Flywheel having a rotational axis for an internal combustion engine

Abstract

The invention relates to a flywheel (1), comprising at least the following components: - a mass disc (4) for connecting to a combustion engine shaft (5); - a central connector (6) for connecting to a transmission input shaft (7); - a torque limiter (8), comprising a first plate spring (9), at least one friction pair (10) which is pressed axially by means of the first plate spring (9); - a friction unit (14), comprising a second plate spring (15), a first friction ring (16), a second friction ring (17) and a mating disc (18) which is rotatable relative to the second plate spring (15); and - a torsional vibration damper (19), comprising at least one energy store element (20), at least one flange (21) and at least one input disc (22, 23) which is fixed rotationally to the mass disc (4), wherein the at least one friction pair (10) of the torque limiter (8) comprises a friction lining (12), a friction disc (13) and a driver plate (11), wherein the friction pair (10) is arranged between the flange (21) of the torsional vibration damper (19) and the central connector (6). The flywheel (1) is, above all, characterized in that the friction rings (16, 17) of the friction unit (14) are arranged radially within the at least one energy store element (20) of the torsional vibration damper (19). The flywheel proposed herein is compact, wherein the friction unit is at the same time protected satisfactorily against an input of heat originating from the torque limiter.

Description

[0001] Flywheel with a rotational axis for an internal combustion engine

[0002] The invention relates to a flywheel comprising at least the following components:

[0003] - a ground plate for connecting to a combustion shaft;

[0004] - a central connection for connecting to a gearbox input shaft;

[0005] - a torque limiter comprising a first disc spring, at least one friction pair which is axially compressed by means of the first disc spring;

[0006] - a friction device comprising a second disc spring, a first friction ring, a second friction ring and a counter-disk rotatable relative to the second disc spring; and

[0007] - a torsional vibration damper comprising at least one energy storage element, at least one flange, and at least one input disk rotationally fixed to the mass disk, wherein the at least one friction pair of the torque limiter comprises a friction lining, a friction disk, and a drive disk, wherein the friction pair is arranged between the flange of the torsional vibration damper and the central connection. The flywheel is characterized primarily by the fact that the friction rings of the friction device are arranged radially within the at least one energy storage element of the torsional vibration damper.

[0008] The invention further relates to a drive train with such a flywheel for a motor vehicle, as well as a motor vehicle with such a drive train.

[0009] Flywheels are known for use with internal combustion engines, particularly crankshafts, to compensate for intrinsic rotational irregularities using their inertial mass. Torsional vibration dampers are also known for this purpose, isolating the remaining torque jolts, for example, dual-mass flywheels or compression spring dampers. A friction device, also known as a hysteresis element, is usually used to dampen vibrations in such a torsional vibration damper. For some applications, particularly in a hybridized powertrain with an electric drive motor integrated into the torque flow, a torque limiter is necessary to prevent excessive torque from being transmitted.

[0010] It is a constant challenge to meet the tight installation space requirements while simultaneously offering a cost-effective component. Various concepts are known for this, with a particularly promising approach being a coherent kit in which all of the above-mentioned functions are integrated and can be pre-assembled for use in the drivetrain production line. However, this can result in inadequate damping characteristics due to insufficient installation space for the flywheel's inertial mass.

[0011] Based on this, the present invention is based on the object of at least partially overcoming the disadvantages known from the prior art. The features of the invention are derived from the independent claims, for which advantageous embodiments are presented in the dependent claims. The features of the claims can be combined in any technically reasonable manner, whereby the explanations from the following description as well as features from the figures, which comprise additional embodiments of the invention, can also be consulted for this purpose.

[0012] The invention relates to a flywheel with a rotational axis for an internal combustion engine, comprising at least the following components:

[0013] - a ground plate for connecting to a combustion shaft;

[0014] - a central connection for connecting to a gearbox input shaft;

[0015] - a torque limiter comprising a first disc spring, at least one friction pair which is axially compressed by means of the first disc spring;

[0016] - a friction device comprising a second disc spring, a first friction ring, a second friction ring and a counter-disk rotatable relative to the second disc spring; and

[0017] - a torsional vibration damper comprising at least one energy storage element, at least one flange and at least one input disk rotationally fixed to the mass disk, wherein the at least one friction pair of the torque limiter comprises a friction lining, a friction disk and a drive disk, wherein the friction pair is arranged between the flange of the torsional vibration damper and the central connection.

[0018] The flywheel is primarily characterized in that the friction rings of the friction device are arranged radially inside the at least one energy storage element of the torsional vibration damper.

[0019] In the following, reference is made to the specified axis of rotation whenever, without explicit indication to the contrary, the axial direction, radial direction, or the direction of rotation and corresponding terms are used. Ordinal numbers used in the preceding and following descriptions serve only to clearly distinguish them and do not reflect the order or ranking of the designated components. An ordinal number greater than one does not necessarily imply that another such component must be present.

