Note: Descriptions are shown in the official language in which they were submitted.
~X64~;~37
The present invention is concerned with
the production of ro-tation bodies.
More particularly, the invention relates
to -the production of rotation bodies having differer.t
S diameters along the leng-th thereof, as well as bodies
of revolution having at least one groove or the like
which extends substantially in the peripheral
direction thereof and whose width, extending in the
axial direction of the body of revolution, decreases
towards the floor of the groove, wherein, during
rotation of a blank about its longitudinal axis, a
pressure which exceeds the yield point of the
material of the blank is locally applied
The previously known methods of that kind
provided for impressing a shaped rib into the blank
as it rotated, the width of the rib, as considered in
the direction of forward feed motion, increasing from
a minimum value to a maximum value and the height
thereof also increasing. In other words, in order to
produce for example a V-shaped groove, the previous
method involved using a shaped rib which was
impressed with its tip leading into the rotating
blank, the rib increasing in width and height in the
course of the orward feed motion.
The disadvantage of such a method o~
manufacture is that the fact that the tip of the
shaped rib was impressed into the material cause the
material to undergo hardening, and the hardened
region had to be further deformed, so that corres-
pondingly high pressures are required and overloading
of the material and thus cracking thereof may very
easily occur.
The aim of the invention is to avoid such
disadvantages and to propose a method of the kind set
forth in the opening part of this specification,
which avoids further deformation of regions of the
workpiece which have already been severely deformedO
,~
S~7
According to the invention, that is
achieved in that the width of action of the
pressure is reduced from a width corresponding
- la -
~ 4~ 7
to the width of the grsove to be prcduced at the p~ripheral surface
of the blank, to the width of the floor of the groove to be
produced, in accordan oe with the progressing depth of i~pression,
wherein the reducti~n in the width of impression, with progressing
depth of impression, is effected in accordance with the inclination
of the walls of the groove.
That provides that it is only ever the regions which have
been less deformed, that are subjected to further deformation, and
extreme levels of hardening and consolidation of the material are
avoided. In addition, deformation of the blanks in that way
requires a smaller amount of energy. When producing screwthreads
by means of the methcd according to the invention, in accordance
with a further feature of the invention, it may be provided that
the screwthread groove is impressed into a blank which is of the
outside diameter of the desired screwthread. m e material which is
pr-essed out of the screwthread grcove in that operation is displaced
in the axial direction so that the finished screwthreaded pin or
bolt is greater in length than the blank used for that purpose.
In relation to screwthreads, in particular trapezoidal
screwthreads or the like, there is the advantage, when using blanks
which axe of the outside diameter, that the material does not
have to flGw up the flanks of the screwthread in ordex completely
to build up the screwthread flights or ribs, which in certain
circumstances can result in overloading of the material and cracking
at the peripheral surface of the screwthread flights, but the
material can ~nly flow axially, thereby ensurin~ that the screw-
thread flights consist of solid material and cannot have any
cracks or cavities which are covered by material which is
displa oe d in an outward direction.
30Another aim of the invention is to provide an apparatus for
carrying o~t the method according to the invention.
' ~LZ~
In an apparatus comprising at least one roller which co-operates
with a ~o-operating pressure surfa oe and which is movable relative
thereto, it is therefore proposed, in accordance with the
invention, that the width of the sh~ped rib or ribs decreases
in the direction of the relative movement between the roller and
the co-operating pressure surface, and ~he height thereof increases.
That ensures that, when producing a peripheral groove or the like,
the blank is first acted up~n, with the n2uui~um width of the
gro~ve to be produced, w~ile the width of impression progressively
decreases and he depth of impression increases in the course of
production.
Another possible configuration of an apparatus for carrying out
the method according to the invention provides that, in an apparatus
comprising two rollers which can he driven in mutually opposite
directions of rotation and of which at least one is provided with
a raised shaped rib and between which ~here is a roll gap, in
accordance with another feature of the invention the rib is
of decreasing width and increasing height in the direction of
rotation of the roller. Such an apparatus also ensures that the
pressure firstly acts on the blank with the greatest width of the
groove to be produced, and the widtJh of action decreases as the
groove is impressed in the blank. In accordan oe with a further
feature of the invention, it may be prc~ided that shaped ribs are
disposed both on a drivable central roller and on the co-operating
surfa oe which is subdivided into segments, which ribs cross each
other in the oourse of the ~utual relative movement.
m ose features mQke it possible for the counterpressure surface
to be advanced to a greater or lesser degree towards the central
roller, as required, without thereby giving rise to a roll or
operative gap which varies over its arcuate length~ Ihat is due to
45~)7
the fact that the mutually crossing ribs only ~o-operate along the
generatrl oe s of the oe ntral roller and the counterpressure surface,
which pass through the point of intersection of the ribs, and thus
apply the necessary pressure to the blank.
In that oonnection, it is advantageous for the segments of the
ccunterpressure surface to be arranged on carriages which are
guuded displaceably radially with respect to the central roller and
which are mKvable preferably independently of each other by means
of a control drive. In that ~ay, it is possible to take account of
wear of the ribs but also differences both in the dimensi~ns of
the blank and also in the properties of the material thereof.
It may also be provided that the control drive o~ the carriages
is oonnected to a ~easuring means fcr measuring the articles when
in the finally deformed condition and displa oe s the carriages
in dependence on the detected measurement data, thereby providing
for automatic ad~ustment of the counterpressure surface. Thus,
it may be provided that random samples of the articles produced
are taken from the stream leaving the apparatus, measured in the
measuring means and compared to a predetermined tolerance range
~0 and the carriages carrying the counterpressure surface are adjusted
such that the produced articles lie in the middle of the tolerance
range.
It is fully possible for one of the mutually crossing ribs to
be disposed perpendicularly to the axis of the oe ntral roller,
but in that case the central roller and the counterpressure surfa oe ,
besides the relative rotaxy movement, must also perfor~ a relative
movement having a oomponent in the axial direction of the roller.
