Abstract
A torsional vibration damping arrangement comprises an input region to be driven in rotation around an axis of rotation and an output region and a first torque transmission path and parallel thereto a second torque transmission path, both of which proceed from the input region, and a coupling arrangement for superposing the torques conducted via the torque transmission paths, which coupling arrangement communicates with the output region, a phase shifter arrangement for the first torque transmission path for generating a phase shift of rotational irregularities conducted via the first torque transmission path relative to rotational irregularities conducted via the second torque transmission path, and a pendulum mass in the phase shifter arrangement and/or in the coupling arrangement.
Claims
1. A torsional vibration damping arrangement (10), comprising: an input region (50) to be driven in rotation around an axis of rotation (A); an output region (60); a first torque transmission path (55) and parallel thereto a second torque transmission path (56), both the first and second torque transmission paths proceeding from the input region (50); a coupling arrangement (61) for superposing the torques conducted via the torque transmission paths (55; 56), the coupling arrangement (61) communicating with the output region (60); a phase shifter arrangement (65) for the first torque transmission path (55) for generating a phase shift of rotational irregularities conducted via the first torque transmission path (55) relative to rotational irregularities conducted via the second torque transmission path (56); a pendulum mass (16) constructed such that the pendulum mass displaces relative to a carrier element under the influence of a torsional irregularity; and additionally comprising a primary mass (1) formed by an engine-side housing shell and a cover plate (2) formed by a transmission-side housing shell connected to the primary mass (1) so as to be fixed with respect to rotation relative to the primary mass (1), the primary mass (1) and cover plate (2) fixedly connected radially outwardly relative to the phase shifter arrangement (65) and forming an enclosure for the phase shifter arrangement (65); and wherein the pendulum mass (16) is connected with the primary mass (1) and/or with the cover plate (2).
2. The torsional vibration damping arrangement (10) according to claim 1, wherein the coupling arrangement (61) comprises: a first input portion (70), a second input portion (71); a superposition unit (75) and an output portion (77), wherein the first input portion (70) is connected to the phase shifter arrangement (65) and superposition unit (75), and the second input portion (71) is connected to the input region (50) and superposition unit (75), and the superposition unit (75) is connected to the first input portion (70), second input portion (71) and output portion (77), and wherein the output portion (77) forms the output region (60).
3. The torsional vibration damping arrangement (10) according to claim 1, wherein the phase shifter arrangement (65) comprises a vibrational system (51) having an intermediate mass (3) which is rotatable with respect to the primary mass (1) around the axis of rotation (A) against the action of a spring arrangement.
4. The torsional vibration damping arrangement (10) according to claim 2, wherein the pendulum mass (16) is coupled in the coupling arrangement (61) with the first input portion (70) or with the second input portion (71) or with the output portion (77).
5. The torsional vibration damping arrangement (10) according to claim 3, wherein the pendulum mass (16) is coupled in the coupling arrangement (61) with the first input portion (70) or with the second input portion (71) or with the output portion (77).
Description
BRIEF DESCRIPTION OF THE DRAWINGS
(1) A preferred embodiment example of the invention and further constructional variants will be described in the following with reference to the accompanying drawings. The drawings show:
(2) FIG. 1 a torsional vibration damper arrangement with a pendulum mass and an adapter piece at a primary mass of the phase shifter arrangement radially inward of an outer damper;
(3) FIG. 2 a torsional vibration damper arrangement according to FIG. 1, but without adapter piece;
(4) FIG. 3 a torsional vibration damper arrangement with a pendulum mass at the primary mass radially outward of an inner damper;
(5) FIG. 4 a torsional vibration damper arrangement with a pendulum mass which is connected to the primary mass and a cover plate connected to the latter, radially outward of the inner damper;
(6) FIG. 5 a torsional vibration damper arrangement with a pendulum mass which is arranged radially outward at the cover plate;
(7) FIG. 6A a torsional vibration damper arrangement with a pendulum mass at a planet carrier of a coupling arrangement;
(8) FIG. 6B a cross-sectional view along the line A-A in FIG. 6A;
(9) FIG. 7A a torsional vibration damper arrangement with a pendulum mass at the planet carrier and a larger mass of the pendulum mass 16 compared to FIG. 6;
(10) FIG. 7B a cross-sectional view along the line A-A in FIG. 7A;
(11) FIG. 8 a torsional vibration damper arrangement with a pendulum mass radially outward at the output portion operating on the Sarazin principle;
(12) FIG. 9 a torsional vibration damper arrangement with a pendulum mass radially outward at the output portion operating on the Salomon principle;
(13) FIG. 10 a torsional vibration damper arrangement with a pendulum mass radially inward at the output portion;
(14) FIG. 11 a torsional vibration damper arrangement with a pendulum mass at the output portion radially outside of a through-aperture at the axial height of the coupling arrangement;
(15) FIG. 12A a torsional vibration damper arrangement with an adjustable fixed-frequency mass damper as pendulum mass radially outward at the output portion;
(16) FIG. 12B a side view of FIG. 12A in the direction of the secondary fly wheel;
(17) FIG. 13 a torsional vibration damper arrangement with a pendulum mass at an intermediate mass;
(18) FIG. 14 a torsional vibration damper arrangement with an adjustable pendulum mass radially outward at the intermediate mass operating on the Sarazin principle;
(19) FIG. 15 a torsional vibration damper arrangement with a pendulum mass at a hub disk of the phase shifter arrangement;
(20) FIG. 16 a torsional vibration damper arrangement with a pendulum mass arranged radially between inner spring set and outer spring set at the hub disk;
(21) FIGS. 17A and B a torsional vibration damper arrangements as a schematic diagram with individual connection options for the pendulum mass.
