spring element in the radial direction.

According to a particularly fourth aspect of the invention, a torsional vibration damper according to the invention preferably comprises an input part and an output part and at least one spring element, wherein the input part and the output part surround the torsional vibration damper against the action of the spring element a first shaft extending coaxially with the axis of rotation and non-rotatably connected to the input part and a first shaft extending coaxially with the axis of rotation and non-rotatably connected with the output part A second shaft, wherein at least one first bearing is arranged between the first shaft and the second shaft, by means of which the first shaft and the second shaft are rotatably supported relative to each other.

The input part and the output part are the drive-side flywheel mass and the output-side flywheel mass, which can be limitedly twisted 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 designed as a sheet metal element, alternatively preferably as a cast or forged part. Furthermore preferably, the production of the output part and the input part is not limited to the production method described. The input part and the output part can also preferably each be produced by different production methods.

The gear wheel is preferably coaxial with the first shaft and is fixed to the first shaft in a rotationally fixed manner, wherein the gear wheel has a toothless region on a circumferential portion of its outer circumference facing the second shaft. The first shaft has a flange section on its circumferential side which is designed to provide a rotationally fixed connection between an input part extending radially and disk-shaped from the first shaft and the gear wheel. For this purpose, the flange section is formed with a bore in the direction of the axis of rotation, through which the gear wheel and the input part are connected in a rotationally fixed manner to the flange section and thus to the first shaft by means of a screw connection. The gear wheel is designed to absorb the corresponding torque and to introduce said torque into the torsional vibration damper or to remove it 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 axis of rotation A. The output part is formed coaxially with the second shaft and has a radial and disc-shaped extension starting from the second shaft. The further bore of the flange section of the second shaft is here also designed to achieve a rotationally fixed connection between the output part and the second shaft by means of rivets. However, other types of form-fitting, friction-fitting and/or material-fitting connections between the input part and the first shaft and the output part and the second shaft are preferably also possible.

In order to achieve a space-saving mounting of the first shaft relative to the second shaft, the second shaft preferably has a longitudinal bore in the direction of the axis of rotation on a side facing the first shaft, wherein the first shaft is rotatable via the first bearing. Supported in longitudinal holes. Furthermore, it is preferred that the first shaft is supported radially relative to the second shaft by a first bearing and in an axial direction by a second bearing. Therefore, the first shaft and the second shaft are supported supporting 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 roller bearings or a combination of sliding bearings and rolling bearings. However, the first bearing and the second bearing can also preferably be designed in combination, for example in the form of plastic bushings with flange geometry.

Preferably, the first rolling bearing is arranged radially above the first bearing and coaxially with the second shaft on the outer circumference of the second shaft, wherein the axial positions of the first bearing and the first rolling bearing are preferably one to the other. same. In contrast, the second rolling bearing is preferably arranged coaxially with the first shaft and on the outer circumferential surface of the first shaft, wherein the second rolling bearing is arranged on a side of the input part facing away from the output part. The described arrangement of the first bearing and the second bearing and the first and second rolling bearing relative to each other achieves an optimal radial runout of the first and second shafts and a possible tilt of the first shaft relative to the second shaft in the machine. becomes difficult. This also saves installation space.

Preferably, the output part has a radial extension 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 in addition extending radially outwardly relative to the axis of rotation A cover is preferred which has an adapted shape on the circumferential side that is complementary to the cylindrical section 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 between them a circumferential channel relative to the axis of rotation, wherein the channel at least partially surrounds the spring element both in the radial direction and in the axial direction relative to the axis of rotation.

A complementary connection between the cylindrical section of the output part and the radially outer end of the cover with respect to the axis of rotation is to be understood as a form-fitting and/or friction-fitting connection between the two elements. For example, the cover can preferably also have on its radially outwardly directed side a cylindrical section that is form-fitting with the cylindrical section of the output part, with which section the cover rests at least partially on the circumferential side. At the inner or outer circumference of the cylindrical section of the output member. Alternatively, however, other embodiments of the connection between the output part and the cylindrical section of the cover are also preferred. The cover is preferably designed as a sheet metal element, alternatively preferably as a cast or forged part. Furthermore preferably, the production of the cover is not limited to the production method described. The cover may also preferably be produced by different manufacturing methods.

As already described, the output part and the cover form between them a channel surrounding the axis of rotation, wherein said channel at least partially surrounds the spring element both in the radial direction and in the axial direction with respect to the axis of rotation. The portions of the output part and of the cover extending radially from the axis of rotation are here designed to prevent axial sliding of the spring element in the direction of the axis of rotation and to axially secure said spring element. 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 said area is formed for the spring element displaced within the channel. friction surface. An additional stop is preferably also formed on the cover for supporting the spring element. Preferably, instead of one spring element, a plurality of spring elements are configured circumferentially distributed.

Preferably, the cover is arranged on its side radially inner with respect to the axis of rotation coaxially with the toothless region of the gear wheel and is rotatably supported on the toothless region by means of a third bearing. If the spring element of the torsional vibration damper is compressed, it presses both against the stops of the output part and the cover and against the stops of the input part. Since the stops of the cover and the output part are not exactly in the same position in the axial direction as the attachment of the output part and the second shaft, but are axially offset relative to this, a moment acts on the output part on the attachment area to the second shaft. This may cause the cover and output member to tilt relative to the second axis. The additional support between the cover and the toothless area of the gear wheel ensures additional guidance of the output part extending onto the cover and ensures a corresponding counter moment. The third bearing is preferably formed for radial support between the cover and the toothless area of the gear wheel and/or for axial support between the cover and the toothless area of the gear wheel. Like the first bearing and the second bearing, the third bearing is preferably embodied as a needle bearing or a combination of a sliding bearing and a rolling bearing. However, the third bearing can also preferably be designed in combination, for example in the form of a plastic bushing with flange geometry.

According to the fifth aspect, a preferred torsional vibration damper is proposed, the torsional vibration damper includes an input part, an output part and at least one spring element, wherein the input part and the output part can oppose the action of the at least one spring element relative to each other around the rotation axis. The gear carrier is connected to the output part in a rotationally limited manner by means of a gear wheel with helical teeth, wherein the gear wheel and the input part are formed on opposite sides of the output part. The torsional vibration damper is characterized in that the axial bearing for the output part is formed on the input part at a bearing radius with respect to the axis of rotation and that the bearing radius is greater than the force radius of the gear, wherein the force radius is the radius at At this radius, forces are transmitted between a gear and another gear, in which a radial bearing is formed, which is formed radially inside the gear carrier.

Unless explicitly stated otherwise, the terms used in this document such as radius, radial, radial direction, axial, axial direction, circumferential and circumferential direction always refer to the axis of rotation.

Torsional vibration dampers are used in particular in starter generators, which can be understood as a combination of a vehicle generator (Generator) for charging the battery and a starter for starting the internal combustion engine. . Here, depending on the operating situation, the torque is transmitted from the input component to the output component and thus to the gear wheel, in particular when the connection to the internal combustion engine is made via the gear wheel and said internal combustion engine has to be started. High torque occurs here. In the second operating state, torque is transmitted from the internal combustion engine via the gear wheel and the output component to the input component and via the input component to the shaft of the starter generator. This is generator operation, in which case the starter generator operates as a generator for charging the battery. In this case, the transmitted torque is small and has a different sign than the torque in the first operating situation.

By using gears with helical teeth, an axial force component is generated during operation, that is, an axial force, which must be absorbed by the bearings. The term “force radius” is understood to be the radius relative to the axis of rotation at which the force is introduced into the gear wheel or from the gear wheel into the meshing gear wheel. The force radius is in particular the maximum radius at which the meshing gears are in contact during meshing. Said force radius is smaller than the bearing radius of the axial bearing at which the output part is supported in the axial direction.

If, for example, when starting an internal combustion engine, an axial force is introduced into the output component from the direction of the gear wheel, the larger bearing radius causes supporting forces on the axial bearing which are directed opposite to the axial force, and this Not only in the region where the force introduction corresponds to the region in which the gear meshes with another gear via which the aforementioned gear is connected to the internal combustion engine, but also in the region offset by exactly 180° around the axis of rotation . Therefore, in the described operating situation, no tilting moment acts on the gear wheel and gear carrier. Forces caused by tangential and radial forces can be absorbed by radial bearings.