In order to avoid that additional movement which, in that
case, can be controlled in any desired manner, and in order thereby
to permit the apparatus to be simpler in construction, it may be
provided, in acoordance ~ith a further feature of the invention, that
~LZ64S~7
each of the mutually crossinq ri~s of the central roller and the
co-operating surface extend at an inclined angle with respect to the
axis of the central rDller. That arrangement ensures that the
ribs constantly intersect each other during the rota~y MOVement
of the central roller, if we disregard an intake and discharge
region of the apparatus, for the feed of blanks and the discharge
of finished articles, which region is kept free of ribs.
In order to ensure precise entrainment and guidan oe of the
blanks during processing thereof between the central roller and the
caunterpressure surface, a further feature of the invention may
provide that the central roller is drivingly connected by way of
transmission means to an entrainment means for the blank, which
entrainment means has at least one but preferably two rotary
members which are spaced from each other in the axial direction cf
the central roller and in which push rods or thrust members are
held displaceably in the longitudinal direction thereof and
engage by n~ans of a sliding memker or the like in a peripheral
control groove which is disposed in a stationary part of the
apparatus, wherein the thrust members which are guided in two
different rotary memkers are axially aligned with each other. Those
features provide that ~he blanks are clamped and thus entrained between
the thrust m~aer and a cam , but better between a respective
pair of mutually axially aligned thrust members. In that arrangement,
it may further be provided that the control groove, with the
exception of a feed and discharge region for the blanks and the
finished bodies of revolution respectively, extends substantially
parallel to the path of the points of intersection of the ribs of the
central roller and the counterpressure surface during the rotary
movement of the roller, wherein the c~ntrol grooves which are
30 associated with the thrust m~mbers guided in both rotary members
5~)7
extend parallel to each other in that region, thereky ensuring a
precise guidance action for the blanks and easy feed of the blanks
and removal of the finished bodies of revolution.
When producing ~odies of revolution with peripheral grooves,
additional compacting or cGnsolidation in the region of the walls
of the qroove may be desired in some cases. In such a situation, the
control gro w e may be inclined with respect to the imaginary line
~hich is formed from the path of the points of intersection of the
ribs of the central roller and the counterpressure surface. By virtue
of that arrangement, the ribs press not only radially against the
blank kNt also axially against the walls of the groDve which are
being formed.
A preferred embodiment of an apparatus aco~rding to the invention
further provides that at least the mutually facin~ end
regions of the thrust memkers are rranged to be rotatable about
the longitudinal axis of the thrust members, wherein preferably
the end regions of the one thrust mem~ers are spring-loaded relative
to the ccaxially aligned thrust members. That avoids friction
between the end faces of the blanks and the thrust members. Ey
virtue of the end regions of the one thrust members being resiliently
suppDrted, that arrange~ent eliminates excessive pressure against
the blank heing processed when the blank grGws in the axial
direction due to the groove being impressed therein. In addition,
that arrangernent also makes it possible to oompensate for dimensional
variations in the blanks. The end regions of the thrust members
may be formed by inserts.
In accordance with a further feature of the invention, it may
also be pro~ided that provided for the entrainment means is a ring g~r or
spur gear which is non-rotatably connected to the c~ntral roll~
and into whic~ engage gear transmissions drivingly conn~cted to
5~)7
support shafts disposed parallel to the thrust
members, wherein the support shafts are held in
the pressure members guiding the thrust members, or
rotary member which are non-rotatably connected thereto.
Those features provide that the blanks are
driven during the operation of processing same, while,
by virtue of suitable matching of the gear transmissions,
the peripheral speeds of the central roller and the blanks
can be matched to each other.
Another purpose of the invention is to propose
a method which is universally suitable for the production
of differently shaped rotating bodies and in which the
gradual use of pressure is possible.
According to the invention, this purpose is
achieved in that two intersecting pressure zones are
processed, the said pressure zones being moved in re-
lation to each other and the blank being moved as a function
of the line passing through the point of intersection
during rela-tive movement of the pressure zones and of
the changes in diameter to be produced.
As a result of the relative movement on the
intersecting pressure zones and guidance of the blank,
it is possible to produce therefrom rotating bodies of
any desired configùration, and the period during which
the pressure zones act upon the blank may also be ex-
tended.
In the case of rotating bodies with peripheral
grooves, it may be desirable for the blanks to be
moved substantially in parallel with the pattern of the
intersections of pressure zones arising during the re-
lative movement thereof.
On the other hand, in producing rotating bodies
having spiral grooves, for example threads, provision
may be made for the blank to move at an angle,
corresponding to the pitch angle of the spiral groove
to be produced, to the line corresponding to the geometrical
location of the intersection of the pressure zones during
~;~6~50~
--;L~
their relative movement, a blank having the outside
diameter of the desired thread being used to produce
the thread.
In the case of threads, especially trapezoidal
threads or the like, the advantage of using blanks having
the outside diameter of the thread is that
material need not flow down the flanks of the threads
in order -to build up the thread ribs completely which,
under certain circumstances may lead to over stressing
of the material and to the formation of cracks in the
outer surfaces of the thread ribs; instead, the material
can flow only axially, thus ensuring that the said
thread ribs are made of solid material and cannot contain
cavities or cracks covered by material expelled outwardly.
On the other hand, in order to produce rotating
bodies having at least two sections of different diameters,
it is desirable for the intersecting pressure zones
to be at least sectionally narrower than the section
of the rotating body to be produced and having a smaller
diameter; moreover the blank is moved at an angle to
the line corresponding to the geometrical location of
the points of intersection of the pressure zones during
the relative movement thereof.
Another purpose of the invention is to propose
an apparatus for the implementation of the method.
In the case of an apparatus comprising a roller, and
a counter pressure surface cooperating therewith, which
are adapted to move in relation to each other, and in
which at least one raised profiled rib is arranged on
the said roller and on the said counter pressure surface,
it is therefore proposed, according to another
characteristic of the invention, that the profiled ribs
be arranged to intersect each other, and that a guide
for the blank be provided, the course of which is re-
lated to the line determined by the points of inter-
section of the ribs during rotation of the roller. This
45~7
is a simple way of ensuring intersecting pressure æones,
it being possible to select the course of the guide for
the blank, depending upon the rotating body to be pro-
duced, in relation to the course of the points of
intersection of the profiled ribs arising during rota-tion
of the roller.