DETAILED DESCRIPTION OF THE PRESENTLY PREFERRED EMBODIMENTS
(22) FIG. 1 shows a torsional vibration damper arrangement 10 which operates on the principle of power splitting or torque splitting. The torsional vibration damper arrangement 10 can be arranged in a powertrain, for example, of a vehicle, between a drive unit, i.e., for example, an internal combustion engine, and the subsequent portion of the powertrain, i.e., for example, a friction clutch, a hydrodynamic torque converter or the like.
(23) The torsional vibration damper arrangement 10 comprises an input region, designated generally by 50, which is rotatable around the axis of rotation A. This input region 50 can be connected, for example screwed, to a crankshaft of an internal combustion engine. In the input region 50, the torque received from a drive unit branches into a first torque transmission path 55, which may also be referred to as main branch 30, and into a second torque transmission path 56 which may also be referred to as superposition branch 31. In the region of a coupling arrangement, designed generally by 61, the torque components conducted via the two torque transmission paths 55, 56 are introduced into the coupling arrangement 61 by means of a first input portion 70 and a second input portion 71 and are combined again in superposition unit 75 and then conveyed to an output region 60 which comprises a secondary flywheel 4 of a friction clutch in the depicted example.
(24) A vibrational system, designed generally by 51, is integrated in the first torque transmission path 55. The vibrational system 51 acts as a phase shifter arrangement 65 and comprises a primary mass 1 which is to be connected, for example, to the drive unit and an intermediate mass 3 which conveys the torque. The primary mass 1 together with the cover plate 2 to which it is connected so as to be fixed with respect to rotation relative to it substantially completely surrounds radially outwardly a spatial region in which an outer spring set 5 for the vibrational system 51 is received. The outer spring set 5 comprises a plurality of spring units 57 which are arranged successively in circumferential direction and also possibly so as to be nested one inside the other. Each spring unit 57 preferably comprises at least one compression coil spring. The spring units 57 of the outer spring set 5 are supported with respect to the primary mass 1 on the one hand and with respect to a hub disk 7 formed as center disk on the other hand. This hub disk 7 is connected, e.g., by threaded bolts 52, to the intermediate mass 3 so as to be fixed with respect to rotation relative to it.
(25) A pendulum mass 16 which is formed in this case with an additional adapter piece 41 is positioned at the primary mass 1 radially inward of the outer spring set 5 in an installation space which is formed by the outwardly bent primary mass 1 and the outwardly bent hub disk 7. The adapter piece 41 serves to reduce friction for an axial stop 42 of the pendulum mass 16. The surface of the adapter piece 41 is formed such that it reduces friction, e.g., by means of specially applied coatings such as Teflon so that the axial friction between the pendulum mass 16 and the axial stop 42 can be minimized.
(26) The pendulum mass 16 shown here operates on the known Salomon principle. However, a pendulum mass 16 operating on the known Sarazin principle or any functionally suitable pendulum mass can also be used for these constructional variants and for the constructional variants hereinafter referring to FIGS. 2-16. Basically, the known Salomon-type pendulum mass or Sarazin-type pendulum mass (which could also be referred to as Sarazin-type mass damper and Salomon-type mass damper) function in the same way. Both pendulum masses are based on the principle of mass displacement relative to their carrier part due to varying rotational speeds. The Salomon-type mass damper is more advantageous with respect to the radial installation space requirement. A further advantage of the Salomon-type mass damper consists in the simple adaptation of the tuning order through corresponding configuration of the track geometry on which the pendulum mass 16 moves. In the Sarazin-type mass damper the centroid radius of the mass bodies must be changed, e.g., through a resiliently supported mass which moves radially outward as the rotational speed increases.
