CN110088501B - Torsional vibration damper arrangement for a drive train of a vehicle - Google Patents

Abstract

A torsional vibration damping device for a drive train of a vehicle, comprising: an input region (50) and an output region (55) drivable to rotate about an axis of rotation (A), wherein the input region (50) and the output region ( 55) between a first torque transmission path (47) and a second torque transmission path (48) parallel to it and a coupling device (51), wherein a phase shift device is provided in the first torque transmission path (47) (44), wherein the coupling device (51) is designed as a fluid transmission (60).

Description

Torsional vibration damping device for the drive train of a vehicle

technical field

The invention relates to a torsional vibration damping device for a drive train of a vehicle, comprising an input region and an output region drivable for rotation about an axis of rotation, wherein between the input region and the output region a first torque transmission path and A second torque transmission path is provided parallel thereto, and a coupling device for superimposing the torque guided via the torque transmission path is provided, wherein a phase shift device is provided in the first torque transmission path for generating the first torque transmission path. The phase shift of the rotational non-uniformity directed by the torque transfer path relative to the rotational non-uniformity directed via the second torque transfer path.

Background technique

From German patent application DE 10 2011 007 118 A a torsional vibration damping device is known, which divides the torque introduced, for example, by the crankshaft of an internal combustion engine into the input region into a torque component transmitted via a first torque transmission path and a second torque The torque component guided by the transfer path. In the case of this torque distribution, not only the static torque is distributed, but also the vibrations or rotational inhomogeneities contained in the torque to be transmitted are distributed proportionally to the two torque transmission paths, wherein the vibrations or rotational inhomogeneities are Properties are generated, for example, by cyclically occurring ignitions in internal combustion engines. The coupling device here again joins the two torque transmission paths and conducts the combined total torque into the output region, for example into the friction clutch or the like.

At least one of the torque transmission paths is provided with a phase shift device, which is designed according to the type of vibration damper, ie with a primary element and an intermediate element, which is rotatable relative to it due to the compressibility of the spring device. A phase shift of up to 180° occurs in particular when the vibratory system transitions into a supercritical state, ie is excited by means of vibrations exceeding the resonance frequency of the vibratory system. This means that with the maximum phase shift, the vibration component output by the vibration system is phase shifted by 180° relative to the vibration component absorbed by the vibration system. Since the vibration components conducted via the other torque transmission path are not subject to a phase shift or, if necessary, a different phase shift, the vibration components contained in the combined torque components and subsequently phase-shifted relative to one another are superimposed with respect to one another in a reduced manner, so that Ideally, the total torque introduced into the output region is a static torque substantially free of vibration components. In this case, the coupling device is designed as a planetary gear.

A torsional vibration damping device as just described is known from DE 10 201 1 086 982 A1, but here the coupling device is designed as a lever gear.

SUMMARY OF THE INVENTION

The object of the present invention is to propose a torsional vibration damping device which has improved damping properties with a simple structure.

According to the invention, the object is achieved by a torsional vibration damping device for a drive train of a motor vehicle, comprising: an input region and an output region drivable for rotation about an axis of rotation (A), wherein the input region and the output region A first torque transmission path and a second torque transmission path for transmitting a first torque component of the total torque transferable between the input and output regions and a second torque transmission path are provided parallel to each other between the regions. Two torque transfer paths for transferring a second torque component; phase shifting means in at least the first torque transfer path to create rotational non-uniformity directed via the first torque transfer path relative to rotation directed via the second torque transfer path A phase shift of inhomogeneities, wherein the phase shift device comprises a vibrating system having a primary element and an intermediate mass capable of rotating relative to the primary element about an axis of rotation (A) against the reset action of the damping element arrangement; coupling means, It is used for combining the first torque component transmitted via the first torque transmission path and the second torque component transmitted via the second torque transmission path and for transmitting the combined torque to the output region, wherein the coupling device comprises a A first input element connected to the torque transmission path, a second input element connected to the second torque transmission path, and an output element connected to the output region, wherein the coupling device is designed as a fluid transmission. Here, the fluid transmission comprises: at least one housing element, a first cylinder and a second cylinder, both of which are arranged in the housing element and are connected to each other by means of connecting openings; and a pair of pistons , the pair of pistons comprises a first piston and a second piston which are movable opposite each other by means of an action medium in corresponding cylinders of the housing element. Here, one of the two pistons is connected to the output of the phase shifting device and is the first input element of the coupling device, while the other of the two pistons is connected to a direct torque transmission path, which is thus is the second input element of the coupling device. The housing element is the output element of the coupling device and is advantageously connected with the output region, for example with the starting clutch or the transmission. If a torque with torsional vibrations is now introduced from the input region, the torque branches to the first and second torque transmission paths. A phase shifter is provided in the first torque transmission path, while the second torque transmission path extends directly, ie rigidly, from the input side. In the case of torque transmission from the input region to the output region, the second piston, which is connected to the direct, ie rigid, torque transmission path, moves in the second cylinder of the housing element and exerts a force on the action medium via its piston surface. Since the second cylinder is connected to the first cylinder by means of the connecting opening, the action medium exerts an oppositely directed force on the face of the first piston, which executes a movement opposite to the second piston and which will consist essentially of a spring The vibration system is preloaded. If a force balance is established between the two piston surfaces, the resulting force at the output element and the resulting torque act on the output element by means of the housing element, more precisely by means of the cylinder rear wall. Therefore, static torque is transferred from the input area to the output area. The dynamic components contained in the static torque, ie the torsional vibrations, are ideally counteracted by the vibrations of the action medium relative to the vibrating system, ie the spring-mass system, and are not transmitted to the output region.

