HK1066584A - The torque converter - Google Patents

Description

Torque converter

Technical Field

The present invention relates to torque converters that hydraulically connect an internal combustion engine to a transmission.

Background

In the context of the present invention, the term "torque converter" is intended to mean a hydrodynamic torque converter, as its detailed name. Such torque converters have been known for decades. It is basically composed of a torque converter housing, a pump, a worm gear and a guide wheel. The pump is fixedly connected with the torque converter shell. The oil injection part is moved by the rotation of the torque converter, wherein the oil flow thus generated drives a worm gear. To improve efficiency, a guide wheel is provided between the worm gear and the pump. Torque is generated in the worm gear by the energy of the oil flow in the worm gear. This torque is derived via a worm gear shaft, also referred to as the transmission input shaft. Since the internal combustion engine has torsional vibrations on its crankshaft and thus also on its flywheel mass, a torque converter is provided in a motor vehicle with a so-called worm gear damper. The worm gear damper stores a large instantaneous torsional vibration amplitude, and it releases the stored amount to the transmission when the instantaneous torsional vibration amplitude is small. Thereby reducing the torsional vibration amplitude as a whole. Torsional vibration dampers also typically have damping elements by which additional interfering torsional vibration energy is absorbed.

Torque converters typically have a torque converter bypass clutch that is closed when the ratio of the speed of the worm gear to the speed of the pump is about 85%. Thereby increasing the efficiency of the torque converter to almost 100%. The closing of the converter bypass clutch is achieved by the oil flow in the torque converter. The oil flow closing the torque converter crossover clutch may be oil flow out between the pump and the worm gear or additional static pressure oil flow.

The energy in the worm gear damper flows through the input member adjacent the worm gear and through the springs, which in turn transfer the energy to the output member (also referred to as the flange). The output member is connected, sometimes integrally, to a hub that retransmits the power flow to a worm gear shaft, also referred to as the transmission input shaft.

In a torque converter, components are provided in the power flow path between the worm gear and the transmission input shaft, which must be subjected to the torque to be transmitted. Furthermore, these components must be guided and/or supported with high quality. This leads to considerable costs in view of the use of torque converters in motor vehicles and the series of products associated therewith.

Disclosure of Invention

The object of the present invention is therefore to provide a torque converter which can be produced cost-effectively.

According to the invention, a cost-effective construction is to be achieved in the region of the worm wheel, the input part adjacent to the worm wheel and the hub. The essence of the invention here is that these components are manufactured essentially without machining.

In a first embodiment of the invention, the worm gear housing or the input part of the worm gear damper is produced from a plate-shaped material, for example a steel plate, and is produced by stamping.

In another embodiment, the worm housing with an internal carrier is produced by a metal forming technique. The carrier has the shape of a bead or a journal, wherein the carrier does not necessarily have to obtain its shape by the manufacturing method. The bracket has the advantage that the essentially disk-shaped worm gear housing has a small cylindrical surface in the region of its inner diameter. The cylindrical surface can be used as a bearing surface, whereby the worm gear case can be supported or braced on the adjacent hub.

In a further embodiment of the invention, the input part of the worm damper adjacent to the worm casing is provided with a carrier, whereby this part can also be supported on the circumferential surface of the hub. It should be emphasized here that either the worm gear housing or the just described input member can be provided with a carrier. Further positioning is also possible by a suitable axial orientation of the carrier.

If the sheet metal is machined by means of metal-forming machining techniques, burrs may be produced and, depending on the pressing direction, corresponding burr orientations or axial indentations independently of the pressing direction may be produced. Burrs or notches can significantly affect bearing and/or sliding performance and, in certain cases, damage the bearing surfaces on the hub. This can be solved by the bracket, i.e. the profiled cylindrical surface, being finished to improve the quality. If the surface is machined by turning, only a few tenths of a millimeter of cutting depth is sufficient to obtain a perfect bearing surface. However, the bearing surface can also be realized by broaching with a broach or by rolling (i.e. a chipless machining method).

The carrier according to the invention has advantages not only when used as a bearing surface on a hub. When, for example, the carrier is clearly spaced from the hub, it can guide the needle bearing provided between the worm wheel and the guide wheel with its inner diameter or with its outer diameter. The diameter of the needle bearing is therefore usually considerably larger than the geometry of the hub, since the relatively large diameter of the needle bearing ensures good guiding quality of the adjacent components.

In an advantageous embodiment of the invention, the worm gear casing and the adjacent input part are connected to one another in a form-fitting manner. The form-locking connection rivet is particularly advantageous, since it does not require any special machining precision for the holes. The riveted connection can be realized here both by means of a rivet bolt and by means of a rivet projection. The connection by means of the riveting lug has the advantage that it does not require: first, holes are punched in both parts, and then rivet bolts are provided in each hole pair for riveting in another process step. In contrast, the riveting projections are only openings in one part. The other component will be "journalled" (expressed simply) where the other component is provided with holes. The end of the "journal" extending into the bore is then upset by compression. Thus, one part of the "journal-bore" connection can be merely plugged and the other part riveted.

