EP0198860A1

EP0198860A1 - Method and machine for fabricating rotation bodies by plastic deformation.

Info

Publication number: EP0198860A1
Application number: EP85905045A
Authority: EP
Inventors: Ludwig Balint
Original assignee: Individual
Current assignee: Individual
Priority date: 1984-10-19
Filing date: 1985-10-15
Publication date: 1986-10-29
Also published as: ATE40059T1; DK289186D0; AU4962585A; US4817408A; AU580347B2; DE3587876D1; KR930009935B1; DE3567592D1; ATE108104T1; KR870700422A; DK289186A; EP0198860B1; WO1986002296A1

Abstract

A process and machine for fabricating a rotation body having different diameters along the length thereof is disclosed, in which a blank is rotated and worked between two pressure zones to apply thereto a local pressure exceeding the flow limit of the blank material whereby circularly extending impressions of the different diameters are worked into the blank, the pressure zones crossing each other. The pressure zones are displaced relative to each other while applying the local pressure, the displacement motion having a component extending in the longitudinal direction of at least one of the pressure zones and the points of intersection of the crossing pressure zones forming a geometric line, and the blank is displaced in dependence on this line and on the different diameters to be produced.

Description

Method and device for producing rotary bodies by flow forming

The invention relates to a method for producing rotary bodies which have different diameters over their length, in which, when the blank is rotated, a pressure locally exceeding the flow limit of the material of the blank is exerted and this is deformed ^* .

In the previously known methods of this type, two parallel pressure zones were mostly used, between which the blank is processed. For this purpose, two rolls are provided with profile ribs, which can be driven in opposite directions, between which a roll gap remains. The blanks are moved through the roll gap essentially transversely to the rolls, which are usually crossed by a small angular amount, which results in the disadvantage of an almost sudden onset and only a very short-term action of the pressure zone determined by the profile ribs.

Furthermore, for the production of threaded bolts, it has already been proposed to deform the blank between two parallel pressure zones, which are determined by profile ribs arranged on a roller and a counterpressure surface interacting with it. However, because there is no possibility of reordering the counter surface to the roller, it is not possible to achieve sufficient accuracy in the finished rotating bodies over a long period of time.

The aim of the invention is to avoid these disadvantages of the known methods and to propose a method which is universally suitable for the production of differently shaped rotating bodies and in which a gradual use of the pressure is possible.

According to the invention this is achieved in that the blank is machined between two crossing pressure zones, the pressure zones being moved relative to one another and the blank depending on the line and the lines to be produced by the crossing points during the relative movement of the pressure zones lend diameter changes is moved. Due to the relative movement of the intersecting pressure zones and the guiding of the blanks, it is possible to produce any shape from these rotary bodies, and a longer duration of action of the pressure zones on the blank is also possible.

For the production of rotary bodies with circumferential grooves, it can be expediently provided that the blanks are moved essentially parallel to the course of the crossing points of the pressure zones which result from the relative movement of the pressure zones.

For the production of rotating bodies with spiral grooves, e.g. On the other hand, threads can be provided for the blanks to be moved at an angle corresponding to the pitch angle of the spiral groove to be produced relative to the line corresponding to the geometrical location of the intersection points of the pressure zones during their relative movement, with threads being produced , preferably a blank having the outer diameter of the desired thread is used.

For threads, especially trapezoidal threads or the like. When using blanks with the outer diameter, there is the advantage that the material does not have to flow up the thread flanks in order to completely build up the threaded ribs, which may be the case. can lead to excessive stress on the material and to the formation of cracks on the lateral surface of the threaded ribs, but can only flow axially, which ensures that the threaded ribs are made of full material and cannot have any cavities or cracks covered by material displaced to the outside.

For the production of rotating bodies with at least two sections with different sections. On the other hand, it is advantageous for diameters if the intersecting pressure zones are at least sections narrower than the section of the rotary body to be produced, which has a smaller diameter, and. The blank is inclined against the line corresponding to the geometrical location of the crossing points of the pressure zones during their relative movement. Another object of the invention is to propose an apparatus for performing the method. In the case of a device which has a roller and a counter-pressure surface interacting with it, which are movable relative to one another and in which at least one raised profile rib is arranged on the roller and the counter-pressure surface, a further feature of the invention is therefore proposed that the profile ribs are arranged crossing one another and a guide is provided for the blanks, the course of which is related to the line determined by the crossing points of the profile ribs during the rotation of the roller. These measures ensure the crossing pressure zones in a very simple manner, the course of the guide for the blank being selected depending on the rotary body to be produced in relation to the course of the crossing points of the profile ribs which result from the rotation of the roller can.

For the production of rotating bodies with circumferential grooves, it can be provided that the guide runs essentially parallel to the lines determined by the crossing points of the profile ribs during the rotation of the roller, the counter surface preferably being subdivided into segments which can be displaced radially to the roller is. It is thereby achieved that the profile ribs act essentially always in the same axial position on the blank during the entire machining. Slight deviations from the parallelism between the guide and the intersection points of the profile ribs resulting from the rotation of the roller can be provided in order to compensate for the increase in length of the blank being machined due to the incorporation of a groove or the reduction of the diameter in sections ¬ view or to solidify the walls of the ribs.

In the case of a counter surface subdivided into segments, it is also possible due to the intersecting profile ribs to feed the counter surface more or less far to the roller. This is possible due to the fact that in extreme cases the intersecting profile ribs can only touch each other along one surface line. In the known devices with parallel profile ribs, on the other hand, this is not possible since In this case, a change in the radial position of the counter pressure surface would result in a gap which changes over the arc length between the interacting surfaces of the profile ribs.

