Hydrodynamic torque converter and torsional vibration damper for same

Abstract

A hydrodynamic torque converter and a torsional vibration damper include a pump wheel connected on the drive side and a turbine wheel which is driven by the pump wheel. Between the housing of the torque converter and an output hub, a torsional vibration damper, which includes an input part that can be connected to the housing by a converter bridging clutch, and an output part, which is connected to the output hub, are provided. In order to allow a special wiring of the torsional vibration damper, an intermediate flange is arranged against a respective spring device, which acts in a circumferential direction, between the input part and the output part, said intermediate flange having a centrifugal pendulum and being connected to the turbine wheel.

Claims

1. A hydrodynamic torque converter comprising a pump wheel connected on a drive side and a turbine wheel driven by the pump wheel, wherein, between a housing of the torque converter and an output hub, a torsional vibration damper which comprises an input part that can be connected to the housing by a converter bridging clutch and an output part which is connected to the output hub are provided, wherein an intermediate flange is provided between the input part and the output part, arranged against a respective spring device which acts in a circumferential direction, wherein said intermediate flange has a centrifugal pendulum and is connected to the turbine wheel.

2. The hydrodynamic torque converter according to claim 1, wherein the spring devices are each formed from linearly designed helical compression springs distributed over the circumference.

3. The hydrodynamic torque converter according to claim 2, wherein the helical compression springs of the spring devices are arranged on substantially the same diameter and alternately over the circumference.

4. The hydrodynamic torque converter according to claim 1, wherein the intermediate flange is formed from two axially spaced, interconnected lateral parts, which receive the input part and the output part therebetween.

5. The hydrodynamic torque converter according to claim 1, wherein the input part and the output part are formed as disc parts which are formed axially adjacently, wherein the input part is centered on the output hub and the output part is connected to the output hub in a non-rotatable manner.

6. The hydrodynamic torque converter according to claim 5, wherein the disc parts have loading regions, arranged in one plane, for end faces of the helical compression springs and the helical compression springs are received in spring windows of the lateral parts of the intermediate flange with loading regions.

7. The hydrodynamic torque converter according to claim 6, wherein the loading regions of the input part and the output part are arranged radially one above the other

8. The hydrodynamic torque converter according to claim 6, wherein at least one loading region of the input part or of the output part has a nose engaging in an interior of a helical compression spring.

9. The hydrodynamic torque converter according to claim 5, wherein the disc parts have radially outwardly open recesses for the spring devices, wherein a support extending over the helical compression spring in the circumferential direction has at least one disc part on a radial outside.

10. A torsional vibration damper for a hydrodynamic torque converter, comprising an input part and an output part and an intermediate flange, wherein the input part, intermediate flange and output part are arranged in series by helical compression springs acting in a circumferential direction, wherein the input part and the output part are designed as axially adjacent disc parts, which are arranged between two axially spaced and interconnected lateral parts of the intermediate flange.

11. The torsional vibration damper according to claim 10, further comprising an output hub including an annular rim and the disc part of the output part is axially fixed between the annular rim and a first securing ring.

12. The torsional vibration damper according to claim 11, wherein the disc part of the input part is centered on the output hub and axially fixed by a second securing ring and the annular rim.

13. The torsional vibration damper according to claim 10, wherein the disc parts of the input part and the output part are axially fixed by an annular rim of an output hub.

14. The hydrodynamic torque converter according to claim 5, wherein the disc parts are axially fixed by an annular rim of the output hub.

15. The hydrodynamic torque converter according to claim 5, wherein the disc part of the output part is axially fixed between an annular rim of the output hub and a securing ring.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The disclosure is explained in more detail with reference to the exemplary embodiments shown in FIGS. 1 to 10. In the figures:

[0019] FIG. 1 shows a schematic representation of a hydrodynamic torque converter having a torsional vibration damper,

[0020] FIG. 2 shows the upper part of a structurally designed embodiment of the torsional vibration damper of FIG. 1 along a first section line,

[0021] FIG. 3 shows the upper part of the torsional vibration damper from FIG. 2 along a modified section line,

[0022] FIG. 4 shows the upper part of the torsional vibration damper from FIGS. 2 and 3 along a modified section line,

[0023] FIG. 5 shows a view of the torsional vibration damper from FIGS. 2 to 4 from the perspective of the converter bridging clutch with the front lateral part removed,

[0024] FIG. 6 shows a view of the torsional vibration damper of FIGS. 2 to 5 from the perspective of the turbine wheel,

[0025] FIG. 7 shows the upper part of a torsional vibration damper modified compared to the torsional vibration damper of FIGS. 2 to 6 in section,

[0026] FIG. 8 shows a detail of the torsional vibration damper from FIG. 7 in view,

[0027] FIG. 9 shows the upper part of a torsional vibration damper modified compared to the torsional vibration damper of FIGS. 2 to 8 in section, and

[0028] FIG. 10 shows a view of the torsional vibration damper of FIGS. 2 to 6, twisted under tensile load, with the upper lateral part removed.