The worm gear housing and the adjacent input part can also be connected to one another in an advantageous manner in a manner forming a power transmission chain. A connection forming a power transmission chain, for example by soldering or gluing, has the advantage over a positive-locking connection that no punching is required in the first place, which can lead to undesirable deformation of the worm gear casing or of the adjacent input part.

A material-bonded connection of the worm gear case and the adjacent input part is also advantageous. No additional holes (for example for riveting) and no additional other types of connecting materials (as in the case of soldering or bonding) are required in the material-bonded connection. In the joining of materials, in particular the joining by welding, the material closely approximates the components to be joined in terms of its properties and its composition, although additional materials are also required. Advantageously, no additional material is required if the fusion welding of the worm gear casing and the input part is carried out by means of laser welding, resistance welding, spot welding or friction welding.

The individual components are first prefabricated during assembly of the torque converter and then assembled together during final assembly. The final process step is typically to mount the pump housing to the other torque converter housing (in which the other components are already installed), with the two housings then being welded to each other. One component in the assembly of the torque converter is a worm gear damper, which is riveted to the inner lamination carrier of the torque converter bypass clutch, for example on the left. Since the worm wheel damper (consisting of the left and right input part, an intermediate output part and the associated spring) is usually riveted on the circumference, the fixed connection (riveting or welding) of the right input part to the worm wheel housing leads to difficulties in processing, since the tolerances of its shape and position are superposed to form large tolerances by means of a plurality of axially arranged components. And in this construction, it is generally not possible to introduce a riveting tool. For this reason, in the prior art, a pluggable, rotationally fixed connection is provided between the input parts adjacent to the worm gear housing. The prior art therefore comprises only the worm gear damper and the inner lamination carrier.

However, in the present invention, the worm gear housing and the input part of the adjacent worm gear damper are not only rotationally fixed but are also permanently connected to one another. This makes it possible to achieve a precise position of the two parts, which position does not change relative to one another. The high mechanical and partial thermal loads of a torque converter can lead to axial displacements of the individual components. Since the output part of the worm wheel damper is connected to the transmission input shaft via the hub and the hub is fixed precisely in the axial direction by means of bearings, the output part of the worm wheel damper, although fixed in a rotationally fixed manner, is axially displaceable and is connected to the hub by means of its contour. This results in a plurality of new construction possibilities, as will be explained in more detail in the description of the figures. In one embodiment of the invention, the input part facing away from the worm gear housing is provided with a circumferential and inwardly located contour. However, the contour of the input part is designed such that a defined maximum relative rotational angle is allowed between the hub and the input part. If the determined maximum relative rotational angle is reached, continued rotation of the input member relative to the hub is stopped. In a preferred embodiment of the invention, the profile is an external toothing on the hub and an internal toothing on the output (or input) part. It is particularly advantageous if the outer and inner toothed segments are self-centering. This self-centering works in such a way that: by the configuration of the "flanks", the externally situated internally toothed segments will assume the same centre of rotation as the hub when torque is placed on them. In a further advantageous embodiment of the invention, the profile is formed substantially as a known multiple-tooth profile, which has a uniform cross section in the axial direction. But in the present invention has at least one raised profile. The raised contour can occur several times in the contour portion and be reproduced periodically in the circumferential direction. The advantages of this profile are: despite the special configuration, the cost of this profile is no higher than that of the multi-toothed profiles of the prior art, since this profile can be produced in a simple manner and with high precision by means of broaching. Since the torque converter according to the invention is intended for motor vehicles, in particular for motor vehicles, and therefore usually has a high number of production pieces, the broaching tool in this way has no influence on the costs. The outer parts, such as the input part and the output part of the worm damper, can also be produced cost-effectively together with their inner contour by stamping.

As described above, the torque converter is constituted by each component separately manufactured in advance. After a torque converter jumper clutch is inserted into the torque converter housing, the hub (which is subsequently attached to the transmission input shaft) and the worm gear damper and the worm gear case attached thereto are inserted. When the worm wheel damper and the hub which may have been installed therein are operated, the hub may slip down due to its axial mobility relative to the output part of the worm wheel damper. In order to prevent this, the geometry of the hub and worm gear damper is configured in such a way that they remain together in the preparation phase of the final assembly of the torque converter. The two components are coupled to each other by a so-called loss prevention section. In one embodiment of the invention, the loss prevention element is realized in such a way that the input part facing away from the worm gear casing has an inner diameter which is smaller than the outer diameter of the hub, as can be seen in the following description of the figures.