For the production of rotating bodies with spiral grooves, on the other hand, it is advantageous if the guide runs at an angle corresponding to the slope of the groove to be produced against the line determined by the crossing points of the profile ribs during the rotation of the roller. Due to the angle corresponding to the increase in the thread to be produced between the course of the guide and the line resulting from the crossing of the profile ribs as a result of the rotation of the roller, it is possible in a very simple manner with only one thread rib corresponding profile ribs Form thread. Of course, the length growth of the blank when pressing in the groove must also be taken into account if a blank having the outer diameter of the thread to be produced is used.

For the production of rotating bodies with sections with at least two sections with different diameters, it can be provided that the guide is inclined against the line determined by the crossing points of the profile ribs during the rotation of the roller, the inclination caused by the inclination The mutual distance of this line from the guide over a distance corresponding to one revolution of the blank is smaller than the width of the profile rib and the difference between the distances of the guide and the line determined by the crossing points in the feed area for the blanks and a removal area for the finished rotary body corresponds to the length of the section with a smaller diameter of the rotary body. These measures ensure that not only pressure is exerted on the blanks to be machined in the radial direction, but also in the axial direction, which facilitates the flow of the material.

The intersecting profile ribs also make it possible to produce bodies with a pointed or streamlined end region. All that is required is the Form the ribs accordingly, these touching one another in the course of the mutual rotation.

In a preferred embodiment of the invention it can further be provided that the segments of the counter surface are arranged on slides which are guided so as to be radially displaceable to the central roller and which can preferably be moved independently of one another by means of a control drive. It is thus possible to compensate for differences in the blanks in a very simple manner both with regard to their dimensions and with regard to their hardness or strength. Provision can also be made to apply signals to an automatic measuring device to the control drive, which checks or measures the finished rotating bodies on a random basis. The counter-pressure surface can thus be adjusted so that the finished rotating body lies in the central area of the intended tolerance field.

According to a further feature of the invention, it can be provided that each of the intersecting profile ribs of the central roller and the counter surface is inclined towards the axis of the central roller. It is entirely possible to arrange one of the crossing profile ribs perpendicular to the axis of the central roller, but in this case the central roller and the counterpressure surface must also perform a relative movement in addition to the relative rotary movement, which movement runs in the axial direction of the roller Has component. This additional movement is superfluous due to the arrangement of the profile ribs of the roller and the counter pressure surface inclined relative to the axis of rotation of the roller.

Another object of the invention is to propose an improved method for producing rotary bodies with different diameters at their two ends or axial sections with different diameters, in which, when the blank is rotated about its longitudinal axis, a pressure locally exceeding the yield point of the blank material is used Reduction of the diameter of the blank is exercised and a device for performing the method.

In the previously known methods of this type, one was A profile rib arranged in a roller is pressed into the blank supported by a counter-pressure roller rotating in the opposite direction of rotation, the width of this profile rib being at least as wide as the section of the blank to be reduced in diameter is long. In practice, this means that the pressure is simultaneously exerted on the entire area to be reduced in diameter.

However, this has the disadvantage that very high forces and therefore also large energies are required for this. In addition, the material begins to flow relatively difficultly in this known method.

It is therefore proposed according to the invention that a pressure zone having a smaller dimension in the longitudinal direction of the blank compared to the axial extent of the area with a reduced diameter of the rotary body to be produced is moved in the axial direction of the blank during rotation thereof. This can be done in such a way that a narrow profile rib is moved in the axial direction over the blank during rotation. In this case, the material is forced to flow in the axial direction of the blank, as a result of which deformation is easier and requires less force.

In any case, during the local pressure treatment of the blank, a force component acting on it in the axial direction also acts on the blank, whereby the flow process triggered by the pressure treatment is considerably facilitated.

In the case of a device for carrying out this variant of the method according to the invention with a roller which interacts with a counter pressure surface and is movable relative to the latter, with a raised profile rib being arranged on the roller and / or the counter pressure surface A further feature of the invention proposes that the profile rib (s) have a smaller width compared to the axial extent of the area with a reduced diameter of the rotary body to be produced and that a guide inclined relative to the profile rib is provided for the blanks. This will cause a movement of the pressure

-7-

zone forced in the longitudinal direction of the blank.

In the production of rotating bodies with circumferential grooves, additional compression in the area of the groove walls may be desirable in some cases. In such a case, the control groove can be inclined against the imaginary line resulting from the course of the crossing points of the profile ribs of the central roller and the counter pressure surface. As a result, the profile ribs not only press radially on the blank but also in the axial direction on the groove walls that form.