In the second operating case, the sign of the torque differs from that in the first operating case, and a corresponding axial force acts from the direction of the output member toward the gear wheel. In this case, the axial bearing cannot absorb the corresponding forces, but the radial bearing, which is completely located radially inside the gear carrier and gear wheel, supports the tilting moment which, due to its smaller magnitude, is significantly smaller than the tilting moment in the first operating situation.

The axial bearing is therefore designed in such a way that it can absorb the axial forces caused by the introduction of the torque via the gear wheel into the output part, while in the radial bearing it supports the axial force caused by the introduction of the torque from the output part into the output part. The axial force caused in the gear.

Preferably, the radial bearing is designed in such a way that it projects beyond the gear wheel in both directions in the axial direction with respect to the axis of rotation. Since the radial bearing projects beyond the gear and gear carrier in both directions in the axial direction, tilting moments caused by the forces that can be introduced through the gear in the radial and tangential directions can be eliminated.

Preferably, the outer radius of the gear is less than or equal to the bearing radius. Since the force radius is smaller than the outer radius of the gear, the force transmission takes place not at the outer radius but in the meshing toothings. Measuring the bearing radius as a function of the outer radius of the gear therefore allows determining the size of the torsional vibration damper which always results in a corresponding absorption of axial forces when a torque is introduced from the input part via the output part into the gear.

Preferably, the input part is connected to the shaft in a rotationally fixed manner, and the radial bearing is supported on the shaft. This is preferably the shaft of the starter generator. The transmission of the torque between the shaft and the input part as primary-side damping element is simple to implement in terms of design and at the same time allows the support of the radial bearing on the shaft. The shaft and the input part are particularly preferably formed in one piece. This simplifies the installation of torsional vibration dampers.

According to another sixth aspect of the invention, a starter generator is proposed including a torsional vibration damper according to the invention. The starter-generator includes in particular a shaft and a torsional vibration damper as described above, in which the shaft is connected in a rotationally fixed manner to the input part and a radial bearing is supported on the shaft. The input part is preferably formed in one piece with the shaft.

In the starter-generator, a direct or indirect connection to the internal combustion engine is established via a gear, either by meshing the gear with the starter ring gear or by ensuring a torque flow via one or more gears connected between them. . Starter generators are used in particular in motor vehicles, preferably motorcycles or cars, and combine the functions of a starter for an internal combustion engine with that of a car generator. The details and advantages described for the torsional vibration damper can be transferred and applied to the starter generator and vice versa.

The second to sixth aspects disclosed within the scope of this document may be combined in any manner with the first aspect and with each other, and at least two aspects selected from the second to sixth aspects may in particular be combined with the first aspect.

Description of the drawings

The invention and the technical field are explained in detail below with reference to the 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 partial aspects of the facts illustrated in the drawings and combine them with other components and knowledge from the description and/or the drawings. It should be pointed out in particular that the figures and in particular the dimensional relationships shown are only schematic. Identical reference numerals designate identical objects, so that explanations from other figures can be used supplementary if necessary. The accompanying drawing shows:

Figure 1 shows a very abstract illustration of the input components of a torsional vibration damper according to the invention;

Figure 2 shows a very abstract illustration of the output component of the torsional vibration damper according to the invention;

Figure 3 shows a very abstract illustration of a torsional vibration damper according to the invention;

Figure 4 shows a schematic longitudinal section of a torsional vibration damper according to the invention;

Figure 5 shows a schematic front view of a torsional vibration damper according to the invention;

Figure 6 shows a schematic view of an input component of a torsional vibration damper according to the invention according to a first embodiment of the second aspect of the torsional vibration damper;

Figure 7 shows a schematic view of the output component of the torsional vibration damper according to the invention according to a first embodiment;

Figure 8 shows a schematic movement sequence a) to d) of a torsional vibration damper according to the invention according to a first embodiment;

Figure 9 shows a schematic sequence of movements a) to d) of a torsional vibration damper according to the invention according to a second embodiment of said aspect of the torsional vibration damper;

Figure 10 shows a schematic representation of an output component of a torsional vibration damper according to the invention according to a third embodiment of said aspect of the torsional vibration damper;

Figure 11 shows a schematic view of an input component of a torsional vibration damper according to the invention according to a third embodiment of said aspect of the torsional vibration damper;

Figure 12 shows a schematic representation of a torsional vibration damper according to the invention according to a third embodiment of said aspect of the torsional vibration damper;

Figure 13 shows an example of a spring element constructed from a coaxial compression spring; and

FIG. 14 shows a damper characteristic curve of the described aspect of the torsional vibration damper that is achievable with the described torsional vibration damper;

Figure 15 shows a schematic longitudinal section of a torsional vibration damper according to the invention, in particular according to a third aspect of the invention;

FIG. 16 shows a schematic illustration of a torsionally fixed connection between a shaft and an output part or an input part according to a first embodiment of a torsional vibration damper according to the third aspect of the invention;

FIG. 17 shows a schematic representation of a torsionally fixed connection between a shaft and an output part or an input part according to a second embodiment of a torsional vibration damper according to the third aspect of the invention;

Figure 18 shows a schematic longitudinal section of a torsional vibration damper according to the invention, in particular according to the above-mentioned fourth aspect of the invention;

Figure 19 shows a longitudinal section of the torsional vibration damper;

Figure 20 shows a longitudinal section through the torsional vibration damper in a first operating situation;

Figure 21 shows a longitudinal section through the torsional vibration damper in a second operating situation; and

Figure 22 shows a schematic view of a starter generator with a torsional vibration damper.

Detailed ways

In particular, FIGS. 1 to 5 apply to the first aspect of the invention, which applies to oil lubrication of a torsional vibration damper. FIG. 1 shows a very abstract illustration of an input component 10 of a torsional vibration damper according to the invention. The input part 10 is a flywheel mass and is preferably designed as a sheet metal element, alternatively preferably as a cast or forged part. The input part 10 is designed as a wing flange 20 , wherein the wing flange 20 has two symmetrically formed wings 22 extending radially away from the wing flange body 21 . In principle, the input part 10 is not limited to the embodiment of the wing flange 20 . Furthermore, the wing flange body 21 has a recess 24 which is formed coaxially with the rotation axis A relative to its outer circumferential surface. The wing flange 20 is designed point-symmetrically with respect to the axis of rotation A. The wings 22 are therefore designed to face each other. Unless otherwise expressly stated, the terms radial or radial direction, axial or axial direction and circumferential direction when used in this document are to be understood always with respect to the axis of rotation A.

FIG. 2 shows a very abstract representation of the output component 2 of the torsional vibration damper according to the invention. The output part 2 is formed as a disk-shaped flywheel mass with a recess 3 formed coaxially with respect to the circumference. Also like the wing flange 20 , the output part 2 is preferably designed as a sheet metal element, alternatively preferably as a cast or forged part. On the circumferential side and opposite each other, the output part 2 has a first channel region 4 and a second channel region 5 , 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 radially outer side, which are also designed symmetrically to each other. The stop and the second stop also extend over a portion of the circumference of the output part 2 and separate the first and second channel areas 4 , 5 from one another. The first and second stops 6 and 8 are formed point-symmetrically with respect to the rotation axis A. 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 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 area 4 in the circumferential direction, and an opposite second stop surface 9 faces the second channel area 5 .

FIG. 3 shows a very abstract illustration of a torsional vibration damper 1 according to the invention, in which the previously described output part 2 and input part 10 are arranged one above the other or coaxially with the axis of rotation A, so that the output part 2 and the recesses 3, 24 of the input part 10 are aligned with each other. According to FIG. 3 , in addition to the input part 10 and the output part 2 , the torsional vibration damper 1 also includes a first spring element 30 and a second spring element 40 , which are each designed as Pressure spring. The input part 10 in the form of a wing flange 20 is designed to be rotatable relative to the output part 2 . The first spring element 30 is mounted movably in the circumferential direction in the first channel region 4 of the output part 2 , and the second spring element 40 is mounted movably in the circumferential direction in the second channel region 5 , wherein The first and second channel areas 4 , 5 serve as guides for the spring elements 30 , 40 . The spring elements 30 , 40 here have an extension in the uncompressed state, which extension 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 second end 31 of the first spring element 30 . Support for the first end 41 of the 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 stops 6 , 8 opposite the stop surfaces 7 , 9 are designed to delimit the respective other spring element 30 , 40 on the circumferential side, but only on the opposite side. If angular momentum is generated in the direction, force can also be absorbed. Opposite the stop surfaces 7 , 9 , 17 , 18 of the first and second stops 6 , 8 , the wing flange 20 also has a stop surface 23 which is designed to serve as the first or second stop. Support portions of the second ends 32, 42 of the two spring elements 30, 40.