As already described, the connection of the hydraulic energy, i.e. the worm wheel energy, to the hub of a rear derailleur can be realized by a component which is produced essentially without machining, in which case the component is made of a plate-shaped material and is constructed as a stamping. In a further embodiment of the invention, the component is produced essentially without machining, is made of sintered metal, preferably sintered steel, and is formed as a molded part. A component made of sintered metal has the advantage that it can be produced with high precision and with high strength by means of a corresponding mold. In general, no finishing is required here. Finishing is only required if a particularly high surface quality is required or if the surface quality is lower than an internal dimension due to shrinkage, i.e. shrinkage by the component during sintering. Sintered components are also particularly advantageous, since the complex mold itself can be realized in a simple manner without further processing costs, for example an outer contour or individual projections extending in the axial direction. It has hitherto been customary to manufacture the hub of a worm gear damper from a swaged part. For this purpose, a die-forming machining operation is used first, in order to subsequently finish the rough-machined component by cutting, for example by turning or broaching. And a ring, by means of which the worm wheel housing is mounted on an outer diameter of the hub and the worm wheel housing is provided with projections, has hitherto been realized as a die forging. This "hub connection" of the worm gear case to the transmission input shaft is very problematic in finishing work by means of turning, since the cutting work is greatly limited by the projections which project from the end face of this "hub connection" of the worm gear case and serve as angle stops.

The hub-the part that introduces torque into the transmission input shaft-is typically a rotationally symmetric part. It can thus be processed without problems on a lathe or by means of a broach. However, the component can also be produced in a significantly simplified manner in that it is to be produced from a sintered metal, preferably sintered steel, and is formed as a molded part.

Drawings

The invention will now be described in detail with the aid of the accompanying drawings. The attached drawings are as follows:

FIG. 1: a partial cross-sectional view of a torque converter having a carrier-like configuration of the input member and a carrier-like configuration of the worm gear case welded to each other, and a vertical circumferential weld having the input members;

FIG. 2: as in the cross-sectional view of fig. 1, but with parallel, circumferential welding of the input members;

FIG. 3: a partial cross-sectional view of a torque converter wherein the connection of the worm gear case to the adjacent input member is achieved by means of a riveted projection;

FIG. 4: a partial cross-sectional view of a torque converter wherein the attachment of the worm gear case to the adjacent input member is accomplished by means of a rivet stud;

FIG. 5: a partial cross-sectional view of a torque converter fitted with axial clamping members between the hub and the hub-like support member of the worm gear;

FIG. 6: a partial cross-sectional view of a torque converter incorporating axial clamping members between the hub and the hub-like support member of the worm gear and the adjacent input member;

FIG. 7: a partial cross-sectional view of a torque converter having an outer profile for the hub and an inner profile for the output member and the input member;

FIG. 8: a radial cross-section of the profile of the hub and the output member according to fig. 7;

FIG. 9: a radial cross-section of the profile of the hub and the input member according to fig. 7;

FIG. 10: a partial cross-sectional view of a torque converter having spaced apart input members;

FIG. 11: a partial cross-sectional view of a worm gear case and an adjacent input member;

FIG. 12: a partial cross-sectional view of a worm gear case having a bracket, the worm gear case being supported on an outer diameter of the hub by the bracket;

FIG. 13: a partial cross-sectional view; wherein the worm gear shell and an output part are respectively provided with a bracket;

FIG. 14 a: a radial cross-sectional view of the edge region of a worm gear damper;

FIG. 14 b: a top sectional view of the part belonging to fig. 14 a.

Detailed Description

Terms used in the following description, such as "upper", "lower", "left" and "right", shall first be defined to refer only to the orientation of the components in the figures. In practice the actual direction may differ from what is described. It should furthermore be noted that in the figures, although in the nature of rotating parts, the surrounding lines have been omitted for clarity.

Fig. 1 shows a partial sectional view of a torque converter 1, which also shows: the components thereof are suitable not only for small but also for large torque converters or worm wheel diameters. The torque converter housing 2 houses a number of components and parts. A pump (not shown; it should be on the right of the broken-out section of the omitted line) is connected to the torque converter housing 2 in a rotationally fixed manner. Other important components are: a worm gear 4, a stator 5, a torque converter bridge clutch 7 and a worm gear damper 26. All the above-mentioned components are rotatable about the common axis of rotation 3 of the torque converter, wherein the stator 5 is mounted on the stator shaft 23 in a rotationally fixed manner by means of a multi-tooth profile 25, and the worm wheel 4 is mounted on the worm wheel shaft 22 in a rotationally fixed manner indirectly by means of a multi-tooth profile 24. The oil flow 47 driven by the pump partially flows out from the clearance between the pump and the worm wheel 4 and flows through the inside of the torque converter 1. The oil flow 47 leaves the torque converter 1 via a second channel, which is designated by reference numeral 15. A first channel, not shown here, is used for feeding the oil flow 47. The worm wheel 4 is driven by the oil flow 47, wherein a torque acts on the worm gear housing 40. Since the worm gear housing 40 is connected to a right input part 29 of the worm gear damper by means of the weld 39, the torque is also introduced into the worm gear damper 26.

