Abstract
A coupling device for transmitting a torque from a flywheel mass to a drive device. A ratchet wheel and a transmission element of the flywheel mass ‘SUE’, which is identical to the flywheel mass (or is connected to the flywheel mass, are axially displaceable relative to one another, and pawls of the ratchet wheel can be moved into cutouts of the SUE, and a friction device, particularly in the form of a friction cone, is connectable to the SUE at least partially in a frictionally engaging manner and is connected to the ratchet wheel in a positively engaging manner.
Claims
1-30. (canceled)
31. A coupling device configured to transmit a torque from a flywheel mass to a drive device, comprising: a ratchet wheel having pawls; a flywheel mass ‘SUE’ having cutouts; and a transmission element of the flywheel mass ‘SUE’, which is substantially identical to the flywheel mass or is connected to the flywheel mass; wherein the ratchet wheel and the transmission element of the flywheel mass ‘SUE’ are axially displaceable relative to one another such that the pawls of the ratchet wheel can be moved into cutouts of the SUE; and a friction device, configured as a friction cone, configured to be connected to the SUE at least partially in a frictionally engaging manner and connected to the ratchet wheel in a positively engaging manner.
32. The coupling device according to claim 31, further comprising: an actuating device having a piston and a spring device for the piston and configured to reduce an axial distance between the ratchet wheel and the SUE.
33. The coupling device according to claim 32, wherein the piston is actuatable by hydraulic pressure, wherein a piston nozzle is arranged for the piston, and the piston is arranged to contact the friction cone for transmission of force.
34. The coupling device according to claim 31, wherein ratchet wheel and/or friction device is configured for actuation by hydraulic pressure.
35. The coupling device according to claim 31, further comprising: spring elements having first areas arranged between the pawls and the cutouts of the SUE, wherein a shape of the spring elements is configured to receive the pawls.
36. The coupling device according to claim 35, wherein the spring elements have second areas arranged between friction device and SUE.
37. The coupling device according to claim 35, wherein the spring elements are arranged on a SUE side.
38. The coupling device according to claim 35, wherein the spring elements extend at least partially under a flat angle relative to at least one of respective lateral surfaces of the pawls and/or respective lateral surfaces of respective cutouts.
39. The coupling device according to claim 38, wherein the spring elements are formed asymmetrically, wherein the spring elements extend at a flat angle on a side directed away from a rotational direction.
40. The coupling device according to claim 31, wherein a surface region of the SUE surrounding a cutout is beveled.
41. The coupling device according to claim 40, wherein the surface region surrounding the cutout is rounded at a transition between surface region and the cutout, particularly on a side directed away from a rotational direction.
42. The coupling device according to claim 31, wherein the cutouts and the pawls are configured to correspond to one another but so as to be asymmetrical.
43. The coupling device according to claim 31, wherein the SUE is supported by at least one sliding bearing.
44. The coupling device according to claim 43, wherein the at least one sliding bearing provides a pressure restriction effect and/or the at least one sliding bearing is a combined rolling bearing/rectangular seal.
45. The coupling device according to claim 31, wherein respective areas on both sides of the ratchet wheel are configured to be acted upon by different pressure of a hydraulic fluid, wherein the respective areas are constantly acted upon by a minimum pressure of a hydraulic fluid.
46. A damping device comprising: a housing; a coupling device configured to transmit a torque from a flywheel mass to a drive device, comprising: a ratchet wheel having pawls; a flywheel mass ‘SUE’ having cutouts; and a transmission element of the flywheel mass ‘SUE’, which is substantially identical to the flywheel mass or is connected to the flywheel mass; wherein the ratchet wheel and the transmission element of the flywheel mass ‘SUE’ are axially displaceable relative to one another such that the pawls of the ratchet wheel can be moved into cutouts of the SUE; and a friction device, configured as a friction cone, configured to be connected to the SUE at least partially in a frictionally engaging manner and connected to the ratchet wheel in a positively engaging manner; a first damping device configured as a torsional damper; a drive transmission element configured as a crankshaft hub; and an output transmission element configured as a hub disk, wherein the SUE is configured as a primary plate of the damping device.
47. The damping device according to claim 46, further comprising a spring element arranged between the ratchet wheel of the coupling device and the drive transmission element.
48. The damping device according to claim 47, wherein the spring element is configured as a radial shaft spring plate.
49. The damping device according to claim 46, wherein the SUE has a rotary seal, configured as a radial shaft sealing ring, for sealing relative to the drive transmission element.