The input part 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 by 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 hereafter referred to as the secondary side of the torsional vibration damper 1 which is driven by 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 part 10 twists relative to the output part 2 , the first and second spring elements 30 , 40 are compressed or exert a counter-torque against twisting. If the drive-side torque acting on the input part 10 is reduced or the applied torque is not subject to fluctuations but is applied identically, the spring elements 30 , 40 can relax at least partially and release their stored energy in order to move the input part 10 relative to each other. due to the torsional rotation of the output member 2.

FIG. 4 shows a schematic longitudinal section through a torsional vibration damper 1 according to the invention for illustrating the oil flow within the torsional vibration damper 1 . The torsional vibration damper 1 includes a shaft 50 which is connected in one piece on the radially outer side to a disk-shaped output part 2 in the form of a flywheel mass. The shaft 50 is mounted rotatably about the longitudinal axis A via two rolling bearings 61 , 62 . The output part 2 has first and second channel areas 4 , 5 opposite each other with respect to the axis of rotation A, said first and second channel areas extending over a part of the circumference of the output part 2 , wherein the outer surface of the output part 2 The circumferential area is flanged in the direction of the axis of rotation A into a pot shape and forms a cylindrical section 100 coaxial with the axis of rotation A. Furthermore, the output part 2 has first and second stops 6 , 8 on the radially outer side, which also extend over a part of the circumference of the output part 2 and separate the first and second stops. The two channel areas 4, 5 are separated from each other.

Furthermore, the side of the shaft 50 facing the output part 2 has an input part 10 configured coaxially with the axis of rotation A. The input part 10 has a recess 24 in the form of a through-hole and is mounted on a shaft 50 by means of a sliding bearing 60 so as to be at least partially rotatable relative to the output part 2 . The input part 10 is fixed on the shaft 50 in the direction of the rotation axis A via a sleeve 71 and a snap ring 70 , wherein a projection of the sliding bearing 60 extending in the radial direction is clamped between the input part 10 and the sleeve 71 . Therefore, the sliding bearing 60 is also prevented from moving axially in the direction of the rotation axis A, and a reliable fit is ensured. Also like the output part 2 , the input part 10 has a radial and disc-shaped extension starting from the shaft 50 . In addition, the input member 10 has stoppers 23 respectively facing the stoppers 6 and 8 of the output member 2 . The spring elements 30 , 40 are each supported in the circumferential direction in a channel region 4 , 5 and between stops 6 , 8 , 23 , the channel regions 4 , 5 serving 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 stops 23 of the input part 10 , The spring elements 30 , 40 resist torsion of the input part 10 relative to the output part 2 .

Furthermore, on the side of the input part 10 facing away from the output part 2 , the gear wheel 80 is fastened by means of a screw connection 81 and is designed to transmit the corresponding torque to the output part 2 via the spring elements 30 , 40 in a damped manner. .

In order to prevent the spring elements 30 , 40 from moving in the axial direction, ie in the direction of the axis of rotation A and thus out of the guide channels 4 , 5 , the end of the spring elements 30 , 40 facing away from the output part 2 or the channel region 4 , 5 The edges are held in the channel areas 4 , 5 by covers 90 . The cover 90 is arranged coaxially with the output part 2 and the input part 10 , is also disk-shaped and has a central recess 91 on the inside facing the axis of rotation A, wherein there are no connections to other components on this side, in particular There is no connection to the input component 10 .

In addition, the cover 90 also has on its radially outwardly directed side a flanged and cylindrical section 101 complementary to the cylindrical section 100 of the output part 2 , with which the cover 90 is positioned around the ring. The circumferential side rests against the inner circumference of the cylindrical section 100 of the output part 2 . 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 of the cover 90 are pressed against each other and together form a circumferential channel 102 therebetween. The spring elements 30 , 40 are therefore held not only in the radial direction by the inside of the cylindrical section 101 of the cover, but also in the axial direction by the channel regions 4 , 5 and the radially outwardly directed side of the cover 90 .

This is because the spring elements 30 , 40 are continuously compressed and relaxed again during operation, ie when the input part 10 is twisted relative to the output part 2 , and in particular along the inner region of the cylindrical section 101 of the cover during said reversible deformation. friction, so lubrication and cooling are provided by oil. Furthermore, a constant friction occurs here also between the input part 10 and the output part 2 , since the input part 10 is supported on one side on the output part 2 and the two parts 2 , 10 form a friction surface 110 between them. Furthermore, lubrication of the sliding bearing 60 also occurs between the shaft 50 and the input part 10 .

In order to enable lubrication of the torsional vibration damper 1 , the shaft 50 has a central bore 51 along the longitudinal axis A, which is continuously filled with oil. Starting from the central hole 51, supply holes 53, 54, 55 are provided radially to the outer circumferential surface 52 of the shaft. The first supply opening 53 here opens into the area of the plain bearing 60 in order to supply said area with lubricant, in particular oil. The second supply opening 54 opens into a surrounding gap 120 , which is formed on the one hand by the shaft 50 and the output part 2 connected in one piece thereto and on the other hand by the input part 10 . Based on this, the third supply opening 55 is guided through the input part 10 in order to discharge the oil from the gap 120 . Owing to the centrifugal force, the oil is conveyed from there into the region of the surrounding channel 102 , whereby the spring elements 30 , 40 are continuously moistened with lubricant. The friction surface 110 between the spring elements 30 , 40 and the inner region of the cylindrical section 101 of the cover 90 is therefore particularly lubricated. Since the input part 10 is interrupted in the circumferential direction for receiving the spring elements 30 , 40 on the circumferential side, the oil can reach the channel areas 4 , 5 .

In order to eliminate the disadvantages previously described in the prior art and to prevent bending of the cylindrical sections 100 , 101 of the cover 90 and of the output part 2 which are pressed against each other, the output part 2 is radially directed towards the axis of rotation A, starting from the spring element 30 Starting from the friction surface 110 in height, there is an oil drain hole 130 in the direction of the rotation axis A. In line with this, an oil drain hole 130 is also formed in the cover 90 . The oil drain opening 130 ensures that oil does not have to accumulate between the output part 2 and the cover 90 as far as the inner edge of the recess 91 of the cover 90 in order to flow out, but rather only in the area to be cooled and to be installed. The lubricated area is supplied with a sufficient amount of oil. The oil drain hole 130 also results in improved cooling of the strongly heated spring elements 30 , 40 through continuous compression and relaxation, thereby increasing the durability of the torsional vibration damper 1 .

FIG. 5 shows a schematic front view of the torsional vibration damper 1 according to the invention from one side of the output part 2 . In order to prevent imbalances due to uneven outflow of oil, the oil drain holes 130 are respectively arranged such that a uniform outflow over the circumference is possible. For example, if the torsional vibration damper 1 has a pair of spring elements 30 , 40 opposite each other, the oil drain openings 130 are preferably also formed on the output part 2 but also on the cover 90 so as to be mirror images of each other relative to the axis of rotation A. .

In order to improve in particular the cooling of the spring elements 30 , 40 and thereby further increase their life expectancy, it is also preferred if the oil drain opening 130 is formed only in the area of the spring elements 30 , 40 . This causes the oil accelerated outwards by centrifugal force to flow towards the oil drain holes 130 at the spring elements 30 , 40 , thus compared to when the oil drain holes 130 are evenly distributed over the circumference of the output part 2 and the cover 90 , the oil drain hole is subjected to a larger volume flow of oil.

The invention relates to a torsional vibration damper 1 having an input part 10 and an output part 2 which can be rotated about an axis of rotation A against the action of spring elements 30 , 40 limited twisting relative to each other. The torsional vibration damper 1 has an oil drain opening 130 , which is formed axially with respect to the axis of rotation A and via which oil can be removed from the torsional vibration damper 1 during operation. This makes it possible to achieve a defined flow of oil, in particular in the area of the spring elements 30 , 40 , and to prevent oil from accumulating in the torsional vibration damper 1 and from undesirable flows that could cause damage to the torsional vibration damper 1 . forces act on the components of the torsional vibration damper 1.

