KR20090014144A - Split flywheel - Google Patents

Abstract

The invention relates to split flywheels, consisting of a primary centrifugal mass (2) that can be connected to a drive, and a secondary centrifugal mass (3) that can be connected to the input part of a gear mechanism, with the flywheels being centered and rotatably mounted in relation to one another against the effect of at least one damper by means of a sliding bearing (16). A radial extension formed on the end of the bearing sleeve turned facing the insertion end of the seat is used to axially secure the bearing bush in the direction of insertion.

Description

Split flywheel {SPLIT FLYWHEEL}

The present invention relates to a split flywheel consisting of a primary centrifugal mass that can be connected to a drive machine and a secondary centrifugal mass that can be connected to a gear input, wherein the centrifugal masses are adapted to the action of at least one damping device. Can rotate relative to one another, in which case one centrifugal mass supports at least one axial attachment, the attachment extending along an axis into a receptacle supported or formed by the other centrifugal mass, There is at least one sliding bearing between and the attachment, the sliding bearing guarantees radial centering of at least two centrifugal masses and has at least one sliding bearing bush provided between the receptacle and the axial attachment, the sliding bearing The bearing bush is along the axis from one end of the receptacle It is inserted into the receptacle.

Fly wheels of this type have been proposed, for example, by DE 19834729 A1 and DE 19834728 A1. Reference may be made to DE 19834728 A1 specifically with regard to the basic arrangement of the sliding bearing, the part surrounding or receiving the sliding bearing and the starting material forming said sliding bearing. No detailed description will be required above.

The object of the present invention is to improve the sliding bearing in a divided flywheel of the type mentioned in the introduction. In addition, a simple and economical method of manufacturing sliding bearings must be ensured.

The underlying objects of the present invention include, among other things, a sliding bearing bush having at least one integrally formed radial extension over its circumference at least locally at its end facing the insertion end of the receptacle. Is achieved by interacting with the stopper region provided in the part with the receptacle in order to secure it along the axis in the insertion direction. The radial extension may be formed by a plurality of diameter extensions integrally formed in a fan shape over the circumference at the corresponding end of the sliding bearing bush. It may be particularly advantageous if the end regions of the sliding bearing bush run in the form of a truncated cone as long as the radial extension is formed. The areas forming the extension may preferably be provided in the axially extending area of the receptacle. The receptacle is preferably formed in a ring shape and preferably restricts the cylindrical wall over at least 70% of its axial extension.

When the extension is formed in the shape of a truncated cone, it is preferable that the inclination angle is less than 45 °, preferably in the size range of 10 ° to 30 °. This case means that the cone ratio or constriction is in the size range of 20 ° to 60 °.

However, the radial extension of one sliding bearing bush can also be formed by radially running curves with slightly radial extensions. In this case the size of the radial extension may be in the range of 1 to 3 mm. The radial extension may extend over the entire circumference of the corresponding end region of the bearing bush, that is to say may comprise only a few fan-shaped regions that form a ring-shaped region or are distributed over the circumference.

Preferably the receiving portion for the sliding bearing bush can likewise comprise at least one radial extension, which extension is adapted to at least one extension of the sliding bearing bush. Preferably, the extension portion of the receiving portion may also be formed in the shape of a truncated cone.

Radial centering between two centrifugal masses can preferably be ensured via a sliding bearing bush provided between the receiving portion and the axial attachment, the axial positioning being made by at least one ring-shaped sliding bearing plate, The sliding bearing plate is disposed at one axial end of the sliding bearing bush and surrounds the attachment, in which case the sliding bearing plate and the sliding bearing bush have integrally formed portions, the integrally formed portions being mutually coupled to the sliding bearing. Resulting in at least one connection fixed to rotate integrally between the bush and the sliding bearing plate. The integrally formed parts may be preferably formed such that an axial protective effect or a connecting action is ensured between the two parts after the axial engagement of the sliding bearing bush and the sliding bearing plate. As such the sliding bearing is formed in two parts, different materials or fabrication materials can be used to form the sliding bearing bush and the sliding bearing plate. Thereby, the optimum fabrication material or material for the individual parts forming the sliding bearing can be selected. This type of shape also makes it possible to form a relatively wide radially area of the sliding bearing, ie the sliding bearing plate, which ensures axial support between the centrifugal masses. Such a possibility of formation cannot be realized in the case of using an integrally formed sliding bearing bush, because the radial ring region or plate region of such a type of sliding bearing bush usually proceeds in its original cylindrical form. It is formed by constructing radially, in which case surface expansion is achieved which causes destruction or damage of the sliding layer, especially when using coated sliding bearing materials.