The transmission ratio of the coupling device can be set by the ratio of the piston surfaces of the first and second cylinders. This type of gear change can be carried out cost-effectively and quickly compared to the embodiments known from the prior art in which the coupling is embodied as a planetary gear or as a lever gear, since only the effective piston surface has to be changed.

It can also be advantageous for the cylinders in the housing element to have a curved or straight course.

Furthermore, incompressible media, ie for example hydraulic fluids, oils or any other known and suitable liquids or also viscous media can be used as action media.

It can also be advantageous for a plurality of fluid transmission devices to be distributed uniformly or non-uniformly in the circumferential direction around the axis of rotation A.

The transmission ratio of the fluid transmission can also be determined by the ratio of the piston surfaces of the first and second pistons.

Description of drawings

Hereinafter, the present invention will be described in detail with reference to the accompanying drawings. The attached figure shows:

FIG. 1 shows a schematic diagram of a prior art torsional vibration damping device with two parallel torque transmission paths.

FIG. 2 shows a schematic diagram of a prior art torsional vibration damping device with a planetary gear as a coupling device.

FIG. 3 shows a prior art vibration damping device with a lever coupling in a linear model.

FIGS. 4-8 show different transmission ratios of the prior art as shown in FIG. 3 .

FIG. 9 shows the damping device according to the invention with the coupling device as a fluid transmission device in a linear model.

FIG. 10 shows a sectional view of a torsional vibration damping device with a fluid transmission device according to the invention.

FIG. 11 shows the torsional vibration damping device of FIG. 10 as a plan view in the region of the coupling device.

Detailed ways

A first embodiment of a torsional vibration damping device, generally designated 10 , is described below with reference to FIG. 1 , which works according to the principle of power or torque branching. The torsional vibration damping device 10 can be provided, for example, in the driveline of a vehicle, between the drive assembly and components of the driveline, such as a transmission, a friction clutch, a hydrodynamic torque converter, or the like.

The torsional vibration damping device 10 shown schematically in FIG. 1 includes an input area generally provided with the reference numeral 50 . The input region 50 can be connected to a crankshaft (not shown) of the drive unit 61 , for example, by screwing. In the input region 50 , the torque absorbed by the drive assembly 61 is branched into the first torque transmission path 47 and the second torque transmission path 48 . In the region of the coupling device generally provided with the reference numeral 51 , the torque components Ma1 and Ma2 conducted via the two torque transmission paths 47 , 48 are combined again to form the output torque Maus and then transmitted to the output region 55 , which The region can be formed here, for example, by means of a gear 63 .

A vibration system, generally provided with the reference numeral 56 , is integrated in the first torque transmission path 47 . The vibration system 56 serves as the phase-shifting device 44 and comprises, for example, the primary element 1 to be connected to the drive assembly and the secondary element 2 that transmits torque. Here, the primary element 1 is rotatable relative to the intermediate mass 5 against the damping element arrangement 4 .

From the preceding description, the vibration system 56 is constructed with one or more spring packs 4 as shown here, depending on the type of torsional vibration damper. By selecting the masses of the intermediate mass 5 and of the primary element 1 and the stiffness of the one or more spring sets 4 it is possible that the resonance frequency of the vibration system 56 is in the desired range in order to achieve torsional vibrations from the first torque transmission path 47 . Favorable phase shift to the torsional vibrations in the second torque transfer path 48 . To make this happen, the first torque transfer path 47 operates supercritically. At the same time, the amplitude of the vibrations in the phase-shifted torque transfer path 47 after the spring set 4 is also reduced. The phase shift of the torsional vibrations should be kept as constant as possible in the second torque transmission path 48 . For this to happen, the path is designed as rigidly as possible and with low mass inertia. The coupling device 51 of the torsional vibration damping device 10 brings together the two torque components Ma1 and Ma2 again. This is done in that the two torque components Ma1 and Ma2 and the torsional vibration components are superimposed in such a way that in the best case the two torsional vibration components are phase-shifted by 180° and in the two torque transmission paths 47 , With the same amplitudes of the two torsional vibration components in 48 , after superimposing in the coupling device 51 , the torque Maus without the torsional vibration components is transmitted to the output region 55 .