The worm damper 26 consists of a right input part 29, a left input part 28, an output part 27 arranged between them and an axial clamping part 36. Furthermore, spring elements are provided which belong to the worm gear damper 26 and which are formed here by an outer spring 32 and an inner spring 33 and which are arranged in a spring window 30 which is provided with a spring window limb 31. In order to prevent the relative angle between the input members 28, 29 and the output member 27 from being exceeded, a rotation angle stop 34 is additionally provided in the worm gear damper 26. In this exemplary embodiment, the angle stop 34 is formed by a web which is stamped out partially in the right input part 29 and which is bent during or after stamping and which at the same time penetrates into a recess (preferably an arc-shaped groove) in the output part 27. The left input part 28 of the worm gear damper is connected to an inner lamination carrier 10 by means of at least one rivet pin 38. A plurality of laminations 8 are located between the inner lamination carrier 10 and an outer lamination carrier 9. The laminations 8 are alternately connected by their contour, as viewed from left to right, to the inner lamination carrier or to the outer lamination carrier without relative rotation. A pressure plate 21 and/or a collar block the lamination stack to the right. If the converter crossover clutch 7 is to be closed, in this embodiment a closing oil flow 48 from inside the worm shaft 22 is directed through the third channel (reference 14) to the back of a hold-down member 11. The pressing part 11 is arranged in a sliding manner on a guide 19, which is also supported on a worm gear shaft 22. In order to prevent relative movement of the pressure element 11 with respect to the guide element 19 or with respect to the upper, cylindrical sealing surface, the pressure element 11 and the guide element 19 are connected to one another in a rotationally fixed manner by means of an axially extending toothed segment 18. The seals 12 and 13 are used for: the pressure of the closing oil flow 48 does not decrease or only slightly decreases in the direction of the oil flow 47. If the closing oil flow 48 now increases its pressure, the pressure element 11 moves in the direction of the lamination stack 8 of the converter bridging clutch 7, which is thus closed. If the closing oil flow 48 reduces its pressure, the oil flow 47 acts increasingly on the other side of the pressing part 11. The oil flow 47 can act on the pressure part 11, since the oil flow 47 passes through the gaps between the parts and components (for example between the laminations 8 and the lamination holders 9 and 10) and can thus act on the right side of the pressure part 11. The oil flow 47 can flow into the second channel (reference 15) through the partial channel 37 (e.g. in the hub 43).

There are many structural specificities in fig. 1. In a first important new construction configuration, the worm gear case 40 is connected to the right input member 29 by means of a weld 39. The weld 39 shown here is for example a laser weld. Welding by means of a laser has the advantage that, as shown in the exemplary embodiment of the figure, two planar parts are placed on top of one another and then the upper part, in this case the worm gear housing 40, and the lower part, in this case the input part 29, can be welded to one another without preparation for a weld seam.

A second constructional particularity is that the right input member 29 is provided with a bracket 42 and is thus mounted like a bearing bush on the outer diameter of the hub 43. Because the worm gear housing 40 is connected to the input member 29, the carrier 42 of the input member is to some extent a hub-like support 35 for the worm gear on the hub 43.

The worm gear case 40 is also provided with a bracket 41. The carrier 41 supports a needle bearing 16 with its inner diameter. The needle bearing 16 is used to reduce the friction between the worm wheel 4 (or the worm wheel housing 40) and the stator 5. When a relative movement is produced between the stator 5 and the worm wheel 4, i.e. when the idle part 6 of the stator is not braked, friction forces may occur.

A further structural feature results from the power connection of the output part 27 to the hub 43, since these two parts are connected to one another by means of a contour 49. The contour is provided with a uniform cross section in the axial direction and can, for example, form an external toothing and an internal toothing.

The profile 49 has a plurality of tasks. The first task is to allow axial relative movement between the two parts when pushed axially onto the worm gear damper 26 and/or the hub 43. If this axial movement is impeded, this can cause an excessive clamping of the worm damper 26 inside and a loss of the frictional force which is determined to be adjusted between the input parts 28 and 29 and the output part 27 in the region of the axial clamping element 36.

