DE102012214362A1 - Torsional vibration damper for drive train of passenger car, has spring assembly including spring elements placed between input side and output side of damper, where receiving elements are provided between adjacent spring elements - Google Patents

Abstract

The vibration damper (100) has a spring assembly (120) including spring elements (130-1-130-5) e.g. spiral springs, placed sequentially between an input side (140) of the torsional vibration damper and an output side of the torsional vibration damper, where receiving elements (170-1-170-6) are provided between adjacent spring elements. A slide surface (190) is rotatably coupled with the input side or the output side of the vibration damper such that the slide surface comes into frictional contact with the receiving elements.

Description

Embodiments relate to a torsional vibration damper, for example, a dual-mass flywheel, as it can be used for example in the context of a drive train of a vehicle.

In the field of vehicle construction, and in particular in the field of motor vehicle construction, the problem repeatedly arises that torsional vibrations can occur in a drive train of a vehicle. These can lead to a mechanical load on the components of the drive train, but also to a ride comfort reduction of the corresponding vehicle.

For example, internal combustion engines do not generate a constant torque and constant speed per crankshaft revolution. Depending on the operating state, these two variables are subject to a fluctuation, so that rotational irregularities can occur on a crankshaft of such an internal combustion engine. For most applications, however, as constant a torque and speed progression as possible is desirable. Therefore, in such applications, the use of an additional system to reduce rotational nonuniformity is often considered.

For better decoupling of rotational irregularities torsion damper, for example, two-mass flywheels can be used. In these, a spring arrangement is connected between an input side and an output side of the respective torsion damper, so that damping of the occurring torsional vibrations can be achieved by means of this spring arrangement.

For example, describes the EP 1 584 838 A1 a torsional vibration damper with at least one consisting of a plurality of spring elements spring means for the resilient coupling of a drive-side primary element with a driven-side secondary element. Also the DE 10 2007 016 744 A1 refers to a torsional vibration damper having a primary side and a secondary side rotatable about an axis of rotation against the action of a damper element assembly with respect to the primary side. In this torsional vibration damper, the damper element arrangement comprises at least one damper element unit which can be supported in the circumferential end regions with respect to the primary side and the secondary side and extends substantially in the circumferential direction. Also the US 4,360,352 refers to a Torsionsschwingungsdämpferanordnung.

Dual-mass flywheels serve to decouple rotational irregularities in the drive train. Depending on the intended use, it may depend on how a corresponding torsional vibration damper is to be designed. Thus, partly conflicting demands on such a torsional vibration damper. Thus, for example, in the interests of the best possible damping of corresponding torsional vibrations, the use of as soft and low-friction spring arrangements as possible is advantageous. On the other hand, this may possibly result in overloading of such a torsional vibration damper due to high torques introduced and / or by excitation in the region of a natural frequency of the torsional vibration damper. There is therefore a need to improve a tradeoff between reliability and operability of such a torsional vibration damper.

However, similar challenges and problems not only exist in the field of vehicle construction. In other areas of mechanical and plant engineering, corresponding torsional vibration dampers are used. Even with these, a compromise between the reliability and the operability of a corresponding torsional vibration damper is often sought. Therefore, there is also a need in these areas to improve the above-mentioned compromise.

This requirement is borne by a torsional vibration damper according to claim 1.

A torsional vibration damper according to an exemplary embodiment, for example for a drive train of a vehicle, thus comprises a spring arrangement with a plurality of spring elements, which are arranged in series between an input side of the torsional vibration damper and an output side of the torsional vibration damper. A torsional vibration damper further comprises a plurality of receiving elements, wherein in each case one receiving element of the plurality of receiving elements is arranged between each two adjacent spring elements.

Such a torsional vibration damper can be used by a targeted design of the spring elements of the spring assembly and the receiving elements of the plurality of receiving elements to improve a compromise between operability and reliability of such a torsional vibration damper. The spring elements can be implemented, for example, as coil springs, barrel springs, bow springs or other mechanical spring elements. These can be in a rest position of the Torsional vibration damper optionally be biased to pressure. Likewise, however, pneumatic and / or elastic spring elements may also be used, in which, for example, a spring action is carried out on the basis of an elastic deformation of, for example rubber-like, material.

In torsional vibration dampers according to an embodiment, the input side and the output side thereof are generally substantially inelastically coupled with the spring assembly. Therefore, no further spring elements are connected in general between the input side and the spring arrangement and the spring arrangement and the output side. It is important in this context that this refers only to the input side and the output side of the actual torsional vibration damper. It can of course be coupled or combined in applications with other components comprising spring elements.

In this case, torsional vibration dampers can be used in a variety of different application scenarios, with respect to which further structural design features are briefly explained below.

Thus, a torsional vibration damper may optionally further comprise a sliding surface which is rotationally fixedly coupled to the input side and / or the output side, the spring arrangement comprising at least two different types of spring elements and the plurality of receiving elements at least two different types of receiving elements. A receiving element of a first type of the at least two different types is in this case designed such that it is at a speed of the input side and / or the output side, which is less than a free flight speed, spaced from the sliding surface along a radial direction. The plurality of receiving elements in such a case comprises at least one receiving element of the first type. As a result, it may be possible to reduce friction in the context of the torsional vibration damper and thus to possibly improve the abovementioned compromise between operational reliability and functional capability of the torsional vibration damper. The free flight speed, which is also referred to as a freewheeling speed, may correspond to at least 10% of a nominal maximum rotational speed of the torsional vibration damper, for example. However, it may also be higher with other torsional vibration dampers, for example at least 20%, at least 25%, at least 40%, at least 50% or at least 75%. With regard to the sliding surface as well, it is generally substantially inelastic or inelastically coupled to the input side or the output side thereof.

Optionally, in such a torsional vibration damper, the receiving element of the first type can be designed such that it comes into contact with the sliding surface above the free-flight rotational speed such that a receiving element of this type comes into frictional contact with the sliding surface. A frictional contact is in this case when two objects, so for example, the respective receiving element and the sliding surface frictionally contact each other, so that between them a force in the case of a relative movement perpendicular to a contact surface between them. Here, a speed difference, so for example, a slip exist. In addition to such a frictional contact, however, a frictional contact also includes a frictional or non-positive connection between the objects in question, in which a corresponding speed difference or slip substantially does not occur. This is a frictional or frictional connection by stiction, a cohesive connection by molecular or atomic interactions and forces and a positive connection by a geometric connection of the respective connection partners come about. The static friction thus presupposes in particular a normal force component between the two connection partners.

Different types of spring elements may have different force-displacement or different force-angle characteristics or characteristics. Additionally or alternatively, however, they can also be implemented by different technologies, from which, if appropriate, corresponding different force-displacement or force-angle characteristics can result.

Optionally, in such a torsional vibration damper, the at least one receiving element of the first type can be arranged between a first and a second spring element and / or between a penultimate and a last spring element according to the sequence of the spring elements. This makes it possible to design the first or last spring element by a specific design of the adjoining this receiving element in terms of its function. This makes it possible, for example, to interpret this as a particularly soft stage or as a particularly hard stage of a complex force-displacement or force-angle characteristic of the spring assembly and the torsional vibration.

Optionally, in the case of a torsional vibration damper, the first and / or the last spring element may be designed according to the sequence of the spring elements, so that this spring element can be deflected at least up to a torque introduced into the input side or the output side, which corresponds for example to at least 110% of a nominal maximum torque , Optionally, the receiving element adjoining this spring element can also be designed accordingly. This may make it possible to implement this first or last spring element as part of a drive or as a stop damper of the torsional vibration damper.

Optionally, in a torsional vibration damper comprising the aforesaid sliding surface, at least one receiving element of the plurality of receiving elements may be designed to be pressed against the sliding surface independently of rotational speed so as to be in frictional contact with it independently of rotational speed. This makes it possible to achieve a targeted damping of the torsional vibration damper even at lowest speeds. This can serve both to increase the reliability of the torsional vibration damper as well as the interpretation of the same for different purposes and thus its functionality.

Optionally, in the case of a torsional vibration damper comprising a corresponding sliding surface, at least one receiving element of the plurality of receiving elements may be designed such that it can make frictional contact with the sliding surface. Optionally, this can be done - as previously mentioned - when a speed of the input side and / or the output side is exceeded by the aforementioned free flight speed. This makes it possible to realize a damping of the torsional vibration damper in dependence on a rotational speed of the input side and / or the output side in order to improve the aforementioned compromise.

Optionally, in the case of a torsional vibration damper, at least one spring element of the spring arrangement can be designed so that this spring element can be deflected at least up to a torque introduced into the input side or the output side, which corresponds at least, for example, to 130% of a nominal maximum torque. As a result, it may be possible to implement and implement an abutment step which prevents the torsional vibration damper from breaking through to an introduced torque which is significantly above the nominal maximum torque of the torsional vibration damper for which it is designed. As a result, thus, the reliability and thus the aforementioned compromise can be further improved.