In this case, the transmission of the coupling device, the spring characteristic curve and the inertia of the intermediate mass 5 can be selected such that the amplitude ratios of the two torque paths 47 ; 48 are the same and the vibration components cancel each other out. The transmission ratio also determines how much torque is guided via the phase-shifted torque transmission path 47 and via the spring set 4 , and how much torque travels through the direct torque transmission path 48 .

FIG. 2 shows a standard solution for the interconnection of torsional vibration damping devices 10 with two torque transmission paths. In this case, the coupling device 51 is designed as a planetary gear 6 . In this case, the planetary gear carrier 8 of the planetary gear 6 is connected to the primary element 1 in a rotationally fixed manner. The phase-shifted torque path 47 is connected to the primary element 1 by means of the drive ring gear 9 . The drive ring gear 9 meshes with the planet gears 13 , which are rotatably mounted on the planet gear carrier 8 and are the intermediate mass 5 . The other driven-side planetary gear 11 is connected to the planetary gear 13 in a rotationally fixed manner. The driven-side planetary gear 11 meshes again with the driven ring gear 12 , wherein the driven ring gear 12 forms the secondary element 2 and is the output element 40 of the coupling device 51 . In this connection variant, standard transmission ratios greater than 1.0 to 1.5 are most meaningful, since good decoupling results can thus be achieved. Here, the planet carrier 8 is in the direct torque transmission path 48 .

FIG. 3 shows a prior art vibration damping device with a lever coupling in a linear model. For better understanding, the reference numerals in the vibration reduction of rotation will also be used here for explanation, since the functions of the elements are similar. Instead of the torque M in the rotational vibration reduction, the force F is transmitted in the linear vibration reduction. For this purpose, the different transmission ratios of the coupling device 51 should be explained according to the successive locations of the output element 40 . In a vibration damping device with two transmission paths 47 ; 48 comprising a lever-coupling transmission, the transmission path 47 , which transmits the phase shift of the first force component, and the direct transmission path 48 , which transmits the second force component, are via the coupling element. 17 is articulated by means of the coupling hinge 29 and thus transmits the total force Fges from the input area 50 to the output area. The output element 40 of the coupling device 51 is likewise connected in an articulated manner, advantageously by means of the hinge connection 28 , to the coupling element 17 , wherein said output element is also the output of the concentrated force Faus of the coupling device 51 . Depending on the connecting position of the output element 40 , the transmission ratio of the lever-coupling transmission can be divided into the following five possibilities, which are shown individually in FIGS. 4 to 8 .

Here, the definition of the transmission ratio i also needs to be specified.

In a rotating system, the gear ratio is expressed as:

i=torque at follower/torque in phase shifted path

In a linear system, the gear ratio is expressed as:

i = force at follower/force in phase-shifted path

Here, the angle effect should be ignored. This consideration should apply to small angles.

Here, the following applies to the following gear ratios.

0<i<1 means that the output element 40 is connected to the coupling element 17 on the side of the phase-shifted transmission path 47 outside the coupling hinge 29 of the direct and indirect transmission path.

i=1 means that the output element 40 is connected to the coupling element 17 directly at the coupling hinge 29 of the phase-shifted transmission path 47 . No distribution of forces or moments takes place. The entire force or the entire moment is guided via a spring set and is similar to that in rotating systems with known dual-mass flywheels.

i>1 means that the output element 40 is connected to the coupling element 17 between the coupling hinges 29 of the direct and phase-shifted transmission paths 48 ; 47 . This is an advantageous design range for known torsional vibration damping devices with two torque transmission paths.

i=∞ means that the output element 40 is connected to the coupling element 17 directly at the coupling joint 29 of the direct transmission path 48 . The transfer path from the input area 50 to the output area 55 is not divided. The entire force Fges or the entire torque Mges is conducted via the direct transmission path 48 . The spring group 4 is thus bridged and cut off. All incentives are channeled directly through.

i<0 means that the output element 40 is connected to the coupling element 17 on the side of the direct transmission path 48 outside the coupling hinge 29 of the direct and phase-shifted transmission path.