Furthermore, by fixedly engaging so as to rotate together between the sliding bearing plate and the sliding bearing bush, the axial sliding bearing is safely formed by the side of the sliding bearing plate provided for this purpose. This formation is ensured by the sliding bearing bush being fixed to rotate with the centrifugal mass and preferably with the centrifugal mass with the receiving portion. For this purpose the sliding bearing bush can be press-inserted into the receptacle.

Sliding bearing bushes, originally made of flat bearing materials, can be rolled in a simple manner. Bearing materials of this type may have a carrier layer, which is provided with a relatively thin sliding bearing layer. The sliding bearing layer consists of at least one layer. Regarding the possibility of constructing this type of sliding bearing layer, reference is made to the prior art mentioned above.

In order to form an engagement fixed to rotate together, the sliding bearing plate may have an axial nose shape which is inserted into a correspondingly adapted incision of the bush after assembly. In this case, the nose shape may be integrally formed around the inner circumference of the sliding bearing plate. The nose shaped portion of this type can be formed by bending the radial nose shaped portion originally formed integrally with the sliding bearing plate in the axial direction. The material blanks necessary to form the bearing bush and the sliding bearing plate can be produced in a simple manner by drilling or cutting from the bearing starting material in the form of panels or bands, for example by laser beam cutting.

The cuts of the sliding bearing bush can have a U-shaped edge waveform, in which case the flanks of the cuts interact with the side flanks of the nose-shaped portion of the sliding bearing plate.

The sliding bearing bush and the sliding bearing plate can be made from different starting materials. It may be desirable at this time if the material for producing the sliding bearing bush is at least slightly thicker than the starting material for producing the sliding bearing plate.

Further advantages and functional and manufacturing technical improvements are described in detail with reference to the drawing descriptions below.

1 is a schematic diagram of a torsional vibration damper in the form of a split flywheel,

2 is an enlarged detail view of a sliding bearing provided between two centrifugal masses forming a split flywheel;

3 is a schematic view of a sliding bearing bush formed according to the invention and an axial sliding bearing ring belonging to the bush before assembly.

1 shows a torsional vibration damper 1 formed as a two-mass flywheel. The torsional vibration damper 1 has a primary centrifugal mass 2 and a secondary centrifugal mass 3 which can be rotated relative to the primary centrifugal mass. The primary centrifugal mass 2 can be connected to a driven shaft of the internal combustion engine, for example a crankshaft, in a known manner. The secondary centrifugal mass 3 can engage the input shaft of the gear via a friction clutch, not shown in detail in the figure. For this purpose the secondary centrifugal mass 3 has a friction surface 4 for the clutch disc. In this case the two centrifugal masses 2 and 3 are supported and centered so as to be rotatable with each other via one sliding bearing 16. In the illustrated embodiment, the sliding bearing 16 is used to axially position the two centrifugal masses 2 and 3 in the direction facing each other at the same time. In other words, in the illustrated embodiment, a so-called compressed friction clutch is mounted on the secondary centrifugal mass 3. In the case of using a so-called drawing clutch, the sliding bearing 16 should ensure the action of supporting the two centrifugal masses 2 and 3 in the axial direction away from each other. It may also be desirable if the sliding bearing 16 is formed to safely protect the centrifugal masses 2 and 3 in two mutually axial directions. Reference will be made, for example, to DE 198 34 729 A1 and DE 198 34 728 A1 with regard to the basic structure and the basic arrangement of the sliding bearing 16 and the components surrounding the sliding bearing.

A torsional vibration damper 5 is provided between the two centrifugal masses 2 and 3, which damper prevents relative rotation of the two centrifugal masses 2 and 3, and the rotation occurring between the internal combustion engine and the gear. Used to filter out vibrations. The torsional vibration damper 5 comprises at least an energy reservoir, in which case the energy reservoir has the form of a screw spring 6 extending in the tangential or circumferential direction. The spring 6 is compressed by the supporting or contacting regions 7, 8, 9, which are supported or formed by the primary centrifugal mass 2 and the secondary centrifugal mass 3. do. The support regions 7, 8 are in this case formed by integrally formed bag-shaped features, which are inserted into the seat parts 11, 12 of the primary centrifugal mass 2 which restrict the chamber 10. It is. The chamber 6 also houses a spring 6 formed as a screw spring. Lubrication means or lubricant may be provided in the chamber 10 to reduce wear. The contact area 9 is formed by a flange body 13, which is fixedly connected to rotate together by a part, in this case a rivet connection 14, which forms a friction surface 14. In the embodiment of the two-mass flywheel shown in FIG. 1, it can be seen that another so-called load friction device 15 is further provided. Regarding further functional and structural details of this type of two-mass flywheel, reference is made, for example, to the aforementioned prior art and DE 3721712 A1 and DE 4117584 A1, in which case the details are described below. The sliding bearing shape according to the invention described can likewise be used.