For the production of rotating bodies with
peripheral grooves, provision may be made for the guide
to run substantially parallel with the line deter-
mined by the points of intersection of the profiled ribs
during rotation of the roller, the counter pressure
surface being preferably divided into segments displaceable
radially of the roller. This ensures that, throughout
the entire process, the profiled ribs always act sub-
stantially in the same axial position upon the blank.
Minor deviations in parallelism between the guide and
the points of intersection of the profiled ribs arising
during rotation of the roller, may be provided in
order to make allowance for the increase in the length
of the blank being processed caused by the incorporation
of a groove or by sectional reduction of the diameter,
or in order to strengthen the walls of the ribs.
In the case of a counter pressure surface
divided into segments, it is also possible, based upon
intersecting profiled ribs, to locate the said counter
pressure surface closer to or farther away from the
roller. This is possible because intersecting profiled
ribs can contact each other in extreme cases only along
a surface line. In the case of known devices having
parallel profiled ribs, however, this is not possible
since, in the event of a change in the radial position
of the counter pressure surface, a gap, varying over
the length of the arc, would be produced between the
cooperating surfaces of the profiled ribs.
On the other hand, in producing rotating bodies
having spiral grooves, it is desirable for the guide
to run at an angle, corresponding to the pitch of the
groove to be produced, to the line determined by the
"
X6~507
fo
points of intersection of the profiled ribs during
rotation of the roller. By means of the angle, corres-
ponding to the pitch of the thread to be produced, between
the course of the guide and the line arising during ro-
tation of the roller and determined by the points of
intersection of the profiled ribs, it is possible to
form the thread in a very simple manner with profiled
ribs corresponding to only one thread rib. In this
connection it is, of course, necessary to make allowance
for the increase in length of the blank caused by
impression of the groove, if a blank having the outside
diameter of the thread to be produced.
In producing rotating bodies having sections
comprising at least two sections of different diameter,
provision may be made for the guide to run at an angle
to the line determined by the points on intersection
of the profiled ribs during rotation of the roller,
the difference, caused by this angle, in the distance
between this line and the guide, along a path corres-
ponding to one revolution of the blank, being less
than the width of the profiled rib, and the difference
in distance between the line determined by the points
of intersection in the feed area for the blank and
a removal area for the finished rotating body corres-
ponding to the length of the smaller diameter section
of the rotating body. This ensures that not only
a pressure in the radial direction is applied to the
blank during processing, but also a pressure in the
axial direction, thus assisting the material to flow.
The intersecting profiled ribs make it possible
also to produce bodies having a pointed or stream-
lined end area. It is merely necessary to design
the profiled ribs accordingly, the said ribs coming
into contact with each other as -they rotate.
Moreover, according to a preferred example
of embodiment of the invention, the segments of the
counter pressure surface may be arranged in carriages
~2~5~17
ff
displaceable radially in relation to the central roller,
the said carriages being adapted to move, preferably
independently of each other, by means of a control
drive. This provides a simple way of compensating
S for differences in blanks as regards their dimensions,
hardness and strength. Provision may also be made
to feed to the control drive signals from an automatic
measuring device which checks the finished rotating
bodies at random and measures them. This makes it
possible to adjust the counter pres.sure surface in
such a manner that the finished rotating body is within
the central region of the tolerance range provided.
Accordin~ to another characteristic of the
invention, each of the intersecting profiled ribs
on the central roller and the counter pressure surface
may run at an angle to the axis of the central roller.
It is quite possible to arrange one of the inter-
secting profiled ribs at right angles to the axis
of the central roller and to cause the counter pres-
sure surface to carry out a relative movement in addition
to the relative rotary motion, the said relative motion
comprising a component running axially of the roller.
This additional movement is unnecessary if the profiled
ribs on the roller and on the counter pressure surface
are at an angle to the axis of rotation of the roller.
The invention also relates to an improved
method for producing rotating bodies having at each
end different diameters or axial sections with different
diameters in which, when the blank is rotated about
its axis, a pressure exceeding the yield point of
the material of the blank is applied locally in order
to reduce the diameter thereof. The invention also
relates to an appara~us for the implementation of
the said method.
In the case of existing known methods of
this kind, a profiled rib arranged upon a roller was
pressed into a blank supported by a counter pressure
roller rotating in the opposite direction, the said
507
profiled roller being at least as wide as the length
of the section of the section of the blank whose
diame-ter is to be reduced. In practice, this
s1gnified that pressure is applied simul-taneously to
the whole area whose diameter is to be reduced.
The disadvantage of this, however, is that
very large forces and a large amount of power are
required. Furthermore, with this known method it is
very difficult to start the material flowing.
According to a further aspect of the
invention, there is thus provided a method of
producing a rotation body having different diameters
along the length thereof, which comprises the steps
of
a) rotating a blank about the longitudinal
axis thereof and working the rotating blank between
two pressure zones to apply thereto a local pressure
exceeding the flow limit of the- blank material
whereby circularly extending impressions of different
diameters are worked into the blank, the pressure
zones crossing each other,
b) displacing the pressure zones relative
to each other while applying the local pressure, one
of the pressure zones being displaced in a direction
at an angle to its longitudinal extension and to the
longitudinal direction of the pressure zone it
crosses and the points of crossing of the crossing
pressure zones forming a geometric line at an angle
with the longitudinal axis of the blank to be worked,
and
c) displacing the blank in dependence on
the geometric line and on the different diameters to
be produced.