In FIGS. 6 to 14 , a second aspect of the torsional vibration damper 1 which concerns spring elements 30 , 40 of different lengths applies in particular. FIG. 6 shows a schematic representation of the input component 10 of the torsional vibration damper according to the invention according to a first embodiment. The input part 10 is a flywheel mass and is preferably designed as a sheet metal element, alternatively preferably as a cast or forged part. The input part 10 is designed as a wing flange 20 according to a first and second embodiment, wherein the wing flange 20 has two radially remote wing flanges that are configured symmetrically to one another in the first embodiment. The body 21 extends from wings 22 . Furthermore, the wing flange body 21 has a recess 24 which is formed coaxially with the rotation axis A relative to its outer circumferential surface. In this embodiment, the wing flange 20 is formed point-symmetrically with respect to the axis of rotation A. The wings 22 are therefore designed to face each other. Unless otherwise expressly stated, the terms radial or radial direction, axial or axial direction and circumferential direction used in this document are understood always with respect to the axis of rotation A.

FIG. 7 shows a schematic representation of the output component 2 of the torsional vibration damper according to the invention according to a first embodiment. The output part 2 is formed as a disc-shaped flywheel mass and has a recess 3 formed coaxially with the circumference. Also like the wing flange 20 , the output part 2 is preferably designed as a sheet metal element, alternatively preferably as a cast or forged part. On the circumferential side and opposite each other, the output part 2 has a first channel region 4 and a second channel region 5 , which extend over a part of the circumference of the output part 2 . The first channel area 4 is formed over a larger circumferential section than the second channel area 5 . Furthermore, the output part 2 has a first stop 6 and a second stop 8 on the radially outer side, which are also designed symmetrically to each other. The stop and the second stop also extend over a portion of the circumference of the output part 2 and separate the first and second channel areas 4 , 5 from one another. The first and second stops 6 , 8 are designed symmetrically with respect to the vertical axis B. 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 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 area 4 in the circumferential direction, and an opposite second stop surface 9 faces the second channel area 5 .

FIG. 8 schematically shows the movement sequences a) to d) of the torsional vibration damper 1 according to the invention according to a first embodiment in order to illustrate its operating principle. In addition to the input part 10 and the output part 2 , the torsional vibration damper 1 also includes 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 designed to be rotatable relative to the output part 2 . The first spring element 30 is mounted movably in the circumferential direction in the first channel region 4 of the output part 2 , and the second spring element 40 is mounted movably in the circumferential direction in the second channel region 5 , wherein The first and second channel areas 4 , 5 serve as guides for the spring elements 30 , 40 . Depending on the expansion of the circumferential sections of the channel regions 4 , 5 in the circumferential direction with respect to the axis of rotation A, the expansion of the spring elements 30 , 40 in each case corresponding to the respective circumferential section when viewed in the circumferential direction also has in each case a Extension in the uncompressed state. The first spring element 30 therefore also has a greater extension in the circumferential direction than the second spring element 40 . The first stop surface 7 of the first stop 6 serves as a support for the first end 31 of the first spring element 30 , wherein the second stop surface 9 of the second stop 8 is designed to serve as a second spring. Support for the first end 41 of the 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 stops 6 , 8 opposite the stop surfaces 7 , 9 are designed to delimit the respective other spring element 30 , 40 on the circumferential side, but if on the opposite side If angular momentum is realized in the direction, force can also be absorbed. Opposite the stop surfaces 7 , 9 , 17 , 18 of the first and second stops 6 , 8 , the wing flange 20 also has a stop surface 23 which is designed to serve as the first or second stop. Support portions of the second ends 32, 42 of the two spring elements 30, 40.

The input part 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 by 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 hereafter referred to as the secondary side of the torsional vibration damper 1 which is driven by 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). However, the torsional vibration damper 1 is not limited to placement between the transmission and the engine. Alternatively, the torsional vibration damper 1 can also be installed as a vibration absorber, preferably together with a pulley coupling. In principle, use in various embodiments is preferred in order to damp torsional vibrations.

In step a), no torque acts on the wing flange 20 , or the wing flange 20 does not twist. Therefore, the first and second spring elements 30 , 40 are not pressurized via the wing flange 20 and are therefore not compressed. According to a first embodiment of the torsional vibration damper 1 , the wings 22 of the wing flange 20 have a smaller extent in the circumferential direction relative to the stops 6 , 8 respectively. Thus, in the rest position, the wings 22 can also be oriented relative to the spring elements 30 , 40 without contact. The wing flange 20 can therefore be twisted by a certain degree about the longitudinal axis A without reaction forces acting on it via the spring elements 30 , 40 .

In step b), a torque acts on the wing flange 20 , which is twisted relative to the output part 2 . Due to the different extensions of the spring elements 30 , 40 , the wing 22 of the wing flange 20 is initially supported on the longer first spring element 30 , wherein the other wing 22 is still connected to the second end of the second spring element 40 42 are spaced apart and oriented. The reaction force is therefore only exerted on the wing flange 20 via the first spring element 30 .

In step c), the torque acting on the wing flange 20 is increased, so that the first spring element 30 is compressed by the wing 22 . This causes a further twisting of the wing flange 20 relative to the output part 2 until the other wing 22 also rests with its stop surface 23 on the second end 42 of the second spring element 40 and the second spring element 40 The additional reaction force resists further rotation of the wing flange 20.

According to step d), if the torque acting on the wing flange 20 increases further, the first and second spring elements 30 , 40 are now compressed by a further twisting of the wing flange 20 relative to the output part 2 .

FIG. 10 shows schematic views a) to d) of a torsional vibration damper 1 according to the invention according to a second embodiment for illustrating its operating principle. The second embodiment relates to a modified first embodiment of the torsional vibration damper 1 . In the second embodiment, the output part 2 differs from the output part 2 of the first embodiment only in that the stops 6 , 8 have a reduced extension in the circumferential direction. Furthermore, in the embodiment described, the stops 6 , 8 are configured opposite one another, so that the first stop 6 can therefore be transformed into the second stop 8 by rotating through 180° about the axis of rotation A. Therefore, the first stop 6 and the second stop 8 are formed point-symmetrically with respect to the rotation axis A in a plane perpendicular to the rotation axis A. The first and second channel areas 4, 5 thus have the same extension in the circumferential direction. In contrast, the extension of the spring elements 30 , 40 in the circumferential direction remains unchanged compared to the first embodiment. The second channel region 5 therefore has a greater extent in the circumferential direction than the second spring element 40 . In contrast to the shortened stops 6 , 8 , the input part 10 in the form of a wing flange 20 according to the second embodiment has wings 22 that are larger in the circumferential direction than those in the first embodiment. The portion 22 has a greater extent and also has a greater extent in the circumferential direction than the stops 6 , 8 . The second spring element 40 is supported with its first and second ends 31 , 32 on mutually facing stop surfaces 23 of the wings 22 , thereby preventing the second spring element 40 from sliding down in the second channel region 5 .

The wing flange 20 of the second embodiment thus differs from the wing flange of the first embodiment in particular in that the wings 22 of the wing flange 20 are arranged asymmetrically and not point-symmetrically with respect to the axis of rotation A. . The wings 22 of the wing flange 20 are symmetrical with respect to an axis perpendicular to the axis of rotation A. As in the first embodiment, according to the second embodiment corresponding further stop surfaces 7 , 9 , 17 , 18 are formed on the output part 2 , on the first and second spring elements 30 , 40 and on the wings of the wing flange 20 between Department 22.

In step a), no torque acts on the wing flange 20 . Therefore, no force acts via the wings 22 on the first spring element 30 which is already in this position with the first end 31 resting against the first stop surface of the first stop 6 7, and the second end 32 abuts against the stop surface 23 of the wing 22 opposite the stop surface 7.

In step b), the torque acting on the wing flange 20 is increased, so that said wing flange is twisted relative to the output part 2 and the first spring element 30 is compressed. The second spring element 40 always rests uncompressed on the wing 22 and moves in the circumferential direction towards the first stop 6 .

