DE102016225865A1 - Torsional vibration damping arrangement for the drive train of a vehicle - Google Patents

Abstract

A torsional vibration damping arrangement for the drivetrain of a vehicle, comprising an input section (50) to be driven for rotation about an axis of rotation (A) and an output section (55), a first torque transmission path (47) between the input section (50) and the output section (55) a second torque transmission path (48) and a coupling arrangement (51) are provided in parallel therewith, wherein a phase shifter arrangement (44) is provided in the first torque transmission path (47), wherein the coupling arrangement (51) is designed as a fluid transmission (60).

Description

The present invention relates to a torsional vibration damping arrangement for the drive train of a vehicle, comprising an input range to be driven for rotation about an axis of rotation and an output range, wherein between the input range and the output range a first torque transmission path and parallel thereto a second torque transmission path and a coupling arrangement for superposition of the torque transmission paths are provided in the first torque transmission path, a phase shifter arrangement for generating a phase shift of rotational irregularities guided over the first torque transmission path with respect to rotational irregularities conducted over the second torque transmission path.

From the German patent application DE 10 2011 007 118 A1 a torsional vibration damping arrangement is known, which divides the introduced into an input area, for example, by a crankshaft of an internal combustion engine in a torque transmitted via a first Drehmomentübertragungsweg torque component and a torque transmission path via a second torque transmission. In this torque distribution, not only a static torque is divided, but also the vibrations contained in the torque to be transmitted or rotational irregularities, for example, generated by the periodically occurring ignitions in an internal combustion engine, are proportionally divided between the two torque transmission paths. Here, the coupling arrangement brings the two torque transmission paths together again and introduces the combined total torque into the output region, for example a friction clutch or the like.

In at least one of the torque transmission paths, a phase shifter arrangement is provided, which is constructed in the manner of a vibration damper, that is to say with a primary element and by means of the compressibility of a spring arrangement with respect to this rotatable intermediate element. In particular, when this vibration system is in a supercritical state, that is excited with vibrations that are above the resonant frequency of the vibration system, a phase shift of up to 180 ° occurs. This means that at maximum phase shift, the vibration components emitted by the vibration system are phase-shifted by 180 ° with respect to the vibration components picked up by the vibration system. Since the vibration components routed via the other torque transmission path experience no or possibly a different phase shift, the vibration components contained in the merged torque components and then phase-shifted with respect to each other can be destructively superimposed on one another, so that in an ideal case the total torque introduced into the output region has essentially no vibration components contained static torque is. In this case, the coupling arrangement is designed as a planetary gear.

Also from the DE 10 2011 086 982 A1 is a torsional vibration damping arrangement as just described known, but here the coupling arrangement is designed as a lever mechanism.

It is the object of the present invention to provide a torsional vibration damping arrangement which, with a simple construction, has an improved vibration damping behavior.