[0020] The flywheel proposed here is preferably designed as a pre-assembled modular system which can be used in a production line in a drive train and / or can be connected, for example screwed, to a combustion shaft (e.g. crankshaft) of an internal combustion engine.

[0021] The mass disc represents the largest mass portion of the flywheel and can be connected (preferably directly) to a combustion engine shaft in a torque-resistant manner, for example by means of an engine connection screw connection formed by a central screw or a plurality of screws arranged in a ring.

[0022] The mass disc is preferably a (particularly preferably single) sheet metal element formed by (preferably cold) forming. For example, a fold is formed on the outer circumference so that a mass concentration is formed there. The sheet metal element preferably has a very high sheet thickness, for example

[0023] 4 mm [four millimeters] to 15 mm, preferably 8 mm to 12 mm.

[0024] The central connection is designed for a torque-resistant connection to a transmission input shaft and / or a rotor shaft. In one embodiment, the central connection comprises a spline, preferably such that a complementarily toothed shaft can be inserted into this spline. Alternatively, the spline can be inserted into a complementary spline. Alternatively or additionally, a screw connection or other connection is formed in the insert.

[0025] Entering via the mass plate, a torque (referred to as tensile torque in a motor vehicle) is transmitted in a uniform, damped and limited manner to the central connection for (usually indirect) delivery to a consumer, and conversely, from the central connection to the mass plate (referred to as shear torque in a motor vehicle), i.e. coming from a consumer.

[0026] The torsional vibration damper is designed as a flange damper, in which the at least one input disk is spring-mounted (and damped) to at least one flange via at least one energy storage element. The at least one flange and the at least one input disk are rotatable relative to one another about the rotation axis up to a predetermined stop angle (e.g., defined by an angle limiter) against a force of the at least one energy storage element. This, usually in conjunction with a (damping) friction effect, delays the transmission of a torque change, thus achieving a more uniform torque transmission. An (almost) static torque transmission is not impaired (in terms of technical relevance) by such a torsional vibration damper.

[0027] The at least one energy storage element is, for example, a helical compression spring, preferably with a straight spring axis, with particularly preferably three, four, or five (but also up to ten) helical compression springs distributed over the circumference. In one embodiment, at least one additional inner spring is provided, for example, to amplify the spring forces and / or to stagger an increase in a spring force coaxially to the spring axis of the respective helical compression spring.

[0028] In a preferred embodiment, one of the input discs is formed integrally with the ground disc. Alternatively, the input disc in question is connected to the ground disc, for example, riveted or welded.

[0029] The torque limiter is designed to interrupt torque transmission in the event of an overload torque. Similar to a friction clutch, the friction pair(s) here comprise at least one friction lining (usually a pair of friction linings) and one friction disc, as well as, if necessary, a separate contact plate and counterplate, which are permanently pressed together by means of a disc spring (referred to here as the first). This defines a maximum transmittable torque (the slipping torque), which can be calculated with sufficiently good approximation from the product of the mean radius and the contact pressure of the (first) disc spring for a friction pair multiplied by the respective friction coefficient (determined by the material pairing), and in turn from the sum of all friction pairs or multiplied by the number of (identical) friction pairs.

[0030] It should be noted that in this technical field, the term "disc spring" is used as a generic term for ring-like spring elements with an inclination relative to the radius. Such a disc spring is, in one embodiment, a diaphragm spring or is composed of individual spring elements that are joined together or installed separately. In one embodiment, a disc spring has tongues on the outer circumference and / or the inner circumference.

[0031] In one embodiment, the friction disc is rotationally fixed to the at least one flange of the torsional vibration damper, and the drive plate is correspondingly rotationally fixed to the central connection. Alternatively, conversely, the drive plate is rotationally fixed to the at least one flange of the torsional vibration damper, and the friction disc is correspondingly rotationally fixed to the central connection.

[0032] In one embodiment, the respective friction lining is fixedly connected to the drive plate or to a pressure plate that is rotationally fixed thereto and axially movable, and rubs against the friction plate in the event of an overload. The drive plate simultaneously forms the counterplate for the axial compression force of the first disc spring. In one embodiment, the respective friction lining is free and, in the event of an overload, rubs against the friction disc and / or the drive plate (or pressure plate). In one embodiment, a friction lining is fixedly connected to the friction disc and, in the event of an overload, rubs against the drive plate (or counterplate and / or pressure plate).

[0033] The friction device (or hysteresis element) is designed to maintain minimal friction between the input and output of the torsional vibration damper, thus achieving defined vibration damping. Its disc spring (referred to here as the second disc spring) is designed to maintain a defined axial contact force, for which purpose the second disc spring is axially supported relative to the mass plate, the flange of the torsional vibration damper, or the central connection. The first friction ring is axially supported on the second disc spring, preferably rotationally fixed to it (e.g., suspended therein or frictionally connected).The second friction ring is arranged axially opposite the first friction ring and is axially supported on the or one of the respectively opposite and rotationally fixed component(s) or component(s) which co-rotate on the torque limiter outside of a slipping process, preferably rotationally fixed thereto (for example, suspended and / or glued).