The second task of the profile 49 is to facilitate assembly. When, for example, the worm gear housing 40 is welded to the right input part 29 and the inner lamination carrier 10 is fixedly connected (e.g., riveted) to the left input part 28, the two "halves" of the worm gear damper 26 can be joined and fixed circumferentially depending on the positioning of the output part 27 and the axial clamping element 36 (e.g., in the form of a disk spring or a corrugated disk). The fastening can be effected, for example, by riveting or, as shown in the figure, by means of a weld 39. The assembly thus formed now extends from the inner lamination carrier as far as the worm wheel.

If the torque converter 1 is now installed in the manner described, it is advantageous: after the hub 43 has been inserted into the converter housing 2, the unit, which is essentially composed of the inner disk carrier 10, the worm damper 26 and the worm gear housing 40, can be guided and pushed in by the contour 49 of the hub 43. In the embodiment shown in fig. 1, however, the left input member 28 is provided with an inner diameter that is significantly smaller than the outer diameter of the profile 49 of the hub 43. The small inner diameter of the input member 28 does not allow the hub 43 to "pierce" the output member 27 afterwards. Conversely, it can be said that the hub 43 is also inserted when the worm damper 26 is preassembled, and then the two input parts 28 and 29 are fixedly connected to one another on their circumference, so that the hub 43 is not lost before the torque converter 1 is finally assembled. The reduced inner diameter of the input member 28 or the increased outer diameter of the hub 43 thereby forms a loss prevention portion 46.

The embodiment of fig. 1 also shows another structural particularity. The left input part 28 extends almost completely radially in the circumferential region, i.e. it forms a disk-like structure here, while the right input part 29 forms a pot-like configuration in the circumferential region. A substantially vertical butt joint of the sheets is thereby obtained in the circumferential region of the input members 28 and 29. If the input parts 28 and 29 are welded to one another only in the circumferential region, at least in succession, a defined intermediate space or distance of the input parts 28 and 29 is obtained for the axial clamping element 36 and the output part 27. A significant advantage is also achieved when the input parts 28 and 29 are welded together, since additional sheet metal is required in the radial direction to provide a location for the rivet head when the input parts are riveted with the rivet pins 38. In other words, by welding the input members 28 and 29, the worm gear damper 26 can be realized with a small diameter under the same technical parameters.

In connection with the description with reference to the other figures, it is emphasized here that the description so far generally also applies to these figures. If there is a difference from the above, the actually described part applies.

In fig. 2, the input parts 28 and 29 are connected to one another circumferentially by means of a weld 39. However, the shaping of the input parts 28 and 29 remains such that, as is known from the circumferential riveting: the sheets lie flat against one another. Although this configuration is well known, the small diameter of worm gear damper 26 is advantageously achieved when welding is used for input members 28 and 29.

In contrast to fig. 1, in fig. 2 the pivot stop 34 is not provided in the inner region of the worm gear damper 26, but rather it is displaced into the circumferential region. The corresponding stamping of the right input part 29 and the output part 27 makes this possible. Here, it can also be seen that a contour is provided between the hub 43 and the output part 27. A loss prevention portion 46 is also formed here by making the inner diameter of the left input member 28 smaller relative to the outer diameter of the hub 43.

In the embodiment of fig. 3, the worm gear case 40 and the right input member 29 are not welded to each other, but are connected to each other by a so-called rivet projection 44. Since two oppositely acting riveting tools are required for riveting and since one riveting tool has to be placed inside the worm gear housing 40, in order to place the other riveting tool with the worm gear damper 26 already pre-assembled, openings for the second riveting tool are necessary in the output part 27 and the left input part 28. However, in the case where the right input member 29 is riveted to the worm housing 40 before the worm wheel damper 26 is formed and then the worm wheel damper 26 is fixed to the input members 28 and 29 in the circumferential region thereof, these openings need not be provided. In fig. 3, the weld 39 is not shown in the circumferential region, nor is the riveting by means of the rivet pin 38 or the riveting cam 44 shown. Because of the large circumferential surface, the input members 28, 29 can be fixed to each other by means of gluing.

In the torque converter 1 of fig. 4, the worm gear case 40 and the right input member 29 are connected to each other by a rivet bolt. The riveting in this area described in connection with fig. 3 also applies here. In fig. 4, it can be seen that both the worm gear case 40 and the right input part 29 and the two input parts 28 and 29, as well as the left input part 28 and the inner lamination carrier 10, are connected by means of rivet bolts. In fig. 4, the worm damper 26 is also fixedly connected by means of only one connection, namely riveting. The worm gear damper can be manufactured cost-effectively because of the elimination of complicated manufacturing.