According to step c), the torque is further increased, so that the wing flange 20 is further twisted relative to the output part 2 and the first spring element 30 is further compressed. The twist develops to the point where the first end 41 of the second spring element 40 also comes into contact with the stop surface 9 of the second stop 8 and exerts a reaction force against the twist of the wing flange 20 .

In step d), the wing flange 20 is loaded with a further increasing torque, so that a further twisting of the wing flange 20 relative to the output part 2 has occurred and the first and second spring elements 30 , 40 are compressed and together A reaction force is applied that is opposite to the torque applied to the spring flange 20 .

Figures 10 and 11 show the output component 2 and the input component 10 of a third embodiment of the torsional vibration damper 1 according to the present invention, wherein Figure 12 schematically shows the entire torsion component including the output component 2 and the input component 10. Vibration absorber 1. The output part 2 and the input part 10 are here also respectively a first flywheel mass and a second flywheel mass. The proposed flywheel mass can each preferably be designed as a sheet metal element, alternatively preferably as a cast or forged part.

The third embodiment differs from the first and second embodiments in particular that the input part 10 is now disk-shaped and is not designed in the form of a wing flange. Here, the output member 2 shown in FIG. 10 is the driven side, and the input member 10 shown in FIG. 11 is the driving side. The first channel region 4 and the second channel region 5 are formed in the form of a half shell in the input part 10 , and the first channel region 11 and the second channel region 12 are formed in the form of a half shell in the output part 2 , so that it follows Four channel areas 4, 5, 11, and 12. In this case, the first spring element 30 is supported in the opposite first channel areas 4 and 11 , and the second spring element 40 is supported in the opposite second channel areas 5 and 12 . Three of the four channel areas 4 , 11 , 12 have the same length in the circumferential direction, with the fourth channel area 5 formed in the input part 10 being larger than the other three channel areas 4 , 11 , 12 Shortly constructed.

As also in the first and second embodiments described above, in both the output part 2 and the input part 10 , mutually symmetrically arranged stops 6 , 8 , 13 , 15 are formed in the channel region 4 , 5, 11, 12, said stops separate the channel areas 4, 5, 11, 12 of the output and input parts 2, 10 respectively from each other. The stops 6 , 8 of the output part 2 have a greater extension in the circumferential direction than the stops 13 , 15 of the input part 10 , wherein the additional extension of the stops 6 , 8 of the output part 2 extends to the third In the area of the second channel area 5 , the second channel area is shortened in the circumferential direction relative to the first channel area 4 . The second channel area 5 of the output part 2 is therefore a shortened channel area 5 relative to the other channel areas 4 , 11 , 12 .

In FIG. 12 , the output part 2 and the input part 10 are arranged one above the other or coaxially with the axis of rotation A, so that the recesses 3 , 16 of the output part 2 and the input part 10 are aligned with each other. The figure shows the circumferentially shortened second channel region 5 of the output part 2 relative to the unshortened second channel region 12 of the input part 10 . As shown in FIG. 12 , the spring elements 30 , 40 also have different extensions in the circumferential direction in this embodiment. The extension of the first spring element 30 in the circumferential direction in the uncompressed state corresponds here to the extension of the circumferential sections of the first channel regions 4 , 11 of the output part 2 and of the input part 10 . In contrast, the second spring element 40 is configured to be shortened relative to the first spring element 30 , its extension in the circumferential direction corresponding to the circumferential section of the shortened second channel region 5 of the output part 2 extension.

As also in the embodiment above, when torque is applied to the driven input member 10 , a twisting of the input member 10 relative to the output member 2 occurs. Here, first spring element 30 is compressed. When the input part 10 rotates relative to the output part 2 , the second spring element 40 is also twisted about the axis of rotation A by this input part but remains uncompressed until it rests against the first side of the input part 10 . 13 stops. The extension of the second spring element 40 and the extension of the shortened second channel region 5 of the output part 2 are coordinated with each other in the circumferential direction, so that even if the second spring element 40 is not yet in contact with the first stop 13 of the input part 10 Engaged in a torque-effective manner, the second spring element 40 is also guided in a targeted manner either through the channel region 12 or also through the stops 6 , 8 . As a result, despite the shorter length, the position of the second spring element 40 in the channel areas 5 , 12 surrounding it is ensured and the effect on the imbalance of the torsional vibration damper 1 is reduced.

FIG. 13 shows an example of a spring element in the form of a spring assembly 250 constructed from a coaxial compression spring, which spring element is supported, for example, in the channel region 4 of the output part 2 according to a third embodiment of the torsional vibration damper 1 , 5 and supported in the channel areas 11 , 12 of the input member 10 . According to the described configuration of the first and/or second spring element 30 , 40 as spring group 250 , the shortened inner spring 252 is coaxially integrated into the corresponding outer spring 251 . The inner spring 252 is shortened relative to the outer spring 251 and is mounted immovably in the outer spring 251 . However, the resistance to compression of the outer spring 251 is not increased by the additional inner spring 252 when only said outer spring is loaded. Only when the outer spring 251 is compressed to the length of the inner spring 252 does the resistance of the inner spring 522 also take effect. The first spring element 30 and the second spring element 40 are each preferably formed as a spring set 250 , wherein the respective inner springs 252 have a mutually individualized length relative to each other, and the respective outer springs 251 have a mutually individualized length relative to each other. length. Therefore, the four springs 251 and 252 are configured to have different lengths from each other. Preferably, the embodiment of the first and second spring elements 30 , 40 in the form of a spring assembly 250 is not limited to the third embodiment of the torsional vibration damper 1 , but also to the first embodiment of the torsional vibration damper 1 This and the second embodiment are preferred as well as other aspects of the torsional vibration damper 1 .

FIG. 14 shows the damper characteristics achievable with the described torsional vibration damper 1 . In the horizontal region designated by a), a twisting of the input part 10 relative to the output part 2 occurs without the first spring element 30 causing a torsional reaction force or moment. When a certain twist is reached, namely the point characterized by b), the first spring element 30 comes into contact both with the stops 15 , 23 of the input part 10 and with the stop 6 of the output part 2 . This is the angle of freedom described above, which in the example is approximately 5°. If the torque now acting on the input part 10 increases further, said input part 10 is further twisted relative to the output part 2 , the torque increasing linearly as a function of the angle of rotation up to point c). At this point, the first spring element 30 has been compressed to the point where the second spring element 40 now also rests against the stops 13 , 23 of the input part 10 and the stop 8 of the output part 2 . This is the transition angle described above. Therefore, the first and second spring elements 30, 40 now jointly resist further torsion. This is illustrated in FIG. 14 by a linearly stronger increase in the resistance moment between points c) and d) with increasing torsion angle. Point d) indicates that the twisting of the input part 10 relative to the output part 2 is limited by design to a specific twisting angle. Points a) to d) in FIG. 14 correspond here to situations a) to d) in FIG. 8 or FIG. 9 .

By using spring array 250 as first spring element 30 and/or second spring element 40 , the steps in the damper characteristic curve can be increased. For example, it is possible to achieve a four-stage damper characteristic curve if the first and second spring elements 30 , 40 are designed as a spring set 250 in which the respective outer spring 251 and inner spring 252 have different extensions relative to one another. . The torque can therefore increase approximately in a curve-like manner with further twisting of the input part relative to the output part.

Figures 15 to 17 relate in particular to the above-mentioned third aspect of the invention. FIG. 15 shows a schematic longitudinal section through a torsional vibration damper 1 according to the invention in order to illustrate further components of the torsional vibration damper 1 . The torsional vibration damper 1 includes a shaft 50 which is connected radially outwardly to a disk-shaped output part 2 in the form of a flywheel mass. In the following, a rotationally fixed connection between the shaft 50 and the output part 2 is assumed, but it is foreseen that the reverse arrangement is also possible, that is, the input part 10 is connected to the shaft 50 in a rotationally fixed manner, and the other parts are correspondingly connected to this. set up.

The output part 2 has first and second channel areas 4 , 5 opposite each other with respect to the axis of rotation A, said first and second channel areas extending over a part of the circumference of the output part 2 , wherein the outer surface of the output part 2 The circumferential area is flanged in the direction of the axis of rotation A into a pot shape and forms a cylindrical section 100 coaxial with the axis of rotation A. Furthermore, the output part 2 has first and second stops 6 , 8 on the radially outer side, which also extend over a part of the circumference of the output part 2 and separate the first and second stops. The two channel areas 4, 5 are separated from each other.