Thus, the transmission ratio of the coupling device 51 can be changed by moving the articulated connection of the output element 40 along the coupling element 17 .

In the case of an ideally designed transmission ratio, the articulated connection of the output element 40 is in the node of vibration.

FIG. 9 shows the damping device according to the invention with a fluid transmission 60 as coupling device 61 in a linear model, wherein the total force Fges via the first transmission path 47 with the first force component and via the second transmission path 48 The output force Faus is transmitted to the output element of the fluid transmission 60 by means of the fluid transmission with the second force component Fa2 as the output force Faus. The interconnection scheme is similar to a lever-coupled transmission. In this case, however, the coupling of the phase-shifted and direct transmission paths 47 ; 48 takes place not via levers or planetary gears, as is known from the prior art, but via the action medium 70 , eg hydraulic fluid 71 , as incompressible medium to carry out.

Actuated via a first piston 65 and via a second piston 66 , which is connected to the phase-shifting transmission path 47 and which can be moved in a first cylinder 67 of the housing element 64 , the second piston The piston is connected to the direct transmission path 48 and said second piston can move in the second cylinder 68 of the housing element 64 . Here, the first cylinder and the second cylinder are connected to each other via the connecting opening 36 . The action medium 70 , which is embodied here as hydraulic fluid 71 , establishes an operative connection between the two pistons 65 and 66 . In this case, the housing element 64 is fixedly connected to the output element 40 .

The transmission ratio is expressed by the ratio of the piston surface AK2 of the direct transmission path 48 to the piston surface AK1 of the phase-shifted transmission path 47,

i=1+(AK2_direct/AK1_phase-shift) or

i=1+│(piston path_direct/piston path_phase shift)│

In this case, only the transmission ratio i in the range >=1 according to the above-mentioned definition can be achieved by adjusting the piston surface. The principle is based on hydraulic force transmission. The pistons 65; 66 must therefore be arranged such that the direct transmission path 48 and the phase-shifted transmission path 47 move in opposite directions. The reason is that, due to the static force component in the linear mode or due to the moment component in the rotational model and the in-phase vibration component with respect to the direct transmission path 48, the vibration component of the output signal of the spring set 4 is in antiphase, The spring group 4 is compressed.

FIGS. 10 and 11 show the design of the torsional vibration damping device 10 with two torque transmission paths and a fluid transmission 60 as coupling device 51 . In this case, the fluid transmission 60 comprises a hydraulic unit of a first and a second piston 65; 66, which can be moved in a first and a second cylinder 67; shaped shape.

When the torque Mges is applied, the second piston 66 of the direct torque transmission path 48 , which is rigidly connected in the direction of movement to the primary element 1 , moves in the second cylinder 68 and via the piston surface AK2 with the aid of the action medium 70 , in the second cylinder 68 . This is the force of the hydraulic fluid 71 acting on the piston surface AK1 of the first piston 65 , which is connected to the primary element 1 by means of the spring set 4 . Due to the inertia of the output element 40 , it can be connected on the one hand to the housing element 64 and on the other hand is the output of the torsional vibration damping device 10 and can be connected, for example, to a transmission or a starting clutch (neither of which are shown). out) connection, the output element 40 remains in the corresponding state and is not accelerated. The spring pack 4 is compressed by the force acting on the piston surface AK1 of the first piston. The two pistons 65; 66 move relative to each other until a force or moment balance occurs. At the latest, as Maus, the torque Mges is transmitted via the action medium 70 via the cylinder rear wall 69 to the output element 40 . Ideally, the dynamic vibration components are counteracted by the vibrations of the spring-mass system in the action medium 70 , here the hydraulic fluid 71 , in the torque transmission path 47 , which overcomes the phase shift, and are not transmitted to the secondary element 2 , here on the output element 40. Piston seals 75; 76 at the first and second pistons 65; 66 of the phase-shifted and direct torque transmission paths 47; 48 seal the cylinder interior space with the action medium 70 from the environment.