50. The damping device according to claim 46, wherein the housing is at least partially formed by a vertical wall of a drive mechanism, wherein the vertical wall has a rotary seal for sealing.
51. The damping device according to claim 50, wherein the housing is at least partially formed by a bell housing which is connected to the vertical wall of the drive device, wherein a seal is at least partially arranged between vertical wall of the drive device and bell housing.
Description
BRIEF DESCRIPTION OF THE DRAWINGS
[0040] Preferred constructions and embodiment forms of the invention are shown in the drawings and are described more fully in the following description Like reference numerals designate like or similar or functionally like component parts or elements.
[0041] The drawings show schematically and in section:
[0042] FIG. 1 is a damping device;
[0043] FIGS. 2a, 2b is a damping device according to FIG. 1 showing an open (FIG. 2a) and closed (FIG. 2b) coupling device;
[0044] FIG. 3 is a damping device;
[0045] FIG. 4 is a damping device;
[0046] FIG. 5 is a damping device;
[0047] FIG. 6 is a damping device;
[0048] FIG. 7 is a damping device;
[0049] FIGS. 8a, 8b is a damping device;
[0050] FIG. 9 is a damping device;
[0051] FIG. 10 is a damping device;
[0052] FIGS. 11a, 11b, 11c are various conditions and configurations of the coupling device;
[0053] FIGS. 12a, 12b is a coupling device;
[0054] FIGS. 13a, 13b, 13c is a coupling device; and
[0055] FIGS. 14a, 14b are various conditions and configurations of a coupling device;
[0056] FIG. 15 are parts of a damping device shown schematically and three-dimensionally; and
[0057] FIG. 16 are parts of a damping device shown schematically and three-dimensionally.
DETAILED DESCRIPTION OF THE PRESENTLY PREFERRED EMBODIMENTS
[0058] FIG. 1 shows a damping device according to an embodiment form of the present invention.
[0059] A damping device 1 in a drivetrain of a hybrid vehicle is shown in detail in FIG. 1. The damping device 1 is connected to a drive element 20 in the form of a crankshaft hub having an outer toothing 21. The outer toothing 21 of the crankshaft hub 20 engages in a corresponding inner toothing of a ratchet wheel 15 for transmitting torque. The SUE is arranged and configured in this case directly as flywheel mass in the form of a primary plate 2a, 2b which is supported on the crankshaft hub 20 via a sliding bearing 19. The motor-side area of the primary plate is designated by reference numeral 2a, and the transmission-side area is designated by reference numeral 2b. Further, a radial shaft sealing ring 11 is arranged between crankshaft hub 20 and primary plate 2a, 2b. The primary plate 2a has cutouts 27 that correspond to pawls 15a of the ratchet wheel 15. In other words, pawls 15a of the ratchet wheel engage in cutouts 27 of the primary plate 2a, 2b and transmit torque.
[0060] The ratchet wheel 15 has an outer toothing on its radial outer side that engages with an inner toothing of a friction cone 14. The friction cone 14 in turn communicates with the primary plate 2a at least partially in frictional engagement. The primary plate 2a, 2b in turn forms the primary side of a torsional damper 4. As is customary, the torsional damper 1 has a spring set 4 and corresponding cover plates 5. The spring set of torsional damper 4 is connected in a known manner to a torsional damper hub 12 via a hub disk 6 and a spline 7. A cover 3b is arranged between the hub disk 6 and the ratchet wheel 15 or friction cone 14 and, together with a cover 3a which covers the cutouts 27 and a portion of the primary plate 2a on the motor side, provides a pressure space for the coupling device. The primary plate 2a, 2b which is U-shaped in this instance substantially surrounds spring set 4 and the hub disk 6 laterally and radially above spring set 4. To this end, the primary plate 2a, 2b has a corresponding covering on the drive side as well as on the transmission side. In the area of the torsional damper hub 12, the area of primary plate 2b arranged on the transmission side is fixed thereto with a closure cover 8 and with an O-ring 9 and a snap ring 10. A radial shaft sealing ring 11 is arranged between closure cover 8 and a bearing shield 33 extending in radial direction. The bearing shield 33 in turn has a further seal 16 at its radial outer side for sealing relative to further transmission parts, for example, a speed-adaptive damper or the like. Further covers 3c, which perform a bearing function on the one hand and serve to connect a hydraulic fluid pressure line or the like on the other hand, are arranged in the area of the torsional damper hub 12. Torsional damper hub 12 and crankshaft hub 20 are supported on an input shaft 24, which has connections 25, 26 downstream of the damping device with respect to torque for connecting a speed-adaptive damper and/or an inner plate carrier or the like. A radial shaft spring plate 37 is arranged between outer toothing 21 of crankshaft hub 20 and ratchet wheel 15 to compensate for axial tolerances.