Furthermore, opposite the output member 2 , the torsional vibration damper 1 has an input member 10 configured coaxially with the rotation axis A. In addition, the input part 10 is connected to the gear wheel 80 in a rotationally fixed manner by means of an intermediate part 82 on the side facing away from the output part 2 via a screw connection 81 . The gear wheel 80 is designed to absorb the corresponding torque and introduce it into the torsional vibration damper 1 . A direct or indirect connection to the crankshaft of the internal combustion engine can preferably be established via a gear 80 . The connection formed by the input part 10 , the intermediate part 82 and the gear wheel 80 has a continuous recess 24 and is supported on a shaft 50 by means of a plain bearing 60 so as to be at least partially rotatable relative to the output part 2 . The input part 10 is fixed on the shaft 50 in the direction of the axis of rotation A by a nut 370 screwed onto the thread 71 on the shaft side, wherein a projection of the sliding bearing 60 extending in the radial direction is between the intermediate part 82 and the nut 370 clamped between. Therefore, axial movement of the sliding bearing 60 in the direction of the rotation axis A is also prevented, and a reliable fit is ensured. Oppositely, the input part 10 is supported or rotatably mounted on the output part 2 with a surrounding friction surface in the form of a friction bearing 63 .

Also like the output part 2 , the input part 10 has a radial and disc-shaped extension starting from the shaft 50 . In addition, the input member 10 has stoppers 23 respectively facing the stoppers 6 and 8 of the output member 2 . The spring elements 30 , 40 are respectively supported in the circumferential direction in channel regions 4 , 5 and between stops 6 , 8 , 23 , the channel regions 4 , 5 serving 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 stops 23 of the input part 10 , The spring elements 30 , 40 resist torsion of the input part 10 relative to the output part 2 .

In order to prevent the spring elements 30 , 40 from moving in the axial direction, ie in the direction of the axis of rotation A and thus out of the guide channels 4 , 5 , the spring elements 30 , 40 face away from the output part 2 or towards the channel region 4 , 5 are held in the channel areas 4 , 5 by covers 90 . The cover 90 is arranged coaxially with the output part 2 and the input part 10 , is also disk-shaped and has a central recess 91 on the inside facing the axis of rotation A, wherein there are no connections to other components on this side, in particular There is no connection to the input component 10 .

In addition, the cover 90 also has on its radially outwardly directed side a flanged and cylindrical section 101 complementary to the cylindrical section 100 of the output part 2 , with which the cover 90 is positioned around the ring. The circumferential side rests against the inner circumference of the cylindrical section 100 of the output part 2 . 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 of the cover 90 are pressed against each other and together form a circumferential channel 102 therebetween. The spring elements 30 , 40 are therefore held not only in the radial direction by the inside of the cylindrical section 101 of the cover, but also in the axial direction by the channel regions 4 , 5 and the radially outwardly directed side of the cover 90 .

On both sides of the torsional vibration damper 1 , the shaft 50 is provided with two bearing seats 351 , 352 , which are designed to receive two rolling bearings 61 , 62 , whereby the shaft 50 is surrounded by these two rolling bearings 61 , 62 The longitudinal axis A is mounted rotatably.

FIG. 16 shows a schematic representation of the torsionally fixed connection between the shaft 50 and the output part 2 or the input part 10 according to a first embodiment of the torsional vibration damper 1 . In the following, with reference to FIGS. 5 and 6 , only the output part 2 connected to the shaft 50 is mentioned here, with the input part 10 preferably also being connected to the shaft.

According to a first embodiment of the torsional vibration damper 1 , the shaft 50 and the output part 2 are produced in one piece. One-piece production is here defined, for example, as the production of the shaft 50 and the output part 2 from one piece of material by milling, so that it is not necessary to produce a connection between the shaft 50 and the output part 2 in the form of a screw connection, a press connection or a welded connection, for example. Subsequent connections.

The two-part embodiment of the shaft 50 and the output part 2 which are then connected to each other in a rotationally fixed manner has proven to be disadvantageous in that the forces introduced into the gear 80 , radial as well as axial forces act on On the torsional vibration damper 1. These forces cause the torsional vibration damper 1 to tilt relative to the shaft 50 , thus causing additional loading of the two ball bearings, but also cause the output part 2 to tilt relative to the input part 10 , and cause an increase in the input part 10 . The resulting distance of the stops 6, 8, 23 of the output part 2 changes accordingly. Due to the high rotational speeds and installation space conditions, in the one-piece construction there are no problems with moments or component loads that would cause shearing of the elements relative to each other, as would be the case in the subsequent connection between the shaft 50 and the output part 2 possible. Furthermore, the one-piece production of the connection consisting of shaft 50 and output part 2 saves installation space.

FIG. 17 shows a schematic representation of the torsionally fixed connection between the shaft 50 and the output part 2 according to a second embodiment of the torsional vibration damper 1 . Unlike in the first embodiment, in the second embodiment the shaft 50 is not connected in one piece with the output part 2 . In the second embodiment of the torsional vibration damper 1 , the output part 2 is then connected to a corresponding receiving point on the shaft 50 in a rotationally fixed manner in a form-fitting, friction-fitting and/or material-fitting manner. The advantage of a two-part embodiment over a one-piece embodiment is that the shaft 50 and the output part 2 can be produced, for example, from different materials adapted to the respective conditions. Furthermore, the separate production also increases the processing range of the respective component. The production costs for a one-piece component are also increased compared to the production costs for a two-piece component. The connection of the output part 2 to the shaft 50 is preferably carried out by riveting, screwing, welding, soldering and/or clamping after processing of the corresponding components.

Said third aspect of the invention relates to a torsional vibration damper 1 having an input part 10 and an output part 2 which can act against spring elements 30 , 40 The actions of the two are limitedly twisted relative to each other about the axis of rotation A. The torsional vibration damper 1 has a shaft 50 extending coaxially with the axis of rotation A, with the output part 2 or the input part 10 being connected to the shaft 50 in a rotationally fixed manner. In order to mount the torsional vibration damper 1 rotatably about the axis of rotation A, a first rolling bearing 61 is provided on the shaft 50 in the direction of the axis of rotation A upstream of the device formed by the input part 10 and the output part 2 and on A second rolling bearing 62 is arranged downstream of the device formed by the input part 10 and the output part 2 .

Figure 18 relates in particular to a fourth aspect of the invention. FIG. 18 shows a schematic longitudinal section through a torsional vibration damper 1 according to the invention in order to illustrate further components of the torsional vibration damper 1 . The torsional vibration damper 1 includes a first shaft 450 arranged coaxially with the rotation axis A and a second shaft 451 also arranged coaxially with the rotation axis A. The first shaft 450 is rotatably supported relative to the second shaft 451 via the first bearing 460 in the longitudinal hole 452 of the second shaft 451 . Furthermore, a second bearing 461 is provided between the first shaft 450 and the second shaft 451 , which is formed as a spacer between the first shaft 450 and the second shaft 451 and connects the first shaft 450 and the second shaft 451 . The second shafts 451 support each other in the axial direction, that is, in the direction of the rotation axis A.

Starting from the axis of rotation A, a second shaft 451 with a first bearing seat 471 is mounted rotatably in the radial direction via a first rolling bearing 470 on a housing (not shown). Correspondingly, a first shaft 450 with a second bearing seat 481 is rotatably supported at its end facing away from the second shaft 451 via a second rolling bearing 480 , offset along the axis of rotation A (not shown). on the casing.

On the circumferential side, the first shaft 450 has a flange section 453 , which is formed for the input part 10 extending radially and disk-shaped from the first shaft 450 by means of a screw connection 454 A torsion-proof connection is achieved with the gear 510 . For this purpose, the flange section 453 is formed with a bore 455 extending in the direction of the axis of rotation A, through which the gear wheel 510 and the input part 10 are connected to the flange section 453 in a rotationally fixed manner by means of a screw connection 454 . Connected to the first axis 450. Gear wheel 510 is designed to absorb the corresponding torque and introduce it into torsional vibration damper 1 or remove the torque from torsional vibration damper 1 . The torsional vibration damper 1 is preferably used in a powertrain of a motor vehicle, which preferably has at least one internal combustion engine as torque source. The torsional vibration damper 1 is preferably connected directly or indirectly via a gear 510 to the crankshaft of the internal combustion engine. The torsional vibration damper 1 is preferably connected to a starter generator, which combines the functions of a starter and that of a vehicle generator.