Optionally, in a torsional vibration damper optionally including the above, at least one receiving element of the plurality of receiving elements may be configured to frictionally engage the sliding surface at a rotational speed of the input side and / or the output side that is above a threshold speed occurs. In this case, the threshold speed can typically be smaller than the free-flight speed or freewheeling speed. This may for example be at 5% of a nominal maximum speed of the torsional vibration damper. However, the threshold speed can also be in other torsional vibration dampers above the aforementioned value, that is, for example, at 10%, 15%, 20% or 25%. It may be advisable to choose these - as mentioned above - smaller than the free flight speed. As a result, damping of the torsional vibration damper which already starts at low rotational speeds can optionally be implemented. Such a receiving element is often referred to as an "aviator", while a receiving element which has up to the free flight speed or at least to the free flight speed the aforementioned distance to the sliding surface, also referred to as "trapped flier". If such a receiving element is correspondingly designed to come into frictional contact with the sliding surface or to be in frictional contact therewith in rotation-independent manner, this may for example comprise a sliding shoe which is designed to form the aforementioned frictional contact with the sliding surface. Sometimes such a receiving element is therefore synonymous synonymous as a shoe or spring plate, although depending on the implementation, the receiving element may include other components.

Optionally, in a torsional vibration damper, the spring assembly may comprise at most two different types of spring elements, wherein the spring elements of the spring assembly and the receiving elements of the plurality of receiving elements may be formed in such a case so that the receiving elements adjacent to the spring elements of one type of the at most two types a torque introduced into the input side or the output side of at most 100% of a nominal maximum torque are movable relative to each other. In other words, the spring elements of the first type and the associated receiving elements may be designed so that they can continue to fulfill their damping function at least partially under load with the nominal maximum torque. This can be it be possible to form the torsional vibration damper so that even at initiation of the nominal maximum torque nor a torsional vibration damping is possible. In this way, a functionality can be made possible over the entire range of the nominally permitted torque of the torsional vibration damper.

Optionally, in such a torsional vibration damper, the spring elements of the spring arrangement and the receiving elements of the plurality of receiving elements may be formed such that all receiving elements are stationary relative to each other upon transmission of a rotational movement with a torque of, for example, at least 120% of the nominal maximum torque. Such a torsional vibration damper can thus be formed without a stop step, which is possible, for example, when an overload of the torsional vibration damper can be reliably prevented by the use of appropriate control mechanisms. Such a torsional vibration damper can be used, for example, in the context of a drive train, which includes an automatic transmission or a different automatic shifting transmission, in which therefore can not or hardly occur in the incorrect operation of the transmission by the driver or operator of the same. In this way, it may be possible to use the additionally obtained by eliminating a stop step space for other spring elements and thus optionally to achieve an improvement in the functionality and functional characteristics of the torsional vibration damper.

In such a torsional vibration damper, all the spring elements of one type may be arranged adjacent to each other and at most one spring element of each type may be arranged adjacent to a spring element of the other type. Adjacent are two objects, between which no further object of the same type is arranged. Immediately adjacent are corresponding objects when they are adjacent, that is, for example, in contact with each other. This may make it possible to prevent an interaction of the spring elements of different types due to a mixed arrangement of the same and thus optionally to improve the operability of the torsional vibration damper.

Optionally, and often as an alternative to the aforementioned options, in a torsional vibration damper all spring elements of a second type different from the first type of the at most two types of spring elements can be arranged adjacent to each other, wherein the spring arrangement comprises at least three spring elements of the first type, wherein all spring elements of the first type of the first type are arranged adjacent to each other except for a single spring element of the first type, and wherein the spring elements of the second type between the spring elements of the first type are arranged. In other words, in such a torsional vibration damper, the spring elements of the second type may be disposed completely between the single spring element of the first type and the other spring elements of the first type. In this way, if appropriate, a stop step or another functionally differing spring stage can be implemented by the single spring element of the first type, without the other spring elements of the first type being possibly affected thereby in terms of their functionality. Likewise, it may thereby be possible to simplify the production of a torsion damper, as a number of spring elements of different types may be limited and a risk of incorrect assembly may be reduced.

In such a torsional vibration damper, which further comprises a corresponding sliding surface, as described above, at least one receiving element, which is in contact with the exactly one single spring element of the first type, may be designed so that this at a rotational speed of the input side and / or the output side, which is above a threshold speed, enters with the sliding surface in a frictional contact. In this way, a targeted damping of the individual spring element of the first type can be implemented in order to achieve, for example, a deviating from the other spring elements spring / damping characteristic. The threshold speed may optionally coincide with the free flight speed, but also deviate from this.

Optionally, in a torsional vibration damper comprising at most two types of different spring members, the spring members of a second type of the at most two types may be formed such that with these contacting members at a torque input to the input side or the output side, that corresponds to at least one starting torque value , are stationary relative to each other. For example, the starting torque may correspond to a value of at most 50% or at most 35% of a nominal maximum torque of the torsional vibration damper. This may make it possible to implement a starting stage which, for example, during a start of an internal combustion engine, which is coupled to the drive train of the vehicle to pass through and thereby damaging the torsional vibration damper by a particularly strong resonant To prevent vibration during starting. For example, torsional vibration dampers may be designed so that they have a natural frequency that is significantly below an idling speed of such an internal combustion engine. Of course, in other application examples, torsional vibration dampers can also be designed with a different, for example higher, natural frequency. For example, torsional vibration dampers can also be used to create a phase shift of an initiated torsional vibration.

Optionally, in a torsional vibration damper comprising at most two types of spring elements and a sliding surface described above, at least one receiving element which is in contact with a spring element of the first type on both sides may be formed so as to reach a rotational speed of the input side and or the output side, which is less than a free flight speed, is spaced from the sliding surface along a radial direction. As a result, if appropriate, friction of the relevant spring element of the first type can be prevented, at least below the already mentioned free-flight speed. As a result, optionally a functionality of the torsional vibration damper can be improved.

Optionally, in such a torsional vibration damper, all the receiving elements which are in contact with a spring element of the first type on both sides may be formed to be up to an input side and / or output side speed lower than the free flight speed Sliding surface to be spaced along a radial direction. As a result, for example, a spring element responsible for damping torsional vibrations during the normal driving operation of a vehicle can be configured with low friction. Thus, it may be possible to improve a damping characteristic of the torsional vibration damper and thus the aforementioned compromise.

Optionally, in a torsional vibration damper, the spring assembly may comprise exactly one spring element of a first type, exactly one spring element of a third type and at least one spring element of a second type, wherein the spring element of the first type and the receiving elements adjacent thereto are formed such that the receiving elements in a torque introduced into the input side or the output side, which corresponds to at least one starting torque value, are stationary relative to each other. The spring element of the third type and the adjacent thereto receiving elements may be formed so that the receiving elements adjacent thereto at a torque of at most 130% of the nominal maximum torque in the input side or the output side movable relative to each other and upon initiation of a torque of at least 150% of the nominal maximum torque in the input side or the output side are stationary relative to each other. The at least one spring element of the second type and the receiving elements adjoining the at least one spring element of the second type may in this case be designed such that the receiving elements adjoining the at least one spring element of the second type upon introduction of a torque of at most 100% of the nominal maximum torque in the input side or the output side are movable relative to each other and stationary at the initiation of a torque of at least 120% of the nominal maximum torque in the input side or exclusively relative to each other. In other words, a torsional vibration damper can be configured as a three-stage torsional vibration damper, in which exactly one spring element of the first type and the second type form a starting stage or an abutment stage, while the at least one spring element of the third type forms a driving stage. This may make it possible, if necessary, to realize a three-stage torsional vibration damper with structurally simple means, which has high functional reliability and at the same time good damping characteristics even under different operating conditions.

Optionally, in such a torsional vibration damper, which further comprises a previously mentioned sliding surface, the spring arrangement comprises at least two spring elements of the third type, wherein at least the receiving elements, which are in contact with a spring element of the third type on both sides, are designed such that they to a rotational speed of the input side and / or the output side, which is less than a free flight speed, is spaced from the sliding surface along a radial direction. As a result, attenuation can optionally be reduced in the driving position, and thus possibly an attenuation characteristic can be improved.

In this case, a mechanical coupling of two components comprises both a direct and an indirect coupling. Electrical or other components in this case are indirectly coupled to one another via another component or directly to one another in such a way that they permit a signal exchange between the relevant components. Thus, the corresponding coupling sections or completely, for example, implemented electrically and optically, magnetically or by radio technology and implemented.

Under an integrally formed component is understood as one which is made exactly from a contiguous piece of material. The term "integral" may therefore be used synonymously with the terms "integral" or "one-piece".

For example, a component may have n-fold rotational symmetry, where n is a natural number greater than or equal to 2. An n-fold rotational symmetry is present when the component in question, for example, about a rotational or symmetry axis by (360 ° / n) is rotatable and thereby merges substantially in terms of form in itself, ie with a corresponding rotation substantially to itself in the mathematical sense is mapped. By contrast, in the case of a complete rotation-symmetrical design of a component in any rotation about any angle about the axis of rotation or symmetry, the component essentially transits itself in terms of its shape, so it is essentially mapped onto itself in the mathematical sense.

Both an n-fold rotational symmetry as well as a complete rotational symmetry is referred to here as rotational symmetry.

A frictional or frictional connection comes about through static friction, a cohesive connection by molecular or atomic interactions and forces and a positive connection by a geometric connection of the respective connection partners. The static friction thus presupposes in particular a normal force component between the two connection partners.

Hereinafter, torsional vibration damper according to an embodiment will be described and explained in more detail with reference to the accompanying figures.

