Drive train having a spur gearing and a centrifugal pendulum

Abstract

A drive train including an internal combustion engine with a crankshaft, and having a spur gear arrangement with at least one transmission input shaft that is coupled to the crankshaft by a friction clutch. A clutch plate within a housing of the friction clutch is connected in a rotationally locked manner to the at least one transmission input shaft and includes a centrifugal force pendulum. To accommodate the centrifugal force pendulum in the drive train in a space saving manner, the centrifugal force pendulum is situated on the at least one transmission input shaft at an axial distance from the clutch plate.

Claims

1. A drive train comprising: an internal combustion engine having a crankshaft; a transmission including a plurality of axially spaced spur gears for setting different transmission gear ratios, and including at least one transmission input shaft coupled to the crankshaft by a friction clutch including a clutch plate received within a clutch housing and connected in a rotationally locked manner to the at least one transmission input shaft, wherein the clutch plate includes a torsional vibration damper to damp torsional vibrations in the spur gears of the transmission; and a centrifugal force pendulum carried on the at least one transmission input shaft and separate from the friction clutch and at an axial distance from the clutch plate, wherein the centrifugal force pendulum includes pendulum masses supported on rollers carried by a radially extending pendulum flange member that is non-rotatably carried on the at least one transmission input shaft; wherein the centrifugal force pendulum is situated at an end of the transmission input shaft that extends through the spur gears, and the spur gears are positioned between the friction clutch and the centrifugal force pendulum.

2. A drive train comprising: an internal combustion engine having a crankshaft; a transmission including a plurality of axially spaced spur gears for setting different transmission gear ratios, and including at least one transmission input shaft coupled to the crankshaft by a friction clutch including a clutch plate received within a clutch housing and connected in a rotationally locked manner to the at least one transmission input shaft, wherein the clutch plate includes a torsional vibration damper to damp torsional vibrations in the spur gears of the transmission; and a centrifugal force pendulum carried on the at least one transmission input shaft and separate from the friction clutch and at an axial distance from the clutch plate, wherein the centrifugal force pendulum includes pendulum masses supported on rollers carried by a radially extending pendulum flange member that is non-rotatably carried on the at least one transmission input shaft; wherein the transmission is a dual-clutch transmission that includes two sub-transmissions, each sub-transmission having a respective transmission input shaft, one of the two sub-transmissions having a hollow transmission input shaft; wherein the centrifugal force pendulum is non-rotatably carried directly on the hollow transmission input shaft; wherein each sub-transmission includes a respective set of spur gears and the centrifugal force pendulum is situated between the sets of spur gears of the sub-transmissions.

3. The drive train according to claim 2, wherein at least one pendulum mass carried by the centrifugal force pendulum is situated radially outwardly of a radially outermost surface of at least one spur gear of one of the sets of spur gears carried on the hollow transmission input shaft, and wherein the at least one pendulum mass at least partially axially overlaps the at least one spur gear.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The invention will be explained in further detail on the basis of the exemplary embodiments depicted in FIGS. 1 through 5. The figures show the following:

(2) FIG. 1 is a schematically depicted cross section of a drive train having a centrifugal force pendulum situated between an internal combustion engine and a friction clutch, and directly on a transmission input shaft.

(3) FIG. 2 is a schematically depicted cross section of a drive train having a centrifugal force pendulum situated between a friction clutch and a spur gear arrangement, and directly on a transmission input shaft,

(4) FIG. 3 is a schematically depicted cross section of a drive train having a centrifugal force pendulum integrated into a spur gear arrangement, and situated directly on a transmission input shaft,

(5) FIG. 4 is a schematically depicted cross section of a drive train having a centrifugal force pendulum situated directly on the end of a transmission input shaft that faces away from the friction clutch, and

(6) FIG. 5 is a schematically depicted cross section of a drive train having a dual-clutch transmission with two sub-transmissions, each sub-transmission having a separate transmission input shaft and each sub-transmission having a centrifugal force pendulum situated on the associated transmission input shaft.

DESCRIPTION OF THE PREFERRED EMBODIMENTS

(7) FIG. 1 shows in schematic, cross-sectional form the upper half of a drive train 1, positioned around the axis of rotation 2, with an internal combustion engine, of which only the crankshaft 3 and the flywheel 4, which can be a single or a dual-mass flywheel, are shown. Situated on the transmission input shaft 5 is a spur gear arrangement 6, with several spur gears 17 for setting different gear ratios with complementary spur gears, not shown, that mesh with spur gears 7 and that are positioned on a transmission output shaft, also not shown. Friction clutch 8 with the clutch housing 9 and the clutch plate 10 are also situated on transmission input shaft 5. The clutch housing 9 receives the torque of the crankshaft 3 through the flywheel 4 and transmits it, dependent upon the engagement state of the friction clutch 8, through the friction linings 11 of the clutch plate 10 to the transmission input shaft 5, to which the clutch plate 10, which includes a torsional vibration damper 12, is connected in a rotationally locked manner.