In this context, according to a further feature of the invention, it can be provided that the profile rib (s) arranged on the central roller and the counter-pressure surface, which is preferably subdivided into segments that can be adjusted in several radial positions relative to the roller (n) Profile rib (s) inclined against the axis of rotation of the roller and cross each other in the course of the mutual relative movement and a guide is provided for the blanks, which is opposite the corresponding edges of the profile ribs when the roller rotates resulting K-Kuzuzpunkt- certain line runs inclined, the inclination-induced difference in the mutual distance of this line from the guide over a distance corresponding to one revolution of the blank being smaller than the width of the profile rib and the difference in the distances between the Guiding of the line determined by the crossing points in the feed area for the blanks and em removal area for the finished rotary body corresponds to the length of the section with a smaller diameter of the rotary body. This ensures that the profile ribs, which are narrow compared to the grooves or sections to be produced with a reduced diameter, are moved in the axial direction over the blank, but without this leading to the formation of spiral grooves. As a result of this axial movement, the flanks of the profile ribs exert pressure on the walls in the axial direction. the groove to be produced or exerted on the shoulder of the section to be produced with a reduced diameter ¹ , which leads to a

Compression of the material in this area leads. In order to ensure an exact driving and guiding of the blanks during their processing between the central roller and the counter pressure surface, it can be provided according to a further feature of the invention that the guiding is formed by a driving device which has at least one, preferably but has two rotating bodies spaced apart from one another in the axial direction of the central roller, in which or which plungers are slidably held in the longitudinal direction thereof or by means of a sliding block or the like. engage in a circumferential control groove arranged in a fixed part of the device, plungers guided in two different rotating bodies being aligned axially to one another and essentially parallel to the axis of rotation of the roller and the blanks by at least one plunger, but preferably between two plungers can be clamped. These measures ensure that the blanks are clamped between the plungers and a link, but better between two plungers which are axially aligned with one another and are thus taken along. It can further be provided that the control groove (s), with the exception of a feed and removal area for the blanks or the rotating bodies, run essentially parallel to one another, thereby ensuring exact guiding of the blanks and simple feeding of the blanks and removal of the finished rotating bodies becomes. A slight deviation in parallelism to compensate for the growth in length of the blank during machining can be provided.

In a preferred embodiment of a device according to the invention it is further provided that at least one another facing end regions of the plungers are rotatably mounted about the longitudinal axis of the plungers, the end regions of the one plunger preferably being spring-loaded against the coaxially aligned plungers. This prevents friction between the end faces of the blanks and the plungers. A resilient support of the end regions of the one plunger prevents the blank being machined from being pressed too strongly if it grows in the axial direction, for example due to the indentation of the groove or a reduction in diameter. In addition, dimensional deviations of the blanks can be compensated for. The end regions of the plunger can be formed by inserts.

According to a further feature of the invention, provision can also be made for a toothed ring, which is connected to the central roller in a rotationally fixed manner, to engage in the gearwheel transmission connected to support shafts arranged parallel to the tappets, the support gear being provided Shafts are held in the rotating body guiding the tappets or in rotating bodies connected to them in a rotationally fixed manner, the circumferential speeds of the central roller and the blanks being able to be matched to one another by appropriate coordination of the gear drives.

The invention will now be explained in more detail with reference to the drawings.

It shows

1A and 1B schematically show tools for carrying out the method according to the invention and the deformation of a blank with such tools, FIG. 2 shows the development of the profile ribs of the tools according to FIGS. 1A and 1B,

FIG. 3 shows an exemplary embodiment of a device for carrying out the method according to the invention in vertical section,

FIG. 4 shows a top view of the device according to FIG. 3,

FIG. 5 shows a detail of the device according to FIGS. 3 and 4 on a larger scale, 6 shows a detail of the tappet guide of the device according to FIGS. 3 and 4 on an enlarged scale, FIG. 7 shows a further detail of the tappet, FIG. 8 shows an exploded view of the driving device of the device according to FIGS. 3 and 4, FIG. 9 shows a view of the driving device and Figure 10 is a plan view of the entrainment device.

FIG. 1A shows the profile ribs 7 and 8 arranged on the counter pressure surface 1, which is divided into five segments 2, 3, 4, 5 and 6, of which the profile rib 7 for forming the shoulder or shoulder 10 of the finished one Rotating body 9 is used. The profile rib 8, on the other hand, is used to form the groove 11 of the finished rotary body 9 ^V and has its greatest width and smallest height at the beginning of the counter pressure surface 1 or at its limit to the input area for the blanks 9 to be machined. Along their path from the beginning of the profile rib 8 to its end on the edge of the segment 6 of the counter pressure surface 1 which runs with respect to the direction of rotation of the roller 12 shown in FIG to, where it ends in a shape that is opposite to that of the groove 11.

The profile rib 7, which brings about the shaping of the shoulder 10 of the finished rotary body, on the other hand takes along its path from the cross section x at the edge of the input area to the cross section x5 at the trailing edge of the segment 6 or at the beginning of the output area for the finished rotary body 9 ^V in width and height too.

The central roller 12 shown in FIG. 1B runs in the space enclosed by the segments 2 to 6 of the counter pressure surface, but a common representation has been left out for reasons of better clarity. The roller 12 is installed in such a way that when the roller 12 is positioned relative to the segments 2 to 6 of the counter-pressure surface 1 in which the beginnings of the profile ribs 7 and 8 are radially aligned, these also in FIG same height.

The interaction of the two groups of profile ribs 7 and 8 or 7 'and 8 ¹ is best seen in FIG. 2, which shows the development of the profile ribs 7 and 8 of the counter pressure surface / Ϊ 1 and the profile ribs 7' and 8 'of the roller 12 shows. The profile ribs 7 and 8 rise from left to right, whereas profile ribs 7 'and 8' fall from left to right. When the roller 12 rotates in the direction of the arrow 13 in FIG. 1B, the profile ribs 7 'and 8' are moved in the direction of the arrow 13 in FIG. 2 with respect to the profile ribs 7 and 8.

As can be seen from Figures IB and 2, the cross-sectional shape of the profile ribs 7 'and 8' changes in the same way as that of the profile ribs 7 and 8, i.e. the profile rib 7 'widens from the cross section x to the cross section x5 and the profile rib 8' decreases in width in the area of its largest elevation and increases in height.