1 shows a plan view of a torsional vibration damper according to an embodiment;

2 shows a schematically simplified representation of the in 1 shown torsional vibration damper;

3 illustrates that in the 1 and 2 shown torsional vibration damper in the case of a zero position without load;

4 shows the in the 1 to 3 shown torsional vibration damper at a low load in the attack of the starting stage;

5 shows the in the 1 to 4 shown torsional vibration damper when subjected to a maximum load until the gear and the stop level are in the attack and a nominal maximum torque is exceeded;

6 shows a linear characteristic of a torsional vibration damper;

7 shows a characteristic of a two-stage torsional vibration damper;

8th shows a characteristic of a three-stage torsional vibration damper;

9 shows a partial perspective view of a spring arrangement with a plurality of receiving elements of a torsional vibration damper;

10 shows a schematically simplified representation of a torsional vibration damper, in which the receiving elements are frictionally configured;

11 shows a schematically simplified representation of a torsional vibration damper, in which the receiving elements are trapped;

12 shows a schematically simplified representation of a torsional vibration damper, in which, in contrast to the in 11 shown embodiment, a primary-side receiving element is frictionally configured;

13 shows a schematically simplified representation of a torsional vibration damper, in which the receiving elements of the spring elements of the driving gear are caught;

14 shows a schematically simplified representation of a torsional vibration damper with a two-stage characteristic for a manual transmission;

15 shows a schematically simplified representation of a torsional vibration damper for an automatic transmission, dual-clutch transmission or other automatically shiftable transmission;

16 shows a torsional vibration damper with two receiving elements, which are pressed independently of rotation against the sliding surface;

17 shows a schematically simplified representation of a torsional vibration damper, in which the receiving elements of the spring element of the starting stage are additionally attenuated by pressing on the sliding surface;

18 shows a schematically simplified representation of a torsional vibration damper with a three-stage characteristic;

19 shows a schematically simplified representation of a torsional vibration damper with a partially caught bow spring;

20 shows a schematically simplified representation of a torsional vibration damper with a partially trapped soft bow spring as a starting stage; and

21 shows a schematically simplified representation of a torsional vibration damper with a trapped hard bow spring.

In the following description of the accompanying drawings, like reference characters designate like or similar components. Further, summary reference numbers are used for components and objects that occur multiple times in one embodiment or in one representation, but are described together in terms of one or more features. Components or objects which are described by the same or by the same reference numerals may be the same, but possibly also different, in terms of individual, several or all features, for example their dimensions, unless otherwise explicitly or implicitly stated in the description.

1 shows a plan view of a torsional vibration damper 100 , which is more specifically a dual mass flywheel 110 for use in a powertrain of a passenger vehicle. torsional vibration damper 100 However, they can also be used in other areas of motor vehicle construction, vehicle construction and other areas of mechanical and plant engineering. The description of torsional vibration dampers 100 in the context of passenger cars is so far no restriction on the possible application of torsional vibration dampers 100 according to an embodiment.

The torsional vibration damper 100 has a spring arrangement 120 with a plurality of spring elements 130-1 , ..., 130-5 on. These are between an input page 140 and a home page 150 , however, in 1 not shown, arranged one behind the other in an order. The input side comprises a primary mass flywheel 160 , which with the spring arrangement 120 is coupled substantially inelastically.

The torsional vibration damper 100 further comprises a plurality of receiving elements 170-1 , ..., 170-6 , which are formed so that they with the spring elements 130 the spring arrangement 120 so in contact. This allows the spring elements 130 over the receiving elements 170 Pick up and release forces. Apart from two outer receptacles 170-1 . 170-6 , which are also referred to as spring plate, are the receiving elements 170-2 . 170-3 . 170-4 . 170-5 in each case between two adjacent spring elements 130 arranged. One of a spring element 130 generated force is so on the adjoining this receiving element 170 to an optionally adjacent spring element 130 transfer.

The two outer receiving elements 170-1 . 170-6 serve beyond that for the mechanical coupling of the spring elements 130 or the spring arrangement 120 to the entrance side 140 and the exit side 150 (not shown in 1 ). For this purpose, the primary flywheel 160 On the input side a connection structure 180 on, about the rotational movement of the primary mass flywheel 160 , that is the input side 140 , on the spring arrangement 120 is transferable. On the output side is the spring arrangement 120 with an in 1 Not shown hub disc into abutment, via which the transmitted force or the transmitted torque from the torsional vibration damper 100 can be derived.

The connection structure 180 as well as in 1 Hub disc not shown here stand with the spring arrangement 120 over the two outer receiving elements 170-1 . 170-6 in contact. These also transmit the corresponding forces and torques.

When displayed in 1 It should be noted that this is only the representation of a "half" dual mass flywheel 110 is. The dual mass flywheel 110 or the torsional vibration damper 100 points so beside the in 1 shown spring arrangement 120 another, for example, identical or deviating designed spring arrangement.

The primary mass flywheel 160 is in the torsional vibration damper shown here 100 designed as a housing shell of the same. It thus also extends along an axial direction to the rotational movement of the torsional vibration damper 100 is damped, such that the spring assembly 120 is at least partially covered radially outward along the axial direction of this. This is how the primary mass flywheel forms 160 at one of the receiving elements 170 facing inner surface of a sliding surface 190 on, with the receiving elements 170 of torsional vibration damper 100 optionally in a frictional contact can occur. For this purpose, the receiving elements 170 For example, a correspondingly shaped Gegengleitfläche 200 have, for example, with respect to the radii used at the radius of the sliding surface 190 oriented.

Here, between the recording elements 170 and the sliding surface 190 so arise the previously mentioned frictional contact, in which between the optionally 190 and the one or more receiving elements 170 a force and thus a torque can be transmitted. In contrast to a frictional or non-positive connection, in the case of a frictional contact, a speed difference, for example, a slip, can occur between the partners involved. However, this is not mandatory for the presence of a frictional contact, so that under the preamble of the frictional contact as well as a frictional or non-positive connection can fall. A frictional or frictional connection and a corresponding frictional contact come about here by stiction, which requires a normal force acting perpendicular to the two connection partners. This may, for example, have a speed-dependent and / or a speed-independent component.

The recording elements 170 are thus designed so that they are the spring elements 130 the spring arrangement 120 lead at least partially and can absorb and transmit a force generated or mediated by these. In addition, they may be compatible with the sliding surface 190 come in contact and contribute to a damping of a torsional vibration.

The sliding surface 190 is at the in 1 shown torsional vibration damper 100 with the input side 140 coupled. However, it can also be used in other torsional vibration dampers with the in 1 not shown output side 150 be coupled. In addition, it should be mentioned at this point that in principle a torsional vibration damping can take place, if not on the input side 140 but rather on the output side 150 (not shown in 1 ) the relevant rotational movement is coupled. It is also appropriate to point out at this point that, of course, in other torsional vibration dampers 100 the number of spring elements used 130 as well as the number of receiving elements 170 can vary.

The spring elements 130 as they are in 1 are shown here belong to two different types of spring elements. Both types are designed in the present case as spiral or barrel springs, wherein the spring elements 130-2 and 130-3 belong to a first type of spring elements. The spring elements 130-1 . 130-4 and 130-5 belong here to a second type of spring elements. The spring elements 130 can optionally be in a prestressed state in the torsion damper 100 are used, so that even in a resting state of the torsional vibration damper 100 can be claimed on pressure. This may make it possible to reduce noise at low speeds and / or in a low-load state (eg, at idle). In other words, the spring arrangement 120 be slightly biased to prevent no-load noise. Thus, the load-changing geometry of the spring elements and their location in the torsional vibration damper has 100 a smaller negative effect on the idling decoupling.

The two types of spring elements 130 differ in terms of two aspects. First, it is the spring elements 130 of the first type (spring elements 130-2 . 130-3 ) to those in which an outer spiral or barrel spring surrounds an inner spiral or barrel spring. The wire thicknesses of the respective springs of the spring elements 130 of the first type in this case have a smaller diameter than that of the second type (spring elements 130-1 . 130-4 . 130-5 ) on. As a result, the spring elements of the second type are much stiffer than those of the first type. The parallel connection of the two spiral or barrel springs of the spring elements 130 the spring elements of the first type compensates for this only partially.

For this reason, form the spring elements of the first type, so the spring elements 130-2 and 130-3 (Springs 2 and 3), a so-called starting stage, which is designed so that at a start of the internal combustion engine of the vehicle in question intercept these torsional vibrations, which otherwise possibly to a deterioration, damage or destruction of the torsional vibration damper 100 could lead. In contrast, the spring elements 130-4 . 130-5 , So the springs 4 and 5 of the spring assembly 120 , arranged so that they form a so-called drive level. The spring elements 130-4 . 130-5 The driving stage serve essentially during a normal driving operation of the vehicle for damping the torsional vibrations occurring. The first spring, so the spring element 130-1 , which is also a spring element of the second type, serves as a stop step. Together with the relevant recording elements 170-1 . 170-2 allows the spring element 130-1 it so that in the case of an introduction of a particularly high torque still a spring effect in torsional vibration damper 100 is available. spring elements 130 an abutment step can thus be designed, for example, such that they are at an introduction of the torque in the spring assembly 120 of at most 130% of a nominal maximum torque are still compressible while being at least 150% of the aforementioned nominal maximum torque incompressible or relatively stationary relative to each other. The nominal maximum torque here is the torque for which the relevant torsional vibration damper is designed. This may, for example, coincide with a maximum torque which the internal combustion engine of the vehicle can engage in the torsional vibration damper.