[0034] In one embodiment, the second disc spring is axially supported on the first input disk and rotationally fixed thereto, and the second friction ring is axially pressed between the second input disk and a connection-side component of the torque limiter (for example the first disc spring) and rotationally fixed, for example, to the second input disk. In one embodiment, the second disc spring is axially supported on the second input disk and rotationally fixed to it (preferably at) and the second friction ring is axially pressed between the first input disk and the flange and rotationally fixed, for example, to (preferably at) the flange. In one embodiment, the second disc spring is axially supported on the central connection and rotationally fixed, and the second friction ring is axially pressed between the first input disk and the counter disk.

[0035] In one embodiment, the counter disc is rotationally fixed to the central connection. In one embodiment, the counter disc is rotationally fixed to the at least one flange of the torsional vibration damper or is formed integrally therewith. In one embodiment, the counter disc is formed by the (first) disc spring of the torque limiter.

[0036] It should be noted that in one embodiment, the friction rings of the friction device are rotationally fixed to the second disc spring or to the counter-disk. Alternatively, the friction rings are free and, upon relative rotation, rub against the antagonists of the friction device with the second disc spring and / or the second input disc.

[0037] Here, it is proposed that the two antagonistic friction rings of the friction device be arranged radially within the at least one energy storage element. This enables the at least one energy storage element of the torsional vibration damper to be arranged at a smaller effective radius to the axis of rotation compared to previously known concepts. This reduces the load on the respective spring guide. Furthermore, due to the reduced outer diameter of the torsional vibration damper, more space is available radially outward for the mass plate of the flywheel. This makes it possible to provide a possibly high required moment of inertia for an internal combustion engine in a small installation space. This effect is further enhanced if not only the friction rings, but also the second disc spring of the friction device is arranged radially within the at least one energy storage element.In an advantageous embodiment, the two opposing friction rings of the friction device are arranged in the area of ​​or within the torque limiter, rather than radially between the energy storage element and the torque limiter. This allows the energy storage element to be arranged radially directly adjacent to the torque limiter, thus saving radial installation space.

[0038] In a preferred embodiment, at least one, preferably both, of the friction rings are axially supported on a component of the torque limiter which, in the event of slipping, is not in direct frictional contact with the friction lining. For example, the friction lining is rotationally driven by the drive plate or the antagonistic pressure plate. Thus, the respective friction ring is thermally better insulated from heat input into the component slipping relative to the at least one friction lining (e.g., the friction disc) by means of the respective friction lining than in the case of direct contact with the (usually metallic) slipping component, because such a friction lining (e.g., made of an organic or ceramic material) is usually a significantly poorer heat conductor.

[0039] It is further proposed in an advantageous embodiment of the flywheel that the torsional vibration damper has a second input disc axially opposite the first input disc with respect to the at least one flange, wherein the second input disc is preferably supported radially on the central connection and / or axially on the torque limiter, particularly preferably on its first disc spring.

[0040] For good housing or (frictional) guidance of an energy storage element, it is advantageous if a second input disk is provided. This second input disk is fixed to the first input disk, for example, by means of a stepped bolt or spacer bolt. This bolt preferably also serves as the stop for the maximum relative angle of rotation (angle limiter) of at least one flange of the torsional vibration damper. In an energy storage element as a helical compression spring, for example, a so-called spring window is formed in the first input disk (or mass disk) and in the second input disk, into which window the helical compression spring inserts or penetrates, axially overlapping the respective disk.

[0041] In an embodiment of the mass disk with increased material accumulation (for example fold of a sheet metal element) on its outer circumference, the second input disk is preferably arranged in axial overlap with, particularly preferably axially within (i.e. towards the section with radial extension of the mass disk), the axial extent of this material accumulation.

[0042] In an advantageous embodiment, the second input disk is supported (relatively rotatably) radially, preferably by means of a friction sleeve, on the central connection. The central connection preferably has a section with a radial extension, with the second input disk being supported radially on the outer circumference of this section. Alternatively, the second input disk is supported on a section of the central connection with an axial extension.

[0043] In an advantageous embodiment, the second input disc is axially supported (relatively rotatable), preferably by means of a friction sleeve (preferably the same as used for radial support), namely on the torque limiter, preferably its (first) disc spring.

[0044] It is further proposed in an advantageous embodiment of the flywheel that the second disc spring of the friction device is suspended in the second input disc, is rotatably fixed and is axially supported thereon, wherein preferably the second friction ring of the friction device is arranged axially between the first input disc and the flange of the torsional vibration damper.

[0045] In this embodiment, the second disc spring is not axially supported on the first input disc (or mass disc), but rather in the second input disc of the flywheel, i.e., axially opposite the mass disc. In one embodiment, the suspension of the second disc spring is arranged radially overlapping the at least one energy storage element. Alternatively, the suspension of the second disc spring is arranged radially inside the at least one energy storage element.