Due to the arrangement of the profile ribs of the counter-pressure surface 1 and the roller 12 which is inclined opposite to one another and to the axis of the roller 12, as the roller 12 rotates, intersection points of these profile ribs continuously result, which result in an imaginary line which is essentially parallel to the dash-dotted line 15 , which corresponds to the geometric location of the crossing points of the profile ribs 8, 8 'which result when the roller 12 is rotated. As can be seen from FIG. 2, the blanks 9 are guided parallel to the line 15 between two plungers 14, 14 ', which line is slightly inclined towards the profile rib 8 in order to take into account the growth in length of the blank when the groove is pressed in.

Since the edge of the profile rib 7 or 7 ′ closer to the line 15 encloses an angle with this, the blank 9 becomes not only due to the increasing height along this path on its way from the cross section x to the cross section x5 between the roller 12 and the counter pressure surface 1 of the profile ribs is exposed to a radially acting pressure, but also to an axial pressure acting on the shoulder 10 which forms, which significantly promotes the flow of the material, in particular in the axial direction and relieved. The change in the shape of the blank 9, which it shows when the individual cross sections x to x5 are reached, is shown in FIG. 1A ".

The intermediate product 9 ¹ corresponds to the state of deformation of the blank 9, as is given at the border x1 between the segment 2 and the segment 3. This shows the cross-sectional shape of the profile ribs in this cross-section. In the same way, the intermediate product 9 "corresponds to the state of deformation of the blank in cross section x2, the intermediate product 9" ¹ corresponds to the state of deformation of the blank in cross section x3 and the intermediate product 9 ^{, v} corresponds to the state of deformation in cross section x4. In cross section x5, the blank is shaped to form the finished rotating body 9 ^V.

From the shape of the intermediate products 9 ', 9 ", 9"', 9 ^{, v} , 9 ^{V it} can clearly be seen that the profile rib 8 and the profile rib 8 '(FIG. 1B) have their greatest elevation in width from the beginning decreases in the respective cross-section, whereas the profile rib 7 and 7 "increase in width.

It can also be seen from FIG. 1A that the blanks 9 are held between two plungers 14, 14 'during processing, which separate from one another in the input and output area lying between the cross sections x5 and x, and thus the input of the blanks 9 and the output of the finished rotary body 9 is possible, which takes place in different planes lying perpendicular to the axis of the roller.

As can be seen in particular from FIG. 2, the profile ribs 8 and 8 'used to form the groove 11 run essentially parallel to the line 15 and thus parallel to the path which the blanks describe during their processing between the roller 12 and the counter pressure surface 1 . The slight inclination of the line 15 to the profile ribs 8, 8 'serves to compensate for the displacement of the groove being worked in with respect to an end face of the blank due to the length growth of the blanks by the indentation of the groove. As is clear from Figures 1A to 2, but in particular from Figure 2, is ^*, it the same design of the profile ribs of the angle by the mere change in the blank at its Bearbei¬ tung to those resulting in rotating the roller by the, by If the crossing of the profile ribs is guided, it is possible to change the deformation of the blank. The profile ribs 8, 8 'could also be changed if the blanks 9 were inclined accordingly, for example according to the dotted line 17 in FIG be used to produce a spiral groove, the angle between the profile ribs 8, 8 'and the path of the blanks determining the slope of such a spiral groove. The only prerequisite for this would be that the profile ribs 8, 8 'are narrower than the pitch of this groove on the rotary body to be produced. If this is not the case, a circumferential groove, the width of which exceeds that of the profile rib 8,8 ', will result when the blanks are guided at an angle to the profile rib 8,8'. Due to the pressure exerted by the profile rib 8, 8 'on the blank in the axial direction, the material would be compressed in the region of a wall of the groove.

With a correspondingly large angle between the profile rib 8, 8 'and the path on which the blanks 9 are guided between the roller 12 and the counter surface, the profile rib 8, 8' can also be used to form a section of the rotary body 9 to be produced smaller diameter can be used. To do this, the blanks only need to be guided on a path that leads upward relative to the profile rib 8, 8 ', e.g. along the dashed line 16 shown in FIG. 2.

D-abei, the pressure zones determined by the profile ribs 8, 8 'would be displaced in the axial direction with respect to the blank, whereas, in the case of the pressure zones determined by the profile ribs 7, 7' and the blanks were guided according to line 15 in FIG 2 only a limitation of the pressure zones is moved in the axial direction with respect to the blank.

Figure 3 shows schematically a device for performing the are shown OF INVENTION _d ungsgemäßen process in vertical section, wherein in particular the one bearing and the installation easier. Also, "are made of manufacturing reasons and for reasons of a simpler assembly consisting of several parts compo ^¬ pen shown in part as one part.

The drive motor 20 drives a shaft 23 via a clutch 21, one half of which is connected to a flywheel 22. This is supported in the usual way via the roller bearings 24 and 251Λ housing 26 and is rotatably connected to a bevel gear 27 and a sprocket 29.

The bevel gear 27 meshes with a further bevel gear 28, which is connected in a rotationally fixed manner to a vertical main shaft 30. The main shaft 30 is held by means of two tapered roller bearings 31 and 32 in a bearing cylinder 33 connected to the housing 26.

A first guide body 34 is placed on this support cylinder 33 and rigidly connected to it. Furthermore, a needle bearing 35 is arranged on the supporting cylinder 33, which is fixed in its axial position by the guide body 34 and a support flange 36 and rotatably supports a rotating body 37 provided with a sprocket 38.