Of course, in other embodiments, other values than the aforementioned 130% or 150% of the nominal maximum torque can be used. Thus, for example, it may also be possible in other embodiments that already at a maximum of 130%, at most 120%, at most 110% or at most 105% already a corresponding compressibility of the spring elements 130 the stop step or to a corresponding relative local strength of the corresponding receiving elements 170 can come to each other.

1 also illustrates by an arrow the occurrence of a tensile torque 210 , This acts on the spring set, so the spring arrangement 120 from the hub disc or a ring gear, so from the output side 150 out. A corresponding thrust torque would affect the corresponding opposite or other side and would be the tensile torque 210 opposite direction.

2 shows a schematically simplified representation of the in 1 shown torsional vibration damper 100 or the part of the same shown there, wherein the round configuration of the torsional vibration damper is projected here on a line or a plane.

On the left side of the 2 is the input side 140 of the torsional vibration damper 100 shown, to which the receiving element 170-1 , and the first spring element 130-1 followed. As well as in 1 is shown, this is then a respective receiving element 170-2 , ..., 170-6 and - in alternating order with the receiving elements 170 - A corresponding spring element 130-2 , ..., 130-5 arranged. The receiving element 170-6 stands here with the output side 150 in contact, for example, by the in 1 also not shown hub disc or may be formed by a ring gear. The entrance page 140 is also used as the primary side, the output side 150 also called the secondary side.

The with the input or output side 140 . 150 connected receiving elements 170-1 . 170-6 are also referred to as spring plate, while the receiving elements 170-2 . 170-3 . 170-4 and 170-5 , which on both sides each with a spring element 130 be in contact, here also referred to as sliding shoes, as these, as well as in 2 is shown by the downward arrows, due to the receiving elements 170 acting radial forces on the slide or sliding surface 190 be pressed. This results in the case of a relative movement of the receiving elements 170 to the sliding surface 190 Friction, so the movement of the receiving elements 170 and the spring elements 130 is dampened. Again, of course, is the sliding surface 190 back in the primary flywheel 160 integrated, as well as in 1 is recognizable.

The 3 . 4 and 5 show a juxtaposition of the in the 1 and 2 shown torsional vibration damper 100 in different stress scenarios. 3 shows here also in 2 illustrated situation when the torsional vibration damper 100 is in its zero position, so is applied without a moment. In contrast illustrated 4 the situation where the torsional vibration damper 100 from the output side 150 , so the secondary side, with a tensile torque 210 is applied, which is sufficient to bring the above-described starting stage in the attack. The tensile moment 210 thus provides a finite, but compared to a maximum load of the torsional vibration damper 100 a small load.

As related to the 1 and 2 has already been explained, in this case form the spring elements of the first type, so the spring elements 130-1 . 130-3 and the associated receiving elements 170-2 . 170-3 and 170-4 the starting level. So is a torque from the side of the output side 150 in the torsional vibration damper 100 coupled, which exceeds a starting torque, the spring elements 130 the starting stage, so in the present case, the spring elements of the first type, as far as compressed, that the associated receiving elements 170-2 . 170-3 and 170-4 are stationary relative to each other. In the illustration shown here, this is illustrated by the fact that the respective recording elements 170 get in touch with each other. This can also be the case in the case of a non-schematic illustration of the torsional vibration damper 100 enter. So also here the recording elements 170 along a circumferential direction of torsional vibration damper 100 contact each other provided the corresponding spring elements 130 that are arranged between them, allow this. For other torsional vibration dampers 100 can the respective spring elements 130 also be compressed so strong here, so that they do not allow further compression. In other words, the receiving elements 170 optionally be characterized by being stationary relative to each other that the spring elements 130 simply be compressed so much so that a further compression of the same is no longer possible without the receiving elements 170 to touch each other.

Although this is the recording elements 170-2 . 170-3 and 170-4 are stationary to each other, these are still based on the sliding surface 190 or the other recording elements 170 and the input side 140 as well as the exit side 150 if necessary, continue to move. Like this in 4 Also indicated by the arrows pointing down, this can cause a corresponding friction due to the prevailing radial forces.

In principle, the starting torque or the starting torque value here can assume any values, which of course should be lower than the nominal maximum torque for which the torsional vibration damper 100 is designed. For example, this can amount to at most 50% of the nominal maximum torque or at most 35% of the nominal maximum torque. For example, in the case of 4 shown situation a torque of at least 89-150 Nm from the side of the output side 150 as a tensile moment 210 in the torsional vibration damper 100 be introduced.

5 finally shows a situation in which the tensile moment 210 assumes such a value, so that all spring elements 130 of the torsional vibration damper 100 are not further compressible. Like this in 5 shown here, this can also be done by the receiving elements 170 get in touch with each other. In other words, each adjacent receiving elements 170 touching each other. As has already been explained above, however, it is also possible here for a contact of the receiving elements 170 completely or partially omitted with each other when the spring elements 130 are designed in such a way that they no longer allow a further compressibility due to their own design.

The tensile moment 210 which belongs to the in 5 In this case, for example, between 1.3 times and 1.5 times the nominal maximum torque of the torsional vibration damper 100 lie. In other words, the tensile torque 210 which of the situation in 5 For example, assume a value of 130% to 150% of the aforementioned nominal maximum torque, which is the maximum torque M _{Mot of} the internal combustion engine of the vehicle, for which the torsional vibration damper 100 is determined.

5 thus shows the situation where the tensile moment 210 reached its maximum load, so that both the speed, the starting level and the stop level were driven into the attack.

Like a comparison in particular the 3 and 5 shows, especially in a tensile load by a on the output side 150 acting tensile moment 210 (Pulling operation) the receiving elements 170 on the sliding surface 190 the biggest way back, the exit side 150 are arranged closest. The recording elements 170 put the smallest way back here. With regard to their compression, the respective spring elements differ 130 Here only in terms of their design, so their type.

The 3 to 5 thus show a comparison and a movement of the spring elements 130 and the receiving elements 170 the spring arrangement 120 in the torsional vibration damper 100 at train.

The 6 . 7 and 8th illustrate different torque-twist characteristics of torsional vibration dampers 100 , The characteristics shown here can be correspondingly to the force-displacement characteristics of the individual spring elements 130 be converted. The characteristics are not least due to a stiffness, the so-called c-value of the spring elements 130 given. The c-value, which is typically measured and determined in the SI unit Nm / °, significantly determines a natural frequency of the torsional vibration damper 100 in the respective stage with. Basically, the smaller the c-value, the smaller the eigenfrequency is.

torsional vibration damper 100 as dual mass flywheels 110 are often brought into a supercritical operation, so as far as possible operated above their natural frequency. To make this possible, have torsional vibration 100 or dual mass flywheels 110 often a soft start. The starting stage here often has a natural frequency which is between an ignition speed of the internal combustion engine at about 200 U / min and 350 U / min. It is thus far below a usual idle speed of a motor, which for example, at about 700 rpm. The supercritical operation is therefore guaranteed while driving and even with a "motor pressure" to low speeds.

The natural frequency of the dual mass flywheel 110 However, it is briefly passed at the engine start. Therefore, friction is often very useful here to prevent the system from swinging up because the damping of the vibration reduces its amplitude.

6 shows a first characteristic 220-1 a torsional vibration damper 100 , which is essentially linear. So rises from a vanishing torque with increasing torsion angle of the input side 140 relative to the output side 150 the torque of the spring assembly 120 linear. The characteristic 220-1 thus essentially corresponds to Hook's law, which is true for many spring elements 130 is approximately valid.

Such a characteristic 220-1 can for example be implemented by spring elements 130 only a single type, for example of the previously described type for the drive level to be implemented. In such a case, however, it may be appropriate to offer the spring arrangement 120 So the spring elements 130 and optionally the receiving elements 170 be designed so that they go into a stop when the torsional vibration damper 100 is applied with a torque which corresponds to between about 130% and about 150% of a nominal maximum torque, so for example, the maximum motor torque M _Mot . In other words, such a characteristic may be 220 offer to use hard springs.

In contrast to this shows 7 a second characteristic 220-2 a torsional vibration damper 100 , which is formed in two stages. This is the characteristic of the characteristic 220-2 two adjoining and substantially linear pronounced part characteristics 230-1 and 230-2 on which together the characteristic 220-2 forms. The first part characteristic 230-1 which runs linearly starting from a vanishing torque at a vanishing angle of rotation can thus be achieved, for example, by spring elements 130 be characterized, which are typical for a starting stage. At one in 7 indicated by a dashed line transition 240 goes the starting stage or its spring elements 130 and the receiving elements 170 in the stop, which in turn can be done at the already mentioned above starting torque. Beyond the transition 240 then closes the part characteristic 230-2 in contrast to the part characteristic 230-1 not determined by the soft springs of the starting stage, but essentially by the hard springs of the driving gear. Again, the second part characteristic obeys 230-2 essentially the Hooke's law, whereby here again the stop of the drive stage takes place at the previously mentioned values of about 130% to about 150% of the nominal maximum torque. The second part characteristic 230-2 is thus essentially determined or characterized by the hard springs of the driving gear.

