WO1997012158A1

WO1997012158A1 - Torque-transmitting arrangement

Info

Publication number: WO1997012158A1
Application number: PCT/DE1996/001764
Authority: WO
Inventors: Ralph Müllenberg
Original assignee: Muellenberg Ralph
Priority date: 1995-09-28
Filing date: 1996-09-18
Publication date: 1997-04-03

Abstract

The invention concerns an arrangement for transmitting torque between a shaft (1) and a structural component (10) which is mounted thereon and comprises an aperture for the shaft (1). The arrangement comprises: a conical clamping device with a pressure ring (4) which has a cylindrical inner peripheral surface (3) resting against the shaft (1), and at least one conical outer peripheral surface (5', 5''); a clamping ring (8); and axially parallel clamping screws (9) by means of which the clamping ring (8) can be tightened axially on the pressure ring (4) in the axial direction by sliding along the conical peripheral surfaces. The pressure ring (4) can be radially compressed and clenched on the shaft (1). On one side, the structural component (10) abuts only the pressure ring (4), and the structural component (10), pressure ring (4) and clamping ring (8) can be tightly fastened by the clamping screws (9).

Description

Arrangement for the transmission of a torque

The invention relates to an arrangement of the type corresponding to the preamble of claim 1.

Such an arrangement is known from DE 32 23 683 C2. In the known embodiment, the clamping screws act between the component and the clamping ring. The tightening takes place until the clamping ring rests with its end face against the component. At the same time, the component lies further inside on the pressure ring and binds an abutment for this when the clamping screws are tightened. With large clamping forces and a component that is not sufficiently stable, the component may bulge radially inside the clamping screws. Components in the form of disks or made of thicker sheet metal cannot advantageously be fastened in this way because they are not able to withstand the bending or buckling loads that occur.

The invention is based on the object of designing an arrangement of the type corresponding to the preamble of claim 1 in such a way that even thinner components can be properly fixed for transmitting the torque on the shaft.

This object is achieved by the invention reproduced in claim 1.

It is thereby achieved that the component rests on one side only on one component, namely the pressure ring and there are no bending and buckling stresses due to the application of forces at radially different locations. By pulling the three parts component / pressure ring / tension ring "on block", the cone tensioning device consisting of the pressure ring and the tension ring forms a compact, quasi one-piece unit, the parts of which do not work against one another when stressed. In addition, the "on block" pulling simplifies the assembly, insofar as the clamping screws only have to be tightened up to the "block" and not, as is the case otherwise, up to a predetermined torque which must be checked during the tightening.

It is understood that the tightening on the block requires a certain dimensioning of the radii of the conical surfaces with relatively small tolerances, so that sufficient radial tension is ensured when the "block" enters.

The system "on block" can be given radially in the area of the clamping screws (claim 2), but it can also extend relatively far radially beyond the clamping screws (claim 3).

This results in a greater rigidity of the clamped arrangement because the component rests on the larger clamping arrangement on the actual clamping arrangement, which in turn acts as a one-piece part after reaching the "on block" state, which is not in works. As a result, there is no buckling stress on the component, because the component rests and is supported radially within the “on block” contact area. The pressure ring is the only contact surface on which nothing can move axially compared to neighboring areas.

The "on block" system at radially wider areas can be realized in the manner set out in claim 4, which also has the practical advantage that the outer periphery of the approach is clearly visible and the achievement of the "on block" state over the vanishing distance to the adjacent contact surfaces of the clamping rings and the component is easily traceable.

The features of claim 5 serve the better use of the axial length to achieve clamping force. The design is known per se from DE-PS 1 190 266.

Various exemplary embodiments of the invention are shown in the drawing.

1 to 6 show longitudinal sections through the axis of the shaft through the upper half of the arrangement.