This rotating body 37 or its sprocket 38 is connected via two chains 39 to sprockets 40, which are connected in a rotationally fixed manner to the output shaft 41 of a gear 42. This gear 42 is driven by two chains 44 and sprockets 43 by the shaft 23 or the sprockets 29 connected to it and held in the housing 26 'by a bracket 46.

The rotating body 37 is connected to a further rotating body 47 via bolts 45 and is mounted on the main shaft 30 via a roller bearing 48. These two rotating bodies 37 and 47 are also connected to one another via slotted guide sleeves 49, in which the plungers 14 'or their guide heads 50 are guided axially displaceably. These guide heads 50 engage with their rotatably held roller 51 in a control groove 52 arranged in the guide body 43. The plungers 14 'pass through the rotating body 47 and are guided in bushings 53 therein. Furthermore, a spray ring 54 is fastened to the rotating body 47 and serves to discharge the oil used for lubrication into an oil sump (not shown) arranged in a ring.

The rotating body 47 is connected by means of supports 55 to a further rotating body 56 which, like the rotating body 47, is provided with sections of dovetail guides which extend in the tangential direction and which serve to receive sliding blocks which are parts of the are shown in FIGS. 8 to 10 and are explained later with reference to these figures. For reasons of better clarity, the corresponding reference numerals have not been entered in FIG. 3.

A chuck body 57 is arranged on the main shaft 30 in a rotationally fixed manner, onto which the roller 12 provided with the profile ribs 7 'and 8' is pushed and held in a rotationally fixed manner by means of a tongue and groove connection. A toothed ring 58 is screwed to the roller 12, from which the drive for the driving device is derived, as will be explained in more detail with reference to FIGS. 8 and 10.

A sleeve 59 is pushed onto a shoulder of the main shaft 30 and connected to it in a rotationally fixed manner via a tongue and groove connection. A rotary body 62 screwed to an internal ring gear 61 is mounted on this sleeve 59 via a roller bearing 60. As can be seen from FIG. 5, the internal toothed ring 61 meshes with intermediate toothed wheels 63, which in turn mesh with further toothed wheels 64, which only serve to reverse the direction of rotation, and which, like the intermediate toothed wheels 63, rotate in a guide body fixed inside the housing 65 arranged ring 66 are held. The gearwheels 64 in turn mesh with a toothed ring arranged on the sleeve 59, which ensures the drive of the rotating body 62 via the toothed wheels 63 and 64 and the toothed ring 61, which supports the guide body 65 via a roller bearing 60 '. The rotating body 62 is Connected via bolts 67 and a sleeve 68 to a ring 69, in which, as in the rotating body 62, bushings 53 in which the plungers 14 are rotatably and axially displaceably held are held. The guide body 65 is formed in two parts and supports the main shaft 30 via a rolling position ^* 69 '. Furthermore, the guide body 65 is provided with a control groove 70, in which, as shown in FIG. 6 on a larger scale, a rotatable roller 51 which is held in each guide head 71 of the plunger 14 engages. The pin 72 carrying the roller 51 engages, as shown in FIG. 6, with a shoulder in a circumferential groove 73 of the tappet 14, as a result of which it is rotatably but axially immovably held in the guide head 71.

The control groove 70 runs parallel to the control groove 52 of the guide body 34 over the large part of the circumference of the guide body 65. Only in the input and output area explained with reference to FIG. 1A does this parallelism not exist and the two control grooves diverge in this area and again together.

The guide body 65 can be connected via a flange body 74 to a support arm 75 in which the main shaft 30 is supported in a slide bearing. The support arm 75 is supported on a support column 76 which is fastened on the housing 26 '. A spindle 77 is arranged in this support column 76 and is supported in its upper region by means of a centering ring 78 against the inner wall of the support column 76 and against a cylindrical bore 79 of the support arm 75. The support arm 75 is clamped to the support column 76 by means of a nut 80. After the untwisting and remo _¬ mother men 80 and releasing the connection of the flange 74 with the support arm 75 the latter can be lifted and pivoted, whereby it is possible to, for example, to replace the means to decompose the roller 12 with another one having a different shaped profile ribs, in order to be able to produce other rotating bodies.

Furthermore, five carriages 81 carrying the segments 2 to 6 of the counter surface 1 are arranged on the housing 26 '. These carriages are guided in housings 82, in each of which a threaded spindle 84, which is supported in a bearing arrangement 83 consisting of axial and radial roller bearings, is arranged. This is driven by a stepping motor 86 via a gear 85 and enforces two mutually offset to compensate for the thread play. tensioned nuts 87, which in turn is connected to the slide body 88, which is guided in the housing 82 and in which a weak point 89 for accommodating strain gauges is incorporated.

On the front side of the slide body 88, a height support is guided, which, together with the associated adjusting spindle, is designated by 90. A segment of the counter surface 1 carrying the profile ribs 7 and 8 is fastened to this height support 90.

On the slide 81 and the support column 76, a circumferential link 92 is held via holding arms 91, which, as will be explained in more detail with reference to FIGS. 8 and 9, is provided for controlling the driver device.

The feed device for the blanks to be deformed, which can be seen more clearly in FIG. 4, is designated in its entirety by 93 and is driven by the gear 42 via a chain wheel 94 and a chain 95.

