DE4239770C2 - Dual Mass Flywheel - Google Patents

Description

The invention relates to a dual mass flywheel for use between an internal combustion engine and a transmission, one with the Ab drive shaft of the internal combustion engine connectable flywheel element and flywheel element which can be connected to the transmission are present and can be operated via egg Centered ne and against the effect of at least one damping device can be rotated relative to one another, one of the flywheel elements has an axially extending sleeve-like extension for receiving egg Nes rolling bearing, the sleeve-like approach forms a seat for this, on or in one of the roller bearing rings from the free end area of the sleeve-like Ansat zes forth axially pushed or pushed.

Dual mass flywheels with roller bearings, where the bearing of one Can be brought together axially with its seat in many designs known forms. For example, the inside of DE 34 48 595 C2 ring of a rolling bearing is pushed onto a seat, being in the axial direction on egg a shoulder or a heel. To protect against relocation of the inner ring in the axial direction opposite to the mounting direction the inner ring pressed on the shoulder. Through the utility model G 84 12 116 has become known to secure storage by means of snap rings or circlips.  

This utility model also allows the use of "blasted" Running or bearing rings excited, which an elastic expansion of the bearings rings enabled. Spacer or spacer sleeves or Support or shims additionally arranged. Of a similar design are the usual types of admission for the outer ring of a Wälzla gers. Here, too, the outer ring of the bearing is pushed axially into its seat, until it rests on a radially projecting collar. For axial securing in the Ge In turn, different elements can serve, such as wise snap rings or circlips or a centering ring set of a bearing cap. From the examples mentioned it appears that for a xial definition of the bearing, additional parts or measures required are necessary, both the structural unit and the required storage expensive, often difficult to assemble and smooth automation can significantly hinder the assembly process.

The present invention was based on the task, the positive locking tion of a rolling bearing in the axial direction without additional che components to provide and this protection against axial displacement to be able to carry out as little space as possible in the axial direction. Farther this device for attaching a rolling bearing ring should be easy to manufacture be by reducing the number of work or assembly steps required in inn be executable in a societal manner and the aforementioned disadvantage of the previous A Eliminate xial specifications.  

This is according to the invention with a dual mass flywheel at the beginning described type achieved in that the approach axially to the seat bordering and slightly radially protruding from this, elastic deformable collar forms the during the axial pressing or pressing the closed bearing ring causes an elastic deformation of the approach and after the bearing ring has been pushed on, it expands again to form the La secure gerring axially against the approach.

An axial definition of a rolling bearing by two in one piece with the bearing seat trained collar areas or borders is known from DE 84 12 116 U1, each but there the federal government is not so elastic that an undivided bearing ü could be pushed over its seat. To the camp to be able to assemble, the races are broken, that is, they are on axially broken a point of the circumference, so that it can widen if necessary NEN. During assembly, the warehouse is expanded, i.e. inside enlarged, then pushed axially over the shelf, at the axial height of the Bearing seat reduced in diameter and in that, the bearing seat ent speaking diameter held. That means the actual assembly to establish the functional relationship between the bearing seat and the bearing ring takes place in the radial direction.  

It can be useful if the federal government has a closed configuration indicates when this elastically deformable collar viewed in the circumferential direction tet is not interrupted and the same radial height at every point of the circumference hey owns.

A particularly advantageous structural design of the invention can provide that the outer ring opened in a sleeve-like area is taken and that the axially projecting area at least over the axial Extension of the federal government is weakened. This deliberate weakening of the sleeve-like area can be done by axially limiting the Wall thickness is reduced over the entire circumference. As particularly expedient It can prove ugly if the bearing seat for the outer ring serves as a backstitch is formed, if this outer ring between two collar areas is taken. The axial fixation can also be dimensioned such that the bearing ring between the two collar areas can be axially displaced to a limited extent, so that this bearing point is designed as a floating bearing. On the other hand, the La gerring be axially fixed to form a fixed bearing, while it is still possible is the inner ring of a rolling bearing on a shaft between two radial front jumps to fix the end areas of the seat.