The arrangement 100 of FIG. 1 comprises a shaft 1 with a cylindrical outer circumference 2, on which a pressure ring 4 rests with its cylindrical inner circumference 3. The cylindrical inner circumference 3 extends over the entire length of the pressure ring 4. The pressure ring 4 has a stepped conical outer peripheral surface. It consists of a first, radially relatively thin-walled part with an outer cone surface 5 'with a cone angle α of 10 ° in the exemplary embodiment, a step with a step surface 5 perpendicular to the axis of the shaft 1 and one on the other side The radially thick-walled part adjoining the step surface 5 with a further cone surface 5 ″ with the same cone angle α.

On the outer circumferential surface 5 ', 5, 5' 'there is a clamping ring 8, the inner circumferential surface of which is complementary to the outer circumferential surface of the pressure ring 4 and thus has the same cone angle α as the conical surface 5' and lies on the conical surface 6 ', a step surface 6 located in front of the step surface 5 and a cone surface 6 ″ having the same cone angle α as the cone surface 5 ″ and resting thereon.

Distributed over the circumference on a pitch circle 7 are closely spaced axial tensioning screws 9, which extend with their head 9 'according to FIG. 1 from the right against the radially inner region of a shaft 2 arranged on it, essentially in a plane perpendicular to this - Apply the disc-shaped component 10 and radially the component 10 and the pressure ring 4 in its thick-walled part reach through in corresponding bores in the area of step 5 and engage in threaded bores in that part of the clamping ring 8 which is on the left in FIG.

If the clamping screws 9 are tightened, the component 10 is clamped between the heads 9 'and the right end face 4' of the pressure ring 4 free of buckling or bending stresses. The tightening takes place until the step surface 6 of the clamping ring 8 bears against the step surface 5 of the pressure ring 4. Then the order is drawn "on block", i.e. the parts 9 ', 10, 4 and 8 virtually form a metallic unit. The system is located on the step surfaces 5, 6 radially in the vicinity of the tensioning screws 9, that is to say to some extent in the interior of the tensioning set formed by the rings 4, 8.

The cone surfaces 5 ', 5' 'and 6', 6 '' are dimensioned in such a radius that they are already in contact with one another before the block position of the step surfaces 5 and 6 is reached. When the clamping screw 9 is further tightened, the pressure ring 4 is radially compressed by the wedge action on the conical surfaces 5 ', 6' or 5 '', 6 '' and clamped non-positively on the peripheral surface 2 of the shaft 1. The design must be such that a sufficiently large radial clamping is ensured when the block position is reached.

The clamping ring 8 is not slotted, so that it can exert large ring tensile stresses. The pressure ring 4, on the other hand, is slotted for optimal use of the tightening forces of the clamping screws 12 at one point in a plane passing through the axis (cf. FIG. 8), which is why it is shown unshaded in the drawing. The clamping screws 9 are seated at a point offset in the circumferential direction with respect to the cutting plane. The pressure ring 4 can be relatively radially compressed by the slit, so that as little as possible of the tightening force of the screws 9 is lost for the mere deformation of the pressure ring 4.

It is important that the component 10 abuts on the left side in FIG. 1 exclusively on the pressure ring 4 takes place and there is a distance 11 between the relevant side of the component 10 and the end face 8 'of the clamping ring 8 there, so that the component 10 is free outside the end face 4' and no buckling or bending moments are exposed.

Insofar as parts corresponding to the function are present in the further embodiments, the same reference numbers are used.

In the arrangement 200 of FIG. 2, the cone rings 14, 18 are not stepped cone rings as in FIG. 1, but simply conical rings, each of which has only one cone surface 5 ', 6'. In the exemplary embodiment in FIG. 2, the clamping screws 9 are screwed in from the left and penetrate through bores in the clamping ring 18 and the flange 17 of the pressure ring 14, in order then to engage in threaded bores in the component 10. The component 10 lies only against the end face 14 'of the pressure ring 14. The tightening of the clamping screws 9 takes place until the parts 10, 14, 18 sit "on block", i.e. the end faces 15, 16 of the pressure ring 14 or the tension ring 18 abut one another. The design is such that there is then a sufficient radial clamping force on the peripheral surface 2 of the shaft 1.