The translation of the gear 42 and the sprockets 40 and 38 and that of the gear formed by the ring gear 61 and the ring gear of the sleeve 59, as well as the gears 63 and 64 is selected so that the rotating body driven by these gears on that of the in these Rotary bodies held plungers 14, 14 'described path have half the peripheral speed of the jacket of the roller carrying the profile ribs.

In the carriage 81 shown in section in FIG. 4, a vibration generator 96 is screwed into the segment of the counter-pressure surface 1, which sets the counter-pressure surface in high-frequency vibrations and thereby facilitates the deformation of the blanks 9, which is carried out by means of one in the figure 4, for reasons of better clarity, the driver device (not shown) is guided between the segments of the counter pressure surface 1 and the roller 12.

The feed device 93 has, as can be seen from FIG. 4, an inclined trough 97 which forms the blanks 9 into one Star wheel 98 conducts. This star wheel 98 transports α e «onunge to a further star wheel 99, a guide plate 100 being provided for the transfer of the blanks 9, which is fastened to the housing 26 'via a holder (not shown for reasons of clarity).

Stamps 101 are guided in the star wheel 99, which rotates in a plane offset from the star wheel 98, only two of which are shown. These stamps protrude beyond the upper end face of the star wheel 99 and slide along the nooke 102. This nooke, which stands still, causes the blanks 9 to be pushed out into the path of the plungers 14, 14 ', from which they are gripped ^* or clamped.

In a different horizontal from the feeder

A magnet 103 is arranged on the plane, which leads the finished rotation elements through the plungers 14, 14 'into a further channel 104.

A switch 105 is installed in the trough 104, which makes it possible, by inserting a baffle 106 by means of the piston-cylinder arrangement 107, to selectively pull out a rotary body which then reaches a measuring device 109 via a trough 108. In this, the rotary body 9 is pushed with a piston 110 into a measuring position in which it rests against a stop 111 which can be pivoted by the piston-cylinder arrangement 112. The measurement itself is carried out by means of an optical measuring head 113, which outputs the measurement result in the form of electrical signals which are sent to a control device, not shown, e.g. be fed to a process computer. In the event that the ascertained measured values go against the limits of a predetermined tolerance field, this gives corresponding control commands to the stepping motors 86 of the slides 81 in order to adjust them accordingly. This enables compliance with very tight tolerances.

After measuring the rotating body 9 ^V , the stop 111 is pivoted by the cylinder-piston arrangement 112 and the cylinder-piston arrangement 110 pushes the already measured rotating body forward to the opening 114, through which it slides outwards via the groove 115. FIG. 7 shows the end regions of the plungers 14 and 14 'on an enlarged scale, these end regions being rotatable about the longitudinal axis of the plungers. An insert 116 is screwed into the end face of the plunger 14 in which a tip is held by means of a pin 119 penetrating a transverse bore 118 of the tip 117 and also penetrating the walls of the insert 116. The tip 117 is held axially displaceably in the insert 116 and acted upon by a spring 120. Since the transverse bore 118 has a larger diameter than the pin, there is a slight axial displacement of the tip 117 with respect to the insert or its sleeve. This makes it possible to compensate for small measurement deviations of the raw lines 9 and for the compensation of the length growth of the blanks during the deformation by the profile ribs 7 and 8 or 7 'and 8' of the counter pressure surface 1 or the roller 12.

A sleeve 121 is screwed onto the threaded pin 120 of the plunger 14 ', into which a slide bush 122 is inserted and secured with an insert 122. This slide bush 122 is a tip

124 rotatably held, the collar of the tip on a slide ring

125 is supported, which in turn is supported on a shoulder of the sleeve 121.

The rotatable tip 124 of the plungers 14 'and the rotatable mounting of the plungers 14 in their guide heads 71 ensure that friction is avoided between the plungers 14, 14' and the blanks 9 held between them .

The driver device _^ is explained in more detail with reference to FIGS. 8, 9 and 10.

The rotating bodies 47 and 56 are provided in sections with tangentially extending, radially projecting dovetail guides 126. Two sliding blocks 127 are slidably disposed on each of the sections of the dovetail guides. The plungers 14 and 14 'run between the approaches of the rotating bodies, whereas the support rollers 128 are rotatably mounted in the bores 129 of the sliding blocks 127. The sliding blocks 127 held in different rotating bodies 47 and 56 are connected to one another via the pressure bodies 130, which are screwed to the sliding rails 127. The pressure bodies 130 are each controlled by a camshaft 131, the axial cylindrical lugs 132 of which pass through the bores 133 arranged in the radially projecting lugs of the rotating bodies 47 and 56 or are rotatably held therein. The upper cylindrical lugs 132 are each clamped in a control lever 134 in a rotationally fixed manner, the lugs 132 engaging in the bores 135 which delimit a slot 136. These control levers 134 slide along the fixed link 92 when the two rotating bodies 47, 56 are rotated.

This backdrop 92 essentially describes a circular arc over the arc region _/ over which the counter pressure surface 1 extends. In the area of the feed and discharge area for the blanks 9 or the finished rotary bodies 9, the link 92 has a recess 137 which enables the control levers to pivot.

The support rollers 128 have an area provided with a rim which comes into contact with the blanks 9 and drives them. The support rollers are driven by the gear wheels 138, which are connected to the support rollers in a rotationally fixed manner. These gears 138 mesh with intermediate gears 139, which are each rotatably supported by a gear 138 in a holder 140, the intermediate gears 139 meshing with the ring gear 58 connected to the roller 12 carrying the profile ribs 7 ', 8' Speed difference between the ring gear 58 and the holders 140 which move due to the movement-locking connection to the rotating bodies 47 and 56, which is provided by the support shafts 128, for rolling the intermediate wheels 139 and thus for driving the support shafts. -

The brackets 140 that belong together are, as can be seen from FIGS. 9 and 10, connected to one another by a bolt 141, the two brackets 140 being clamped together by two springs 142.

