CN110088501A - The torsional vibration damper of power train for vehicle - Google Patents

Abstract

A kind of torsional vibration damper of the power train for vehicle, it include: that can drive around the input area (50) and output area (55) of pivot center (A) rotation, the first torque transmission paths (47) and the second torque transmission paths (48) in parallel and coupling (51) are wherein equipped between input area (50) and output area (55), phase changer (44) wherein are equipped in the first torque transmission paths (47), wherein coupling (51) is configured to fluid transmission means (60).

Description

Torsional vibration damping device for a 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 area drivable to rotate about an axis of rotation and an output area, wherein a first torque transmission path and a first torque transmission path are provided between the input area and the output area Parallel to this, there is a second torque transmission path and a coupling device for superimposing the torque conducted via the torque transmission path, wherein in the first torque transmission path there is a phase shifting device for generating torque via the first torque transmission path. A phase shift of the rotational non-uniformity directed via the torque transfer path relative to the rotational non-uniformity directed via the second torque transfer path.

Background technique

From the German patent application DE 10 2011 007 118 A a torsional vibration damping device is known which distributes the torque introduced into the input region, for example via the crankshaft of an internal combustion engine, into a torque component transmitted via a first torque transmission path and a torque component transmitted via a second torque transmission path. Transmits the path-guided torque component. In this torque distribution, not only the static torque is distributed, but also vibrations or rotational inhomogeneities contained in the torque to be transmitted are distributed proportionally to the two torque transmission paths. The properties are generated, for example, by the ignition that occurs periodically in an internal combustion engine. In this case, the coupling device again combines the two torque transmission paths and directs the combined total torque into an output region, for example into a friction clutch or the like.

In at least one of the torque transmission paths there is a phase shifting device which is designed according to the type of a shock absorber, ie is formed with a primary element and an intermediate element which is rotatable relative thereto due to the compressibility of the spring device. In particular, a phase shift of up to 180° occurs when the vibration system transitions into the supercritical state, ie is excited by vibrations above the resonance frequency of the vibration system. This means that, at 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 guided via the other torque transmission path undergo no phase shift or possibly a different phase shift, the vibration components contained in the converging torque component and which are subsequently phase-shifted relative to each other are superimposed relative to each other so that Ideally, the total torque introduced into the output region is a static torque which is substantially free of vibration components. In this case, the coupling device is designed as a planetary gear.

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

SUMMARY OF THE INVENTION

The object of the present invention is to provide a torsional vibration damper which has improved damping properties with a simple construction.

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 area and an output area drivable to rotate about an axis of rotation (A), wherein between the input area and the output A first torque transmission path for transmitting a first torque component of a total torque transmittable between an input area and an output area and a second torque transmission path are arranged parallel to each other between the areas. Two torque transmission paths for transmission of a second torque component; phase shifting means at least in the first torque transmission path to generate rotational inhomogeneity directed via the first torque transmission path relative to rotation directed via the second torque transmission path Inhomogeneous phase shifting, wherein the phase shifting device comprises an oscillating system with a primary element and an intermediate mass rotatable relative to the primary element about an axis of rotation (A) against a return action of a damping element arrangement; coupling means, It serves to combine a first torque component transmitted via a first torque transmission path and a second torque component transmitted via a second torque transmission path and to transmit the combined torque to an output region, wherein the coupling device comprises a coupling with the first A first input element connected to a torque transmission path, a second input element connected to a second torque transmission path, and an output element connected to an output region, wherein the coupling device is formed as a fluid transmission. Here, the fluid transmission device 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 a connecting opening; and a pair of pistons , the pair of pistons comprises a first piston and a second piston, the first and second pistons being movable in opposite directions to each other in corresponding cylinders of the housing element by means of an active medium. In this case, 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 to the output region, for example to the starter clutch or the transmission. If a torque with torsional vibrations is now introduced from the input region, the torque branches off into the first and the second torque transmission path. A phase shifting device is provided in the first torque transmission path, while the second torque transmission path runs directly, ie rigidly, from the input side. When torque is transmitted 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 via its piston surface on the active medium. Since the second cylinder is connected to the first cylinder by means of the connection opening, the acting medium exerts an oppositely directed force on the face of the first piston, which performs an opposite movement to the second piston and will mainly consist of a spring The vibration system is preloaded. If a force balance is provided 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 component contained in the static torque, ie the torsional vibration, is ideally counteracted by the vibration of the active medium relative to the vibration system, ie the spring-mass system, and is not transmitted to the output region.