According to the invention, this object is achieved by a torsional vibration damping arrangement for a drive train of a vehicle, comprising an input region to be driven for rotation about a rotation axis and an output region, between the input region and the output region parallel to each other a first torque transmission path for transmitting a first torque component and a second torque transmission Torque transmission path for transmitting a second torque component of a total torque to be transmitted between the input portion and the output range, a phase shifter assembly at least in the first torque transmission path, for generating a phase shift of rotational irregularities conducted over the first torque transmission path with respect to rotational irregularities conducted via the second torque transmission path, the phase shifter assembly being a vibration system with a primary element and a g egen the restoring effect of a damper element arrangement with respect to the primary element about the axis of rotation (A) rotatable intermediate mass comprises a coupling arrangement for combining the transmitted over the first Drehmomentübertragungsweg first torque component and transmitted via the second Drehmomentübertragungsweg second torque component and for forwarding the combined torque to the output range, said the coupling arrangement comprises a first input element connected to the first torque transmission path, a second input element connected to the second torque transmission path and an output element connected to the output range, wherein the coupling arrangement is designed as a fluid transmission. In this case, the fluid transmission comprises at least one housing element, a first Cylinder and a second cylinder, both of which are arranged in the housing member and are connected to each other by means of a connection opening, and a pair of pistons, comprising a first piston and a second piston, which are mutually displaceable in the respective cylinders of the housing member by means of an active medium in opposite directions. In this case, one of the two pistons is connected to the output of the phase shifter arrangement and thus represents the first input element of the coupling arrangement, whereas the other of the two pistons is connected to the direct torque transmission path, which thus represents the second input element of the coupling arrangement. The housing element represents the output element of the coupling arrangement and is advantageously connected to the output area, for example to a starting clutch or a transmission. If a torque with torsional vibrations is introduced from the input area, then the torque branches to the first and the second torque transmission path. In the first torque transmission path, the phase shifter arrangement is provided, whereas the second torque transmission path runs directly, ie rigidly from the input side. In the torque transmission from the input region to the output region of the second piston, which is connected to the direct, ie rigid torque transmission path, displaced in the second cylinder of the housing member and exerts a force on its piston surface on the active medium. Since the second cylinder is connected to the first cylinder by means of the connection opening, the active medium exerts a counteracting force on the surface of the first piston, which performs a counter to the second piston movement and biases the vibration system, which consists mainly of springs. If a force equilibrium has been established between the two piston surfaces, a resultant force and thus a resulting torque acting on the output element acts on the output element by means of the housing element, more precisely by means of the cylinder rear walls. Consequently, a static moment is transmitted from the input area to the output area. The dynamic component contained in the static torque, the torsional vibrations are ideally extinguished by swinging the active medium against the vibration system, the spring-mass system, and not transmitted to the output range.

By a ratio of the piston surfaces of the first and second cylinders, a transmission ratio of the coupling arrangement can be adjusted. This type of ratio change is compared to the known in the prior art embodiments, in which the coupling arrangement is designed as a planetary gear or a lever mechanism, implement cost and quickly, since only the effective piston area must be changed.

It may also be advantageous if the cylinders have a curved or straight course in the housing element.

Further, as the active medium, an incompressible medium, such as a hydraulic fluid, an oil or any other known and suitable liquid or even a viscous medium can be used.

It may also be advantageous if a plurality of fluid transmission are distributed uniformly or non-uniformly in the circumferential direction about the axis of rotation A.

Also, a gear ratio of the fluid transmission may be determined by a ratio of the piston areas of the first and second pistons.

• 1 das Grundprinzip einer Drehschwingungsdämpfungsanordnung mit zwei parallelen Drehmomentübertragungswegen als Stand der Technik.
• 2 das Grundprinzip einer Drehschwingungsdämpfungsanordnung mit einem Planetengetriebe als Koppelanordnung als Stand der Technik
• 3 eine Schwingungsdämpfungsanordnung in einem linearen Modell mit einer Hebelkoppelanordnung als Stand der Technik
• 4 - 8 verschiedene Übersetzungen wie in 3 dargestellt als Stand der Technik
• 9 eine erfindungsgemäße Schwingungsdämpfungsanordnung in einem linearen Modell mit einem Fluidgetriebe als Koppelanordnung
• 10 eine Schnittansicht einer erfindungsgemäßen Drehschwingungsdämpfungsanordnung mit einem Fluidgetriebe als
• 11 eine Drehschwingungsdämpfungsanordnung aus 10 als Draufsicht im Bereich der Koppelanordnung.

The present invention will be described below in detail with reference to the accompanying drawings. It shows:

• 1 the basic principle of a torsional vibration damping arrangement with two parallel torque transmission paths as prior art.
• 2 the basic principle of a torsional vibration damping arrangement with a planetary gear as a coupling arrangement as prior art
• 3 a vibration damping arrangement in a linear model with a lever coupling arrangement as prior art
• 4 - 8th different translations as in 3 represented as prior art
• 9 a vibration damping arrangement according to the invention in a linear model with a fluid transmission as a coupling arrangement
• 10 a sectional view of a torsional vibration damping arrangement according to the invention with a fluid transmission as
• 11 a torsional vibration damping arrangement 10 as a plan view in the region of the coupling arrangement.