As already mentioned, an axial clamping element 36 (for example, in the form of a disk spring or a corrugated disk (Well-Scheibe)) is used between the output part 27 and at least one input part 28 or 29 in order to damp torsional vibrations in the worm damper 26. In one embodiment of the invention, as can be seen in fig. 5, an axial clamping element 36 is provided between the hub-like bearing 35 of the worm wheel and the axial securing ring 20 on the hub 43. Due to the relative movement of the hub 35 with respect to the hub 43, an axial clamping element 36 can reduce the torsional vibrations at this point, since the energy of the vibrations is absorbed by the frictional forces which are formed there. However, an axial clamping element 36 can also be inserted between the outer diameter region of the hub 35 and the right input part 29 in order to absorb vibration energy, as can be seen from fig. 6.

There are two points in common in the torque converter 1 of fig. 5 and 6. The first common point is that the worm gear housing 40 is welded to the hub bearing 35. The welding is here effected by means of friction welding. Since the worm gear housing 40 is not welded to the right input part 29 of the worm gear damper, as shown in fig. 1 to 4, and the hub bearing 35 is inserted into the worm gear damper only by means of a projection (Nocken) shown by a dashed line, the worm gear 4 and the hub bearing 35 have no axial guide in the unassembled state and must therefore be fastened to the hub 43 by means of an axial securing ring 20. The second common denominator is: the hub bearing 35 is not formed as a swaged part as is usual, but here it is a part made of sintered metal, preferably sintered steel, and is formed as a molded part. As is apparent from fig. 5 and 6, in the case of a die forged component, the projections projecting from the flat surfaces at the time of finishing, for example, at the turning of the end face on the left end face, make the finishing impossible.

In fig. 7, the input members 28 and 29 are riveted to each other in a particular manner. Instead of the bend, which is usually provided for at least one input part 28, 29, and thus the two parts being adjacent in the circumferential region, the two input parts 28 and 29 of the worm gear damper 26 are parallel to one another and planar. In order to leave a place for the output part 27 and the axial clamping part 36, spacer pins 45 for riveting are used here. The spacer pin 45 is advantageous to a certain extent because it makes it possible to achieve a precise spacing of the input parts 28, 29 and at the same time to create an advantageous oil passage over the circumference of the worm gear damper 26 in the region between the input parts 28, 29, the output part 27 and the axial clamping element 36.

The connection of the output part 27 and the left input part 28 to the hub 43 is also shown in fig. 7. The connecting portion is also shown in fig. 8 and 9. Also disclosed in fig. 7 is a loss prevention portion 46, which is achieved here by the lamination holder having a smaller inner diameter relative to the outer diameter of the hub 43.

Fig. 8 and 9 each show a radial section of the hub 43, which is simultaneously oriented perpendicularly with respect to the longitudinal axis of the hub 43. Since the radial cross section represents only a small segment, the extension from left to right appears as a straight line. But in practice the profile 49 has an arc shape. The illustrated profile has a substantially constant cross-section in the axial direction. The profile of the hub 43 shown in figure 8 is therefore the same as that of figure 9.

In fig. 8, the contour of the output part 27 is complementary to the contour of the hub 43, so that the output part 27 fits on the hub 43 substantially without relative rotation and without play. Different heights of cyclically repeating "teeth" are not required in the profile 49 between the hub 43 and the output member 27.

In fig. 9, the hub 43 is paired with the input members 28, 29. The "teeth" of the input members 28, 29 are not too high and do not mesh into the small teeth of the hub 43. Because the "teeth" of the input members 28, 29 are also made "narrower," their "flanks" do not normally contact the "flanks" of the hub 43. This results in a defined rotational play between the input elements 28, 29 and the hub 43. Since the input members 28, 29 must be made rotatable relative to the output member 27 of the worm damper 26 in order to damp torsional vibrations and the relative rotation must also be limited in order to protect the spring, the contour 49 shown in fig. 8 and 9 is perfectly suited to this task. The contour 9 in fig. 9 represents a precise, compact and space-saving angle stop 34 for the worm gear damper 26.

The spacer pins 45 have been described with respect to fig. 7. In the embodiment of fig. 10, a spacer pin 45 also serves at the same time as the angle stop 34. The spacer pins 45 have a reduced diameter in their end regions, so that the shoulders of the spacer pins 45 can bear against the inner surfaces of the input parts 28, 29. By upsetting (riveting) the outer ends of the spacer pins 45, a fixed connection that can withstand high loads is obtained. However, if the spacer pins 45 are not only arranged on the circumference of the worm wheel damper 26, but also at least one spacer pin 45 is arranged such that it can be inserted into an arc-shaped circumferential groove of the output part 27, the at least one spacer pin 45 will serve as the angle of rotation stop 34.