[0046] In an advantageous embodiment, it is proposed that the second friction ring (antagonistic to the second disc spring) is arranged axially between the first input disk and the flange. The second friction ring is axially pressed between them by means of the second disc spring. The flange preferably comprises two partial flanges, one of which is guided axially close to the first input disk, such that a narrow axial gap is filled (or stressed) by the second friction ring. The other partial flange is then preferably guided opposite, axially close to the second input disk, such that a somewhat wider axial gap is filled (or stressed) by the second disc spring and the first friction ring.

[0047] It is further proposed in an advantageous embodiment of the flywheel that the second disc spring is axially supported on the mass disc and is rotationally fixed to the mass disc, preferably by means of an opening in the mass disc.

[0048] In this alternative embodiment, the second disc spring of the friction device is supported on the mass disc as an abutment for the axial preload force on the first friction ring. The mass disc usually extends far radially inward, allowing the first friction ring to be arranged at a large (or thermally well-insulated) distance from the component into which the majority of the frictional heat is introduced when the torque limiter slips, for example, the friction disc of the torque limiter. In one embodiment, an even more radially compact design is possible by forming a radial overlap with the torque limiter.

[0049] In one embodiment, the second disc spring of the friction device is rotationally fixed to the mass disk, for example, suspended therein (for example, an opening) or in the screw heads of a motor connection screw connection and / or a tab of a cover disk fixed by the motor connection screw connection. In this embodiment, the first friction ring is preferably arranged radially within the motor connection screw connection. The antagonistic second friction ring is, for example, fastened to the second input disk, for example as part of a friction sleeve, which is also designed to axially support the second input disk on the central connection.

[0050] It should be noted that in one embodiment, the first friction ring is arranged adjacent to the mass disc or to the second input disc and the second disc spring is rotationally fixed to the connection side.

[0051] It is further proposed in an advantageous embodiment of the flywheel that the drive plate of the torque limiter and the counter plate of the friction device are formed in one piece.

[0052] For simple assembly and / or cost-effective construction, it is advantageous to form the drive plate and the counter plate in one piece, preferably from a single sheet metal element, particularly preferably (preferably cold-) formed. This component is rotationally fixed to the central connection, for example, riveted. In one embodiment, an annular recess for the screw heads of a motor connection screw connection is formed at the connection to the central connection, thus achieving a particularly narrow axial design.

[0053] It is further proposed in an advantageous embodiment of the flywheel that the first friction ring or the second friction ring of the friction device is pressed axially against the first disc spring.

[0054] In one embodiment, the first disc spring of the torque limiter is used as a counterbearing for the first friction ring, which is axially pressed against it by the second disc spring, or for the antagonistic second friction ring of the friction device. The first disc spring is (at least in this embodiment) rotationally fixed with sufficiently precise approximation to at least one flange of the torsional vibration damper. Due to the radial overlap of the second disc spring with the torque limiter, a particularly compact radial design can be achieved.

[0055] In one embodiment (with the first disc spring of the torque limiter on the side of the first input disc), the first friction ring or the second disc spring is axially supported on the first input disc, and the antagonistic second friction ring is axially supported on the second input disc. Alternatively, this is reversed, and the first disc spring of the torque limiter is arranged on the axially opposite side (the second input disc) compared to the aforementioned embodiment.

[0056] It is further proposed in an advantageous embodiment of the flywheel that the drive plate of the torque limiter forms an axial force clamp for the first disc spring, the at least one friction lining and the at least one friction disc.

[0057] The axial force clamp ensures that the axial compression of the first disc spring, which sets the desired slipping torque, does not have to be transmitted to the surrounding components and assemblies. Thus, at least all axially compressed components of the torque limiter are arranged axially within the force clamp.

[0058] In one embodiment, this axial force clamp is formed by the drive plate (and preferably also the counter plate) and the central connection. The friction plate is then rotationally fixed to (preferably directly to) the at least one flange of the torsional vibration damper. In one embodiment, this axial force clamp is formed by the at least one flange (and also the drive plate, and preferably the counter plate, of the torque limiter) of the torsional vibration damper. The friction plate of the torque limiter is then rotationally fixed to (preferably directly to) the central connection.

[0059] It is further proposed in an advantageous embodiment of the flywheel that the flange of the torsional vibration damper comprises a first partial flange and a second partial flange, wherein preferably a first contact surface for one of the energy storage elements and / or a second contact surface for an angle limiter of the at least one input disk is formed exclusively by the first partial flange.

[0060] Here, it is proposed that the flange of the torsional vibration damper is divided into a first partial flange and a second partial flange, which are rotationally fixed to each other, for example riveted or welded.

[0061] For example, the partial flanges are designed as (preferably cold-) formed sheet metal elements. This allows, for example, an axial force clamp for the torque limiter, preferably with a one-piece drive plate, to be formed.

[0062] For simple and reliable assembly and / or more cost-effective production, it is advantageous for only one of the two partial flanges to form the (closely) toleranced surfaces for the first contact surface and / or the second contact surface. For the first contact surface, for example, a window in the second partial flange is larger than in the first partial flange. For the second contact surface, for example, the second partial flange is radially shorter.