With reference to the 1 Hereinafter, a first embodiment of a generally designated 10 torsional vibration damping arrangement is described, which operates on the principle of power or torque split. The torsional vibration damping arrangement 10 may be in a powertrain, such as a vehicle between a prime mover and the following part of the powertrain, For example, a transmission, a friction clutch, a hydrodynamic torque converter or the like can be arranged.

The in the 1 Schematically illustrated torsional vibration damping arrangement 10 includes an input area, generally designated 50. This entrance area 50 For example, by screwing to a crankshaft, not shown, a drive unit 61 be connected. In the entrance area 50 this branches off from the drive unit 61 recorded torque in a first torque transmission path 47 and a second torque transmission path 48 on. In the area of a generally designated 51 coupling arrangement, the over the two torque transmission paths 47 . 48 guided torque components Ma1 and Ma2 again to an output torque mouse merged and then to an exit area 55 For example, here through a gearbox 63 can be executed, forwarded.

In the first torque transmission path 47 is integrated with a generally designated 56 vibration system. The vibration system 56 is as a phase shifter arrangement 44 effective and includes a example to be connected to the drive unit primary element 1 , as well as a torque transmitting secondary element 2 , Here is the primary element 1 against a damper element assembly 4 to the intermediate mass 5 relatively rotatable.

From the foregoing description, it can be seen that the vibration system 56 in the manner of a torsional vibration damper with a, as shown here, or more spring sets 4 is trained. By a selection of the masses of the primary element 1 and the intermediate mass 5 , as well as the stiffness of the spring sets or the 4 For example, it becomes possible to set a resonant frequency of the oscillation system 56 in a desired range to obtain a favorable phase shift of torsional vibrations in the first torque transmission path 47 to the torsional vibrations in the second torque transmission path 48 to reach. To achieve this, the first torque transmission path 47 operated supercritically. At the same time, the oscillation amplitude in the phase-shifted torque transmission path also decreases 47 after the spring set 4 , In the second torque transmission path 48 If possible, the phase position of the torsional vibrations should be maintained. To achieve this, this way is carried out as stiff as possible and with low inertia. The coupling arrangement 51 the torsional vibration damping arrangement 10 leads the two torque components Ma1 and Ma2 together again. This is done by the two torque components Ma1 and Ma2 and thus the torsional vibration components are superimposed in the form that in an optimal case with a 180 ° phase shift of the two torsional vibration components and the same amplitude of the two torsional vibration components in the two torque transmission paths 47 . 48 after the overlay in the coupling arrangement 51 a torque mouse without torsional vibration components at the exit area 55 is forwarded.

Here is a translation of the coupling arrangement, a spring characteristic and an inertia of the intermediate mass 5 are to be chosen so that the amplitude ratios of both torque paths 47 ; 48 are the same and thus the vibration components cancel each other out. The translation also determines how much torque is required via the phase-shifted torque transmission path 47 and thus on the spring set 4 and how much torque through the direct torque transmission path 48 runs.

In the 2 is a standard schematic of the interconnection of a torsional vibration damping arrangement 10 shown with two torque transmission paths. Here is the coupling arrangement 51 as a planetary gear 6 executed. This is a planet carrier 8th of the planetary gear 6 non-rotatable with the primary element 1 connected. The phase-shifted torque path 47 is by means of a drive ring gear 9 with the primary element 1 connected. The drive ring gear 9 meshes with a planetary gear 13 that is rotatable on the planet carrier 8th is stored and thus provides the intermediate mass 5 dar. With the planetary gear 13 is another output-side planetary gear 11 rotatably connected. The driven-side planetary gear 11 meshes with a driven ring gear again 12 , wherein the Abtiebshohlrad 12 the secondary element 2 forms and the initial element 40 the coupling arrangement 51 represents. In this circuit variant stand translations of greater than 1.0 to 1.5 are the most meaningful, since thus a good decoupling result can be achieved. The planet carrier 8th is here in the direct torque transmission path 48.