(8) In the exemplary embodiment shown in FIG. 1, the centrifugal force pendulum 13 is accommodated in the construction space between the flywheel 4 and the friction clutch 8, and is connected directly to the transmission input shaft 5 in a rotationally locked manner such as by a meshing connection. The pendulum flange 14 of the centrifugal force pendulum 13 receives the pendulum masses 17 by means of rollers 16 on both sides of pendulum flange 14, and by means of the internal teeth 15 meshes in a rotationally locked manner with the complementary external teeth 18 of the transmission input shaft 5. Alternatively, the pendulum flange 14 can be received on a hub (not shown), which, in turn, is connected to the transmission input shaft 5 in a rotationally locked manner such as by a meshing connection, and on which the pendulum flange 14 is received in a rotationally locked manner or with limited torque by interposing a slip clutch (not shown).

(9) In contrast to drive train 1 of FIG. 1, FIG. 2 shows a drive train 1a, with a friction clutch 8a that is spaced from the spur gear arrangement 6a. In this case, the centrifugal force pendulum 13a is received with its pendulum flange 14a directly on the transmission input shaft 5a in the construction space between friction clutch 8a and the spur gear arrangement 6a.

(10) FIG. 3 shows, as a modification of drive trains 1, 1a of FIGS. 1 and 2, the drive train 1b, with a pendulum flange 14b of centrifugal force pendulum 13b received directly on transmission input shaft 5b. Centrifugal force pendulum 13b is positioned within spur gear arrangement 6b and—as shown—is positioned axially next to and upstream of the spur gears 7b on the transmission input shaft 5b. Alternatively, the centrifugal force pendulum 13b can be positioned between the spur gears 7b.

(11) In a further modification, the drive train 1c of FIG. 4 is equipped—in contrast to the drive trains 1, 1a, 1b of FIGS. 1 through 3—with the centrifugal force pendulum 13c positioned directly on the transmission input shaft 5c on the downstream side of the spur gear arrangement 6c, the side of spur gear arrangement 6c that faces away from the friction clutch 8c. To that end, the transmission shaft 5c is extended axially to extend through the spur gear arrangement 6c, and receives the pendulum flange 14c of the centrifugal force pendulum 13c on the extended end 19 of transmission shaft 5c in a rotationally locked manner.

(12) FIG. 5 shows a schematic cross-sectional depiction of the upper half of the drive train 1d positioned around the axis of rotation 2, which, in contrast to the drive trains 1, 1a, 1b, 1c of FIGS. 1 through 4, contains the spur gear arrangement 6d in the form of a dual-clutch transmission 20 including two sub-transmissons 21, 22, each having gear sets with spur gears 7d, 7e situated on separate transmission input shafts 5d, 5e. Accordingly, the dual clutch 8d is provided with the clutch plates 10d, 10e, which independently of each other transmit the torque that is transmitted from a crankshaft 3d to the housing 9d of the dual clutch 8d to the transmission input shafts 5d, 5e.

(13) Transmission input shafts 5d, 5e are positioned coaxially to each other. To that end, the transmission input shaft 5e is designed as a hollow shaft 23 and is situated around the transmission input shaft 5d. Connected to each of the two transmission input shafts 5d, 5e is a respective centrifugal force pendulum 13d, 13e, which is connected to the respective transmission input shaft in a rotationally locked manner. In the depicted exemplary embodiment, the centrifugal force pendulum 13e carried on the hollow shaft 23 is positioned within the dual-clutch transmission 20. The depicted exemplary embodiment shows the centrifugal force pendulum 13e situated between the two sets of gears of the respective sub-transmissions 21, 22. The pendulum masses 17e of centrifugal force pendulum 13e lie radially outwardly of the nearest spur gear of the spur gears 7d having the smallest diameter. Depending on the design of the complementary spur gears (not shown) of the transmission input shaft, for example when designing the reverse gear, the nearest of the pendulum masses 17e can at least partially axially overlap the nearest of the spur gears 7d, for reasons of construction space.

(14) In the depicted exemplary embodiment, the centrifugal force pendulum 13d assigned connected to the transmission input shaft 5d is positioned on the end of the transmission input shaft 5d between the dual-clutch 8d and the crankshaft 3d, with an inertial mass, such as a single-mass or dual-mass flywheel that can be situated on the latter.