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

It can also be advantageous if the cylinder in the housing element has a curved or straight course.

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

It can also be advantageous if a plurality of fluid transmission devices are distributed evenly or unevenly in the circumferential direction about the axis of rotation A.

The transmission ratio of the fluid transmission can also be determined via 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 accompanying drawings show:

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

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

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

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

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

FIG. 10 shows a sectional view of a torsional vibration damping device with a fluid transmission 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 indicated at 10 , which operates according to the principle of power or torque branching, is described below with reference to FIG. 1 . The torsional vibration damper device 10 can be arranged, for example, in the drive train of a vehicle between the drive unit and components of the drive train, 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 region generally designated with the reference numeral 50 . The input region 50 can be connected, for example by screwing, to a not shown crankshaft of the drive unit 61 . In the input region 50 , the torque absorbed by the drive unit 61 branches off into the first torque transmission path 47 and the second torque transmission path 48 . In the region of the coupling device generally designated 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 are then transmitted to the output region 55 , which The region can be formed here, for example, by the transmission 63 .

Integrated in the first torque transmission path 47 is an oscillating system generally designated with the reference numeral 56 . The vibration system 56 acts as the phase shifting device 44 and comprises, for example, the primary element 1 to be connected to the drive unit and the torque-transmitting secondary element 2 . In this case, the primary element 1 is rotatable relative to the intermediate mass 5 against the damping element arrangement 4 .

It is clear from the preceding description that the vibration system 56 is designed with one or more spring assemblies 4 as shown here, depending on the type of torsional vibration damper. By selecting the mass of the intermediate mass 5 and the primary element 1 and the rigidity 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 vibration from the first torque transmission path 47 Favorable phase shifting of torsional vibrations into the second torque transfer path 48 . To make this possible, the first torque transfer path 47 operates supercritically. At the same time, the vibration amplitude in the phase-shifted torque transmission path 47 downstream of the spring pack 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 . In order to make this possible, the path is designed to be as rigid as possible and to have a low mass inertia. The coupling device 51 of the torsional vibration damper device 10 combines the two torque components Ma1 and Ma2 again. This takes place in that the two torque components Ma1 and Ma2 and the torsional vibration component are superimposed in such a way that in the best case both torsional vibration components are phase shifted by 180° and between the two torque transmission paths 47, With the two torsional vibration components at 48 having the same magnitude, the torque Maus without torsional vibration components is transmitted to the output region 55 after being superimposed in the coupling device 51 .

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 identical and the vibration components cancel each other out. The transmission ratio also determines how much torque is conducted via the phase-shifted torque transmission path 47 and via the spring pack 4 , and how much torque passes over the direct torque transmission path 48 .

FIG. 2 shows a standard concept for the interconnection of torsional vibration damping device 10 with two torque transmission paths. In this case, the coupling device 51 is designed as a planetary gear 6 . In this case, the planet 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 . Drive ring gear 9 meshes with planet gears 13 , which are rotatably mounted on planet carrier 8 and are intermediate masses 5 . The planetary gear 11 on the other driven side is connected to the planetary gear 13 in a rotationally fixed manner. The driven-side planetary gears 11 in turn mesh 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 of greater than 1.0 to 1.5 make the most sense, since good decoupling results can thus be achieved. The planet carrier 8 is here in the direct torque transmission path 48 .

FIG. 3 shows a prior art damping device with a lever coupling in a linear model. For a better understanding, the reference numbers also used for the explanation in the reduction of rotational vibrations are used here because the functions of the elements are similar. Instead of a torque M in the rotational vibration reduction, a force F is transmitted in the linear vibration reduction. In this regard, the different transmission ratios of the coupling device 51 are to be explained depending on the successive positions 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, via the coupling element 17 is articulated by means of a coupling joint 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 to the coupling element 17 , advantageously by means of an articulation connection 28 , wherein the output element is also the output of the concentrated force Faus of the coupling device 51 . Depending on the successive position of the output element 40 , the transmission ratio of the lever coupling can be divided into the following five possibilities, which are shown separately in FIGS. 4 to 8 .