[0063] It should be noted that the angle limiter is a tab and / or a connecting plate and / or a stepped bolt which is rotationally fixed to the first input disc.

[0064] According to a further aspect, a drive train for a motor vehicle is proposed, comprising at least the following components:

[0065] - an internal combustion engine as a torque source for providing torque via its combustion shaft;

[0066] - at least one consumer for converting at least part of a torque provided by at least one of the torque sources; and

[0067] - a transmission for transmitting at least part of a torque provided by the torque sources to the consumer, wherein at least one flywheel according to an embodiment according to the above description is arranged between the combustion shaft and the at least one consumer, wherein preferably an electric drive machine with a rotor shaft is provided as a further torque source and the flywheel is arranged interposed between the combustion shaft and the rotor shaft.

[0068] When multiple drive motors are used (preferably all usable as a torque source for a single consumer), they must be synchronized with each other or decoupled. The latter is generally not implemented in current applications due to the cost of a separating clutch and the rapid controllability of electric drive motors. In a hybrid powertrain with one of the drive motors designed as an internal combustion engine, torsional vibration damping is necessary due to the rotational irregularities inherent in an internal combustion engine due to the ignition timing, or can be adjusted even more effectively than in pure combustion operation. At the same time, there is often even less installation space available.

[0069] The transmission comprises at least one gear pair, preferably exclusively spur gear teeth, the tooth flanks of which are prevented from lifting off from one another by means of the at least one damper shaft in a low-load operating state, or at least from hitting one another again at a reduced speed (namely damped), so that noise emission is prevented or at least significantly reduced.

[0070] According to a further aspect, a motor vehicle is proposed, comprising at least one drive wheel and a drive train according to an embodiment according to the above description, wherein a torque can be delivered from the at least one drive motor of the drive train to the at least one drive wheel for propelling the motor vehicle.

[0071] The motor vehicle is, for example, a passenger car, a truck, or a motorized two-wheeler. The motor vehicle has a drivetrain according to one embodiment as described above. The torque output by the at least one drive motor (forming the torque source) is transmitted via the transmission to the at least one drive wheel (consumer). The transmission referred to here comprises, in one embodiment, a switchable transmission. In one embodiment, the transmission comprises a differential.

[0072] The motor vehicle proposed here comprises a drive train with at least one flywheel, which is particularly compact and / or particularly effective and at the same time is cost-effective and easy to manufacture.

[0073] The invention described above is explained in detail below against the relevant technical background with reference to the accompanying drawings, which show preferred embodiments. The invention is in no way limited by the purely schematic drawings, whereby it should be noted that the drawings are not to scale and are not suitable for defining proportions. It is shown in

[0074] Fig. 1 : a flywheel in a first embodiment;

[0075] Fig. 2: a flywheel in a second embodiment;

[0076] Fig. 3: a flywheel in a third embodiment; and

[0077] Fig. 4: a motor vehicle with a drive train.

[0078] Fig. 1 shows a flywheel 1 in a first embodiment in a schematic diagram in half section. The rotational axis 2 is shown here on the right and running vertically. A combustion shaft 5 (see Fig. 4) can be connected at the bottom by means of the engine connection screw 38 (here a ring-like arrangement of screws) and at the top by means of a spline via the central connection 6 to a transmission input shaft 7 or rotor shaft 37 (see Fig. 4) for a damped and limited torque transmission.

[0079] The mass disk 4, which gives the flywheel 1 its name, is a thick sheet metal element with a fold on its outer circumference, forming a mass accumulation there. An additional mass 47 (preferably designed as a circumferential ring) is provided purely optionally (therefore shown in dashed lines), which still finds space due to the radially compact design of the other functional components of the flywheel 1. Alternatively, the fold (or another mass accumulation) can be displaced radially further inward (to the right as shown).

[0080] The functional unit of the torsional vibration damper 19 is directly connected to the mass plate 4, of which the (first) input plate 22 is also formed in one piece. Axially opposite, a second input plate 23 is arranged, which is axially and rotationally fixed to the mass plate 4 by means of a spacer bolt 46 (or stepped bolt). An energy storage element 20 for exerting a spring force in the circumferential direction is supported on the mass plate 4 and the second input plate 23. The energy storage element 20 is designed here as a helical compression spring, for example, with a straight spring axis. The helical compression spring is arranged so as to be axially immersed (i.e., overlapping) with the mass plate 4 and the second input plate 23, for which purpose a spring window 45 is formed in each case.In one embodiment, a friction system is formed between the helical compression spring and the spring window 45 in the region of its outer peripheral side for guidance and, if necessary, for damping. (Relative to a tensile torque when used in a motor vehicle 31), the mass plate 4 is arranged on the input side. On the output side, a flange 21 is shown, which is supported opposite (for the respective torque direction) on the energy storage element 20. It should be noted that both a tensile torque and a thrust torque (damped and limited) can be transmitted by means of this flywheel 1.