DETAILED DESCRIPTION

[0029] FIG. 1 shows a schematic view of the hydrodynamic torque converter 1 with the torsional vibration damper 3 integrated in its housing 2. The torsional vibration damper 3 contains the input part 4, the output part 5 and the intermediate flange 6. The intermediate flange 6 is elastically coupled to the input part 4 and the output part 5 by means of the spring devices 7, 8 and carries the centrifugal pendulum 9.

[0030] The converter bridging clutch 10 is arranged between the housing 2 and the input part 4 of the torsional vibration damper 3. The pump wheel 11 is connected to the housing 2. When the converter bridging clutch 10 is open, the pump wheel 11 drives the turbine wheel 12. Between the pump wheel 11 and the turbine wheel 12, an idler wheel (not shown) is effectively arranged to increase the torque during a start-up process. The turbine wheel 12 is connected to the intermediate flange 6 so that the torsional vibration damper 3 has two different inputs, the torque of which is transmitted via the output part 5 to the output hub 13 and the transmission input shaft 14 of a transmission connected thereto.

[0031] The torsional vibration damper 3 therefore acts as a so-called lock-up damper when the converter bridging clutch 10 is closed, with the speed-adaptive centrifugal pendulum 9 and the turbine wheel 12 suspended as inertial mass on the intermediate flange 6 as damper components. In converter operation with the converter bridging clutch 10 open, the torsional vibration damper 3 acts as a turbine damper between the intermediate flange 6 connected to the turbine wheel 12 and the output hub 13.

[0032] The spring devices 7, 8 are preferably formed from linear helical compression springs or helical compression spring assemblies with nested linear helical compression springs arranged over the circumference.

[0033] FIG. 2 shows the upper part of the structurally designed torsional vibration damper 3, which can be rotated about the rotational axis d, in section. The input part 4 is connected to the output-side plate carrier 15 of the converter bridging clutch 10 by means of the rivets 16 distributed over the circumference. The input part 4 is received in a rotatable centered manner on the output hub 13. The output part 5 is connected to the output hub 13 in a non-rotatable manner. The input part 4 and output part 5 are designed as disc parts 17, 18 arranged parallel to one another. The disc part 17 is axially fixed and rotatably received by means of the securing ring 27 and the annular rim 28 of the output hub 13 and is centered on the output hub 13. The disc part 18 is axially fixed between the annular rim 28 and the securing ring 29 and is held in a non-rotatable manner on the output hub 13 by means of toothing (not shown).

[0034] The intermediate flange 6 is formed from the two axially spaced lateral parts 21, 22 which are interconnected by means of the spacer bolts 19. The disc parts 17, 18 are axially received between the lateral parts 21, 22 of the intermediate flange 6. The lateral part 21 facing the converter bridging clutch 10 is recessed radially on the inside in order to enable the connection of the disc carrier 15 to the input part 4.

[0035] The lateral parts 21, 22 form the pendulum mass carrier 20 of the centrifugal pendulum 9 and receive, between them, the pendulum masses 23, which are formed, for example, from riveted sheet metal discs that are distributed over the circumference. The pendulum masses 23 are suspended in the centrifugal force field of the torsional vibration damper 3 rotating about the rotational axis d by means of pendulum bearings (not shown) on the pendulum mass carrier 20 along a predetermined pendulum track. The spacer bolts 19 have stop buffers 30 to delimit the oscillation angle of the pendulum masses 23.

[0036] Spring devices 7, 8 (FIG. 1) act between the input part 4, the intermediate flange 6 and the output part 5, of which spring devices only the spring device 7 is shown in FIG. 2. The spring devices 7, 8 are arranged in series, that is, when the input part 4 is rotated relative to the output part 5 about the rotational axis d, depending on the direction of the applied torque, the spring devices between the input part 4 and the intermediate flange 6 and the spring devices 7, 8 arranged to act between the intermediate flange 6 and the output part 5 are loaded in series.

[0037] The spring device 7 is formed from linear, nested helical compression springs 24, 25 which are arranged distributed over the circumference.