(27) FIG. 2 shows a torsional vibration damper arrangement 10 basically like that shown in FIG. 1, but with a pendulum mass 16 which is positioned at the primary mass 1 radially inward of the outer spring set 5 without the adapter piece 41. As a result of the omission of the adapter piece 41, the axial stop 42 rubs directly against the primary mass 1 and the pendulum mass 16 can be made larger due to the absence of the adapter piece 41. Since, as a rule, the primary mass need not be reworked or coated with a friction-reducing coating such as Teflon, the friction between the primary mass 1 and pendulum mass 16 can be higher than when using an adapter piece as described in FIG. 1. The increased friction between the pendulum mass 16 and the primary mass 1 can have an influence on the efficiency of the pendulum mass 16. In a further embodiment, not shown, the primary mass 1 can be coated with a friction-reducing coating such as Teflon at the frictional surface with the axial stop 42 of the pendulum mass 16. The pendulum mass 16 shown here operates on the Salomon principle.
(28) FIG. 3 shows a torsional vibration damper arrangement 10 basically like that shown in FIG. 1, but with a pendulum mass 16 which is fastened at the primary mass 1 radially outward of an inner spring set 6. This inner spring set 6 also comprises a plurality of spring units 58 which are arranged successively in circumferential direction and also possibly so as to be nested one inside the other. Each spring unit 58 is preferably formed with at least one compression coil spring. The spring units 58 of the inner spring set 6 are supported on at least one shroud 14 on one side and on the hub disk 7 on the other side. The outer spring set 5 is not provided in this embodiment. The pendulum mass shown here operates on the Salomon principle.
(29) FIG. 4 shows a torsional vibration damper arrangement 10 basically like that shown in FIG. 1, but with a pendulum mass 16 which is fastened radially outward of the inner spring set 6 at the primary mass 1 on one side and at the cover plate 2 on the other side. In this embodiment, the outer spring set 5 is not provided. The pendulum mass 16 shown here operates on the Salomon principle.
(30) FIG. 5 shows a torsional vibration damper arrangement 10 basically like that shown in FIG. 1, but with a pendulum mass 16 which is fastened radially outward at the cover plate 2. This arrangement of the pendulum mass 16 is particularly efficient due to its being positioned radially far outward. Compared to FIG. 1, this embodiment of the torsional vibration damper arrangement 10 has in addition to the outer spring set 5 an optional inner spring set 6 as was already described referring to FIG. 3. The pendulum mass 16 shown here operates on the Sarazin principle.
(31) FIGS. 6A and B shows a torsional vibration damper arrangement 10 basically like that shown in FIG. 1, but with a pendulum mass 16 positioned radially outward at the planet carrier 8 between the planet wheels 9. In order to reduce installation space, the pendulum masses can be rounded off at the outer diameter. Because of its positioning on the radially outer side, the pendulum mass 16 is particularly efficient compared to an installation located farther radially inward. The pendulum mass 16 shown here operates on the Salomon principle.
(32) FIGS. 7A and B shows a torsional vibration damper arrangement 10 basically like that shown in FIG. 6, but with a pendulum mass 16 having a larger damper mass 68. This larger damper mass 68 can be fastened to the existing mass of the pendulum mass 16 by means of a screw connection. As shown in FIGS. 6A and B, the pendulum mass 16 operates on the Salomon principle.
(33) FIG. 8 shows a torsional vibration damper arrangement 10 basically like that shown in FIG. 1, but with a pendulum mass 16 which is positioned radially outward at the secondary flywheel 4 and can be very efficient due to this radially outward position. Because of the fixed geometric conditions, there is no ability to vary frequency. In this case, a fixed frequency mass damper is provided. Compared to FIG. 1, this embodiment of the torsional vibration damper arrangement 10 has an optional inner spring set 6 in addition. The pendulum mass 16 shown here operates on the Sarazin principle.
(34) FIG. 9 shows a torsional vibration damper arrangement 10 basically like that shown in FIG. 8, but with a Salomon-type pendulum mass 16.
(35) FIG. 10 shows a torsional vibration damper arrangement 10 basically like that shown in FIG. 6, but with a pendulum mass 16 which is positioned radially inward on the side of a coupling, which is to be flanged for example, at the secondary flywheel 4 by means of an offset connection plate 36. This embodiment is used chiefly in radially limited installation spaces for the torsional vibration damper arrangement 10. The pendulum mass 16 shown here is a Salomon-type mass damper.