As long as the control lever 134 on the arcuate portion of the Link 92 ent-fitoggleiteu, these are deflected and the camshafts 131, which are rotatably connected to them, press the pressure body 130 and the support shafts 128 held with them in the sliding blocks 127 against the tappets 14, 14 'and thus ge ¬ against the blanks 9 to be deformed. The holders 140 are also forced apart against the force of the springs 142. If one of the control levers 134 slides into the recess in the link, it can deflect and the springs 142 can push the support shafts 128 away from the tappets, which also causes the control lever 134 to pivot, which is caused by the springs 142 in Contact with the backdrop 92 is kept.

As can be seen from FIG. 10, the intermediate wheels 139 rotate in two different horizontal planes and are rotatably fastened on axle stubs held in the respective holder 140 on one side. The translation of the gears 58, 139, 138 and the support shaft 128 or their diameter in the bordered area are matched to one another such that the peripheral speed of the bordered area of the support shafts 128 and thus also that of the blanks 9 lying against them, equal to the peripheral speed of the jacket which is the roller 12 carrying the profile ribs. The blanks 9 are set in motion simply by rolling on the stationary counter-pressure surface 1 and the jacket of the roller 12, as is indicated by the arrows in FIG. 10, but it can last! the deformation of the blank also cause the blank to slide on these surfaces. This is prevented by the additional drive of the blanks by the support shafts, wherein, as can be seen from FIG. 10, each blank 9 is always supported and driven between the support shafts 128 held in adjacent pairs of holders 140.

As is apparent from Figure 8 ^* * ^*, 130 have the pressure body a the supporting shafts 128 facing groove, which are in in the axial Rich¬ extends tung and held in the roller bodies 144, which project beyond the outer over the edges of the groove 145th The friction between the support shafts and the pressure bodies 130 is thus largely avoided.

When the control levers 134 pass from the circular region of the link 92 into its recess 137, an additional one occurs Movement of the intermediate wheels 139 with respect to the ring gear 58 due to the approach of the two holders 140 connected to the bolt 141, which is caused by the springs 142. Although this additional movement leads to a change in the speed of the support shafts, this is irrelevant since the support shafts 128 move away from the blank 9.

The control grooves 52, 70, which determine the path of the blanks 9, run in the area covered by the counterpressure surface 1 in accordance with line 15 in FIG. 1A or parallel to this. Outside of this area, the course of the control grooves has opposing bulges, the circumferential control grooves 52, 70 moving farther apart and approaching each other again, so that there is no clamping of the blanks 9 or of the rotary bodies 9 in this area Area comes and the blanks can be fed and the finished rotary body can be removed.

Of course, the control grooves 52, 70 in the area which is the same as the counter pressure surface 1 can have a course which deviates from the line 15 in FIG. 1A and, for example, run parallel to the line 16 or 17 in FIG. This depends on the shape of herzu¬ sstteelllleennddeenn RRoottaattiioonnss body 9 ^V and the formation of the profile ribs 7.8;! 7 ', 8' from.

In the illustrated embodiment, the counter pressure surface has a curvature corresponding to the roller 12. However, this is by no means absolutely necessary. Thus, a flat counter pressure surface can also be provided, over which the roller moves, it being immaterial whether the counter pressure surface is moved relative to the axis of the roller or whether it is moved parallel to the counter pressure surface.

Claims

1. Process for the production of rotary bodies which have different diameters over their length, in which, when the blanks are rotated, a pressure which exceeds the inlet limit of the blank material is exerted locally and, as a result, circumferential grooves, threads or gradations of the diameter are pressed in, characterized in that the blank is machined between two crossing pressure zones, the pressure zones being moved relative to one another and the blank depending on the line resulting from the crossing points during the relative movement of the pressure zones and the or the change in diameter (s) to be produced is moved.

2. The method according to claim 1 for the production of Rotationskör¬ cores with circumferential grooves, characterized in that the blanks are moved substantially parallel to the course of the crossing points resulting from the relative movement of the pressure zones of the pressure zones.

3. The method according to claim 1 for the production of Rotations¬ bodies with spiral grooves, characterized gekenn¬ characterized in that the blanks in an angle corresponding to the pitch of the spiral groove to be produced to the geometric location of the crossing points of the pressure zones during their relative movement corresponding line are moved, a thread having the outside diameter of the desired thread preferably being used for producing threads.

4. The method according to claim 1 for the production of Rotations¬ bodies with at least two sections with differing diameters, characterized in that the intersecting pressure zones are at least partially narrower than the section to be produced, which has a smaller diameter, and the section to be produced and Blanks inclined towards the the geometrical location of the crossing points of the pressure zones during their Relative movement corresponding line are moved.

5. Device for carrying out the method according to one of claims 1 to 4, which has a roller and a co-operating with this counter pressure surface, which are movable relative to each other and in which at least one raised profile rib is arranged on the roller and the counter pressure surface are characterized in that the Profilrip¬ pen (7,8,7 ', 8') are arranged crossing each other and a guide for the blanks (9) is provided, the course of which on the crossing points of the profile ribs during rotation of the Roller (12) specific line is related.