8th finally shows a third characteristic 220-3 a three-stage torsional vibration damper 100 which are three substantially linear part characteristics 230-1 . 230-2 and 230-3 that is at respective transitions 240-1 and 240-2 merge. The first part characteristic 230-1 , which runs comparatively flat starting from a vanishing torque at a vanishing angle of rotation, here again by the soft springs, so the spring elements 130 the starting level, given. Reaches the twist angle the first transition 240-1 , the starting stage goes into the attack at the above-mentioned values of the starting torque, followed by the second part characteristic 230-2 followed. This runs steeper than the part characteristic 230-1 and is by springs of medium hardness of the spring elements 130 the driving level determined. If the twist angle reaches the second transition 240-2 , These springs go at a torque between about 110% and about 120% of the nominal maximum torque, so for example the maximum torque of the internal combustion engine in the attack.

At the second transition 240-2 closes the third part characteristic 230-3 steadily to the second part characteristic 230-2 at. The third part characteristic 230-3 here points to the second part characteristic 230-2 a greater slope, due to the hard springs of the spring elements 130 the stop step is determined. These are at the previously mentioned values of about 130% to about 150% of the nominal maximum torque in their attack on.

In the characteristics of the torsional vibration damper 100 For example, the dual mass flywheel 110 as they are in the 6 to 8th are shown, of course, the part characteristics go by design 230 steadily merging into each other's characteristics 220 to build.

torsional vibration damper 100 and dual mass flywheels 110 Optionally, these are combined with optimized friction pairings, captive spring plates, internal dampers, absorbers, torsionally damped clutch plates, electric machines, torque converters, power split systems, and other components better decoupling of rotational irregularities of an internal combustion engine combined. To reduce friction, for example, in the drive, it may be advisable, the recording elements 170 such that they do not or only above a so-called free flight speed or freewheeling speed with the sliding surface 190 contact. The free flight speed may in this case, for example, at least 10%, at least 20%, at least 30%, at least 40% or at least 50% of a nominal maximum torque of the torsional vibration damper 100 correspond. Is it one or more recording elements 170 such, at least at speeds between a threshold speed and the free-flight speed not with the sliding surface 190 is in contact, that has a corresponding distance in the radial direction, this can be realized for example by appropriate holding plates, as in the following in connection with 9 will be described in more detail. In such a case, so keep the recording elements 170 the spring elements 130 why such a solution is also referred to as a solution with trapped springs, which is used to minimize the friction in the system.

torsional vibration damper 100 which are currently used for decoupling of rotational irregularities in drive trains of vehicles used, therefore, may not reach their highest efficiency, if between the input side 140 and the output side 150 too much friction exists. This can have an adverse effect on the decoupling of the rotational irregularities. A particularly high influence here is the friction between the receiving elements 170 (Spring plate and shoes) on the one hand and the primary mass flywheel 160 and its sliding surface 190 on the other hand. These frictional forces increase due to the spring elements and the receiving elements 170 acting centrifugal forces and optionally other radial spring force components with increasing speed and torque, if necessary, strong. Through the use of appropriate captive recording units 170 So can a corresponding friction between these and the sliding surface 190 of the primary mass flywheel 160 or a corresponding component of the output side 150 be reduced. This makes it possible to achieve not only a more optimal decoupling in terms of rotational irregularities, it may also be possible to reduce or prevent wear.

9 shows a perspective view of a spring assembly 120 with three receiving elements 170-1 . 170-2 and 170-3 , Between the recording elements 170 are corresponding spring elements 130-1 and 130-2 arranged. As already related to 1 and 2 has been explained, it is the spring element 130-1 a helical or torsion spring which has a harder spring characteristic than the spring element 130-2 , which is designed as two nested, parallel screw or barrel springs. The springs of the spring element 130-2 have a smaller diameter with respect to their wire than the spring of the spring element 130-1 on.

The recording elements 170 are in the spring arrangement shown here 120 executed in several parts. The recording elements 170 here have a guide component 250 on, which can be made of a plastic, for example, to effect a noise reduction when the guide member 250 for example, with the sliding surface 190 of the primary mass flywheel 160 comes into contact. The primary mass flywheel 160 is typically made of a metallic material, for example a metal or a metallic alloy, so that when using a likewise made of a steel or other metallic material guide member 250 possibly a significant noise from the torsional vibration damper 100 could be vocal.

The receiving element 170 , which is also referred to as a receiving member, further comprises along an axial direction 260 on both sides of the guide component 250 one holding component each 270-1 . 270-2 , The holding components 270 can be made for example of a sheet, but also of a plastic. So it may be with the material from which the holding components 270 are optionally made to act the same material from which also the guide member 250 is made.

The holding components 270 are here in corresponding recesses 280 the guide components 250 introduced and via a riveted joint 290 with the guide component 250 connected.

9 shows here for each of the three recording elements 170-1 . 170-2 and 170-3 each on both sides of the guide components 250 a corresponding holding member 270 , These are along the axial direction 260 arranged equidistantly, but can of course be arranged differently. The axial alignment of the holding components 270 is with the recording elements shown here 170 realized by the recesses 280 the different recording elements 170 different depths along the axial direction 260 exhibit.

The holding components 270 in this case have guide portions which are opposite to an extension in the radial direction and circumferential direction in the region of the rivet connections 290 are significantly lower in the circumferential direction. Along the axial direction 260 have the holding components 270 and thus also the leadership sections 300 a substantially constant thickness, so that due to the elongated configuration in the radial direction of the guide portions 300 upon rotation or rotation of the spring assembly 120 through the on the receiving elements 170 radially outwardly acting centrifugal forces the guide components 250 be accelerated radially outward. The guide sections 300 can now be just designed so that they extend so long due to the centrifugal forces, so that the guide components 250 an output distance, they at a standstill of the spring assembly 120 from the sliding surface 190 have overcome. The exact configuration of the guide sections 300 For example, using the finite element method, taking into account the geometrical relationships of the receiving elements 170 , ie in particular the guide components 250 , the distance of the sliding surface 190 from the recording elements 170 and the materials used.

The recording elements 170 are also referred to as fliers in such a case, since they at least at standstill of the spring assembly 120 the aforementioned distance from the sliding surface 190 exhibit. Are the recording elements 170 as previously described, configured so that it does not frictionally contact with the sliding surface until free flight speed 190 have, above it, but a corresponding develop or form, the guide components 250 also referred to as sliding shoes.

Instead of the riveted connection 290 Of course, other connection techniques can be used when the receiving elements 170 are executed in several parts. The holding components 270 catch the guide components as described 250 which is why they are also referred to as trapped. The connection of the holding components 270 to the guide member may, for example, alternatively to the rivet connection 290 by screwing, gluing, plugging, clipping, crimping, pouring or another, for example, positive connection.

By using appropriate trapped guide components 250 , So corresponding recording elements 170 , which are above the free flight speed in frictional contact with the sliding surface 190 If necessary, such mechanical overstressing by centrifugal forces can be reduced or prevented if necessary. In addition, it may be possible, a targeted friction from a certain speed of the spring assembly 120 and thus adjust corresponding centrifugal forces.

However, depending on the specific implementation, it may be advisable to avoid unnecessarily strong imbalances that the radial distance of the receiving elements 170 from the sliding surface 190 possibly limited. The holding components 270 For this reason, they are also called catcher.

Of course, the in 9 shown holding components, but also the guide components 250 and the spring elements shown there 130 be implemented in a different form. So basically any spring elements 130 and spring arrangements 120 be caught in this or a similar way. The connection can be made to sliding shoes, spring plates and other components of any kind that can hold and guide the corresponding springs. In addition to the previously mentioned spiral and barrel springs, the spring elements 130 also as bow springs or based on pneumatic springs and on the basis of other elastic materials, for example an elastic polymer or an elastic rubber.

As will be explained in more detail below, by a clever arrangement of the spring elements in combination with the receiving elements 170 (Sliding shoes and spring plate) the function of the torsional vibration damper 100 be adapted more closely depending on the application. So it is possible, for example, a corresponding dual mass flywheel 110 or another torsional vibration damper 100 for a manual transmission, an automatic transmission, a dual-clutch transmission, a hybrid drive or another drive concept tailor-made. So it can generally be recommended the receiving elements 170 in front of the speed step elements 130 with respect to the direction of movement in the dual mass flywheel 110 catch in order to minimize friction in the driving position.

The recording elements 170 however, if necessary, the starter springs should rub so that the system does not swing up too high at engine start-up and the associated passage of the resonance speed. If necessary, the amplitude can only be minimized by a friction, that is, a corresponding damping. Depending on the specific embodiment, it can be regarded as a very rough rule of thumb, from which, however, it may and must be deviated from, that the number of captured receiving elements is less than 1 of the number of speed step springs.

The holding components 270 in this case do not necessarily have to be designed symmetrically and opposite guide components 250 to catch. Rather, it may also be possible a unilateral force absorption of the radial forces, but it may then be advisable, if necessary, the radial forces occurring over z. B. take a centering, which, however, if necessary, friction could be generated again.