[0061] FIGS. 2a, b show a damping device according to FIG. 1 with open (FIG. 2a) and closed (FIG. 2b) coupling device.
[0062] FIGS. 2a and 2b basically show a damping device according to FIG. 1. The open position SO of the coupling device in which the ratchet wheel 15 does not engage with the primary plate 2a, 2b is shown in FIG. 2a, while the closed position SG of the coupling device in which ratchet wheel 15 engages with the primary plate 2a, more accurately in which the pawls 15a engage in cutouts 27 of the primary plate 2a, is shown in FIG. 2b.
[0063] In the open position SO, the area designated by reference character HD is acted upon by oil under high pressure. Basically, this refers to the areas between the transmission-side primary plate 2b, spring set 4 of the torsional damper and primary plate 2a, including cutouts 27. The low-pressure area ND is substantially formed by leakage oil returns 28 in the area of the crankshaft hub 20 and the areas of friction cone 14 and ratchet wheel 15 on the remote side of the cutouts 27 of primary plate 2a. The higher oil pressure in the cutouts 27 prevents the ratchet wheel 15 from engaging in the cutouts 27.
[0064] In the closed position SG according to FIG. 2b, the areas of high pressure HD and low pressure ND substantially switch. If the area of the friction cone 14 and ratchet wheel 15 remote of the cutouts 27 of primary plate 2a is acted upon by higher oil pressure than the area of the cutouts 27, the pressure difference causes the ratchet wheel 15 to be pressed in direction of the primary plate 2a and the friction cone 14 is brought into axial contact with the primary plate 2a. Accordingly, torque can then be transmitted correspondingly from the primary plate 2a ultimately to the crankshaft 20.
[0065] FIG. 3 shows a damping device according to a further embodiment form of the present invention.
[0066] FIG. 3 basically shows a damping device 1 according to FIG. 1. In contrast to the damping device 1 according to FIG. 1, the rotary seal 11 in the form of the radial shaft ring at the primary plate 2a can be omitted in the damping device 1 according to FIG. 3. Instead, a corresponding rotary seal 30 is arranged toward primary plate 2a between a vertical motor rear wall 31 in order to achieve a corresponding seal. Further, leakage oil returns 28 via the crankshaft hub 20, a toothing of an input shaft 24 and possibly further additional boreholes in the wet space are depicted by a dashed line.
[0067] FIG. 4 shows a damping device according to a further embodiment form of the present invention.
[0068] FIG. 4 basically shows a damping device 1 according to FIG. 3. In contrast to the damping device 1 according to FIG. 3, the rotary seal 30 in the damping device 1 according to FIG. 4 is arranged through a seal 32 between motor rear wall 31 and a bell housing 31′. This defines a first wet space NR1 of torsional damper 4 and coupling element between motor rear wall 31 and transmission, wherein the return is carried out via a bearing shield 33 into the transmission. Accordingly, the bearing shield 33 separates the first wet space NR1 from the wet space of the transmission NR2.
[0069] FIG. 5 shows a damping device according to a further embodiment form of the present invention.
[0070] FIG. 5 basically shows a damping device 1 according to FIG. 1. In the damping device 1 according to FIG. 5, in contrast to the damping device 1 according to FIG. 1, the closure cover 8, which is fixed to the transmission-side portion of the primary plate 2b via an O-ring 9 and snap ring 10 is supported on the transmission side in the area of a hydraulic connection 47, 49 by a bearing 35 relative to the transmission-side bearing shield 33 in addition to the bearing support at the crankshaft hub 20. Bearing support 35 is preferably constructed as a sliding bearing, the latter providing a pressure restricting effect. Bearing support 35 can also be constructed as a combination of a rolling element bearing and a rectangular ring seal.
[0071] FIG. 6 shows a damping device according to a further embodiment form of the present invention.
[0072] FIG. 6 basically shows a damping device 1 according to FIG. 5. In the damping device 1 according to FIG. 6, in contrast to the damping device 1 according to FIG. 5, a spring plate 54 is arranged between ratchet wheel 15 and cutouts 27 of primary plate 2a for backlash-free force transmission, tolerance compensation and/or for damping an engagement impact of the pawls 15a in cutouts 27. The spring plate 54 can also be arranged in the area 54′ of the friction cone 14 in such a way that the latter forms an opposing friction surface in the friction cone 14. One of the advantages achieved by this consists in that the primary plate 2a, 2b can be produced from deep-drawable material.