[0038] The thrust washer 26, made in particular of plastic and suspended in a non-rotatable manner in the lateral part 22, delimits the axial play of the intermediate flange 6. The intermediate flange 6 is rotatably received and centered on the output hub 13 by means of the lateral part 22. The intermediate flange 6 is balanced by means of the balancing weights 31.

[0039] FIG. 3 shows the upper part of the torsional vibration damper 3 of FIG. 2, which is arranged so as to be rotatable about the rotational axis d, along a modified section line through the helical compression springs 32, 33 of the spring device 8. The loading of the helical compression springs 32, 33 becomes clear from FIG. 3. For the maximum overlapping loading of the helical compression springs 32, 33 by means of the disc parts 17, 18, these are cranked. In the illustration shown, the loading region 34 of the disc part 18 is formed axially centrally in the cross section of the helical compression springs 32, 33. The nose 35 extending in the circumferential direction into the interior of the inner helical compression spring 33 stabilizes the position of the helical compression springs 32, 33. The loading of the helical compression springs 32, 33 occurs on this end face on the output side. Correspondingly, the disc part 17 is provided on the other end face of the helical compression springs 32, 33 for loading on the input side with a loading region provided with a nose, which loading region is formed in the center of the cross section of the helical compression springs 32, 33.

[0040] The helical compression springs 32, 33 are received in spring windows 36, 37 of the lateral parts 21, 22 that are axially projected radially on the outside. In this case, the helical compression springs 32, 33 are loaded by radial walls of the spring windows 36, 37.

[0041] To reduce the radial friction of the outer helical compression springs 32, the supports 38, 39 are arranged on the disc parts 17, 18, widened in the circumferential direction and radially support at least the end turns of the helical compression springs 32, 33 on the two end faces.

[0042] FIG. 4 shows the upper part of the torsional vibration damper 3 of FIGS. 2 and 3, which is arranged so as to be rotatable about the rotational axis d, along a line of intersection between the spring devices 7, 8. In addition to the spacer bolts 19 (FIG. 2), the two lateral parts 21, 22 are connected to further spacer bolts 40 at the radial height of the spring devices 7, 8. The spacer bolts 40 with the disc parts 17, 18 form stops of the intermediate flange 6 in the circumferential direction to delimit the angle of rotation in order to keep the helical compression springs 24, 25 and the helical compression springs 32, 33 (FIG. 3) alternating with them over the circumference from a block position. The walls 41, 42 of the spring windows 36, 37 load the helical compression springs 24, 25, 32, 33 (FIGS. 2 and 3) in each case with respect to the intermediate flange 6.

[0043] FIG. 5 shows the torsional vibration damper 3 of FIGS. 2 to 4 in a view with the lateral part 21 (FIG. 2) of the intermediate flange 6 removed. The two spring devices 7, 8 are arranged alternately over the circumference and are formed from linear helical compression springs 24, 25, 32, 33 of different spring capacities arranged on the same diameter, so that depending on the direction of the relative rotation, different characteristics are formed when torque is introduced in the pushing or pulling direction. The helical compression springs 24, 25, 32, 33 are each serially loaded by the input part 3 (covered, FIG. 2) designed as a disc part 17, the intermediate flange 6 formed from the lateral parts 21 (FIG. 2), 22 which are axially spaced by means of the spacer bolts 19, 40 and the output part 5 designed as a disc part 18. The helical compression springs 24, 25, 32, 33 are each housed as helical compression spring assemblies in the spring windows 37 of the lateral part 22 and the lateral part (not shown) and loaded by the walls 42 of the same and the loading regions 34 of the disc part 18 with the supports 39 overlapping the helical compression springs 24, 32 in the circumferential direction and in a non-visible manner by the loading regions of the other disc part in the circumferential direction. The disc parts 17, 18 have corresponding recesses 43 which each receive helical compression springs 24, 25, 32, 33 of both spring devices 7, 8.

[0044] Radially outside of the spring devices 7, 8, the pendulum masses 23 of the centrifugal pendulum 9 are received in a pendulous manner by means of the pendulum bearings 44 on the intermediate flange 6. For this purpose, recesses 45, 46 with mutually complementary raceways 47, 48 are provided in the pendulum masses 23 and in the lateral parts 21, 22, wherein a pendulum roller 49 axially overlaps the recesses 45, 46 and rolls on the raceways 47, 48. The stop buffers 30 of the spacer bolts 19 serve as elastic stops for the pendulum masses 23 to delimit their oscillation angle.