The 3 shows a vibration damping arrangement in a linear model with a lever coupling arrangement as prior art. For a better understanding, the reference symbols which are also used in a rotational vibration reduction are used here for the explanation, since the function of the elements is comparable. Instead of a torque M in the rotational vibration reduction, a force F is transmitted in the linear vibration reduction. This is the purpose of the different translations of the coupling arrangement 51 depending on the location of the connection of the output element 40 be explained. In the vibration damping arrangement with two transmission paths 47 ; 48 with lever coupling gear are the phase-shifted transmission path 47 which transmits a first force component and the direct transmission path 48 , which transmits a second share of force, via a coupling element 17 by means of coupling joints 29 articulated and thus transmit a total force fges from the entrance area 50 to the exit area. The starting element 40 the coupling arrangement 51 , which is also the output of the merged force Faus from the coupling arrangement 51 is also articulated, advantageously by means of a hinge connection 28 , with the coupling element 17 connected. Depending on a connection position of the output member 40, the translation of the linkage can be divided into the following 5 ways that in the 4 to 8th are shown individually.

Here, the definition of the translation i has to be specified.

For a rotating system, the gear ratio means:
i = torque at output / torque in phase shift path

For a linear system, the gear ratio means:
i = power at the output / force in the phase shift path

Here, the angle influences should be neglected. The consideration should apply to small angles.

The following applies to the following transmission ratios.

0 <i <1 means a connection of the output element 40 on the coupling element 17 outside the coupling joints 29 the direct and indirect transmission path on the side of the phase-shifted transmission path 47 ,

i = 1 means a connection of the output element 40 on the coupling element 17 directly at the coupling joint 29 the phase-shifted transmission path 47 , There is no division of the force or the torque. The entire force or the entire moment is passed over the spring set and is therefore comparable to the rotary system with a known dual mass flywheel.

i> 1 means a connection of the output element 40 on the coupling element 17 between the coupling joints 29 the direct and the phase-shifted transmission path 48 ; 47 , This is the advantageous design range for a known torsional vibration damping arrangement with two torque transmission paths.

i = ∞ means a connection of the output element 40 on the coupling element 17 directly at the coupling joint 29 the direct transmission path 48 , There is no division of the transmission path from the input area 50 to the exit area 55 , The entire force fges or the entire torque mges is via the direct transmission path 48 directed. The spring set 4 is thus bypassed and thus switched off. All suggestions are forwarded directly.

i <0 means a connection of the output element 40 on the coupling element 17 outside the coupling joints 29 the direct and the phase-shifted transmission path on the side of the direct transmission path 48 ,

By a shift of the articulated connection of the output element 40 along the coupling element 17 Thus, a translation of the coupling arrangement 51 to be changed.

In an ideal interpretation of the translation is the articulated connection of the output element 40 in a vibration node.

The 9 shows a vibration damping arrangement according to the invention in a linear model with a fluid transmission 60 as a coupling arrangement 51 in the case of a total force fges over a first transmission path 47 with a first portion of force and a second transmission path 48 with a second share of force f a2 by means of the fluid transmission as an output force Faus to an output element of the fluid transmission 60 is transmitted. The wiring scheme is similar to that of a lever linkage. The coupling of the phase-shifted and the direct transmission path 47 ; 48 However, this does not take place via a lever or a planetary gear, as known from the prior art, but by an active medium 70, such as a hydraulic fluid 71 , as an incompressible medium.

The control takes place via a first piston 65 , with the phase-shifted transmission path 47 is connected and in a first cylinder 67 a housing element 64 is displaceable and via a second piston 66 that with the direct transmission path 48 is connected and in a second cylinder 68 of the housing element 64 is displaceable. In this case, the first cylinder with the second cylinder via a connection opening 36 connected with each other. The active medium 70 , here as hydraulic fluid 71 executed, puts between the two pistons 65 and 66 an active compound ago. The housing element 64 is with the starting element 40 firmly connected.