[0081] The functional unit of the torque limiter 8 is arranged in the torque flow, starting from the engine connection screw connection 38, behind the functional unit of the torsional vibration damper 19. This comprises two friction pairs 10, each formed by a friction lining 12 and a friction disc 13 arranged axially between the two friction linings 12. The friction disc 13 is also formed integrally with the flange 21 of the torsional vibration damper 19. The drive plate 11 of the torque limiter 8 is formed by a separate (purely optionally sheet metal) component and is connected to the central connection 6, here purely optionally riveted. In the embodiment shown, the (lower) friction lining 12 is again purely optionally riveted to the drive plate 11 (here also the counter plate 49) in a rotationally fixed manner, so that in the event of an overload torque, the friction lining 12 is rotated relative to the friction disc 13.The opposite friction lining 12 is similarly rotationally fixed by a pressure plate 42 (also referred to as a support plate). The pressure plate 42 is suspended radially on the inside of the drive plate 11 and is thus rotationally fixed to it, but mounted so as to be axially displaceable. The two friction pairs 10 are axially pressed together by means of a (first) disc spring 9, whereby here (purely optionally) the first disc spring 9 is supported on the central connection 6. In this embodiment, an axial force clamp is formed by the drive plate 11 (counter plate 49) and the central connection 6. The first disc spring 9 therefore presses the friction linings 12 axially against the friction plate 13, so that a defined friction torque for a desired slipping torque is set for it via the spring characteristic curve of the first disc spring 9 and the axial installation height.

[0082] The functional unit of the friction device 14 (or the hysteresis element) is provided in the torque flow, connected in parallel to the functional units of the torsional vibration damper 19 and the torque limiter 8. It should be noted that the design of the friction device 14 can be selected largely independently of the configuration of the torsional vibration damper 19 and / or the torque limiter 8, for example, as shown in Fig. 2 or Fig. 3 explained below.

[0083] The friction device 14 comprises (in this axial order starting from the mass disk 4) a (second) disc spring 15, a first friction ring 16, a second friction ring 17, and a counter disk 18. The second disc spring 15 is here attached by means of its suspension tongues 43 via the screw heads of the motor connection screw connection 38 and / or via recesses in a cover disk 44, which is rotationally fixed by the motor connection screw connection 38 to the mass disk 4 (or to the first input disk 22). The axially opposite counter disk 18 is axially and rotationally fixed to the central connection 6. Here, purely optionally, the counter plate 18 is formed in one piece with the drive plate 11 (counter plate 49), wherein an annular recess 50 for the screw heads of the motor connection screw connection 38 is formed between these two functional areas and at the same time the connection (here riveting) to the central connection 6 is formed in this recess 50.From the second disc spring 15, the first friction ring 16 is pressed directly against the counter disk 18 and indirectly via the friction pairs 10 of the torque limiter 8, the first disc spring 9 is pressed axially against the second friction ring 17 and this in turn against the second input disk 23, so that a defined friction torque for a desired hysteresis behavior is set here via the spring characteristic curve of the second disc spring 15 and the axial installation height for this.

[0084] In this (first) embodiment, a friction sleeve 48 is also provided purely optionally (largely independent of the design of the functional units), by means of which the second input disc 23 of the torsional vibration damper 19 is supported radially (here at the radial extension of the central connection 6) so that it can rotate relative to the output side. This friction sleeve 48 also (purely optionally) forms the second friction ring 17, and is thus supported axially and rotatably relative to the output side on the rear side of the first disc spring 9 of the torque limiter 8.

[0085] Fig. 2 shows a flywheel 1 in a second embodiment in a schematic diagram in half section. The rotation axis 2 is also shown here running to the right and vertically. For the sake of clarity, the illustration is largely identical to the first embodiment shown in Fig. 1. Reference is made to the previous description without excluding generality, and only the differences are discussed here.

[0086] The torque limiter 8 is constructed in reverse here compared to the first embodiment shown in Fig. 1. Therefore, the friction disc 13 is arranged on the output side and the drive plate 11 (as well as the pressure plate 42 and first disc spring 9) is arranged on the input side, i.e., it is rotationally fixed to the flange 21 of the torsional vibration damper 19. Not as a mandatory feature, but advantageously, the flange 21 is designed with a first partial flange 25 and a second partial flange 26, which form an axial force clamp for the torque limiter 8.

[0087] The first disc spring 9 is thus axially supported on the second partial flange 26, and (as a preferred embodiment) the pressure plate 42 is suspended in the second partial flange 26. The drive plate 11 (counter plate 49) is formed by the first partial flange 25. The friction disc 13 is axially and rotationally fixed to the central connection 6. Here (purely optionally), the aforementioned components of the torque limiter 8 are designed as formed sheet metal elements.