[0073] FIG. 7 shows a damping device according to a further embodiment form of the present invention.
[0074] FIG. 7 basically shows a damping device 1 according to FIG. 5. In the damping device 1 according to FIG. 7, in contrast to the damping device 1 according to FIG. 5, channels 38 are arranged in the bearing shield 33 for connecting a hydraulic pressure supply line 39, for example, from the transmission housing with external feed, for example, in the form of a hose line and/or pipe line.
[0075] FIGS. 8a, b show a damping device according to a further embodiment form of the present invention (FIG. 8a) and a detail of the damping device according to FIG. 8a (FIG. 8b).
[0076] FIG. 8a basically shows a damping device 1 according to FIG. 1. In the damping device 1 according to FIG. 8, in contrast to the damping device 1 according to FIG. 1, a housing 41 for this damping device 1 is arranged for screwing to the motor rear wall 31. The housing 41 has channels 41′ for the internal leakage oil return. Further, housing 41 is supported on the motor side in the area of the primary plate bearing at crankshaft hub 20 by a bearing support 44. Further, as is shown in FIG. 8b, blades 40 are arranged on the radial outer side of the primary plate 2a—that is, basically at the radial outer side of the housing for the torsional damper with spring set 4 and hub disk 6 in order to control the oil flow F corresponding to a rotational direction of the motor MDR for the coupling device.
[0077] FIG. 9 shows a damping device according to a further embodiment form of the present invention.
[0078] FIG. 9 basically shows a damping device 1 according to FIG. 5. In the damping device 1 according to FIG. 9, in contrast to the damping device 1 according to FIG. 5, instead of forming the friction cone 14 and ratchet wheel 15 itself as piston, a corresponding piston 42 is now arranged for actuating ratchet wheel 15 and friction cone 14. The piston 42 presses on the friction cone 14 in the area of the primary plate 2a. A plate spring 17 pushes the ratchet wheel 15 into the closed position. Oil for actuating the piston 42 can flow via a piston nozzle 43 into the oil pressure chamber of the spring set 4 and hub disk 6. In order to cancel the coupling of ratchet wheel 15, friction cone 14 and primary plate 2a again, the oil is correspondingly rerouted and the piston 42 returns to its initial position, wherein the plate spring 17 is pressed back by the ratchet wheel 15.
[0079] FIG. 10 shows a damping device according to a further embodiment form of the present invention.
[0080] FIG. 10 basically shows a damping device 1 according to FIG. 1. In the damping device 1 according to FIG. 10, in contrast to the damping device 1 according to FIG. 1, a spring plate 22 with tangential spring arms is arranged at the crankshaft hub 20 instead of the toothing between ratchet wheel 15 and crankshaft hub 20, which spring plate 22 is fixed to the crankshaft hub 20 by a screw-on plate 23. With the spring arms of spring plate 22, which extend substantially in radial direction, the ratchet wheel 15 is fixed to this spring plate 22 via a rivet connection 18. Further, a cover 3d for forming the torsional damper wet space NR1 is constructed as a bearing shield 33. A receiving borehole 49 is arranged in the bearing shield 33 for receiving a connection 47. Connection 47 can be formed for receiving a hydraulic hose and/or a pipe line for a hydraulic fluid, for example, from a separate valve block in the bell housing or the like. Further, a rubberized intermediate layer 48 is arranged as compensation element for movements of the crankshaft.
[0081] FIGS. 11a, 11b and 11c show various conditions and configurations of the coupling device according to a further embodiment forms of the invention.
[0082] The coupling device is shown in the open position in FIG. 11a, running against a bevel in FIG. 11b, and in the closed position in FIG. 11c.
[0083] In FIG. 11a, the pawl 15a of the ratchet wheel 15 does not engage in the cutouts 27 of primary plate 2a. The area around the cutouts 27, i.e., the peripheral area of the cutouts 27 in the direction of the ratchet wheel 15, is provided with a bevel 50. Further, the pawl 15a is likewise provided with a bevel 51 which extends substantially under the same angle as the bevel 50 of pawl 15a.
[0084] In FIG. 11b, the ratchet wheel 15 now runs against the bevel 50 of the primary plate 2a with its pawl 15a, but does not engage in cutouts 27.
[0085] FIG. 11c shows the condition of the coupling device with pawls 15a engaging in the cutouts 27.