It can be particularly advantageous if the sleeve-like region has an insertion tion slope, which facilitates the assembly of the rolling bearing in that whose outer ring is centered during the assembly process. The assembly of  Rolling bearing can with appropriate dimensioning of the radial projections or the radial projection essentially at room temperature or at im bear substantially the same temperature of the rolling bearing and the bearing seat the part done.

However, it can also prove to be advantageous if for mounting the roller bearing in a bore at least the collar has a higher temperature than the warehouse. This can be achieved after temperature compensation a larger dimensional coverage between the collar and bearing outer ring is, which also means a game fit or transition fit with the help the recording according to the invention can be realized. When assembling the Wälzla gers on a wave, it can be particularly useful if the The temperature of the shaft is lower than that of the bearing. Here too, ent speaking of what has been described above, he has a greater dimensional coverage range or even a press fit.

For some types of storage, such as the design of the roller bearings as a full spherical bearing, it can prove to be useful if for Filling the bearing with balls one of the rings is blown up when the rolling but not disassembled during assembly, which brings it together with its seat and is essentially closed. In any case, assembly is carried out via the elastic deformation of at least one of the parts to be joined.  

A particularly advantageous embodiment of the invention Dual mass flywheel is present when the roller bearing is the pilot bearing of a transmission input shaft. Likewise, a shaft can be accommodated in the bearing, with a gear input shaft can be connected and represents an intermediate shaft as it for example in the transaxle construction of motor vehicles use fin det. According to a further preferred embodiment, the roller bearing, which is held in the receptacle of the dual mass flywheel according to the invention, the storage of the two Form flywheels in this dual mass flywheel.

In the figures, the design of the receptacle becomes radial fixed mounting of a rolling bearing of the dual mass swing according to the invention rads shown using the example of a pilot bearing for a transmission input shaft integrated therein.

Here, FIG. 1 shows a dual-mass flywheel in section,

Fig. 2 shows an enlarged detail of the pilot bearing receptacle,

Fig. 3 is a further enlarged section of part of the pilot Lageraufnah me.

The dual mass flywheel 1 shown in FIG. 1 is divided into two flywheel elements 2 and 3. The flywheel element 2 can be fastened on a crankshaft (not shown) of an internal combustion engine via the bores 4 with the aid of fastening screws. With the help of fastening supply thread 5 , a switchable friction clutch, not shown, can be screwed onto the second flywheel element 3 . Between the flywheel element 2 and the flywheel element 3 , a device for damping torsional vibrations is provided, which enables a relative rotation between the two flywheel elements 2 and 3 . The two flywheel elements 2 and 3 are rotatably positioned coaxially to one another via a bearing 6 .

The flywheel element 2 , which is the input part of the damping device 7 , forms a housing which delimits an annular chamber 8 in the circumferential direction, in which part of the damping device, in this case arc-shaped helical spring sets 9 , is received.

The flywheel element 2 , which has the annular chamber 8 , consists essentially of two housing parts 10 , 11 which are radially tightly connected to one another. The output part for the part of the damping device 7 received in the annular chamber 8 is formed by a radial flange 12 which is arranged axially between the two housing parts 10 , 11 made of sheet metal. The flange 12 has on its outer circumference radial arms 13 which form areas of application for the coil spring sets 9 . The support areas for the arcuate coil spring sets 9 are formed by axial impressions 14 , 15 in the housing parts 10 , 11 . In the example shown, the housing part 10 carries on its outer circumference a donor ring gear 16 for engine management and the housing part 11 on its outer circumference the starter ring gear 17 .

In the interior of the annular chamber 8 , which is at least partially filled with pasty medium, such as fat, shell bodies 18 are provided radially on the outside as wear protection, on which the arcuate coil spring sets 9 can be supported at least under centrifugal force. The inner parts of the shell bodies 18 are at least substantially matched to the outer contour of the coil springs 9 and partially encompass them.