The present invention also provides, in
another aspect thereof, an apparatus for producing a
rotation body having different diameters along thc
length thereof from a rotating blank, which
comprises:
- 12 -
126~5C)7
a) a roll having at least one radially
pro~ecting profiled rib,
b) a counteracting pressure surface
cooperating with the roll and remaining in a constant
position relative to the roll in an axial direction,
the pressure surface having at least one radially
projecting profiled rib crossing the rib on the roll,
c) means for rotating the roll abo~t the
longitudinal axis thereof relative to the counteract-
ing pressure surface whereby the displacement motion
between the roll and the counteracting pressure
surface has a component extending circumferentially
about the roll and the points of crossing of the
crossing ribs form a geometric line at an angle with
the longitudinal axis, and
d) guide means for displacing the blank
relative to the geometric line in the axial direction
in dependence on the differen-t diame-ters to be
produced while the blank is rotated and subjected to
pressure exceeding the flow limit of the blank
material between the roll and the pressure surface.
According to still a further aspect of the
invention, there is provided an apparatus for
producing a rotation body having different diameters
along the axial length thereof from a rota-ting blank,
which comprises:
a) a roll having a longitudinal axis,
b) a counteracting pressure surface
cooperating with the roll, the pressure surface and
the roll having a radially projecting profiled rib,
the profiled ribs being inclined with respect to the
longitudinal axis of the roll and crossing each
other,
c) means for ratating the roll about the
longitudinal axis thereof and applying to the
rotating blank between the roll and the pressure
surface a local pressure exceeding the flow limit of
the blank material to reduce the diameter of the
- 13 -
5~7
blank along an axial sec-tion thereof by displacing,
each rib in a dlrection parallel to the longitudinal
axis, each rib having a smaller dimension in the
axial direction of the blank tildrl the reduced
diameter blank section whereby the displacement
motion between the roll and counteracting pressure
surface has a componen-t extending circumferentially
about the roll and the points of crossing of the
crossing ribs form a geometric line, and
d) guide means for displacing the blank
inclined with respect to the geometric line.
- 13a -
~Z~507
In producing ro-tating bodies with peripheral
grooves, additional compacting in the vicinity of
the walls of the grooves may be required in many cases.
In such a case, the control groove may be at an angle
to -the imaginary line arising from the course of the
points of intersection of the profiled ribs on the
central roller and the counter pressure surface. In
this case the profiled applied pressure to the blank
not only radially, but also axially to the incipient
walls of the grooves.
In this connection, and according to another
characteristic of the invention, provision may be
made for the profiled rib(s) on the central roller,
and those arranged on the counter pressure surface,
preferably divided into a plurality of segments ad-
justable radially in relation to the roller, to run
at an angle to the axis of rotation of the roller,
and to intersect in the course of their mutual re-
lative motion, a guide being provided for the blank,
the said guide running at an angle to the line deter-
mined by the points of intersection, arising during
rotation of the roller, of the edges, corresponding
to each of the profiled ribs, the difference, caused
by this angle, in the distance between this line and
the guide, along a path corresponding to one revolution
of the blank, being less than the width of the profiled
rib and the difference in the distance between the
guide and the line determined by the points of inter-
section in the feed area for the blank and the removal
area for the finished rotating body corresponding
to the length of the smaller diameter section of the
rotating body. This ensures that, as compared with
the grooves or sections to be produced, the narrow
profiled ribs with reduced diameter are ~oved axially
over the blank, although this does not result in the
forming of spiral grooves. This axial movement, how-
ever, causes a pressure to be applied through the
12~45~7
flanks of the profiled ribs, in the axial direction,
to the walls of the groove to be produced, or to the
shoulder of the section, with reduced diameter, to
be produced, and this leads to compacting of the ma-
terial in this area.
The invention will now be described in greater
detail with reference to the drawings in which:
Figures lA and lB diagrammatically show
tools for carrying out the method according to the
invention and deformation of a blank using such tools,
Figure 2 shows the development of the shaped
ribs of the tools shown in Figures lA and lB,
Figure 3 is a view in vertical section of
an embodiment of an apparatus for carrying out the
method according to the invention,
Figure 4 is a plan view of the apparatus
shown in Figure 3,
Figure 5 is a detail of the apparatus shown
in Figures 3 and 4 on a larger scale,
Figure 6 is a detail of the thrust member
guide arrangement of the apparatus shown in Figures
3 and 4, on an enlarged scale,
Figure 7 shows a further detail of the thrust
members,
Fi.gure 8 is an exploded view of the entrainment
means of the apparatus shown in Figures 3 and 4,
Figure 9 is a front view of the entrainment
means, and
Figure 10 is a plan view of the entrainment
means.
Figure lA is a diagrammatic view of the
shaped ribs 7 and 8 which are disposed on the counter-
pressure surface 1 which is subdivided into five seg-
ements 2, 3, 4, 5 and 6. The rib 7 serves to form
the step or shoulder 10 of the finished article 9v
produced from the blank 9. On the other hand, the
rib 8 serves to form out the groove
4~5~7
~p
11 of the finished article and has its maximum width
and minimum height at the beginning of the counter
pressure surface or at the boundary of the intake
region for the blanks 9 which are to be handled. Along
its path from the beginning of the rib 8 to the end
thereof at the edge of the segment 6 which, as will
be described hereinafter, is the trailing edge as
considered in the direction of rotation of a central
roller, the width of the rib 8 progressively decreases
and it terminates in a form which is equal and opposite
to the groove 11.
Profiled rib 7, which forms shoulder 10
in the finished rotating body, increases in width
and height on the way from cross-section x, at the
edge of the input area, to cross-section x5 at the
run out edge of segment 6 and the beginning of the
discharge area for the finished rotating body 9V.
The central roller 12 shown in Figure lB
runs in the space enclosed by the segments 2 to 6
of the counterpressure surface, but was not shown
jointly therewith, for the sake of enc'hanced clarity
of the drawings. The roller 12 is installed in such
a way that, in-a position of the roller 12 relative
to the segmen-ts 2 to 6 of the counter pressure sur-
Eace 1 in which the beginnings of the ribs 7' and
8' are radially aligned with the beginnings of the
ribs 7 and 8, they are also at the same height.