List of reference signs

1 Primary element

2 secondary components

3 Damping element device

4 spring set

5 Intermediate quality

6 Planetary gear

8 Planetary carrier

9 drive ring wheel

10 Torsional vibration damping device

11 Planetary gear on the driven side

12 driven hollow wheel

13 Planetary gear

17 Coupling elements

20 First input element

28 Hinged connections

29 Coupling hinges

30 Second input element

36 Connection opening

40 output elements

44 Phase shifter

47 First torque transmission path

48 Second torque transmission path

50 input fields

51 Coupling device

55 Output area

56 Vibration system

60 Fluid Transmission

61 Drive assembly

62 Piston Pairs

63 Transmission

64 Housing elements

65 first piston

66 Second piston

67 first cylinder

68 Second cylinder

69 cylinder rear wall

70 Action medium

71 Hydraulic fluids

75 Piston seal

76 Piston seal

80 cylinder interior space

A Rotation axis

Piston face of the first cylinder of AK1

Piston face of the second cylinder of AK2

d1 diameter of the first piston

d2 Diameter of the second piston

Mges total torque

Mal torque component 1

Mal torque component 2

Maus output torque

Fges total power

Fa1 Force component 1

Fa2 Force component 2

Faus output

Claims (10)

1. A torsional vibration damping device (10) for a drive train of a motor vehicle, comprising: an input region (50) and an output region (55) that can be driven to rotate about an axis of rotation (A), wherein the A first torque transmission path (47) and a second torque transmission path (48) are provided parallel to each other between the input region (50) and the output region (55), the first torque transmission path being used to transmit the torque to be transmitted. A first torque component (Ma1) of the total torque (Mges) transferred between the input region (50) and the output region (55); and the second torque transfer path is used to transfer to be at the input the second torque component (Ma2) of the total torque (Mges) transferred between zone (50) and said output zone (55), - a phase shifting device (44) at least in said first torque transmission path (47) to generate rotational inhomogeneities directed via the first torque transmission path (47) relative to via the second torque transmission path (48) Guided phase shift of rotational inhomogeneities, wherein the phase shift device (44) comprises a vibration system (56) having a primary element (1) and a reset action energy to overcome the damping element device (3) relative to the intermediate mass (5) of the primary element (1) rotating about the axis of rotation (A), - a coupling device (51) for connecting a first torque component (Ma1) transmitted via said first torque transmission path (47) and a second torque component transmitted via said second torque transmission path (48) (Ma2) merges and serves to transmit the merged torque (Maus) to the output region (55), wherein the coupling device (51) comprises a first torque transmission path (47) connected to the first an input element (20), a second input element (30) connected to the second torque transmission path (48), and an output element (40) connected to the output region (55), wherein the coupling device ( 51 ) is designed as a fluid transmission ( 60 ) comprising at least one piston pair ( 62 ), a housing element ( 64 ) and an action medium ( 70 ), the piston pair ( 62 ) comprising A first piston (65) and a second piston (66), wherein said housing element (64) comprises a first cylinder (67) and a second cylinder (68), wherein said first cylinder (67) and said Second cylinders (68) are connected to each other by means of connecting openings (36), characterized in that the first piston (65) is movably arranged in the first cylinder (67) and the second piston (66) Displaceably arranged in the second cylinder ( 68 ), the two pistons ( 65 ; 66 ) are operatively connected by means of an action medium ( 70 ). 2 . The torsional vibration damping device ( 10 ) according to claim 1 , wherein one of the two pistons ( 65 ; 66 ) is connected to the first input element of the coupling device ( 51 ). 3 . (20) is connected and the other of the two pistons (65; 66) is connected to the second input element (30) of the coupling device (51) and wherein the housing element (64) ) is connected to the output element (40). 3 . The torsional vibration damping device ( 10 ) according to claim 1 , wherein a relative position of one of the two pistons ( 65 ; 66 ) with respect to the housing element ( 64 ) takes place. 4 . In case of change, the other of the two pistons (65; 66) changes its position in the opposite direction. 4. The torsional vibration damping device (10) according to claim 1 or 2, wherein the diameter d1 of the first piston (65) is greater than or equal to or less than the diameter d2 of the second piston (66) . 5 . The torsional vibration damping device ( 10 ) according to claim 1 , wherein the first and second cylinders ( 67 ; 68 ) have a curved or straight course. 6 . 6 . The torsional vibration damping device ( 10 ) according to claim 1 , wherein one of the two cylinders ( 67 ; 68 ) has a curved course and the two cylinders ( 67 ; 68 ) The other cylinder has a straight course. 7. The torsional vibration damping device (10) according to claim 1 or 2, characterized in that the action medium (70) is an incompressible medium. 8. The torsional vibration damping device (10) according to claim 7, wherein the incompressible medium is a fluid. 9. Torsional vibration damping device (10) according to claim 1 or 2, characterized in that two or more fluid transmission devices (60) are uniformly distributed in a circumferential direction around the axis of rotation (A) or unevenly distributed. 10. Torsional vibration damping device (10) according to claim 1 or 2, characterized in that the ratio of the piston surfaces (AK1; AK2) of the first piston and the second piston (65; 66) is passed The transmission ratio of the coupling device (51) is determined.

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