The flange 12 has recesses 19 lying radially further inward, which form areas of application for further spring sets 20 , as a result of which the flange 12 represents the input part of this part of the damping device 7 . The radially inner spring sets 20 are arranged in spring windows 21 , 22 of the side windows 23 , 24 and are supported in the circumferential direction on the edge regions of these spring windows 21 , 22 . The side windows 23 , 24 are axially spaced on both sides of the radial flange 12 and axially and non-rotatably connected to the secondary side flywheel element 3 via rivet elements 25 . Between the side window 24 and the secondary-side flywheel element 3 , the radially inner region of a sealing membrane 26 is clamped, the radially outer region of which rests axially resiliently on the radially inner region of the housing part 11 and thus ensures the sealing of the annular chamber 8 from the outside.

A friction device 27 is provided radially inside the rivet elements 25 , which comes into operation when the two flywheel elements 2 , 3 are rotated relative to one another. The friction elements can be controlled so that they are effective from the start of the relative rotation, as well as so that they are only used after a certain clearance angle. The bearing 6 is provided with sealing caps 28 , 29 , which can also be used for thermal insulation of the rolling bearing. The inner ring of the bearing 6 is secured until the assembly of the two-mass flywheel 1 on the crankshaft of an internal combustion engine by means of a washer 30 which is connected via a pin connection 31 to the hub 32 of the flywheel element 2 .

The cast in the embodiment, for. B. cast iron, manufactured hub 32 carries in its inner region on its side facing away from the internal combustion engine in an axially extending extension or sleeve-shaped region 33, the pilot bearing or guide bearing 34 , which forms a support for a transmission input shaft and in the manner according to the invention within the axial approach 33 is supported. In the example shown, this pilot or inner bearing 34 is arranged in approximately the same axial position as the secondary-side flywheel element 3 .

The mounting of the bearing 34 according to the invention is described in more detail below with reference to the enlarged representations in FIGS. 2 and 3, with FIG. 3 showing a further enlarged representation of the area marked "X" in FIG. 2.

The axial extension 33 is the hub 32, as can be seen from the figures, viewed in the axial direction, divided into different inner diameter sections, all of which are integrally formed with the hub 32 and with their axial approach 33rd The smallest diameter has the first inner diameter area 35 , which has on its side facing the bearing 34 a radially extending portion on which the outer ring of the bearing 34 can be axially supported, whereby with this diameter area 35 a trained in a conventional manner axial Bearing stop is formed.

The second inner diameter area 36 is the area with the largest inner diameter within the axial shoulder 33 of the hub 32 , forms the bearing seat for the bearing 34 and is matched to the outer diameter of the outer ring of the bearing 34 according to the load case or according to the selected tolerance field.

The third inner diameter region 37 has a smaller diameter than the bearing seat 36 , as a result of which a second form-fitting axial securing region or axial stop for the bearing 34 , which is produced in one piece with the axial extension of the hub 32 , is formed. In this inner diameter area 37 , which is limited in FIGS . 2 and 3 in the axial direction by the broken line 39 and the solid line 40 , the dimensional coverage of the axial extension 33 of the hub 32 and the outer ring of the roller bearing 34 is greater than in the area of Bearing seat, that is, the inner diameter area 36 , which results in a higher pressure when mounting the bearing 34 in the axial extension 33 , which causes an elastic deformation of the parts to be joined.

The inner diameter region 36 forms a groove-like bearing seat, so that the bearing 34 is arranged in an undercut in the assembled state. The axially of the positive bearing lock 37 according to the invention on the side facing away from the bearing 34 upstream conical surface 38 serves as a mounting or threading bevel for the bearing 34th

In the region of the radially inwardly projecting collar 37 , the axial extension 33 of the hub 32 is provided with an area of reduced wall thickness 41 . This area of reduced wall thickness 41 lies essentially on the side of the roller bearing 34 facing away from the axial stop 35 and in this case is formed by the reduced outside diameter area 42 .