The arrangement 300 of FIG. 3 differs only from the arrangement 100 of FIG. 1 in that the pressure ring 4 on the side facing the component 10 has a bush-like extension 24 with an inner circumferential surface resting on the outer circumferential surface 2 of the shaft 1 and a conical surface ¬ has the outer peripheral surface, which projects into a cylindrical recess 20 of the inner peripheral surface of the component 10. On the conical outer circumferential surface, a conical ring 25 is seated with a conical inner circumferential surface, which is supported radially in the recess and radially compresses the shoulder 24 when the clamping screw 9 is tightened and ensures an increase in the radial clamping force on the shaft 1.

While in the embodiments 100, 200, 300 the component 10 only rests on one side on a conical ring, in the embodiments 400, 500, 600 it is on both sides clamped between rings, but only one ring is present on one and the same side of the component 10.

In the arrangement 400 of FIG. 4, the part to the left of the component 10 corresponds to the arrangement 100. The pressure ring 4 has a socket-like extension 34 projecting to the side of the component 10, which has a cylindrical section 30 under the component 10, on which the component 10 is centered with its cylindrical inner circumference 10 '. Outside of component 10, i.e. On the right side in FIG. 4, the insert 34 has a conical surface 35, the radial wall thickness of which decreases towards the outside, and on which an additional clamping ring 38 with its conical inner circumferential surface 36 has the same conical angle before it is applied according to FIG. 4 left end face 38 'has come into contact with component 10.

The clamping screws 9 pass through bores in the additional clamping ring 38, the component 10 and the pressure ring 4 'and engage in threaded bores in the clamping ring 8. Tightening the clamping screws 9 is carried out until all parts are "on block". Appropriate dimensioning of the "radii" of the conical surfaces ensures that a suitable radial clamping force is present in the block position.

In the arrangement 500 of FIG. 5, the pressure ring 44 which is slotted longitudinally at one point is again a single ring with a radial flange 45, to which a sleeve-like extension 34 with a cylindrical part 30 for centering the inner circumference 10 ′ of the component 10 is connected on the component side. The additional clamping ring 38 and the flange 45 clamp the radially inner part of the component 10 between them. The clamping screws 9 pass through through holes in the additional clamping ring 38 and in the component 10, in order to then engage in threaded holes in the flange 45 of the pressure ring 44. In principle, arrangement 500 corresponds to the right half of arrangement 400.

In the arrangement 600 of FIG. 6, an arrangement 100 is not on a shaft, but on a shaft journal 1 attached, which merges in a step perpendicular to the axis with an end face 50 'into the outer circumference of a shaft 50 of larger diameter. The fastening screws 9 pass through through bores in the clamping ring 8, the pressure ring 4 and the component 10, in order then to engage in axially parallel threaded bores in the end face 50 ′ facing the component 10.

In this exemplary embodiment, too, the radially inner region of the component 10 is clamped between the step surfaces 4 'and 50', but in the rest of the component 10 is free and is not exposed to any buckling or bending stresses.

In the arrangement of FIGS. 7 and 8, the “on block” arrangement of the pressure ring 54 and the clamping ring 8 no longer takes place “inside”, that is to say in the immediate vicinity of the clamping screw 9, but radially outside the same in the area of a radial outwardly projecting annular projection 52 which, as can be seen from FIG. 7, engages radially between the right end face 8 'of the clamping ring 8 and the left side of the component 10. The system which limits the further mutual axial movement of the rings 54, 8 and which blocks them together to form a quasi one-piece unit thus takes place in this exemplary embodiment radially outside the clamping screw 9 on the left and right (FIG. 7) end face 52 ', 52 "of the shoulder 52 instead. This has the advantage that the support surface for the component 10 also extends radially outward and ends in the area of the outer circumference of the shoulder 52 or the clamping ring 8. The distance 11 in the embodiments of FIGS 1 and 3 corresponding necessary distance 21 is here between the step surfaces 5 and 6.