Figure 11 shows a detailed scheme. The worm gear housing 40 is here provided with a bracket 41 which faces away from the guide wheel 5, i.e. in this case is bent to the left. The carrier 41 also has its inner diameter (as described for the other embodiments) as a radial support for the needle bearing 16, which is arranged between the stator 5 and the hub-like support 35 of the worm wheel. To achieve the orientation of the carrier 41, a recess or protrusion is provided on the adjacent input member 29, which is oriented toward the worm gear case 40. In one advantageous embodiment of the invention, the input part 29 and the worm gear housing 40 are connected to one another in the region of the recess or projection by a weld 39, optionally resistance welded.

Fig. 12 shows: not only can the input part 29 serve as the radial hub bearing 35 of the worm wheel 4, but also the worm wheel housing 40 itself can fulfill this task. In fig. 12, the worm housing 40 is lowered onto the outer diameter of the hub 43 and the carrier 41 is provided. The inner diameter 51 of the carrier of the worm gear casing is now supported on the hub 43 as a bearing bush. The needle bearing 16 is now no longer arranged within the inner diameter 51, but rather is guided over the outer diameter 50. Since the input part 29 is guided radially by the worm gear housing 40, it does not require radial support in the embodiment of fig. 12.

Fig. 13 again shows a variant in which the input part 29 and the worm housing 40 form brackets 42, 41. As just shown in fig. 12, the worm housing 40 uses its bracket 41 as a radial support member. But the bracket 41 initially faces the stator 5 and then turns toward the hub 43. Whereby its outer diameter 50 also supports the bearing 16. The bracket 41 is at the same time a fixed part of the bracket 42 of the input member 29. The weld 39 supports the torsional strength of the worm gear 4 (or worm gear housing 40) and the worm gear damper 26 (or input member 29). The nested brackets 41, 42 have the advantage that the worm wheel 4 is easy to position concentrically with respect to the worm wheel damper 26 when the respective worm wheel damper parts are preassembled.

In fig. 7 and 10, spacer pins 45 are shown, which space the input elements 28, 29 apart from one another by a defined distance. The intermediate plate 52 is disclosed in fig. 14a and 14b, wherein fig. 14a is a radial sectional view of the worm gear damper and fig. 14b is a top view of the associated part. The cross-section of which can be seen in figure 14 b. The intermediate plate 52 rests with its inner, essentially straight, parallel side faces on the inner faces of the input parts 28, 29. The input members 28, 29 are provided with notches in which the tongues 54 of the spacer plates 52 are inserted. To prevent the input members 28, 29 from moving apart, the tongue 54 caulks the input members 28, 29 to one another. Here, the recesses of the input parts 28, 29 can initially be designed as dovetails. In another embodiment of the tongue 54 and the recess, they do not have a wedge-shaped cross section, but are rectangular. A rectangular cross section is also particularly advantageous since it can be produced simply, for example by stamping. In order to impart axial strength to the connection of the input members 28, 29, the spacer plate 52, the tongue 54 must be upset, thereby forcing and/or hooking the material into one another and/or forming a rivet head with the tongue 54.

The use of a spacer plate 52 is very advantageous because its end faces can be used as stop faces 53, 53' for the maximum permissible angle of rotation between the input members 28, 29 and the output member 27. And: the maximum allowable rotation angle can be determined according to the length of the spacing plate (refer to the description in fig. 14 b). In other words, standard parts can be used for the input and output parts of different worm wheel damper sizes, while only one simple part has to be modified for a specific maximum permissible angle of rotation.

It should be understood that the spacer plate does not necessarily have to be used as a stop within the scope of the invention. It can also be arranged in multiple fashion only as a multiple on the circumference of the worm gear damper.

Claims (37)

1. A torque converter for hydraulically connecting an internal combustion engine to a transmission, wherein the torque converter is provided with a worm gear damper and the connection of hydraulic energy to the transmission input shaft of the downstream transmission is realized by means of a hub and a component.

2. The torque converter of claim 1, wherein: the component is manufactured substantially without machining.

3. The torque converter according to claim 1 or 2, characterized in that: the transmission input shaft is a transmission input shaft of a continuously variable CVT transmission.

4. The torque converter according to claim 1 or 2, characterized in that: the transmission input shaft is a transmission input shaft of an automatic transmission.

5. The torque converter according to one of claims 1 to 4, characterized in that: the component is an input component of a worm gear shell or a worm gear damper, and is composed of a plate-shaped material and is formed as a stamping part.

6. The torque converter according to one of claims 1 to 5, characterized in that: the worm housing is rotatably supported by a bracket on the circumference of a hub provided on the transmission input shaft.

7. The torque converter according to one of claims 1 to 6, characterized in that: a part of the worm gear damper, the so-called input part, is rotatably mounted by a carrier on the circumference of a hub provided on the transmission input shaft.

8. The torque converter according to one of claims 1 to 7, characterized in that: the carrier of the worm gear case or the carrier of the worm gear damper input member is significantly spaced relative to the cylindrical surface of the hub and can be used to guide a thrust bearing.