The sliding bearing 16 has a radial sliding bearing section 17 which is used for the centering of the two centrifugal masses 2 and 3 and an axial sliding bearing section which causes the axial support action of the centrifugal masses 2 and 3 ( 18). The radial sliding bearing section 17 is arranged between the axial attachment 19 in the form of a pipe of the primary centrifugal mass 2 and the ring-shaped recess 20 of the secondary centrifugal mass 3. An axial sliding bearing section 18 is provided between the front face 21 of the secondary centrifugal mass 3 and the shoulder 22 of the primary centrifugal mass 2.

The sliding bearing 16 formed according to the invention, shown in FIGS. 2 and 3, comprises a sliding bearing bush 23 which ensures radial sliding bearing action between two centrifugal masses 2 and 3. It can be seen from FIG. 3 that the sliding bearing bush 23 was originally formed by rolling a flat band-shaped sliding bearing material. In this case, the band-shaped sliding bearing blank may be manufactured by laser beam cutting or by perforation. The end regions of the band forming the sliding bearing bush 23 are joined via a connecting portion 24 in a shape coupling manner. In the illustrated embodiment there is only a shape coupling type connection 24, but there may also be two or more connections 24 arranged side by side in the axial direction.

The sliding bearing bush 23 is press-inserted into the cylindrical receiving portion provided in the secondary centrifugal mass 3 in this case as can be seen from FIG. 2. If necessary, the sliding face 25 can be corrected as described in DE 19834728 A1.

In the illustrated embodiment the cylindrical receiving portion 20 is deformed into a truncated conical shaped region 31, which extends radially, wherein the frusto-shaped region faces the ring-shaped recess facing the internal combustion engine in the illustrated embodiment. On the side of 20 is provided. The sliding bearing bush 23 likewise has a conical extended region 32, which is adapted to correspond to the conical shaped region 31, with the bearing bush 23 having a cylindrical receptacle 20. It interacts with the region 31 for safe protection in the axial direction from the inside to the right.

In the illustrated embodiment, the regions 31 and 32 are formed in the shape of a truncated cone. However, the regions may have other waveforms, such as trumpet shapes or may be formed as radial attachments.

The truncated or expanded region 32 of the bearing bush 23 may be previously formed integrally or only integrally after the bearing bush 23 is pressed into the receiving portion 20 using a corresponding tool. It may be formed.

In the embodiment shown, the truncated conical region 31 extends over the entire circumference of the bearing bush 23. However, multiple sections formed in the shape of segments, distributed over the perimeter, may also be provided, which sections may have the same or similar waveform as the truncated conical region 31 in axial direction. When the region 31 or 32 is formed in the shape of a truncated cone, the size of the cone angle is in the range of 20 ° to 90 °, preferably in the range of 40 ° to 60 °. After the sliding bearing bush 23 is assembled into the receiving portion 20, when the truncated conical region 32 is integrally formed, the truncated conical shaped portion having the bearing bush 23 integrally formed at both end regions ( By having 32), the bearing bush is consequently secured in both axial directions inside the receptacle 20.

The sliding bush 23 has a cutout 27 which is used to securely maintain rotation of the axial sliding bearing plate 28 at least on the axial side. In the illustrated embodiment, the ring-shaped sliding bearing plate 28 has two axial protrusions 29, which are formed in the shape of a nose. The nose feature 29 is fixed so as to be able to rotate at least together between the two parts 28 and 23 when the axial sliding bearing plate 28 axially engages with the radial sliding bearing bush 23. It was formed to ensure engagement and was adapted to the cut 27. In this case, it is preferred if there is at least one shape engaging connection formed by the cutout 27 and the nose-shaped portion 29. In the illustrated embodiment, there are two such connections. However, three or more such connections may be provided. The cuts 27 and the nose features 29 may be adapted to each other so that the sliding bearing plate 28 is secured axially with respect to the sliding bearing bush 23. The nose feature 29 can be formed in a simple manner by bending the tongue, originally radially oriented, in the axial direction. Thus, the sliding bearing plate 28 can likewise be perforated or cut in a simple manner, for example by laser beam cutting or high pressure liquid cutting (spray cutting). As can be seen in FIG. 2, it is preferable if at least the tongue region 30 of the tongue 29 inserted into the cutout 27 has a thickness thinner than the sliding bearing bush 23. By means of dimensional design in this manner it can be ensured that the tongue area 30 is positioned at least slightly radially backward with respect to the sliding bearing face 25. It may be desirable if the starting material for producing the sliding bearing plate 28 has a thinner thickness than the starting material for producing the sliding bearing bush 23.