The cooperation between the two groups of
profiled ribs 7, 8 and 7', 8' is best seen from Fig. 2
which shows the development of profiled ribs 7, 8
on counter pressure surface 1 and of profiled ribs
7', 8' on roller 12. Profiled ribs 7, 8 ascend from
left to right, while profiled ribs 7', 8' descend
from left to right. As roller 12 rotates in the dir-
ection of arrow 13 in Figure lB, profiled ribs 7',
8' will be moved in the direction of arrow 13 in Figure
2 in relation to profiled ribs 7, 8.
~;~6~507
~ .;;i'
As may be gathered from Figures lB and 2,
the cross-sectional shapes of profiled ribs 7', 8'
varies in the same way as that of profiled ribs 7,
8, i.e. profiled xib 7' widens from cross-section
x to cross-section x5, while profiled rib 8' increases
in width, in the vicinity of its maximal elevation,
and in height.
As a result of the arrangement of the profiled
ribs on counter pressure surface 1 and roller 23 opposed
1~ to each other and at an angle to roller 12, rotation
of the said roller produces continuously points of
intersection of these ribs. These produce an imaginary
line substantially parallel with dotted line 15 which
corresponds to the geometrical location of the points
of intersection of profiled ribs 8, 8' arising when
roller 12 rotates. As may be gathered from Figure
2, blanks 9 are guided in parallel with line 15 between
two tappets 14, 1~', line 15 being at a slight angle
to profiled rib 8, in order to make allowance for
the increase in the length of the blank when the groove
is impressed therein.
Since the edge of profiled rib 7 or 7' closer
to line 15 form an angle therewith, blank 9, on its
way from cross-section x to cross-section x5, is
subjected, between roller 12 and counter pressure
surface 1, not only to a radial pressure, not only
because of the increasing height of the profiled ribs
along this path, but also to an axial pressure applied
to shoulder being formed. This pressure promotes
and facilitates, to a considerable extent, the flow
of material, especially in the axial direction. The
change in the shape of blank 9, upon reaching individual
cross-sections x to x5, is shown in Figure lA.
The change in the cross-sectional form of
rib 8 from segment to segment or from segment boundary
to segment boundary can be clearly seen from the change
in the configuration of the blank 9, to give the finished
07
/~
article. I'hus, the intermediate product 9' corresponds
to the condition of deformation of the blank 9, as
occurs at the boundary xl between the segment 2 and
the segment 3. That shows the cross-sectional form
of the ribs in that cross-section. In the same fashion,
the intermediate product 9" corresponds to the condition
of deformation of the blank in the cross-section x2,
the intermediate product 9''' corresponds to the con-
dition of deformation of the blank at the cross-section
x3 and the intermediate product giV corresponds to
the condition of deformation at the cross-section
x4. In the cross-section x5, the blank is formed
to give the finished body of revolution 9V,
It will be clearly seen from the form of the intenmediate products
9~, 9,,, 9" " giv~ gv, that ths rib 8 and the rik~ 8' ~Figure
lb), fxom their begLnning, decrease in respect of their width
at their location of yreatest height, in their respective cross-
S secti~n, whereas the ribs 7 and 7' increase in width.
It will also be seen fro~ Figure.LA that during processing theblanks 9 are held between two thrust members or pushrods 14 and
14' which separate fro~ each other in the intake and discharge
re~ion which is between the cross-sections 5x and x, and thus
~0 enable the blanks 9 t~ be intxoduced and the finished articles
to be rem~ved, such operations occurrin~ in different planes.
~ igure lB diagrammatically shows the central roller 12 which.
oo-operates with the counterpressure surface 1. The roller 12 is
proYided with two shaped ribs 7' and 8' which correspond to the
ribs 7 and 8 but which are inclined in the opposite direction
_ to the ribs 7 and 8 so that when the central roller 12 is
fitted between the segments 2 to 6, the ribs 7, 7' and 8, 8'
respectively cross each other when the central roller 12
rotates in the direction indicated by the arr~w 13.
AS can be seen fron ~iyure 2 which shows a developT~nt of
the ribs 7, B, 7' and 8', the ribs 7' and ~' are m~ved past
the ribs 7 and 8 in the direction indicated by the arrow 13,
whereby the points of intersection of the ribs move incl~edly
dow~w~rdly towards the r~ght. In that arranyement, the ~lank
9 is guided bv the two thrust n~bers 14 an~ 14' substantially
along the line which corresponds to the geometrical locus of
the points of intersection o~ the ribs 8 an~ 8' during ~he
relative mov~ment of the ribs 7 and 8 with respe~t to the ribs
7' and 8'~
~he thrust m~mb~rs 14 and 14' are guided between the bour~laries .
x and x5 of the segments of the surface 1 along the imaginary b2se
... .
~26~07
lines 15 and 15' which are shown in dash-dotted fo~m
and which extend parallel to the ribs 8 and 8'. The
lines 15 and 15' are slightly inclined with respect
to the line corresponding to the geometrical locus
of the points of intersection, thereby taking account
oE the axial growth in length of the blank 9 due to
the groove 11 being impressed therein.
It will be appreciated that the blanks 9
are not guided along two different paths, but the
dash-dotted lines 15 only indicate the path of the
blanks with respect to the ribs 7, 8 and 7' and 8'
respectively. In practice, as will be described in
greater detail hereinafter, the blanks are in principle
controlled by a groove which is provided in a stationary
part of the machine and the configuration of which
substantially corresponds to that of the rib 8.
With the above-described arrangement, as
considered from the central roller 12, the path of
movement of the blanks is parallel to the rib 8'.
As may be gathered from Figures lA to 2,
especially from Figure 2, with profiled ribs of the
same design it is possible, merely by altering the
angle, at which the blank is guided during processing,
to the line produced during rotation of -the roller
and determined by the points of intersection of the
profiled ribs, to change the shaping of the blank.