[0088] Here, the second disc spring 15 of the friction device 14 is suspended directly into an opening 24 of the mass disk 4. The counter disk 18 is formed here (purely optionally) at the rear by the first disc spring 9 of the torque limiter 8. Alternatively, for example, the second partial flange 26 is formed to extend radially further inward, or a separate element is provided, for example, rotationally fixed to the central connection 6. In contrast to the embodiment of the friction device 14 according to the first embodiment shown in Fig. 1, here the torque limiter 8 is connected downstream of the friction device 14 in the torque flow, i.e. the friction device 14 is connected exclusively in parallel with the torsional vibration damper 19.

[0089] Here, too, a friction sleeve 48 is provided on the second input disk 23, which is again supported radially on the central connection 6 and also (comprising the second friction ring 17) axially on the torque limiter 8. However, the friction sleeve 48 is supported axially on the drive disk 11 and at the same time on the first partial flange 25, i.e. on the flange 21 of the torsional vibration damper 19. Alternatively, the second input disk 23 is axially supported, for example, on the friction disk 13 or directly on the radial extension of the central connection 6.

[0090] Fig. 3 shows a flywheel 1 in a third embodiment in a schematic diagram in half section. The rotation axis 2 is also shown here running to the right and vertically. For the sake of clarity, the illustration is largely identical to the first and second embodiments shown in Fig. 1 and Fig. 2, respectively. Reference is made to the previous description without excluding generality, and only the differences are discussed here.

[0091] The torque limiter 8 is functionally identical to the second embodiment according to Fig. 2. However, due to the arrangement of the friction device 14 on the axially opposite side to the mass disk 4, an axial support is formed by means of a friction sleeve 48, wherein for this purpose the second partial flange 26 is formed extending radially further inward.

[0092] The friction device 14 is here suspended in the second input disc 23 and the counter disc 18 is also enclosed here by the torque limiter 8 and the flange 21 of the torsional vibration damper 19, namely formed at the rear by the first partial flange 25.

[0093] In this embodiment, the two partial flanges 25, 26 of the flange 21 of the torsional vibration damper 19 are designed with different (in this case, sheet metal) thicknesses (largely independent of the embodiments of the functional units). It is advisable here for the first contact surface 27 for the energy storage element 20 and / or the second contact surface 28 for limiting a maximum relative angle of rotation of the flange 21 to the first input disk 22 via the spacer bolt 46 (functioning as an angle limiter 29) to be formed exclusively by the first partial flange 25. In one embodiment, the second partial flange 26 is radially shorter and does not extend to the spacer bolt 46, so that no second contact surface 28 is formed by the second partial flange 26.In one embodiment, a window for the energy storage element 20 is formed in the second partial flange 26 that is larger than the first partial flange 25, so that no first contact surface 27 is formed by the second partial flange 26. It should be noted that this can also be carried out for partial flanges 25, 26 of the same thickness (as shown, for example, in the second embodiment according to Fig. 2). This simplifies assembly and reduces manufacturing costs. Fig. 4 shows a schematic plan view of a motor vehicle 31 with a drive train 30. The motor vehicle 31 has a longitudinal axis 40 and an engine axis 41, wherein the engine axis 41 is arranged (purely optionally) transversely in front of the driver's cab 39 here.The drive train 30 comprises, as a torque source 32, a first drive machine 3, which is preferably designed as an internal combustion engine 3, with a first machine shaft 5 (then, for example, the combustion shaft 5), a second (preferably electric) drive machine 36 (for example, designed as a so-called hybrid module) with a rotor shaft 37, and a transmission 35 (here, for example, a belt transmission [CVT: continuous variable transmission]). Often, a further (usually electric) drive machine is also integrated into the drive train 30, for example, coaxially with the combustion shaft 5 or parallel to it.

[0094] In one embodiment according to the preceding description, the combustion shaft 5 is connected to the shaft (here the rotor shaft 37) by means of a flywheel 1 in a damped and limited torque-transmitting manner. Preferably, an (actively releasable) separating clutch is also provided between the combustion shaft 5 and the rotor shaft 37. The rotor shaft 37, in turn, is connected to the transmission 35 (for example, by means of a possibly further separating clutch, not designated here) via a transmission input shaft 7, and the transmission 35, in turn, is connected to a left drive gear 33 and a right drive gear 34 in a torque-transmitting manner. A (tractive) torque for the drive train 30 can be delivered simultaneously or at different times by means of both drive motors 3, 36 or via their machine shafts 5, 37. The drive gears 33, 34 can thus be supplied with a (preferably variable) gear ratio by the drive motors 3, 36.However, a (thrust) torque can also be absorbed, for example by means of the internal combustion engine 3 for engine braking and / or by means of the electric drive motor 36 for recuperation of braking energy.

[0095] By means of the flywheel 1, a torque can be transmitted from the combustion shaft 5 to the rotor shaft 37 and vice versa in a damped and limited manner. By means of the integrated torque limiter 8, a torque can be transmitted from the combustion shaft 5 to the rotor shaft 37 and vice versa only up to a predetermined torque limit (slipping torque). By means of the integrated torsional vibration damper 19, the electric drive motor 36 (combustion side) is protected from system-related

[0096] The friction device 14 prevents premature activation of the

[0097] Torsional vibration damper 19 or a swinging of the torsional vibration damper 19, which is often perceived as disturbing, is prevented.