A deformation, for example a bulge, of the holding components 270 under load can be optionally avoided by an appropriate design in terms of thickness, geometry and structure, so that the holding components 270 do not touch each other or grind on other components. This in turn would register friction and wear in the system. Also, corresponding multi-part holding components can be used, which can also be produced by a corresponding arrangement and connection of the items produced and by a corresponding configuration in terms of their deformation. Basically, there is the possibility of identical holding components 270 to be used together. However, retaining members having reinforcing rings, two or more half retaining members, or other ring members may be interconnected. Again, the previously mentioned connection techniques, such as riveting, crimping, welding or plugging can be used again.

In connection with the 10 to 21 Now different arrangement possibilities of spring elements 130 and differently configured receiving elements 170 described. So shows 10 already in the 1 to 5 Torsional vibration damper described in detail 100 in which all the recording elements 170 are designed as rubbing. This arrangement will hereinafter be referred to as a standard dual mass flywheel.

11 on the other hand shows a torsional vibration damper, which differs significantly from the previously described. So are all spring elements in this 130 at least with regard to their characteristics identical. In addition, all the recording elements 170 designed such that they are completely trapped, so that even until reaching a nominal maximum speed, these not in contact with the primary mass flywheel 160 reach. For this purpose, the receiving elements 170-2 , ..., 170-5 the holding components described above 270 on. But also the two outer receiving elements 170-1 . 170-6 , which with the input side 140 or the output side 150 are connected, are via corresponding holding components 270 connected with these so that they too no frictional contact with the primary mass flywheel 160 can produce.

Of course, however, can or can in a torsional vibration damper 100 one or more receiving elements 170 be designed so that this optionally with a in 11 not shown sliding surface 190 can come in contact during a rotational movement. This, that the receiving elements 170 So caught, no friction occurs here.

In the 11 embodiment shown can be used, for example, if sufficient space is available. With her are all recording elements 170 caught, so that no dynamic friction arises. In this way it may be possible to achieve the highest possible decoupling quality in pull and push operation. This arrangement may be in the form of hybrid applications with identical spring elements, for example 130 can be used, which have substantially the same c-value for all spring elements. In other words, an implementation of a starting stage may be omitted here if necessary. This may be possible, for example, when using an electric motor of the hybrid drive a corresponding counterforce when driving through the resonance of the torsional vibration damper 100 can be generated to prevent damage to this case.

Otherwise, of course, for this friction-poorest variant, any spring arrangement 120 selectable if no additional friction is required or if there are no problems with engine start with natural frequency transit.

12 shows a further arrangement possibility, which differs from the in 11 shown essentially differs in that now the primary-side spring plate, so the first receiving element 170-1 , Is designed as a rubbing receiving element. This can thus at the latest from exceeding a threshold speed with the sliding surface 190 , in turn, at the receiving elements 170 facing side of the primary mass flywheel 160 is formed and therefore with the input side 140 rotatably connected, couple. The retaining component is also corresponding 270 with respect to the first receiving element 170-1 in the embodiment of the torsional vibration damper shown here 100 omitted.

13 shows another torsional vibration damper 100 who is from the in 1 to 5 described embodiment of the torsional vibration damper 100 this distinguishes that the receiving elements 170-1 . 170-5 and 170-6 through appropriate, in 11 holding components so shown 270 are caught.

In other words, the receiving elements 170-2 . 170-3 and 170-4 configured such that they with the sliding surface 190 can come into frictional contact. Between these are the spring elements 130-2 and 130-3 arranged, which are the spring elements of the first type, that is the starting stage. At the in 13 As shown arrangement are the receiving elements 170 the starting stage rubbing while only the receiving elements 170 the step springs, so in particular the spring elements 130-4 and 130-5 are trapped. This variant allows better damping when passing the resonance point. Will also the spring element 130-1 attributed to the driving gear due to the identical configuration, ie of the same type of spring elements, can also be the last or first sliding shoe (eg receiving element 170-2 ) frictionally configured, since here the smallest movement on the sliding surface 190 occurs and this is therefore least involved in the trip decoupling.

At the in 13 The embodiment shown, the speed control spring elements 130-1 . 130-4 and 130-5 For example, they may be designed to be up to 1.3 times to 1.5 times the nominal maximum torque (motor torque MMot) responsible for travel decoupling. The friction of these spring elements 130 can be kept so comparatively low, as this on the captured recording element 170 and the corresponding holding member 270 be supported. The speed step elements 130-2 and 130-3 On the other hand, while the engine is being used, it should and can be frictionally engaged with the sliding surface 190 form, so as to achieve a resonance damping, which is why the sliding shoes of the receiving elements 170-2 . 170-3 as non-captured recording elements 170 are executed. The stop spring element 130-1 should cover in the embodiment shown here only the stop moment, so as to avoid voltage spikes, if necessary. For this reason, here friction can be positive, which is why the receiving element 170-2 with the sliding surface 190 can get in touch.

14 shows a simplified schematic representation of a torsional vibration damper 100 that differ from the in 13 shown only slightly different. More specifically, it differs essentially in that the receiving element 170-2 which is between the hard spring element 130-1 (second type) and the soft spring element 130-2 (first type) is arranged, in which the in 13 shown rubbing receiving element 170-2 against a corresponding captive receiving element 170-2 was exchanged. This has a corresponding holding member 270 on, over which the corresponding frictional contact with the sliding surface 190 this receiving element 170-2 is prevented at least at lower speeds.

At the in 14 shown arrangement for a dual mass flywheel 110 or a torsional vibration damper 100 for a drive train with a manual transmission, which two-stage with a damped starting stage (spring elements 130-2 . 130-3 and receiving element 170-3 ) is executed. Again, the driving gear is designed substantially frictionless.

In a modification not shown in the figures of a corresponding torsional vibration damper 100 In addition, the soft spring element can 130-3 possibly also against a trapped hard spring element 130-2 be exchanged, so be replaced by a spring element of the second type.

15 shows a further variant of a torsional vibration damper 100 , which can be used for example for a drive train with an automatic transmission or a dual-clutch transmission or a similar, automatically operated transmission. The corresponding torsional vibration damper 100 So has a damped starting stage, which is complemented by a frictionless drive.

So are in this torsional vibration damper 100 the first spring element 130-1 and the second spring element 130-2 designed as soft spring elements of the first type, whereas the other spring elements 130-3 . 130-4 and 130-5 are implemented as hard spring elements of the second type. The two spring elements 130-1 and 130-2 thus form the starting stage, while the three other spring elements 130-3 . 130-4 and 130-5 form the driving level.

Apart from the first receiving element 170-1 , which by a corresponding holding member 270 is caught, so are the other recording elements 170-2 and 170-3 the starting level spring elements 130-1 . 130-2 as rubbing receiving elements 170 designed. In contrast, the receiving elements 170-4 to 170-6 the speed step elements 130-3 to 130-5 via corresponding holding components 270 executed executed.

That the primary side, so with the input side 140 coupled spring element of the torsional vibration damper shown above can be omitted in this arrangement option, is essentially because it is designed for a drive train in the overload torque or abusive switching operations by a driver Transmission side by an appropriate safeguard, such as a corresponding protection circuit can be prevented. So it is, as previously explained, in the in 15 shown embodiment just by such that is provided for automatic transmission, dual-clutch transmission or other electronically connected transmission in which appropriate overload torque or abuse typically can not occur.

16 shows another torsional vibration damper 100 who is different from the one in 14 shown essentially differs in that instead of the frictional receiving elements 170-3 . 170-4 at the in 16 shown arrangement such receiving elements 170-3 . 170-4 are used, the speed independent of the sliding surface 190 be pressed so that they are independent of speed in frictional contact with the sliding surface 190 stand. In contrast to the rubbing receiving elements 170-3 . 170-4 out 14 , in which optionally the frictional contact occurs only after exceeding a threshold speed, are at the corresponding receiving elements 170 of the torsional vibration damper 100 out 16 this already at standstill, so speed independent, against the sliding surface 190 pressed.

So even at very low speeds, which may be less than the threshold speed (for example, 5% of a nominal maximum torque of the torsional vibration damper 100 ), a corresponding attenuation can be realized.

The term "speed-independent" does not mean that the force component with which the respective receiving elements 170 against the sliding surface 190 are pressed, are actually independent of speed. Rather, it merely means that a corresponding force component is already present independent of rotational speed, so that even at standstill a reliable frictional contact between the respective receiving elements already exists 170 and the sliding surface 190 consists.

Technically, this can be implemented, for example, by replacing the in 9 shown holding components 270 corresponding contact components 310 are used, which are designed according to such that they already when installed in the torsional vibration damper the relevant contact pressure of the receiving elements 170 on the sliding surface 190 exercise. If appropriate, these can also be made of one of the in connection with the holding components 270 be made of these materials. They can be made for example of a sheet-like material, which is why they are also referred to as pressing holding plates. Generally, they are also commonly used as pushing receptacles 170 designated.

The in 16 strong torsionally simplified shown torsional vibration damper 100 thus differs from the in 14 essentially in that the starting step spring elements 130-2 . 130-3 additionally by appropriate pressing receiving elements 170-3 . 170-4 are damped, while the driving level remains frictionless.