(36) FIG. 11 shows a torsional vibration damper arrangement 10 basically like that shown in FIG. 10, but with a pendulum mass 16 which is positioned at the secondary flywheel 4 by means of a connection plate 36 radially outward of the through-aperture 67 at the axial height of the coupling arrangement 61. This embodiment is particularly advantageous with respect to space requirement because the space between the coupling arrangement 61 and secondary flywheel 4 can be used. The pendulum mass 16 shown here operates on the Salomon principle.
(37) FIGS. 12A and B shows a torsional vibration damper arrangement 10 basically like that shown in FIG. 11, but with an adjustable fixed-frequency mass damper 15 as pendulum mass 16. In the case of the fixed-frequency mass damper 15, its mass is connected via a leaf spring 17 to the mass to be damped, in this case the secondary flywheel 4. By means of a sliding block 18 which is spring-loaded and moves radially outward against the spring force as a result of the centrifugal force, the flexible length of the leaf spring 17 can be decreased as the rotational speed increases and the stiffness of the leaf spring 17 can accordingly be increased. By changing the flexible length of the leaf spring 17 in this way, the principal engine order can be damped at different rotational speeds. If the length of the leaf spring 17 were always the same, the pendulum mass 16 would only work on one excitation frequency.
(38) FIG. 13 shows a torsional vibration damper arrangement 10 basically like that shown in FIG. 10, but with a pendulum mass 16 which can be positioned radially outward on both sides or also on one side at the intermediate mass 3. The large connection radius is advantageous for the efficiency of the pendulum mass 16. The pendulum mass 16 operates in this case on the Salomon principle.
(39) FIG. 14 shows a torsional vibration damper arrangement 10 basically like that shown in FIG. 13, but with a Sarazin-type pendulum mass 16. Here, in contrast to FIG. 13, the connection radius or centroid radius of the pendulum mass 16 is variable over centrifugal force (=rotational speed) and is accordingly frequency-variable. The connection radius of the pendulum mass is transformed via a resilient bearing.
(40) FIG. 15 shows a torsional vibration damper arrangement 10 basically like that shown in FIG. 1, but with a pendulum mass 16 which is positioned on both sides at the hub disk 7 radially inward of the outer spring set 5. An inner spring set 6 is not provided in this constructional variant. This embodiment can be seen as particularly advantageous with respect to installation space because it utilizes the installation space radially inward of the outer spring set 5. The pendulum mass 16 shown here is a Salomon-type mass damper.
(41) FIG. 16 shows a torsional vibration damper arrangement 10 basically like that shown in FIG. 15, but with a pendulum mass 16 which is arranged radially between the outer spring set 5 and the inner spring set 6 at the hub disk 7. As in FIG. 15, the Salomon-type mass damper is shown here.
(42) Finally, FIGS. 17A and B are schematic depictions of a torsional vibration damper arrangement with individual connection options for the pendulum mass.
(43) Thus, while there have shown and described and pointed out fundamental novel features of the invention as applied to a preferred embodiment thereof, it will be understood that various omissions and substitutions and changes in the form and details of the devices illustrated, and in their operation, may be made by those skilled in the art without departing from the spirit of the invention. For example, it is expressly intended that all combinations of those elements and/or method steps which perform substantially the same function in substantially the same way to achieve the same results are within the scope of the invention. Moreover, it should be recognized that structures and/or elements and/or method steps shown and/or described in connection with any disclosed form or embodiment of the invention may be incorporated in any other disclosed or described or suggested form or embodiment as a general matter of design choice. It is the intention, therefore, to be limited only as indicated by the scope of the claims appended hereto.
REFERENCE NUMERALS
(44) 1 primary mass 2 cover plate 3 intermediate mass 4 secondary flywheel 5 outer spring set 6 inner spring set 7 hub disk 8 planet carrier 9 planet wheels 10 torsional vibration damper arrangement 14 shroud 15 fixed-frequency mass damper 16 pendulum mass 17 leaf spring 18 sliding block 22 bearing intermediate mass 23 bearing intermediate mass 24 bearing secondary flywheel 29 crankshaft 30 main branch 31 superposition branch 32 coupling gear unit 36 connection plate 38 stiffness planet carrier 39 clutch disk 40 clutch disk damper 41 adapter piece 42 axial stop 50 input region 51 vibrational system 52 screw bolt 53 spring arrangement 54 installation space 55 first torque transmission path 56 second torque transmission path 57 spring units 58 spring units 60 output region 61 coupling arrangement 65 phase shifter arrangement 67 through-aperture 68 enlarged damper mass 70 first input portion 71 second input portion 75 superposition unit 77 output portion A axis of rotation A