For many applications it may be desirable to form the sliding bearing 16 such that the axial sliding bearing plate 28 is provided on both axial sides of the sliding bearing bush 23.

For many applications it may also be desirable if the sliding bearing bush 23 has projections integrally formed axially on at least one axial side, the projections correspondingly adapted to the inner circumference of the plate 28. It is inserted into the incision provided in. In this case, it is preferable that the axial nose shape of the sliding bearing bush 23 has an axial extension smaller than the thickness of the sliding bearing plate 28.

It is also preferred if the inner diameter 30a of the axial sliding bearing plate 28 is at least slightly larger than the diameter of the sliding face 25 of the sliding bush 23.

The sliding bearing plate 28 may be directly supported by the axial support shoulder 22 provided in the primary centrifugal mass 2. However, it may also be desirable if the support is arranged in the middle of at least one ring, preferably made of plastic. In this regard, reference is again made to the prior art already mentioned above.

Explanation of symbols on the main parts of the drawings

1: torsional vibration damper 2: primary centrifugal mass

3: secondary centrifugal mass 4: friction surface

5: torsional vibration damper 6: spring

7, 8, 9: support or contact area 10: chamber

11, 12: seat part 13: flange body

14: rivet connection 15: load friction device

16: sliding bearing 17: radial sliding bearing section

18: axial sliding bearing section

19: Pipe-shaped attachment 20: Ring-shaped recess

21: front 22: axial support shoulder

23: sliding bearing bush 24: connection part of the shape coupling method

25: sliding surface 26: axial limit stopper

27: cutout 28: sliding bearing plate

29: axial protrusion 30: snow area

30a: internal diameter 31, 32: cone-shaped area

Claims (13)

A divided flywheel consisting of a primary centrifugal mass that can be connected to a drive machine and a secondary centrifugal mass that can be connected to a gear input, The centrifugal masses are rotatable relative to one another against the action of at least one damping device, one centrifugal mass supporting at least one axial attachment, the attachment into a receptacle supported by another centrifugal mass. Extending along an axis, there is at least one sliding bearing between the receptacle and the attachment, the sliding bearing guarantees radial centering of the two centrifugal masses and at least one sliding bearing bush provided between the receptacle and the axial attachment And wherein the sliding bearing bush is inserted into the receptacle along an axis from one end of the receptacle. The bearing bush has at least one integrally formed radial extension over its circumference at least locally at its end facing the insertion end of the receptacle, the bearing bush for securing the sliding bearing bush along the axis in the insertion direction. A segmented fly wheel, characterized in that the radial extension interacts with a stopper region provided in the part having the receptacle. The method of claim 1, And the extension is in the form of a truncated cone. The method according to claim 1 or 2, An extended area of the sliding bearing bush is characterized in that it extends around at least almost the entire end of the sliding bearing bush. The method according to any one of claims 1 to 3, And the receptacle has at least one radial extension, the radial extension adapted to at least one extension of the sliding bearing bush. The method of claim 4, wherein Split portion fly wheel, characterized in that the expansion portion of the receiving portion is formed in the shape of a truncated cone. The method according to any one of claims 1 to 5, Radial centering of the centrifugal mass is ensured through a sliding bearing bush provided between the receiving portion and the axial attachment, the axial positioning is made by at least one ring-shaped sliding bearing plate, the sliding bearing plate being a sliding bearing bush Arranged at one end of the enclosure and surrounding the attachment, wherein the sliding bearing plate and the sliding bearing bush have an integral part causing at least one connection fixed to rotate together between the parts. Fly wheel. The method according to any one of claims 1 to 6, And the sliding bearing bush is rolled from the original flat bearing material. The method according to any one of claims 1 to 7, And the sliding bearing plate has an axial nose shape, the nose shape being inserted into a correspondingly adapted cutout of the bush after assembly is made. The method of claim 8, And the nose feature is integrally formed around the inner circumference of the sliding bearing plate. The method according to claim 8 or 9, And wherein the nose feature is formed by axially bending a radial nose feature integrally formed in the original sliding bearing plate. The method according to any one of claims 8 to 10, And the cutout of the sliding bearing bush has a U-shaped edge waveform. The method according to any one of claims 1 to 11, The sliding bearing bush and / or the sliding bearing plate are made of a sliding bearing material, wherein the sliding bearing material has a carrier layer and a sliding coating consisting of at least one layer applied over the carrier layer. Fly wheel. The method according to any one of claims 1 to 12, And wherein the material forming the sliding bearing bush has a greater thickness than the material forming the sliding bearing plate.

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