[0086] FIGS. 12a and 12b show coupling devices according to further embodiment forms of the present invention.
[0087] FIG. 12a basically shows the arrangement of primary plate 2a and ratchet wheel 15 according to FIG. 11 a. In the ratchet wheel 15 according to FIG. 12a, in contrast to the primary plate 2a according to FIG. 11a, the edge 52 is now rounded behind the beveled area 50, particularly in the form of a tractrix 53, which would result due to wear on soft parts.
[0088] FIG. 12b again shows a primary plate 2a according to FIG. 11a. In contrast to the bevel 50 of the primary plate 2a of FIG. 11a, the primary plate 2a of FIG. 12b now has a rounded area, for example, in the form of a curve. In other words, the engaging edge 52 does not have a bevel but rather only a rounded area 53.
[0089] FIGS. 13a, 13b and 13c show coupling devices according to further embodiment forms of the present invention in various conditions.
[0090] FIG. 13a basically shows the coupling device 1 according to FIG. 11a. In the coupling device according to FIG. 13a (open coupling device) and FIG. 13b (closed coupling device), in contrast to the coupling device 1 according to FIG. 11a, a spring element in the form of a spring plate 54 is now arranged on primary plate 2a and in cutouts 27. The spring element 54 has a flat-tapering angle 55 in the cutouts 27 of the primary plate 2a for backlash-free force transmission. In contrast to the embodiment forms in FIGS. 13a and 13b, FIG. 13c shows an asymmetrically formed spring element 54 with planar contact on the drive side 54a and flat spring angle 55 on the coast side 54b based on the rotational direction of the motor MDR.
[0091] FIGS. 14a and 14b show a coupling device in the open condition and closed condition according to a further embodiment form of the present invention.
[0092] In FIGS. 14a and 14B, the cutouts 27 in the primary plate 2a and the pawls 15a of the ratchet wheel 15 are formed asymmetrically. In this case, the drive side 54a is formed in a planar manner with respect to the rotational direction of the motor MDR and the coast side 54b is beveled, the bevel being configured such that the cutout 27 increases in diameter in direction of the ratchet wheel 15. A further alternative embodiment form is shown in dashed lines. In this further alternative embodiment form, a spring plate 54 is arranged at the ratchet wheel 15 and/or a spring plate can be arranged at the primary plate 2a. The advantage of these embodiment forms consists in a toothing that is free from backlash or at least has minimal backlash. Further, axial restoring forces result from the bevel only from smaller coasting torque.
[0093] FIG. 15 shows a three-dimensional depiction of parts of the damping device in open position of the coupling device according to a further embodiment form of the present invention, and FIG. 16 is a three-dimensional depiction of parts of the damping device in closed position according to a further embodiment form of the present invention.
[0094] FIGS. 15 and 16 basically show a part of a damping device 1 according to FIG. 1 in three-dimensional form. Radially from inside to outside, the crankshaft hub 20 is shown first with its outer toothing engaging in an inner toothing of the ratchet wheel 15. A corrugated spring 37 is arranged between the inner toothing of the ratchet wheel 15 and the outer toothing of the crankshaft hub 20. As in FIG. 1, pawls 15a of the ratchet wheel 15 are arranged opposite cutouts 27 of the primary plate 2a. The primary plate 2a is supported at the crankshaft hub 20 via a sliding bearing 19. An outer toothing which engages in an inner toothing of a friction cone 14 is arranged on the radial outer side of the ratchet wheel 15. When the coupling device is actuated, the friction cone 14 is connected at least partially in a frictionally engaging manner to a radial inner side 13a of the primary plate 2a but not to an axial inner side 13b. The motor-side cover 3a and the primary plate 2a are hidden in FIG. 16.
[0095] In summary, the invention and, in particular, embodiment forms thereof show a simple, compact and economical coupling device for a fast start of an internal combustion engine through transmission of torque from a rotating flywheel mass to a crankshaft. Further, the speed difference between SUE and ratchet wheel can be adjusted in a very precise manner, which allows a particularly reliable and defined coupling engagement. A further advantage consists in that few component parts are required, particularly when the ratchet wheel and friction cone themselves are formed as piston for pressure actuation.
[0096] Further, embodiment forms of the invention allow a toothing which is free from backlash or at least has minimal backlash, a transmission of force, a simple production, tolerance compensation and a damped engagement impact of the ratchet wheel in the SUE, which prolongs service life.
[0097] While the present invention has been described with reference to preferred embodiment examples, it is not limited to these embodiment examples but rather may be modified in various ways. 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.