The second shaft 451 also has at its end facing the first shaft 450 a corresponding further flange section 56 with a further bore 57 formed in the direction of the axis of rotation A. Coaxially with the second shaft 451 , the output part 2 is formed with a radial and disc-shaped extension starting from the second shaft 451 . The further bore 57 of the further flange section 56 of the second shaft 451 is here also designed 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 opposite each other with respect to the axis of rotation A, which extend over a part of the circumference of the output part 2 , wherein The outer circumferential area of the output part 2 is flanged in the direction of the axis of rotation A into a pot shape 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 radially outer side, which are also located on a part of the circumference of the output part 2 extending and separating the first and second channel areas 4, 5 from each other.

The input member 10 has stoppers 23 respectively opposed to the stoppers 6 and 8 of the output member 2 . The spring elements 30 , 40 are respectively supported in the circumferential direction in channel regions 4 , 5 and between stops 6 , 8 , 23 , the channel regions 4 , 5 serving as guides for the spring elements 30 , 40 . Because the spring elements 30 , 40 are supported according to FIG. 3 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 stops 23 of the input part 10 so that the spring elements 30 , 40 resist torsion of the input part 10 relative to the output part 2 .

In order to prevent the spring elements 30 , 40 from moving in the axial direction, ie in the direction of the axis of rotation A and thus out of the guide channels 4 , 5 , the spring elements 30 , 40 face away from the output part 2 or towards the channel region 4 , 5 are held in the channel areas 4 , 5 by covers 90 . The cover 90 is arranged coaxially with the output part 2 and the input part 10 and is also disk-shaped in the radial direction starting from the axis of rotation A. In order to ensure uniform loading of the spring elements 30 , 40 in their direction of extension and to avoid possible twisting, a first stop 91 and a second stop 92 are also formed on the cover 90 so as to act in the same direction, to support the stoppers 6 and 8 of the output member 2 .

In addition, the cover 90 also has on its radially outwardly directed side a flanged and cylindrical section 101 complementary to the cylindrical section 100 of the output part 2 , with which the cover 90 is positioned around the ring. The circumferential side rests against the inner circumference of the cylindrical section 100 of the output part 2 . 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 of the cover 90 are pressed against each other and together form a circumferential channel 520 therebetween. The spring elements 30 , 40 are therefore held not only in the radial direction by the inside of the cylindrical section 101 of the cover, but also in the axial direction by the channel regions 4 , 5 and the radially outwardly directed side of the cover 90 .

The cover 90 is formed on its radially inwardly directed side with a further flanged and cylindrical section 502 , which is formed opposite the radially outer cylindrical section 101 . In the radial direction, the toothless area 111 of the gear 510 overlaps a further cylindrical section 502 , wherein a third bearing 462 is arranged between the cylindrical section 502 and the toothless area 111 of the gear 510 , said third bearing 462 The three bearings support the further cylindrical section 502 relative to the toothless region 111 of the gear wheel 510 both in the radial direction and in the axial direction, ie in the direction of the axis of rotation A.

The invention relates, in particular according to a fourth aspect, to a torsional vibration damper 1 having an input part 10 and an output part 2 which can counteract the spring elements 30 , 40 The effects are limitedly twisted relative to each other about the axis of rotation A. The torsional vibration damper 1 has a first shaft 450 which extends coaxially with the axis of rotation A and is connected in a rotationally fixed manner to the input part 10 and a first shaft 450 which extends coaxially with the axis of rotation A and is connected in a rotationally fixed manner with the output part 2 Second axis 451. In order to support the torsional vibration damper 1 rotatably about the rotation axis A, a first bearing 460 is provided between the first shaft 450 and the second shaft 451 , which utilize said first bearing 460 . A bearing is mounted rotatably relative to one another.

In FIGS. 19 to 21 , the above-mentioned fifth aspect of the invention is explained in particular more detail. FIG. 19 shows a torsional vibration damper 601 with an input part 602 and an output part 603 . The input part 602 and the output part 603 can be twisted relative to each other about the axis of rotation A against the action of at least one spring element 605 . This embodiment includes two spring elements 605 . The input part 602 is in this example formed in one piece with a shaft 604 which is rotatable about the axis of rotation A. Unless otherwise expressly disclosed, the terms radial, radial direction, axial, axial direction, circumferential, circumferential direction and tangential direction are always understood herein with respect to the axis of rotation A.

A cover 606 is connected in a rotationally fixed manner to the input part 602 and together with the input part 602 forms a channel 607 in which at least one spring element 605 , preferably including at least one arc-shaped compression spring, is accommodated and in which was guided. In this case, the spring element 605 rests in circumferential direction on a first side against a stop 608 of the input part 602 and on a second side opposite the first side against a stop of the output part 603 . Block 609.

The gear carrier 610 is connected to the output element 603 in a rotationally fixed manner. The gear 611 with helical teeth is connected to the gear carrier 610 in a rotationally fixed manner via bolts 612 . The gear 611 has a plurality of teeth 613 .

The output part 603 is axially supported on the input part 602 via an axial bearing 614 . The gear carrier 610 is formed at least partially radially inside the gear wheel 611 and is mounted on the shaft 604 via a radial bearing 615 which is formed radially inside the gear carrier 611 . Via the snap ring 616 , the gear carrier 610 and thus the gear 611 and the output part 603 are also fixed against displacement in the axial direction, ie in the direction of the rotation axis A.

The torsional vibration damper 601 is preferably installed as part of a starter generator, which combines the functions of a starter for the internal combustion engine with that of a vehicle generator. In this case, shaft 604 is the shaft of the starter generator. The starter generator is directly or indirectly connected to the internal combustion engine via a gear 611 with helical teeth. By using a torsional vibration damper 601 at the starter generator, very different operating situations are possible. FIG. 20 shows a first operating situation with a high applied torque for starting the internal combustion engine via gear 611 , while FIG. 21 shows a first operating situation with an applied lower torque of opposite sign in generator operation for generating electrical energy. 2. Operation status.

FIG. 20 shows the operating situation when starting the internal combustion engine. In this case, the torque is transmitted from the starter-generator shaft 604 via the input part 602, the spring element 605, the output part 603 and the gear carrier 610 to the gear wheel 611 and via this gear to another gear connected to the internal combustion engine that is in meshing engagement. On one gear. The necessary torque, the sign of which is here defined as positive in order to better distinguish it from the second operating case (Fig. 21), is significantly higher in magnitude than in the second operating case and is, for example, 100 Nm [Newton] rice].

In the described operating situation, due to the helical toothing, a first axial force 617 in the negative x-direction (see the coordinate system shown), a first radial force 618 in the negative y-direction and A first tangential force 619 directed outward from the plane of the figure. The radial bearing 615 is formed entirely in the radial direction within the gear carrier 610 and the gear wheel 611 . Therefore, the first radial force 618 and the first tangential force 619 are supported via the radial bearing 615 (see first radial reaction force 620). The first radial force 618 and the first tangential force 619 cause a tilting moment acting on the radial bearing 615 . The first axial force 617 causes a tilting moment, which is however absorbed in the axial bearing 614 since the bearing radius 621 of the axial bearing 614 relative to the axis of rotation A is greater than the force radius 622 . The generated supporting force (the first supporting force 623 on the angular coordinate showing the action of the first axial force 617 and the second supporting force 624 on the angular coordinate rotated by 180°) is positive, where the first The supporting force 623 is greater than the second supporting force 624 so that the tilting moment is absorbed and the gear carrier 610 and thus the radial bearing 615 do not tilt.

FIG. 21 shows an alternative second operating situation in which the corresponding starter-generator is operated in generator mode. In this case, torque is transmitted from the internal combustion engine via gear wheel 611 , gear carrier 610 , output part 603 , spring element 605 and input part 602 to shaft 604 of the starter generator. In this case, the torque is significantly smaller in magnitude than in the first operating case and has an opposite sign compared to the first operating case. For example, the torque is approximately 13 Nm in magnitude when the generator is running.