6. Device according to claim 5 for the production of Rotations¬ bodies with circumferential grooves according to the method according to An¬ claim 2, characterized in that the guide substantially parallel to the through the crossing points of the profile ribs (7,8,7 ', 8 ') runs during the rotation of the roller (12), the counter surface (1) preferably being divided into segments (2, 3, 4, 5, 6) which can be displaced radially to the roller (12).

7. Device according to claim 5 for the production of Rotations¬ bodies with spiral grooves according to the method according to claim An¬ 3, characterized in that the guide in one of the slope of the groove to be manufactured angle corresponding to the through the crossing points of the profile ribs (7th , 8,7 ', 8') runs during the rotation of the roller (12) certain line.

8. Device according to claim 5 for the production of Rotations¬ bodies with at least two sections with different diameters, according to the method according to claim 4, da¬ characterized in that the guide against by the crossing points of the profile ribs (7,8,7 ', 8') during the rotation of the roller (12) certain line extends inclined, the difference due to the inclination of the mutual distance of this line from the guide over a distance corresponding to one revolution of the blank is smaller than the width of the profile ribs (7, 8, 7 ', 8') and the difference in the distances of the guide from the line determined by the crossing points in the feed area for the blanks (9) and a removal area for the finished rotary body ( 9 ^V ) corresponds to the length of the section with the smaller diameter of the rotating body (9 ^V ).

9. Device according to one of claims 5 to 8, characterized gekennzeiGh- ^' that the ^' segments (2,3,4,5,6) on the counter surface (1) radially to the central roller (12) slidably guided slide (81) are arranged, which vorzugs¬ by means of a steering drive (85,86) ^{"independently} of each other are movable.

10. Device according to one of claims 5 to 9, characterized in that each of the intersecting Profilrip¬ pen (7,8 ', 7', 8 ') of the central roller (12) and the counter surface (1st ) runs obliquely inclined against the axis of the central roller (12). .

11. Process .. for the production of rotating bodies with different diameters at their two ends or axial sections with different diameters, in which, when the blank is rotated about its longitudinal axis, a pressure locally exceeding the yield point of the material of the blank is used to reduce the diameter of the blank is exercised, characterized in that a pressure zone having a smaller dimension in the longitudinal direction of the blank compared to the axial extent of the area with a reduced diameter of the rotary body to be produced is moved in the axial direction of the blank during rotation thereof.

12. Device for carrying out the method according to claim 11, which has a roller which interacts with a counter-pressure surface and is movable relative thereto, wherein a raised profile rib is arranged on the V / alze and / or the counter-pressure surface, characterized in that that the profile rib (s) (7,7 ') one with respect to the axial -26- of the area with a reduced diameter of the rotary body (9 ^V ) to be produced has a smaller width and for the blanks (9) a guide inclined with respect to the profile ribs (7, 7 ') is provided.

13. A device for performing the method according to claim 12, which has a roller which cooperates with a counter-pressure surface and is movable relative to this, wherein a raised profile rib is arranged on the roller and / or the counter-pressure surface, characterized in that the the central roller (12) arranged (n) rib (s) (7 ') and on the preferably divided into several radially adjustable to the roller (12) segments (2,3,4,5,6) counter pressure surface (1) arranged (n) profile rib (s) (7) inclined against the axis of rotation of the roller (12) and cross each other in the course of the mutual relative movement and a guide for the blanks (9) is provided which is opposite to that of each other Corresponding edges of the profile ribs (7, 7 ') run at a certain line when the roller (12) crosses the crossing points, the difference due to the inclination of the mutual distance of this line from the guide over a distance corresponding to one revolution of the blank is smaller than the width of the profile rib (7,7 ', 8,8') and the difference in the distances of the guide from the line determined by the crossing points in the feed area for the blanks (9) and one The removal area for the finished rotary body (9) corresponds to the length of the section with a smaller diameter of the rotary body (9 ^V ). 14. Device according to one of claims 5 to 10, 12, 13, characterized in that the guide is formed by an entrainment device which at least one, but preferably two, spaced apart from one another in the axial direction of the central roller (12) Rotary body (37,47; 62,69) has, in which or which plunger (14,14 ') are held displaceably in the longitudinal direction thereof or the like by means of a sliding block. engage in a circumferential control groove (52, 70) arranged in a stationary part of the device, wherein guided in two different rotating bodies (34, 47; 62, 69) Tappets (14, 14 ') are aligned axially to one another and essentially parallel to the axis of rotation of the roller (12) and the blanks by at least one tappet (14, 14'), but preferably between two tappets (14,

14 ') can be clamped.

15. Device according to claim 14, characterized in that at least the mutually facing end regions of the plunger (14, 14 ') are rotatably held about the longitudinal axis of the plunger (14, 14'), preferably the end regions of the one plunger (14 ) are spring-loaded against the coaxially aligned plunger (14 ').

16. Device according to claim 14, characterized in that a gear rim (58) connected in a rotationally fixed manner to the central roller (12) is provided for the driving device, in which support shafts (128) arranged parallel to the plungers (14, 14 ') are provided ^ Gear drive (139, 138) connected in the drive connection, the support shafts (128) being held in the rotating bodies guiding the tappets or rotating bodies (47, 56) connected to them in a rotationally fixed manner.

17. The device according to claim 14, characterized in that the utenteutenuten (52,70) with the exception of a feed and Ent¬ removal area for the blanks (9) or the Rotationskör¬ per (9) run substantially parallel to each other.