From Fig. 2 it can be seen that the diameter in the reduced th outer diameter region 42 is considerably smaller than the outer diameter of the outer diameter region 43 , which is located axially at the height of the inner diameter region 36 , that is, the bearing seat.

This area of reduced wall thickness 41 achieves a coarser elasticity of the axial extension 33 , especially in the axial area of the inner diameter 37 , which can be dimensioned such that the parts, namely the hub 32 and the bearing 34, also at room temperature or with the same temperatures can be added, after the joining, that is, when the bearing is in its groove-like seat in the area of the inner diameter 36 , a mechanical positive axial securing of the bearing 34 in the area of the inner diameter area 37 is given. However, it is also possible to mount the bearing 34 and the hub 32 with a temperature difference, as a result of which, for example, a greater dimensional coverage of the inner diameter region 37 and the outer diameter of the outer bearing ring can be achieved. This increased dimensional coverage results in an even increased axial fuse, so that the bearing can also be designed as a floating bearing, for example.

The roller bearing 34 can also be designed as a full spherical bearing, for example to increase the load rating or increase the service life. If in such a bearing a ring for filling the bearing with balls is blown, that is to say divided in the axial direction, it may prove expedient if the bearing ring is left undivided, which cooperates with the fastening device or bearing securing device 37 according to the invention.

The invention is not illustrated and described on the NEN embodiments limited, but also includes Variants, in particular by combining individual, in connection with the different embodiments described features or elements are formed can. Furthermore, individual, in connection with the in the embodiments shown in the figures Features or modes of operation taken on their own represent independent invention.

Claims (10)

1. Dual mass flywheel for use between one internal combustion engine machine and a gearbox, one with the output shaft of the internal combustion engine machine connectable flywheel element and a ver with the transmission bindable flywheel element are available, the zent about storage riert and against the effect of at least one damping device are rotatable with one another, one of the flywheel elements being one axially extending sleeve-like approach for receiving a Rolling bearing, the sleeve-like approach forms a seat for this, on or in one of the rolling bearing rings from the free end area of the sleeve-like Ansat zes forth axially pushed or pushed in and the approach continues one axially adjacent to the seat and slightly radial to it protruding, elastically deformable collar that forms during the axi alen pressing or pressing the closed bearing ring an elastic Deformation of the approach causes and after the bearing has been pushed on ges widened again to the bearing ring axially opposite the approach to back up. 2. Dual mass flywheel according to claim 1, characterized in that the sleeve-like approach has a closed configuration.   3. Dual mass flywheel according to one of claims 1 to 2, characterized ge indicates that the bearing outer ring opened in a sleeve-like approach is taken and that the axially protruding from the bearing outer ring Area of the approach is weakened. 4. Dual mass flywheel according to at least one of the previous types Sayings, characterized in that the bearing seat is designed as a backstitch det. 5. Dual mass flywheel according to at least one of the previous types Sayings, characterized in that the sleeve-like approach introduces has slope. 6. Dual mass flywheel according to one of claims 1 to 5, characterized ge indicates that for mounting the rolling bearing in a hole in the Ansat zes at least the approach has a higher temperature than the bearing. 7. Dual mass flywheel according to one of claims 1 to 6, characterized ge indicates that for mounting the rolling bearing on a sleeve-like the temperature of the latter is lower than that of the bearing. 8. Dual mass flywheel according to at least one of the previous types sayings, characterized in that for filling the rolling bearing with Ku geln one of the rings is blown up, but the rolling bearing during assembly is not disassembled and essentially closed.   9. Dual mass flywheel according to one of claims 1 to 8, characterized ge indicates that the roller bearing is the pilot bearing for a transmission input wave is. 10. Dual mass flywheel according to one of claims 1 to 8, characterized ge indicates that the rolling bearing supports the two flywheels of the dual mass flywheel to each other.