[0045] FIG. 6 shows the torsional vibration damper 3 of FIGS. 2 to 5 in a view from the direction of the turbine wheel 12 of the hydrodynamic torque converter 1 in accordance with FIG. 1. The lateral part 22 of the intermediate flange 6 has the fastening openings 50 distributed over the circumference for receiving the turbine wheel 12, for example by riveting.

[0046] FIG. 7 shows the upper part of the torsional vibration damper 3a, which can be rotated about the rotational axis d, in section. In contrast to the torsional vibration damper 3 of FIGS. 2 to 6, the disc part 18a designed as output part 5a is shortened radially on the outside, so that only the disc part 17a designed as input part 4a has supports 38a extending over the helical compression springs 32a in the circumferential direction.

[0047] FIG. 8 shows a detail of the torsional vibration damper 3a of FIG. 7 in the region where the helical compression springs 24a, 32a are loaded. The loading region 34a of the disc part 18a has the nose 35a engaging in the interior of the helical compression springs 24a, 32a and therefore centers the cross section of the helical compression springs 24a, 32a on the loading region 34a radially within the support 38a, which is provided by the disc part 17a.

[0048] FIG. 9 shows the upper part of the torsional vibration damper 3b modified compared to the torsional vibration dampers 3, 3a of FIGS. 2 to 8, in section. In contrast to the torsional vibration dampers 3, 3a, no nose centering the helical compression springs 24b, 32b is provided on the loading regions 34b of the disc parts 17b, 18b; the loading regions 34b are planar. The disc parts 17b, 18b each have supports 38b, 39b that overlap the end turns of the helical compression springs 24b, 32b radially on the outside in the circumferential direction for radial support thereof.

[0049] FIG. 10 shows the torsional vibration damper 3 of FIGS. 2 to 6 under maximum tensile load in a view with the front lateral part 21 removed (FIG. 2). Both spring devices 7, 8 with the outer helical compression springs 24, 32 that slide to the block and therefore obstruct the view of the inner helical compression springs 25, 33 (FIGS. 2 and 3) are maximally compressed. The disc parts 17, 18 are rotated against each other maximally about the rotational axis d, so that one end face of the helical compression springs 24, 32 of the disc parts 17, 18 is pretensioned against the intermediate flange 6 formed from the lateral parts 21, 22.

LIST OF REFERENCE NUMBERS

[0050] 1 Hydrodynamic torque converter [0051] 2 Housing [0052] 3 Torsional vibration damper [0053] 3a Torsional vibration damper [0054] 3b Torsional vibration damper [0055] 4 Input part [0056] 4a Input part [0057] 5 Output part [0058] 5a Output part [0059] 6 Intermediate flange [0060] 7 Spring device [0061] 8 Spring device [0062] 9 Centrifugal pendulum [0063] 10 Converter bridging clutch [0064] 11 Pump wheel [0065] 12 Turbine wheel [0066] 13 Output hub [0067] 14 Transmission input shaft [0068] 15 Plate carrier [0069] 16 Rivet [0070] 17 Disc part [0071] 17a Disc part [0072] 17b Disc part [0073] 18 Disc part [0074] 18a Disc part [0075] 18b Disc part [0076] 19 Spacer bolt [0077] 20 Pendulum mass carrier [0078] 21 Lateral part [0079] 22 Lateral part [0080] 23 Pendulum mass [0081] 24 Helical compression spring [0082] 24a Helical compression spring [0083] 24b Helical compression spring [0084] 25 Helical compression spring [0085] 26 Thrust washer [0086] 27 Locking ring [0087] 28 Annular rim [0088] 29 Securing ring [0089] 30 Stop buffer [0090] 31 Balancing weight [0091] 32 Helical compression spring [0092] 32a Helical compression spring [0093] 32b Helical compression spring [0094] 33 Helical compression spring [0095] 34 Loading region [0096] 34a Loading region [0097] 34b Loading region [0098] 35 Nose [0099] 35a Nose [0100] 36 Spring window [0101] 37 Spring window [0102] 38 Support [0103] 38a Support [0104] 38b Support [0105] 39 Support [0106] 39b Support [0107] 40 Spacer bolt [0108] 41 Wall [0109] 42 Wall [0110] 43 Recess [0111] 44 Pendulum bearing [0112] 45 Recess [0113] 46 Recess [0114] 47 Raceway [0115] 48 Raceway [0116] 49 Pendulum roller [0117] 50 Fastening opening [0118] d Rotational axis