A translation is determined by the ratio of piston areas AK2 from the direct transmission path 48 to the piston surface AK1 from the phase-shifted transmission path 47 represented.
i = 1 + (AK2_direkt / AK1_phasenverschoben) or
i = 1 + | (piston_path_direct / piston_path_phase_shifted) |

In this case, only translations i, according to the above definition, in the range> = 1 can be achieved by adapting the piston surfaces. The basic principle is a hydraulic power transmission. The arrangement of the pistons 65 ; 66 must be done so that an opposite movement of the direct 48 and the phase-shifted transmission path 47 he follows. Background is the compression of the spring set 4 by the static force component, in the linear model or by the torque component in the rotary model, and the antiphase oscillatory component of the output signal of the spring assembly 4 based on the in-phase oscillation component of the direct transmission path 48 ,

The 10 shows with the 11 a constructive design of a torsional vibration damping arrangement 10 with two torque transmission paths and a fluid transmission 60 as a coupling arrangement 51 , In this case, the fluid transmission comprises 60 a hydraulic unit of a first and a second piston 65 ; 66 in a first and a second cylinder 67 ; 68 are displaceable and executed here by way of example in a curved form.

When applying a torque mges shifts stiff in the direction of movement of the primary element 1 attached second piston 66 the direct torque transmission path 48 in the second cylinder 68 and acts on the piston surface AK2 by means of the active medium 70 , here the hydraulic fluid 71 , on the piston surface AK1 of the first piston 65 that by means of a spring set 4 with the primary element 1 connected, a force out. Due to the inertia of the output element 40 on the one hand with the housing element 64 and on the other hand, the output of the torsional vibration damping arrangement 10 represents and, for example, with a transmission or a starting clutch, both not shown here, may be connected, the output element remains 40 in each state and will not be accelerated. By the force acting on the piston surface AK1 of the first piston, the spring set 4 compressed. The two pistons 65 ; 66 are shifted in opposite directions until a force equilibrium or moment equilibrium sets in. At least now is the torque mges about the active medium 70 over a cylinder rear wall 69 on the starting element 40 transmitted as a mouse. A dynamic vibration component is ideally by swinging the active medium 70 , here the hydraulic fluid 71 against the spring-mass system in the phase-shifted torque transmission path 47 extinguished and not on the secondary element 2 , here the starting element 40 transfer. The piston seals 75 ; 76 on the first and second pistons 65 ; 66 the phase-shifted and the direct torque transmission path 47 ; 48 seal the cylinder interior 80 with the active medium 70 from the environment.

LIST OF REFERENCE NUMBERS

1.

primary element

2

secondary element

Third

Damper element assembly

4th

spring set

5

intermediate mass

6

planetary gear

8th

planet

9

drive internal gear

10

Torsional vibration damping arrangement

11

output-side planetary gear

12

output ring

13

planet

17

coupling element

20

first input element

28

articulation

29

coupling joint

30

second input element

36

connecting opening

40

output element

44

Phase shifter arrangement

47

first torque transmission path

48

second torque transmission path

50

entrance area

51

coupling arrangement

55

output range

56

vibration system

60

fluid transmission

61

power unit

62

piston pair

63

transmission

64

housing element

65

first piston

66

second piston

67

first cylinder

68

second cylinder

69

Cylinder rear panel

70

active medium

71

hydraulic fluid

75

piston seal

76

piston seal

80

Cylinder interior

A

axis of rotation

AK1

Piston surface of the first cylinder

AK2

Piston surface second cylinder

d1

Diameter of the first piston

d2

Diameter second piston

mges

total torque

Ma1

Torque share 1

Ma1

Torque share 2

mouse

output torque

fges

total power

fa1

Force share 1

f a2

Force share 2

Faus

output power

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

• DE 102011007118 A1 [0002]
• DE 102011086982 A1 [0004]