Thus profiled ribs 8, 8' with a guide inclined according
to them, e.g. corresponding to dotted line 17 in Figure
2, could also be used to produce a spiral groove,
and the angle between profiled ribs 8, 8' and the
path of the blank would determine the pitch of such
a spiral groove. The only requirement would be that
profiled ribs 8, 8' be narrower than the lead of the
groove on the rotating body to be produced. If this
is not so, arranging the guide at an angle to profiled
rib 7', 8' will produce a peripheral groove, the width
thereof exceeding that of profiled rib 8, 8'. The
pressure applied axially to the blank by profiled
, .
~;~6~SO~
rib 8, 8' would produce cornpacting of the material
in the vicinity of one wall of the groove.
If the angle between profiled rib 8, 8'
and the path along which blank 9 is guided between
roller 12 and the counter pressure surface is large
enough, profiled rib 8, 8' may also be used to form
a section of rotating body gv having a smaller dia-
meter. This merely requires that the blanks be guided
along a path which leads upwardly in relation to pro-
filed rib 8, 8', for example along dotted line 16
shown in Figure 2.
This would cause the pressure zones determined
by profiled ribs 8, 8' to shift axially in relation
to the blank, whereas in the case of pressure zones
determined by profiled ribs 7, 7' and guidance of
the blank according to line 15 in Figure 2, only a
restriction of the pressure zones in the axial direction
in relat.ion to the blank is moved.
As can be seen from Figures lB and 2, the
cross-sectional shape of the ribs 7' and 8' also alters
in the same ashion as that of the ri.bs 7' and 8',
that is to say, the rib 8' increases in height from
its beginning to its end and decreases in width in
the region of its maximum height.
Figure 3 is a diagrammatic view of an ap-
paratus for carrying out the method according to the
invention, in vertial section, in which in particular
the mounting and bearing means and the installation
thereof are shown in simplified form. In addition,
structural groups and units which, for manufacturing
reasons and for reasons of greater ease of assembly,
consis-t of a number of parts, are shown in part as
being formed as one part.
The drive motor 20 drives a shaft 23 by
way of a clutch 21 of which one half is connected
to a flywheel 22. The shaft 23 is
5~)7
~/
supported in the housing 26 in ccnventional manner by way of the
rolling bearings 24 and 25 and is non-r~tatably connected to a
bevel gear 27 and a chain wheel 29~
m e bevel gear 2~ meshes with a further bevel gear 28 which is
non-rot.atably oDnnected to a vertically disposed main shaft 3~.
m e main shaft 30 is held by means oi ~wo tapered roller kearings
31 and 32 in a carrier cylinder 33 connected to the housing 26.
A first guide member 34 is fitted on the cylinder 33 and is
rigidly connected thereto. In addition, disposed on the cylin~er
33 is a needle bearing 35 which is axially fixed in position by
the guide member 34 and a support flange 36~ and which rotatably
mounts a rotary member 37 provided with a chain ring 38. The
rotary member 37 or the chain ring 38 thereof is connected by
way of two chains 39 to chain wheels 40 which are non-rotatably
connected to the output shaft 41 of a transmission 42. ~e
transmission 42 is driven by way of two chains 44 and chain wheels
43 by the shaft 23 or the chain wheels 29 connected thereto, and
is held in the housing 26' by way of a bracket 46.
The rotary ~ember 37 is connected by way of pins 45 to a further
rotary ~ember 47 and is mcunted to the main shaft 30 by way of a
rol1ing bearing 48. The two rotary members 37 and 47 are also
connected together by way of slotted guide sleeves 49 in which the
thrust memkers 14' or the guide heads 50 thereof are axlally
slidably guided. The guide heads 50 engage with their rotatably
mounted roller 51 into a oontrol groove in the guide n~ber 43.
The thrust memkers 14' pass through the rotary ~ r 47 and
are guided therein in bushes 53. In addition, secured to the rotary
mem~er 47 is a splash ring 54 which serves to car~y the oil
used for lubrication purposes away into an annularly disposed oil
sump (not shcwn).
5~7
,.,
m e rotary n~ er 47 is connected to a further rotary n~ber 56
by way of struts 55. Llke the rotary member 47, the rotary
member 56 is provided with tangentially extending portions of
dcvetail guides which serve to acco~cdate sliding members
which are parts of the entrainment means shown in Fiyures 8 to 10
and are descri~ed hereinafter with reference to those ~igures. For
the sake of enhanced clarity of the drawing, ~he correspondiny
reference numerals are not shown in Figure 3.
. N~n-rotatably disposed on the main shaft 30 is a chuck
body 57 on to which is fitted the roller 12 which ~ears the
ribs 7~ and 8'1 being held in position non-ro~atably
by means of a key and gro~ve connection. Screwed to the roller 12
is a ring gear or spur gear 58 from which the drive for the
entrainment means is derived, as will be described in greater detail
hereinafter with reference to Fi~ures 8 and 10.
A sleeve 59 is fitted on a stepped portion of the main shaft
30 and non-rotatably connected thereto by way of a key and groove
D tion. Mkunted on the sleeve 59 by way of a rolling bearing
60 is a rotary n~ er 62 which is screwed to an internal ring gear
61. P~s can be seen from Figure 5, the ring gear 61 meshes with
interm~diate gears 63 which in turn mesh with further gears
64 which serve only to xeverse the direction of rotation and which,
like the intermediate gears 63, are mounted rotatably in a ring
66 disposed in the in~erior of a further ~uide memker 65 which is
fixed with respec* to the housing. m e gears 64 in turn mesh
with a ring gear which is dis~osed on the sleeve 59 and which
provides for the drive for the rotary member 62 by way of the gears
63 and 64 and the ring gear 61 which supports the guide n~ er
by way of a rolling bearing 60'.
The rotary member 6~ is connected by ~ay of pins 67 and a sleeve
68 to a ring 69 in which are mounted bushes 53 in which the thrust
~6~5~7
members lg are rotatably and axially displaceably guided,
just as in the r~tary n~ er 62.
The guide member 65 is of a two-part construction and supports
the main shaft 30 by way of a rolling bearing 69'~ In addition,
the guide member 65 is provided with a oontrol groove 70 into
which engages a rotatable roll~r 51 carried in each guide head
71 of the thrust members 14, as shown on a larger scale in
Figure 6. As shown in Figure 6, the pin 72 carrying the roller 51
engages with an extension portion into a peripheral groove
73 in the thrust member 14 whereby the latter is mounted rotatably
but axially displaceably in the guide head 71.