[0098] The flywheel proposed here is compact, while at the same time the friction device is well protected against heat input from the torque limiter.

[0099] Reference symbol

[0100] Flywheel 36 electric drive machine

[0101] Rotation axis 37 rotor shaft

[0102] Internal combustion engine 38 Engine connection screw connection ground disk 39 Driver's cab combustion shaft 40 Longitudinal axis central connection 41 Engine axis gearbox input shaft 42 Pressure plate torque limiter 43 Suspension tongue first disc spring 44 Cover plate friction pair 45 Spring window

[0103] Drive plate 46 Spacer bolt Friction lining 47 Additional mass

[0104] Friction disc 48 Friction sleeve Friction device 49 Counter plate Second disc spring 50 Annular recess First friction ring Second friction ring Counter disc

[0105] Torsional vibration damper Energy storage element Flange First input disc Second input disc Opening First partial flange Second partial flange First contact surface Second contact surface Angle limiter Drive train Motor vehicle Torque source Left drive gear Right drive gear

[0106] Gearbox

Claims

Patent claims 1 . Flywheel (1) with a rotational axis (2) for an internal combustion engine (3), comprising at least the following components: - a mass disc (4) for connection to a combustion shaft (5); - a central connection (6) for connection to a transmission input shaft (7); - a torque limiter (8) comprising a first disc spring (9), at least one friction pair (10) which is axially compressed by means of the first disc spring (9); - a friction device (14) comprising a second disc spring (15), a first friction ring (16), a second friction ring (17) and a counter-disk (18) rotatable relative to the second disc spring (15); and - a torsional vibration damper (19), comprising at least one energy storage element (20), at least one flange (21) and at least one input disk (22, 23) rotationally fixed to the mass disk (4), wherein the at least one friction pair (10) of the torque limiter (8) comprises a friction lining (12), a friction disk (13) and a drive disk (11), wherein the friction pair (10) is arranged between the flange (21) of the torsional vibration damper (19) and the central connection (6), characterized in that the friction rings (16, 17) of the friction device (14) are arranged radially inside the at least one energy storage element (20) of the torsional vibration damper (19).

2. Flywheel (1) according to claim 1, wherein the torsional vibration damper (19) has a second input disk (23) which is axially opposite the first input disk (22) with respect to the at least one flange (21), wherein the second input disk (23) is preferably radially attached to the central Connection (6) is supported and / or axially on the torque limiter (8), particularly preferably on its first disc spring (9).

3. Flywheel (1) according to claim 2, wherein the second disc spring (15) of the friction device (14) is suspended in the second input disc (23) and is rotatably fixed and axially supported thereon, wherein preferably the second friction ring (17) of the friction device (14) is arranged axially between the first input disc (22) and the flange (21) of the torsional vibration damper (19).

4. Flywheel (1) according to claim 1, wherein the second disc spring (15) is axially supported on the mass disc (4) and is rotationally fixed to the mass disc (4), preferably by means of an opening (24) in the mass disc (4).

5. Flywheel (1) according to one of the preceding claims, wherein the drive plate (11) of the torque limiter (8) and the counter plate (18) of the friction device (14) are formed in one piece.

6. Flywheel (1) according to one of the preceding claims, wherein the first friction ring (16) or the second friction ring (17) of the friction device (14) is pressed axially against the first disc spring (9).

7. Flywheel (1) according to one of the preceding claims, wherein the drive plate (11) of the torque limiter (8) forms an axial force clamp for the first disc spring (9), the at least one friction lining (12) and the at least one friction plate (13).

8. Flywheel (1) according to one of the preceding claims, wherein the flange (21) of the torsional vibration damper (19) comprises a first partial flange (25) and a second partial flange (26), wherein preferably a first contact surface (27) for one of the energy storage elements (20) and / or a second contact surface (28) for a Angle limiter (29) of the at least one input disc (22,23) is formed exclusively by the first partial flange (25).

9. Drive train (30) for a motor vehicle (31), comprising at least the following components: - an internal combustion engine (3) as a torque source (32) for providing a torque via its combustion shaft (5); - at least one consumer (33, 34) for converting at least part of a torque provided by at least one of the torque sources (32); and - a transmission (35) for transmitting at least part of a torque provided by the torque sources (32) to the consumer (33, 34), wherein at least one flywheel (1) according to one of the preceding claims is arranged between the combustion shaft (5) and the at least one consumer (33, 34), wherein an electric drive machine (36) with a rotor shaft (37) is preferably provided as a further torque source (32) and the flywheel (1) is arranged interposed between the combustion shaft (5) and the rotor shaft (37).

10. Motor vehicle (31), comprising at least one drive wheel (33, 34) and a drive train (30) according to claim 9, wherein for propelling the motor vehicle (31) a torque can be delivered from the at least one drive machine (3, 36) of the drive train (30) to the at least one drive wheel (33, 34).

Images