Claims (13)

A torsional vibration damping arrangement (10) for a drive train of a motor vehicle, comprising an input region (50) to be driven for rotation about an axis of rotation (A) and an output region (55), a first torque transmission path parallel to each other between the input region (50) and the output region (55) (47) for transmitting a first torque component (Ma1) and a second torque transmission path (48) for transmitting a second torque component (Ma2) between the input region (50) and the output region (55) to be transmitted total torque (Mges) are provided - a Phase shifter means (44) at least in the first torque transmission path (47) for producing a phase shift of rotational irregularities conducted via the first torque transmission path (47) with respect to rotational nonuniformities directed via the second torque transmission path (48), the phase shifter assembly (44) being a vibratory system tem (56) with a primary element (1) and against the restoring action of a damper element arrangement (3) with respect to the primary element (1) about the axis of rotation (A) rotatable intermediate mass (5), - a coupling arrangement (51) for merging the over the first torque transmission path (Ma1) and the second torque transmission path (48) transmitted second torque component (Ma2) and for forwarding the combined torque (mouse) to the output region (55), wherein the coupling assembly (51) a first Input element (20) connected to the first torque transmission path (47), a second input element (30) connected to the second torque transmission path (48) and an output element (40) connected to the output region (55), characterized in that the Coupling arrangement (51) is designed as a fluid transmission (60). Torsional vibration damping arrangement (10) according to Claim 1 , characterized in that the fluid transmission (60) comprises at least one pair of pistons (62), a housing element (64) and an active medium (70). Torsional vibration damping arrangement (10) according to Claim 2 characterized in that the pair of pistons (62) comprises a first piston (65) and a second piston (66), the housing member (64) comprising a first cylinder (67) and a second cylinder (68), the first cylinder (67) and the second cylinder (68) are interconnected by means of a connection opening (36). Torsional vibration damping arrangement (10) according to Claim 3 , characterized in that the first piston (65) in the first cylinder (67) and the second piston (66) in the second cylinder (68) is slidably disposed, wherein the two pistons (65, 66) by means of the active medium (70 ) are in operative connection. Torsional vibration damping arrangement (10) according to Claim 3 or 4 , characterized in that one of the two pistons (65, 66) is connected to the first input element (20) of the coupling arrangement (51) and that the other of the two pistons (66, 65) is connected to the second input element (30) of the coupling arrangement (30). 51) and wherein the housing member (64) is connected to the output member (40). Torsional vibration damping arrangement (10) according to one of Claims 3 to 5 , characterized in that at a relative change in position of one of the two pistons (65; 66) to the housing member (64) of the other of the two pistons (66, 65) changes its position in opposite directions. Torsional vibration damping arrangement (10) according to one of Claims 2 to 6 , characterized in that a diameter d1 of the first piston (65) is greater than or equal to or smaller than a diameter d2 of the second piston (66). Torsional vibration damping arrangement (10) according to one of Claims 3 to 7 , characterized in that the first and the second cylinder (67, 68) have a curved course or a straight course. Torsional vibration damping arrangement (10) according to one of Claims 3 to 7 , characterized in that one of the two cylinders (67; 68) has a curved course and the other of the two cylinders (68; 67) has a straight course. Torsional vibration damping arrangement (10) according to one of Claims 2 to 9 , characterized in that the active medium (70) is an incompressible medium. Torsional vibration damping arrangement (10) according to Claim 10 , characterized in that the incompressible medium is a fluid. Torsional vibration damping arrangement (10) according to one of Claims 1 to 11 , characterized in that in the circumferential direction about the axis of rotation (A) two or more fluid transmission (60) are distributed uniformly or non-uniformly. Torsional vibration damping arrangement (10) according to one of Claims 3 to 12 , by characterized in that a transmission ratio of the coupling arrangement (51) is determined by a ratio of the piston surfaces (AK1; AK2) of the first and second pistons (65; 66).

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