Over the major part of the periphery of the guide member 65,
the oDntrol groove 70 extends parallel to the control groove
52 of the guide ~ember 34. It is only in the intake and discharge
regi~n which was described with reference to Figure lA that the
above-indicated parallel condition does not occur and in that
region the two control grooves move apart and ~ack towards each
other again.
~he guide member 65 can be connected ~y way of a flanged member
74 to a support arm 75 in which the main shaft 30 is supported in
a plain bearing. The support aLm 75 is supported on a carrier
pillar 76 which is fixed on the housing 26'. Disposed in the pillar
76 is a spindle 77 which is supported relative to the inside wall
surface of the pillar 76 and relative to a cylinlrical b~re 79
~5 of the support arm 75 by means of a centering ring 78 in its
upper region. The support arm 75 is clamped to the pillar 76
by means of a nut 80.
After unscrewing and removing the nut 80 and releasing the
connection between the flanged member 74 and tbe support arm 75,
the latter can be lift~d and pivoted whereby it is possible to
5(~
dism~ntle ~he apparatus, in crder for example to replace the roller
12 by another roller with ribs of a different canfiguration in order
to be able to produ oe different bodies ~f revolution.
Also arranged on the housing 26'are five carriages 81 which
carry the segments 2 to 6 of the oO-Dperating surfa oe 1. The carriages
Bl are guided in housings 82 in each of which is disposed a screw-
~hreaded spindle 84 supported in a bear m g arrangement 83 eomprisin~
thrust and radial rolling be~rings. Ihe spindle 84 is driven by
a stepping motor 86 by way of a transmision 85 and it passes
through two nuts 87 which are braced relative to each other to
o sate for play at the spindle, which in turn is connected
to the carriage or slide body 88 which is quided in the housing 82
and which incorporates a weak location 89 for carrying wire strain
gauges.
~ounted at the end of the body 88 is an ~djustable-height
~ ~ support, which, tcqether with the adjustinq spindle associated there-
with, is generally denoted by reference nu~eral 90. Secured
to the support 90 is a seqment of the co-operating surface 1 which
bears the ribs 7 and 8.
A peripheral cam 92 is unted to the carriages 81 and the pillar
76 by way of mounting arms 91. As will be described in greater
detail hereinafter with reference to Figures 8 and 9, the cam 92
is provided for controlling the entrainment means.
m e feed means for the blanks to be worked upon, which can be
better seen from Figure 4, is indicated generally by reference
numeral 93 and is driven by the transmission 42 by way of a
chain wheel 94 and a chain g5.
The step-up ratio of the transmission 42 and the chain wheels
40 and 38 as well as ~hat of the transmission f~rmed by the ring
gear 61 and ~he ring gear of the sleeve 59 and the gears 63 and
%~ ~ 507
64 is such that ~he rotaLy members wh~ch are driven by those
transmissions, cn the path of mcvement described ky the thrust
memkers 14 and 14' which are mounted m the rotary mimbers, move
at half the peripheral speed of the peripheral surface of the roller
bearing the ri~s.
In the carriage 81 shown in sect.ion in Figure 4, a vibration
generator 96 is screwed into the segment of the oounterpressure
surface 1 and causes ~he counterpressure surface to be displaced
with high-frequency vibrations or oscillati~ns, thereby facilitating
deformation of the blanks 9 which are guided between the seoments
of the surface 1 and the roller 12 ky means of an entrainment
arrangement which is not shcwn in Figure 4 for the sake of enhan oed
clarity of the drawing.
As can be seen from Figure 4, the supply means 93 has an
inclinedly extend m g channel 97 which guides the blanks ~ into the
star wheel 98~ The star wheel 98 transports the blanks to a fur~her
star wheel ~9, while for the purposes of transferring the blanks
the a~rangement includes a guide plate 100 which is secured
to the housing 26' by way of a hold OE which is not shown for the
sake of enhanced clarity of the drawings.
Punches 101 of which only two are illustrated are guided in the
star wheel 99 which rotates in a plane which is displaced with
respect to the star wheel 98~ The punches 101 project beyond the
upper fa oe of the star wheel 99 and slide against the cam 102.
The cam 102 which is stationary causes the blanks to be pushed out
into the path of thie thrust mRmbers 14 and 14' ~y which they are
engaged or clamped.
Disposed in ahorizontal plane which is different fr~m that of
the feed means is a magnet 103 which, after the finished bodies
of revolution gv are released by the thrust m~mbers 14 and 14',
conducts them into a further channel 104.
~4SOt7
Inoorporated into the channel 104 is a switching means 105
which pe~mlts a body of revolution to be selectively removed
from the channel by a deflection plate 106 being inserted thereinto
by means of the piston-cylinder arrangemen ~ m e ~ody of
revolution which is remKved from the ch~nnel in that way then passes
~y way of a chan~el lOB to a measuring device 109 in which the body
of revolution is pushed by means of a piston 110 into a measuring
position in which it bears against an abutment 111 which is pivotable
by n~ns of a piston-cylinder arrangement 112. The ~easuring operation
itself is carried out by means of an optical measuring head 113 which
pxoduces the measuring result in the form of electrical signals
which are passed to a control means (not shown) for example a process
computer. In the case where the measurement values obtained are
tcwards the limits of a predetermined tolerance range, the control
means passes suitable control instructions to the stepping tors
86 of the carriages 81, to provide for suitable adjustn~nt thereof.
That makes it possible to observe very close toleran oe s.
After the operation of measuring the body of revolution, the
abutment 111 is pivoted by the piston-cylinder arrangement 112
and the piston-cylinder arrangement 110 pushes the body of revolution
which has already been measured to the openlng 114 through which
it slips to the exterior by way of the channel 115.