The in 17 shown torsional vibration damper 100 is similar to the one in 15 shown, and differs from this also essentially in that instead of the rubbing receiving elements 170-2 . 170-3 now also pressing receiving elements 170-2 . 170-3 be used. Also with these are corresponding Anpressbauteile 310 implemented, which in turn instead of in 9 shown holding components 270 can be used. The torsional vibration damper 100 out 17 is thus designed so that the starting stage in addition by the pressing receiving elements 170-2 . 170-3 is damped, whereas again the driving gear is completely frictionless.

In other words, the holding components 270 also be used as a friction device and thus to increase the friction, for example, for the starting stage spring elements. This can be made possible for example by the reverse design, in which the original holding components 270 by pressing components 310 be replaced, which has a defined interference fit between the receiving elements 170 and the sliding surface 190 produce. So holds the Anpressbauteil 310 the relevant guide components not radially inward, but rather pushes them to the sliding surface 190 , By the appropriate arrangement of the spring elements 130 even friction can only be generated in the starting stage. For this purpose, it may be advisable, the soft starting spring elements 130 at the end of the direction of movement of the springs in the torsional vibration damper 100 So for example the dual mass flywheel 110 to arrange at train. As a result, it may be possible that they are already in abutment during operation in the drive stage and thus no longer perform any relative movement. The speed step spring elements can then, for example, by pulling holding components 270 from the sliding surface 190 be kept completely or at least up to a free flight speed and work accordingly frictionless.

18 shows another torsional vibration damper 100 which, more specifically a three-stage torsional vibration damper 100 is. Again, this can as a dual mass flywheel 110 be used. With him, three different spring element types are used. Although this again has a total of 5 spring elements 130-1 , ..., 130-5 but having at least three different characteristics.

The first spring element 130-1 is designed here as a stop spring element of a third type, which has a correspondingly steep spring characteristic and a correspondingly high c-value. In contrast, it is the second spring element 130-2 around a soft spring element of the first type, which is the starting stage of the respective torsional vibration damper 100 forms. The other three spring elements 130-3 . 130-4 and 130-5 provide spring elements of the second type with a relation to the first and third type average characteristic. These form the spring elements of the drive. So they are softer than the first spring element 130-1 but harder than the second spring element 130-2 , Such an implementation can be done, for example, by using correspondingly thick wires.

The two edge receiving elements 170-1 and 170-6 are in turn by appropriate holding components as trapped receptacles 170 designed. In contrast, the receiving elements 170-2 . 170-3 attached to the spring element 130-2 border the start stage, designed as touching or rubbing receiving elements. The two other recording elements 170-4 . 170-5 on both sides with spring elements 130 of the second type, so the driving gear, are in contact, are by appropriate holding components 270 also designed as a prisoner.

The in 18 shown torsional vibration damper 100 thus enables an implementation of a frictional starting stage (spring element 130-2 and receiving elements 170-2 . 170-3 ) and a friction-optimized drive with the spring elements 130-3 to 130-5 , About the receiving element 170-2 is also the stop step (spring element 130-1 ) designed as rubbing.

Such as the arrangement option in 18 has shown, here are the spring elements 130 arranged in groups sorted by type. In this way, a more targeted interpretation of the characteristics of the starting stage, the gear stage and possibly the stop level, if they are implemented accordingly. Thus, thereby also an arrangement and design of the corresponding receiving elements 170 be relieved.

19 shows another torsional vibration damper 100 , in which instead of the previously shown each 5 spring elements 130-1 to 130-5 now only 3 spring elements 130-1 . 130-2 and 130-3 be used. Accordingly, this torsional vibration damper also has only 4 receiving elements 170-1 . 170-2 . 170-3 and 170-4 on, of which only the second receiving element 170-2 as rubbing or touching with respect to the sliding surface 190 is designed. The other recording elements 170-1 . 170-3 and 170-4 are here as captured recording elements 170 designed, which has corresponding holding components 270 completely or at least up to a free flight speed at a contact with the sliding surface 190 be prevented.

Optionally, the hard spring 330 possibly also omitted. Due to the design as a bow spring 320 This occurs at least in the area in which the spring 330 is implemented, from a certain speed with the sliding surface 190 in contact, so that over this a corresponding friction can be achieved.

Between the second and third receiving element 170-2 . 170-3 is as a second spring element 130-2 a combination of a bow spring 320 and an internal spring 330 designed. The spring element 130-2 is thus implemented as a combination with a partially caught bow spring, which is dimensioned as a soft bow spring and assigned according to the start level. The feather 330 in the bow feather 320 is arranged, but not completely related to the bow spring along the circumferential direction 320 extends, is designed here as a hard spring, so that the second spring element 130-2 as quasi two-stage bow spring is implemented. The second spring element 130-2 acts as a start and as a driving step.

In addition, optionally, the first spring element 130-1 Also be designed as a soft spring element or as a stop step spring element with a harder characteristic. Of course, alternatively, the receiving elements here 170-1 . 170-2 and optionally the spring element 130-1 as frictional, trapped or oppressive.

20 shows a torsional vibration damper 100 who in the 19 shown resembles. However, this is the receiving element 170-2 now as a captured receiving element with a corresponding holding member 270 designed while the third receiving element 170-3 is now implemented as rubbing or touching. In addition, the second spring element 130-2 now exclusively as a soft bow spring 320 implemented without any internal feather 330 is provided. Regardless, however, in this torsional vibration damper 100 as well the bow spring 320 with the if necessary 190 come into contact to generate a corresponding friction.

The torsional vibration damper 100 in 20 shows a combination with a partially caught soft bow spring 320 as a starting stage, of course, here again either a short inner spring, like the spring 330 in 19 can be implemented.

21 finally shows another torsional vibration damper 100 who is different from the one in 20 shown essentially differs in that now a hard bow spring 320 as a second spring element 130-2 is implemented and that the first spring element 130-1 is implemented as a soft spring element and thus as a starting stage. Even if in 21 the second receiving element 170-2 as a trapped receptacle 170 is shown, this can of course also be performed rubbing or pushing. The same applies in principle also for the captured receiving element 170-3 , this in 20 as a rubbing receiving element 170 is implemented.

torsional vibration damper 100 Thus, for example, dual-mass flywheels with captured receiving elements 170 (Sliding shoes) are implemented to minimize friction.

torsional vibration damper 100 may in principle be used in all types of propulsion for passenger cars and commercial vehicles, and for all internal combustion engines and machinery, where minimizing or decoupling of rotational irregularities is advisable or necessary, unless application or design reasons dictate otherwise. These can be combined, for example, with dual-mass flywheels of any kind, torsion dampers, outer dampers, inner dampers, torsionsgedämpften and standard clutch plates, torque converters, electric machines, absorbers of any kind, power split components, slipping clutches and other rotational nonuniformity reducing components and assemblies. Likewise, basically all types of transmissions with corresponding torsional vibration dampers 100 coupled, such as dual-clutch transmission of any kind, automatic transmission and manual transmission. Likewise, if appropriate, all types of starting elements or couplings can be used in the context of corresponding drive trains. These may include, for example, hydrodynamically cooled clutches, dual clutches, multi-plate clutches and single-disc clutches.

Of course, for example, to increase the friction at engine start torsional vibration 100 be combined with any friction, so as to allow damping particularly when passing through resonance speeds. Such friction devices include, among others, friction disks for high friction at high vibration angles and small friction at correspondingly small vibration angles. Likewise, this may include viscous friction devices and other components. Optionally, it may be useful at this point to arrange them in such a way that they have as little or as little effect as possible in the driving gear, on the one hand, to minimize friction and thereby correspondingly not impair the damping effect.

torsional vibration damper 100 Thus, for example, with pulling flyers, but also with pressing fliers, so corresponding recording elements 170 be implemented. A torsional vibration damper 100 Thus, for example, at least two different types of spring in a spring set or a spring arrangement 120 so that its characteristic is at least two stages. Likewise, in such a torsional vibration damper 100 at least two different types of spring-passing elements, ie receiving elements 170 to be implemented. For example, one of these at least two types may be a pulling member 170 include. Such is in accordance with the spring arrangement 120 also active. Likewise, the at least one trapped flier in the pulling direction between a first and a second spring element 130 be arranged. The first spring element in the pulling direction can thus be deflected in operation up to a spring moment which corresponds to at least 1.1 times a maximum engine torque.

Likewise, optionally pressing receiving elements or pressing Anpressbauteile 310 be used. Likewise, optionally at least one spring element 130 the spring arrangement 120 be designed for a stop moment of at least 1.3 times the maximum engine torque. Optionally, moreover, at least one non-captured receiving element 170 in the spring arrangement 120 includes his.

torsional vibration damper 100 can be used depending on the configuration as a two-stage torsional vibration damper for a manual transmission, as a three-stage variant of a manual transmission and for automated transmission.

As already explained at the outset, it goes without saying that torsional vibration dampers can be used 100 different numbers of receiving elements 170 and spring elements 130 be used. The torsional vibration damper shown in the present description with 5 or 3 spring elements 130 are therefore to be understood as exemplary only. Also, in the present specification, the sliding surface 190 always with the input side 140 been rotatably connected. Again, with other torsional vibration dampers 100 optionally a non-rotatable connection with the output side 150 be implemented. This can be done, for example, that the hub disc is designed accordingly or the role of input side 140 and home page 150 in a torsional vibration damper 100 be reversed.

Through the use of a torsional vibration damper 100 According to one embodiment, it may be possible to improve a compromise between its reliability and its operability.