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

In a rotating system, the transmission ratio expresses:

i = torque at driven part/torque in phase shift path

In a linear system, the transmission ratio expresses:

i = force at follower/force in phase shift path

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

Here, the following applies for the transmission ratios described below.

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 joint 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 joint 29 of the phase-shifted transfer 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 direct and phase-shifted transmission path 48 ; 47 of the coupling joint 29 . 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 on the coupling joint 29 of the direct transfer 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 pack 4 is thus bridged and disconnected. All stimuli are directed 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 joint 29 of the direct and phase-shifted transmission path.

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

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

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

The actuation takes place via a first piston 65 , which is connected to the phase-shifted transmission path 47 and which is displaceable in a first cylinder 67 of the housing element 64 , and via a second piston 66 . The piston is connected to the direct transmission path 48 and the second piston is displaceable in a second cylinder 68 of the housing element 64 . Here, the first cylinder and the second cylinder are connected to one another via a connecting opening 36 . Activating medium 70 , here embodied 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 transmission ratios i in the range >=1 according to the above definition can be achieved by adjusting the piston surfaces. The underlying principle is hydraulic force transmission. The pistons 65 ; 66 must therefore be arranged in such a way that the direct transmission path 48 and the phase-shifted transmission path 47 move in opposite directions. The reason is that the vibration component of the output signal of the spring set 4 is out of phase due to the static force component in the linear mode or due to the moment component in the rotational model and the vibration component in phase with respect to the direct transmission path 48, The spring set 4 is compressed.

FIGS. 10 and 11 show the design of a torsional vibration damper device 10 with two torque transmission paths and a fluid transmission 60 as coupling device 51 . The fluid transmission 60 here comprises a hydraulic unit of a first and a second piston 65 ; 66 , which are displaceable in a first and a second cylinder 67 ; 68 and are embodied here as an example in an arc shaped shape.

With an applied torque Mges, the second piston 66 of the direct torque transmission path 48 , which is rigidly connected in the direction of motion to the primary element 1 , moves in the second cylinder 68 and is moved via the piston face AK2 by means of the active medium 70 , at This is because the hydraulic fluid 71 exerts a force on the piston face 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, said output element can be connected with the housing element 64 on the one hand and the output of the torsional vibration damping device 10 on the other hand and can be connected, for example, to a transmission or a starting clutch (both of which are not shown). OUT) connection, the output element 40 remains in the corresponding state and does not accelerate. The spring pack 4 is compressed by the force acting on the piston face AK1 of the first piston. The two pistons 65 ; 66 move relative to each other until a force or torque equilibrium occurs. At the latest at this time, as Maus, the torque Mges is transmitted via the active medium 70 via the cylinder rear wall 69 to the output element 40 . Ideally, the dynamic vibration components are counteracted by the active medium 70 , here the hydraulic fluid 71 , against the vibrations of the spring-mass system in the phase-shifted torque transmission path 47 and are not transmitted to the secondary element 2 , here for output element 40. The piston seal 75; 76 at the first and second piston 65; 66 of the phase-shifted and direct torque transmission path 47; 48 seals the cylinder interior with the active medium 70 from the environment.

List of reference signs

1 primary element

2 secondary components

3 Damping element device

4 spring sets

5 intermediate mass

6 Planetary gearing

8 Planet carrier

9 Drive ring gear

10 Torsional vibration damper

11 Planet gears on output side

12 Driven hollow gear

13 planetary gear

17 Coupling elements

20 First input element

28 hinge connection

29 coupling hinge

30 Second input element

36 connection opening

40 output elements

44 phase shifting device

47 First torque transfer 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 Acting medium

71 hydraulic fluid

75 Piston seal

76 Piston seal

80 cylinder interior space

A axis of rotation

Piston face of AK1 first cylinder

Piston face of AK2 second cylinder

d1 diameter of the first piston

d2 Diameter of the second piston

Mges Gross torque

Mal Torque component 1

Mal torque component 2

Maus output torque

Fges total force

Fa1 Force component 1

Fa2 Force component 2

Faus output force

Claims (13)