Although the "on block" system is not provided here on both sides of the screws 9, there is also no buckling stress on the component 10 here because it only rests against the end face of the pressure ring 54. Neither radially inside nor radially outside the contact area on the attachment 52, the component 10 bears against counter surfaces which could shift axially relative to the contact area. In order to be able to detach the rings 54 and 8 from each other again in the presence of self-locking cone angles, pressure threads 22 are provided at some points evenly distributed over the circumference, into which push-off screws (not shown) can be screwed after the tensioning screws 9 and the component 10 have been removed , which meet bore-free points in the clamping ring 8 and allow the same to be pressed off the supporting ring 54 in the axial direction.

Similar to the arrangements 400 and 500, the arrangement 700 on the pressure ring 54 has a circumferential, axially projecting bush-like extension 23 on the outer circumferential surface of which the inner opening 25 of the component 10 is seated and whose inner circumferential surface is flush with the cylindrical inner circumferential surface 3 of the pressure ring 4 transforms.

The arrangements 100, 300 and 700 have the same cone angle in the case of the conical surface pairs 5 ', 6' and 5 ", 6" which follow one another in the axial direction. However, it is possible to choose the cone angle of the cone surfaces 5 ", 6" adjacent to the component 10 to be somewhat larger, as is shown in the arrangements 400 and 600. With a suitable dimensioning of the radii, the areas of the clamping ring 8 on the right in the drawings lie particularly strongly on the counter surface 5 ".

The cone angle α for the arrangements 100, 300 and 700 is 10 ° and is therefore outside the self-locking range. However, it is also possible to use self-locking, i.e. use cone angles below approximately 7 °, in which case the forcing threads 22 are provided in order to be able to detach the parts of the cone clamping device from one another again. It is also possible to choose the cone angles of the axially successive conical surface pairs 5 ', 6' or 5 ", 6" differently, e.g. at 5 ', 6' below and at 5 ", 6" above the self-locking angle. It is understood that the conical surfaces in all embodiments are arranged in such a way that their radius increases in the direction of the axial tensile force exerted by the screws 9 on the respective conical ring having the conical surface.

Claims

Patent claims

1. Arrangement for transmitting a torque between a shaft (1) and a component (10) arranged thereon and having a passage for the shaft (1), with a cone clamping device with a pressure ring (4, 14, 44, 54) a cylindrical inner circumferential surface (3) which rests on the cylindrical outer circumferential surface (2) of the shaft (1), and at least one conical outer circumferential surface (5 ', 5''), and with a clamping ring (8, 18, 38) at least one conical inner circumferential surface (6 ', 6 "; 36) which has the same cone angle (et) as the outer circumferential surface (5', 5"; 35) of the corresponding pressure ring (4, 14, 44, 54) and on the conical outer circumferential surface (5 ', 5''; 35) of the pressure ring (4, 14, 44, 54) bears, with axially parallel clamping screws (9) distributed over the circumference, by means of which the clamping ring (8, 18, 38) axially pullable along the conical circumferential surface onto the pressure ring (4, 14, 44, 54) and the pressure ring (4, 14, 44, 54) can be pressed radially together and on the shaft (1), the component (10) being fixable by means of screws on the front side of the cone clamping device, characterized in that the component (10) on one side only on the pressure ring (4th , 14,44,54) and component (10), pressure ring (4,14,44,54) and clamping ring (8,18,38) through the clamping screw - Lo ¬ ben (9) "on block" are draggable.

2. Arrangement according to claim 1, characterized in that the system "on block" is given radially in the area of the Spann¬ screws (9).

3. Arrangement according to claim 1, characterized in that the system "on block" is given radially outside the area of the clamping screws (9).

4. Arrangement according to claim 3, characterized in that the pressure ring (54) has a radially projecting, between the component's (10) and the end face (8 ') thereof facing the clamping ring (8) engaging annular circumferential approach (52) , on the lateral end faces (52 ', 52 ") of which there is" on block "of the component (10), the pressure ring (54) and the clamping ring (8).

5. Arrangement according to one of claims 1 to 4, characterized in that the pressure ring (4, 14, 44, 54) and the clamping ring (8) each have at least two stepped conical outer and inner peripheral surfaces (5 ', 6'; 5 ", 6"), of which the conical surface pair (5 ", 6") closer to the component (10) each has the larger average diameter.