The features disclosed in the foregoing description, the appended claims and the appended figures may be taken to be and effect both individually and in any combination for the realization of an embodiment in its various forms.

LIST OF REFERENCE NUMBERS

100

torsional vibration damper

110

Dual Mass Flywheel

120

spring assembly

130

spring element

140

input side

150

output side

160

Primary mass flywheel

170

receiving element

180

connection structure

190

sliding surface

200

countersliding

210

traction torque

220

characteristics

230

partial signature

240

crossing

250

guiding member

260

axial direction

270

holding member

280

recess

290

rivet

300

guiding member

310

pressing member

320

bow spring

330

feather

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• EP 1584838 A1 [0005]
• DE 102007016744 A1 [0005]
• US 4360352 [0005]

Claims (18)

Torsional vibration damper ( 100 ), for example for a drive train of a vehicle, having the following features: a spring arrangement ( 120 ) with a plurality of spring elements ( 130 ) between an input page ( 140 ) of the torsional vibration damper ( 100 ) and an output side ( 150 ) of the torsional vibration damper ( 100 ) are arranged one behind the other in an order; and a plurality of receiving elements ( 170 ), wherein between each two adjacent spring elements ( 130 ) each a receiving element ( 170 ) of the plurality of receiving elements ( 170 ) is arranged. Torsional vibration damper ( 100 ) according to claim 1, further comprising a sliding surface ( 190 ) connected to the input side ( 140 ) or the output side ( 150 ) is non-rotatably coupled, wherein the spring arrangement ( 120 ) at least two different types of spring elements ( 130 ), wherein the plurality of receiving elements ( 170 ) at least two different types of receiving elements ( 170 ), wherein a receiving element ( 170 ) of a first type of the at least two different types is designed such that it reaches a speed of the input side ( 140 ) and / or the output side ( 150 ), which is less than a free flight speed, from the sliding surface ( 190 ) is spaced along a radial direction, and wherein the plurality of receiving elements ( 170 ) at least one receiving element ( 170 ) of the first type. Torsional vibration damper ( 100 ) according to claim 2, wherein the at least one receiving element ( 170 ) of the first type between a first and a second spring element ( 130 ) and / or between a penultimate and a last spring element ( 130 ) according to the order of the spring elements ( 130 ) is arranged. Torsional vibration damper ( 100 ) according to one of the preceding claims, wherein the first and / or the last spring element ( 130 ) is formed according to the order of the spring elements such that this spring element ( 130 ) at least up to one in the input side ( 140 ) or the output side ( 150 ) introduced torque corresponding to at least 110% of a nominal maximum torque. Torsional vibration damper ( 100 ) according to one of the preceding claims, further comprising a sliding surface ( 190 ) connected to the input side ( 140 ) or the output side ( 150 ) is rotatably coupled, wherein at least one receiving element ( 170 ) of the plurality of receiving elements ( 170 ) is designed such that it is independent of rotational speed against the sliding surface ( 190 ) to be in a frictional contact with this speed independently. Torsional vibration damper ( 100 ) according to one of the preceding claims, further comprising a sliding surface ( 190 ) connected to the input side ( 140 ) or the output side ( 150 ) is rotatably coupled, wherein at least one receiving element ( 170 ) of the plurality of receiving elements ( 170 ) is designed such that it with the sliding surface ( 190 ) can come into frictional contact. Torsional vibration damper ( 100 ) according to one of the preceding claims, in which at least one spring element ( 130 ) of the spring arrangement ( 120 ) is designed such that this spring element ( 130 ) at least up to one in the input side ( 140 ) or the output side ( 150 ) introduced torque corresponding to at least 130% of a nominal maximum torque. Torsional vibration damper ( 100 ) according to one of the preceding claims, further comprising a sliding surface ( 190 ) connected to the input side ( 140 ) or the output side ( 150 ) is rotatably coupled, wherein at least one receiving element ( 170 ) of the plurality of receiving elements ( 170 ) is designed so that this at a speed of the input side ( 140 ) and / or the output side ( 150 ), which is above a threshold speed, with the sliding surface ( 190 ) enters a frictional contact. Torsional vibration damper ( 100 ) according to one of the preceding claims, wherein the spring arrangement ( 120 ) at most two different types of spring elements ( 130 ), wherein the spring elements ( 130 ) of the spring arrangement ( 120 ) and the receiving elements ( 170 ) of the plurality of receiving elements ( 170 ) are formed such that the to the spring elements ( 130 ) of a first type of the at most two types of adjacent receiving elements ( 170 ) at one in the input side ( 140 ) or the output side ( 150 ) introduced torque of at most 100% of a nominal maximum torque are movable relative to each other. Torsional vibration damper ( 100 ) according to claim 9, wherein the spring elements ( 130 ) of the spring arrangement ( 120 ) and the receiving elements ( 170 ) of the plurality of receiving elements ( 170 ) are formed such that all receiving elements ( 170 ) are stationary in transmitting a rotational movement having a torque of at least 120% of the nominal maximum torque relative to each other. Torsional vibration damper ( 100 ) according to one of claims 9 or 10, in which all spring elements ( 130 ) of a type adjacent to each other and at most one spring element ( 130 ) of any type adjacent to a spring element ( 130 ) of the other type is arranged. Torsional vibration damper ( 100 ) according to one of claims 9 or 10, in which all spring elements ( 130 ) of a second type different from the first type of the at most two types of spring elements ( 130 ) are arranged adjacent to each other, wherein the spring arrangement ( 120 ) at least three spring elements ( 130 ) of the first type, wherein all spring elements ( 130 ) of the first type except for a single spring element ( 130 ) of the first type are arranged adjacent to each other, and wherein the spring elements ( 130 ) of the second type between the spring elements ( 130 ) of the first type are arranged. Torsional vibration damper ( 100 ) according to claim 12, further comprising a sliding surface ( 190 ) connected to the input side ( 140 ) or the output side ( 150 ) is rotatably coupled, wherein at least one receiving element ( 170 ), which with the just a single spring element ( 130 ) of the first type is formed so that it at a rotational speed of the input side ( 140 ) and / or the output side ( 150 ), which is above a threshold speed, with the sliding surface ( 190 ) enters a frictional contact. Torsional vibration damper ( 100 ) according to one of claims 9 to 13, in which the to the spring elements ( 130 ) of a second type of at most two types are formed such that contact elements ( 170 ) at one in the input side ( 140 ) or the output side ( 150 ) introduced torque corresponding to at least one starting torque value, are stationary relative to each other. Torsional vibration damper ( 100 ) according to one of claims 9 to 14, further comprising a sliding surface ( 190 ) connected to the input side ( 140 ) or the output side ( 150 ) is rotatably coupled, wherein at least one receiving element ( 170 ), which on both sides with a spring element ( 130 ) of the first type, are formed so that this up to a rotational speed of the input side ( 140 ) and / or the output side ( 150 ), which is less than a free flight speed, from the sliding surface ( 190 ) is spaced along a radial direction. Torsional vibration damper ( 100 ) according to claim 15, wherein all the receiving elements, which on both sides with a spring element ( 130 ) of the first type, are formed so that they are up to a rotational speed of the input side ( 140 ) or the output side ( 150 ), which is less than the free flight speed, of the sliding surface ( 190 ) are spaced along a radial direction. Torsional vibration damper ( 100 ) according to one of claims 1 to 8, in which the spring arrangement ( 120 ) exactly one spring element ( 130 ) of a first type, exactly one spring element ( 130 ) of a third type and at least one spring element ( 130 ) of a second type, wherein the spring element ( 130 ) of the first type and the adjacent thereto receiving elements ( 170 ) are formed such that the receiving elements ( 170 ) at one in the input side ( 140 ) or the output side ( 150 ), which corresponds to at least one predetermined starting torque value, are stationary relative to one another, wherein the spring element ( 130 ) of the third type and the adjacent thereto receiving elements ( 170 ) are formed such that the adjacent to this receiving element ( 170 ) when a maximum torque of 130% of the nominal maximum torque is applied to the input side ( 140 ) or the output side ( 150 ) relative to each other and upon introduction of a torque of at least 150% of the nominal maximum torque in the input side ( 140 ) or the output side ( 150 ) are stationary relative to each other, and wherein the at least one spring element ( 130 ) of the second type and the at least one spring element ( 130 ) of the second type adjacent receiving elements ( 170 ) are formed such that the to the at least one spring element ( 130 ) of the second type adjacent receiving element ( 170 ) when a maximum torque of 100% of the nominal maximum torque is applied to the input side ( 140 ) or the output side ( 150 ) relative to each other and upon introduction of a torque of at least 120% of the nominal maximum torque in the input side ( 140 ) or the output side ( 150 ) are stationary relative to each other. Torsional vibration damper ( 100 ) according to claim 16, further comprising a sliding surface ( 190 ) connected to the input side ( 140 ) or the output side ( 150 ) is non-rotatably coupled, wherein the spring arrangement ( 120 ) at least two spring elements ( 130 ) of the third type, wherein at least the receiving element ( 170 ), which on both sides with a spring element ( 130 ) of the third type, are formed so that they are up to a rotational speed of the input side ( 140 ) and / or the output side ( 150 ), which is less than one Free-running speed is, from the sliding surface ( 190 ) is spaced along a radial direction.

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