9. The torque converter of claim 8, wherein: the thrust bearing is disposed in the inner diameter of the carrier.

10. The torque converter of claim 8, wherein: the thrust bearing is disposed on an outer diameter of the carrier.

11. The torque converter according to one of claims 1 to 10, characterized in that: the worm gear casing and the adjacent input part are connected to one another in a form-fitting manner, in particular by riveting.

12. The torque converter of claim 11, wherein: the two parts are riveted to one another by means of a rivet bolt.

13. The torque converter of claim 11, wherein: the two parts are riveted to one another by means of a riveting lug.

14. The torque converter according to one of claims 1 to 13, characterized in that: the worm gear housing and the adjacent input part are connected to one another in a power transmission chain, in particular by welding or gluing.

15. The torque converter according to one of claims 1 to 14, characterized in that: the worm gear casing and the adjacent input part are connected to one another in a bonded manner, in particular by welding (a positive connection, a force chain connection and a bonded connection can also be combined).

16. The torque converter of claim 15, wherein: the welding is effected by means of laser welding, resistance welding, spot welding or friction welding.

17. The torque converter according to one of claims 1 to 16, characterized in that: at least one output part of the worm gear damper and the hub are connected to each other on the transmission input shaft by means of profiles on both sides in a rotationally fixed and axially displaceable manner (for example with a single cam and usually circular; this configuration is new and can be combined with a sintered or stamped part).

18. The torque converter of claim 17, wherein: the input part of the worm gear damper facing away from the worm gear housing is provided with an inner circumferential contour which, in combination with the contour of the hub, allows a defined maximum relative rotational angle between the hub and the input part.

19. The torque converter according to claim 17 or 18, wherein: the profiles are configured as outer and inner tooth portions.

20. The torque converter of claim 19, wherein: the outer and inner tooth portions are configured to be self-centering.

21. The torque converter according to one of claims 17 to 20, characterized in that: the profile consists of an axially uniform cross-section, wherein high and low profile regions alternate circumferentially.

22. The torque converter of claim 21, wherein: the alternating contours in the circumference are formed cyclically.

23. The torque converter according to one of claims 17 to 22, characterized in that: the profile is produced by broaching or, when applied to an outer part (input or output part), preferably by punching.

24. The torque converter according to one of claims 1 to 23, characterized in that: the geometry of the wheel hub relative to the worm gear damper allows the two parts to move relative to each other, but to be alternately coupled to each other.

25. The torque converter of claim 24, wherein: the inner diameter of the input part facing away from the worm wheel housing or the inner diameter of the inner lamination carrier is smaller than the outer diameter of the hub.

26. The torque converter according to one of claims 1 to 4, characterized in that: the component consists of sintered metal, preferably sintered steel, and is formed as a molded part.

27. The torque converter of claim 26, wherein: the molding is provided with an outer contour on which an inner contour of the input part, which is located in the vicinity of the worm gear casing, engages.

28. The torque converter according to claim 26 or 27, wherein: the at least one projection of the sintered part engages in a groove, preferably curved, of the output part and serves as a stop for a defined relative angle of rotation.

29. The torque converter according to one of claims 26 to 28, characterized in that: at least one projection of the output part engages in a groove, preferably curved, of the sintering part and serves as a stop for a defined relative angle of rotation.

30. The torque converter according to one of claims 1 to 29, characterized in that: the hub is made of sintered metal, preferably sintered steel, and is formed as a molded part.

31. The torque converter according to one of claims 1 to 30, characterized in that: the two input parts are connected to one another by spacer pins, wherein at least one of the spacer pins can be moved in an endmost, preferably curved, groove of the output part of the worm gear damper and acts as a stop at the respective opposite angle of rotation of the output part relative to the input part.

32. The torque converter according to one of claims 1 to 31, characterized in that: in order to damp torsional vibrations, a damping ring in the form of a disk spring or a bellows disk is provided between the hub and the axial securing ring.

33. The torque converter according to one of claims 1 to 32, characterized in that: in order to damp torsional vibrations, a damping ring in the form of a disk spring or a bellows disk is provided between the worm wheel hub and the input part facing it.

34. The torque converter according to one of claims 1 to 33, characterized in that: the input parts of the worm gear damper are welded to one another and arranged parallel to one another on the circumference, at least in sections.

35. The torque converter according to one of claims 1 to 33, characterized in that: the input parts of the worm gear damper are welded to each other at least partially on the circumference and are connected to each other substantially at right angles.

36. The use of a torque converter according to one of claims 1 to 35 in a motor vehicle, in particular in a motor vehicle.

37. The torque converter according to one of claims 1 to 36, characterized in that: the torque converter is provided with a torque converter crossover clutch.