1. a kind of torsional vibration damper (10) of power train for motor vehicle comprising: it can be actuated to surround pivot center (A) input area (50) and output area (55) rotated, wherein in the input area (50) and the output area (55) Between be equipped with the first torque transmission paths (47) and the second torque transmission paths (48) in parallel with each other, first torque transmits Path stays in the total torque (Mges) transmitted between the input area (50) and the output area (55) for transmitting to have First torque component (Ma1)；And second torque transmission paths stay in the input area (50) and institute for transmitting The second torque component (Ma2) of the total torque (Mges) transmitted between output area (55) is stated,

Phase changer (44) at least in first torque transmission paths (47) transmits road via the first torque to generate Phase of the rotation inhomogeneities of diameter (47) guidance relative to the rotation inhomogeneities guided via the second torque transmission paths (48) It moves, wherein the phase changer (44) includes vibrational system (56), the vibrational system has primary element (1) and overcomes damping The reset response of component arrangement (3) can surround the intermediate mass (5) of pivot center (A) rotation relative to the primary element (1),

Coupling (51) is used for the first torque component (Ma1) that will be transmitted via first torque transmission paths (47) The torsion that the second torque component of ground (Ma2) is converged and is used to be converged is transmitted with via second torque transmission paths (48) Square (Maus) is transferred to the output area (55), wherein the coupling (51) includes and first torque transmission paths (47) the first input element (20) connected, the second input element (30) for being connect with second torque transmission paths (48) and The output element (40) being connect with the output area (55), which is characterized in that the coupling (51) is configured to fluid biography Dynamic device (60).

2. torsional vibration damper (10) according to claim 1, which is characterized in that the fluid transmission means (60) includes At least one piston is to (62), casing member (64) and interaction medium (70).

3. torsional vibration damper (10) according to claim 2, which is characterized in that the piston includes first living to (62) (65) and second piston (66) are filled in, wherein the casing member (64) includes the first cylinder (67) and the second cylinder (68), wherein described First cylinder (67) and second cylinder (68) are connected to each other by connection opening (36).

4. torsional vibration damper (10) according to claim 3, which is characterized in that the first piston (65) can be movably It is arranged in first cylinder (67) and the second piston (66) can be movably arranged in second cylinder (68), wherein The two pistons (65；66) effectively connection is in by means of interaction medium (70).

5. torsional vibration damper (10) according to claim 3 or 4, which is characterized in that the two pistons (65；66) in One piston is connect with first input element (20) of the coupling (51), and the two pistons (65；66) in Another piston connect with second input element (30) of the coupling (51), and the wherein casing member (64) it is connect with the output element (40).

6. torsional vibration damper (10) according to any one of claim 3 to 5, which is characterized in that in the two pistons (65；66) in the case that relative to the casing member (64) relative position variation occurs for a piston in, the two pistons (65；66) change its position to another piston reverses direction in.

7. the torsional vibration damper according to any one of claim 2 to 6 (10), which is characterized in that the first piston (65) diameter d1 is greater than or equal to or is less than the diameter d2 of the second piston (66).

8. the torsional vibration damper according to any one of claim 3 to 7 (10), which is characterized in that first cylinder and Second cylinder (67；68) trend with curved trend or straight line.

9. the torsional vibration damper according to any one of claim 3 to 7 (10), which is characterized in that the two cylinders (67； 68) cylinder in has curved trend and the two cylinders (67；68) another cylinder in has the trend of straight line.

10. the torsional vibration damper according to any one of claim 2 to 9 (10), which is characterized in that the interaction medium It (70) is incompressible medium.

11. torsional vibration damper (10) according to claim 10, which is characterized in that incompressible medium is stream Body.

12. torsional vibration damper (10) according to any one of claim 1 to 11, which is characterized in that two or more A fluid transmission means (60) is homogeneously or heterogeneously distributed along the circumferential direction around the pivot center (A).

13. the torsional vibration damper according to any one of claim 3 to 12 (10), which is characterized in that pass through described One piston and the second piston (65；66) piston area (AK1；AK2 the transmission of coupling described in ratio-dependent) (51) Than.