Thus, due to the helical toothing, a second axial force 625 directed in the positive x direction (see the coordinate system shown), a second radial force 626 directed in the negative y direction and a second radial force 626 directed in the plane of the figure are exerted on the gear 611 Second tangential force 627. The radial bearing 615 is designed in such a way that the entire gear wheel 611 is exceeded on both sides by the radial bearing 615 in the axial direction, so that the second radial force 626 and the second tangential force 627 are always over the length of the radial bearing 615 Act within, so no tilting moment can be generated. Compared to the first operating situation, the second axial force 625 is significantly smaller in magnitude than the first axial force 617 . The radial bearing radius 630 of the radial bearing 615 is smaller than the force radius 622 . Due to the opposite direction of the second axial force 625 compared to the first axial force 617 , a tilting moment is generated that is not absorbed via the axial bearing 614 . However, the small tilting moment is absorbed by the radial bearing 615 via the reaction force pair consisting of the first radial reaction force 628 and the second radial reaction force 629 , so that the radial bearing 615 can support the tilting moment.

The here proposed torsional vibration damper 601 according to a fifth aspect of the invention comprises an input part 602 and an output part 603 which can be opposed about a rotation axis A against the action of at least one spring element 605 limited twists on each other. Regarding the axis of rotation A, the input member 602 is provided on a first side of the output member 603 , and the gear carrier 610 and the gear 611 are provided on a second side opposite the first side of the output member 603 . Gear 611 has helical teeth. If a torque is transmitted from the shaft 604 via the input part 602 , at least one spring element 605 , the output part 603 , the gear carrier 610 and the gear wheel 611 , for example, to the internal combustion engine, the resulting axial force is supported on an axial bearing 614 . Because its bearing radius 621 is larger than the force radius 622 of the gear 611, no tilting moment is generated because the corresponding axial reaction forces 623, 624 are larger than the corresponding axial force 617.

A sixth aspect of the invention, which may be combined with the first to fifth aspects, is particularly illustrated in FIG. 22 . FIG. 22 shows very schematically a starter-generator 631 with a shaft 604 which is connected on the one hand to a starter-generator base part 632 including the remaining components of the starter-generator 631 and on the other hand to the starter-generator 631 as described above. The input member 602 of the torsional vibration damper 1, 601 is connected.

List of reference signs

1 torsional vibration absorber

2 output parts

3 Leave blank

4 First channel area

5 Second channel area

6 first stop

7 first stop surface

8 second stopper

9 first stop surface

10 input parts

11 First channel area

12 Second channel area

13 first stopper

15 Second stopper

16 Leave blank

17 First stop surface

18 Second stop surface

20 wing flange

21 Wing flange body

22 wings

23 Stop

24 Leave blank

30 First spring element

31 first end

32 second end

40 Second spring element

41 first end

42 Second end

50 axis

51 central hole

52 The outer ring surface of the shaft

53 First supply hole

54 Second supply hole

55 Third supply hole

56 Another flange section

57 additional holes

58 rivets

60 sliding bearing

61 rolling bearings

62 rolling bearings

63 friction bearings

70 snap ring

71 sleeve

80 gears

81 bolt connection mechanism

82 middle part

90 covers

91 Leave blank

92 Second stopper

100 Cylindrical section of the output part

101 Cylindrical section of cover

102 channels

110 friction surface

111 toothless area

120 clearance

130 oil drain hole

250 spring set

251 outer spring

252 inner spring

351 bearing seat

352 bearing seat

370 nut

450 first axis

451 Second axis

452 longitudinal hole

453 flange section

454 bolt connection mechanism

455 holes

460 first bearing

461 Second Bearing

463 Third bearing

470 First rolling bearing

471 First bearing seat

480 Second rolling bearing

481 Second bearing seat

502 Another cylindrical section of the cover

510 gear

520 channels

601 torsional vibration absorber

602 Input widget

603 output part

604 axis

605 spring element

606 cover

607 channel

608 Stop

609 Stop

610 gear rack

611 gear

612 bolts

613 teeth

614 Axial Bearing

615 radial bearing

616 snap ring

617 First axial force

618 First radial force

619 First tangential force

620 First radial reaction force

621 Bearing Radius

622 force radius

623 The first support force

624 Second Support Force

625 Second axial force

626 Second radial force

627 Second tangential force

628 First radial reaction force

629 Second radial reaction force

630 radial bearing radius

631 starter generator

632 Basic components of starter generator

A axis of rotation

Claims (8)

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 mounted so as to be rotationally limited relative to each other about the axis of rotation (A) of the torsional vibration damper (1) against the action of the spring element (30, 40), The output part (2) has a radial extension relative to the axis of rotation (A) and is formed circumferentially and coaxially with the axis of rotation (A) towards the spring element (30, 40 ) oriented cylindrical section (100); a cover (90) extending radially outwards relative to the axis of rotation (A), said cover having on the circumferential side complementary to the cylindrical section (100) has an adapted shape and is connected in a rotationally fixed manner to the cylindrical section (100) of the output part (2), wherein the output part (2) and the cover (90) are formed between them relative to the a channel (102) surrounding the axis of rotation (A), wherein the channel (102) at least partially surrounds the spring element (30) not only in the radial direction but also in the axial direction with respect to the axis of rotation (A), 40), wherein the channel (102) forms a friction surface (110) for the spring element (30, 40) extending coaxially with the axis of rotation (A), wherein the output part (2) and/or the cover (90) has an oil drain hole (130) in the region of the section (140, 141) extending in the radial direction towards the rotation axis (A), It is characterized in that the oil drain hole (130) is formed radially inside the friction surface (110). 2. The torsional vibration damper according to claim 1, wherein at least a first spring element (30) and a second spring element (40) are formed, wherein the second spring element (40) is relative to the The first spring element (30) is designed to be shortened. 3. Torsional vibration damper (1) according to any one of the preceding claims, 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) resist the action of the spring element (30, 40) about the rotation axis (A) of the torsional vibration damper (1) relative to a shaft (50) extending coaxially with the axis of rotation (A), wherein the output part (2) or the input part (10) and the shaft (50) connected in a rotationally fixed manner, wherein the shaft (50) is mounted rotatably about the axis of rotation (A) and in the direction of the axis of rotation (A) by the input part (10) A first rolling bearing (61) is provided upstream of the device formed by the output part (2), and a second rolling bearing (62) is provided downstream of the device formed by the input part (10) and the output part (2). ). 4. Torsional vibration damper (1) according to claim 3, characterized in that the shaft (50) is in one piece with the output part (2) or the input part (10). 5. Torsional vibration damper (1) according to claim 3, characterized in that the shaft (50) and the output part (2) and/or the input part (10) are multi-piece of. 6. Torsional vibration damper (1) according to any one of the preceding claims, 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) resist the action of the spring element (30, 40) about the rotation axis (A) of the torsional vibration damper (1) relative to A first shaft (450) extending coaxially with the axis of rotation (A) and connected in a rotationally fixed manner with the input part (10) and a first shaft (450) with the axis of rotation (A) A second shaft (451) extending coaxially and connected to the output part (2) in a rotationally fixed manner, wherein at least one shaft (451) is arranged between the first shaft (450) and the second shaft (451) A first bearing (460) by means of which the first shaft (450) and the second shaft (451) are rotatably supported relative to each other. 7. The torsional vibration damper (1, 601) according to any one of the preceding claims, comprising: an input part (10, 602), an output part (2, 603) and at least A spring element (30, 40, 605), wherein the input part (10, 602) and the output part (2, 603) are capable of resisting the action of said at least one spring element (30, 40, 605) about the axis of rotation (A) limited rotation relative to each other, wherein the gear carrier (10) together with the gear wheel (611) with helical teeth is connected to the output part (2, 603) in a rotationally fixed manner, wherein the gear wheel (611) and the input part (10, 602) is formed on the opposite side of the output part (2, 603), characterized in that an axial bearing (614) for the output part (2, 603) is located on the input part (10, 602) is formed at a bearing radius (621) with respect to the rotation axis (A), and the bearing radius (621) is greater than the force radius (622) of the gear (611), wherein the force The radius (622) is the radius at which forces are transmitted between the gear wheel (611) and another gear wheel, in which a radial bearing (615) is formed, which is formed in the gear wheel. radially inside the frame (610). 8. A starter generator (631) comprising a torsional vibration damper (1, 601) according to any one of the preceding claims.