Figure 7 shGws the end regions of the members 14 and 14'
on an enl~rged scale, said end regions beiny rotatable about the
l~ngitudinal axis of the n~bers 14 and 14'. In that arrangement,
screwed into the thrust member 14 in the end thereof is an insert
116 in which a tip 117 is held by means of a pin 119 which passes
thr~ugh a transverse 118 in the tip 117 and which also passes
through the walls of the insert 116. The tip 117 is axially
displaceably held in the insert 116 and is subjected to th~ for oe
~ ~L~?~ 5 O 7
of a spring 120. As the transverse ~ore 118 is larger in diameter
than the tip, this arrange~ent provides for a slight amount of
axial displacement of the tip 117 relative to the insert or the
casing thereof. That makes it possible to ccmFensate for slight
S dimensional variations in the blanks 9 and to compensate for the
growth in length of the blanks while they are being deformed by
the ribs 7, 8 and 7', 8' respectively of the counterpressure
surface 1 and the roller 12.
A sleeve 121 is screwed on to the screwthreaded spigot 120
of the thrust memker 14'. A slide bush 122 is fitted into the sleeve
121 and secured therein with an inse~t mimber 123. A tip 124 is
rotatably carried in the bush 122, the collar on the tip being
supported against a slide ring 125 which in turn is supported
against a shoulder of the sleeve 121.
~he arrangement of the rotatable tip 12~ of the thrust mem~ers
14' and the r~tatable unting of the thrust members 14 in the
guide heads 71 thereof ensures that friction between the thrust
members 14, 14' and the blanks 9 which are held therebetween is
elimlnated.
The entrainme~t means will be described in greater detail with
reference to Figures 8, 9 and 10.
m e rotary members 47 and 56 are provided in a section-wise
manner with tangentially extending, radially projecting dovetail
guides 126. Two slide members 127 are displaceably disposed on
each of the sections of the dovetail guides. Ihe thrust members 14
and 14' pass be~ween the projections on the r~tary n~nbers
whereas the support rollers l?B are rotatably mounted in the
bores 129 of the slide n~ ers 1~7. m e slide ~embers ~27 which
are mounted in different rotary members 47 and 56 respectively
are connected together by way of the pressure members 130 which
3L;~6~5~
~CI
are screwed to the s~de n~s~ers 127.
The members 130 are controlled ky respective cam shafts 131
whose cylindrical projections 132 extend thrcugh and are rotatably
mcunted in the ~ores 133 disposed in the radially proj~cting
S porticns of the rotary nY~ers 47 and 56. The upper cylindrical
projections 132 are each non-rotatably clamped in a respectiv~
control lever 134 while the projections 132 ~ngage into the
bores 135 which define a slot 136. m e control levers 134
slide alony the stationary cam 92 upon rotary mavement of the
two rotary members 47 and 56.
Over the arcuate region over which the counterpressure surface
1 extends, the cam 92 describes substantially a circular arc. In
the reyion of the feed and discharge area for the blanks ~ and
the finished bodies of revoluti~n respectively, the cam 92
has a depression 137 which permits-pivotal--mcvement of the
control levers.
The support rollers 128 have a region which is provided with
knurling and which comes into contact with and drives the blanks
9. The support rollers are driven ky the gears 138 which are non-
rotatably connected to the support rollers. The g OE s 138 mesh
with intermediate gears 139 which are rotatably mounted with a
respective gear 138 in a holder 14~, the intermediate gears
139 meshing wnth the gear 58 oonnected to the roller 12
carrying the ribs 7' and 8'. In that arrangement, because of the diff-
erence in speed between the gear 58 and the holders 140 which
are also moved by virtue of the driving connection to the rotary
~embers 47 and 56 which is prcvided by the support shafts 128,
a rolling mKvement of the intermediate gears 139 is produced and
thus the suFport shafts are driven.
As can be seen from Figures 9 and 10, the respectively
~69~507
~g ,
assoclated holders 140 are connec,~ed together by a pin 141, with
the t~o holders 140 being braced tcwards each other by two springs
142.
As long as the co~trol levers 134 slide along the arcuate region
S ~f the cam 94, they are deflected and the cam shafts 131 which are
non-rotatably oonnec,ted thereto urge the mem~ers 130 and the support
shafts 128 which are held therewith in the slide n~ ers 127
against the thrust memkers 14 and 14' and thus against the blanks
9 to be deformed. ~hen that happens, the holders 140 are urged
apart against the force of the sprin~s 142. When one of the control
lever~ 134 slides into the depression in the cam, that control lever
can be deflected and the springs 142 can urge the support shafts
128 away from the thrust members whereby, by way of the pivotal
movement of the cam shaft 131, the control lever 134 is alsD caused
to pivot, being beld_in contact with the cam 92 by the springs
1~2.
As can be seen fro~ Figure 10, the intermediate gears 39
rotate in two different horizontal planes and are rotatably
fixed on axle journals which are held at one end in thP respective
holders 140. The step-up ratio of the transmissions 58, 139, 138
and the support shaft 128 or the diameter of the knurled region
~hereof are matched to each other in such a way that the peripheral
speed of the knurled region of the support shafts 128 and thus
also that of the blanks 9 ~earing thereagainst is equal to the
peripheral speed of the periphery of the roller 12 carrying the
ribs~ Although the blanks 9 are caused to rotate solely by the
rolling ~ vement against the stationary co-operating surfaoe 1
and the peripheral surfa oe of the roller 12, as indicated by the
arrows in Figure 10, nonetheless a certain sliding mavement of
the blank against such surfaces may also occur during w~rking of
'12~S~7
the blank. Ihat is prevented by the additional drive for the blanks
by the support shafts, while, as can be seen from Figure 10, the
blank 9 is always supported a~d driven between the support shafts
1~8 which are mounted in adjacent pairs of holders 140.
As can be seen from Figure 8, the pressure ~embers 130 have
a groove ~hich is towards the supp~rt shafts 128 and which ext~nds
in the axial direction and in which are disposed rolling memkers
14~ which project beyond the outer edges of the groove 145.
That substantially elimunates friction between the support sh2fts
and the pressure n~s~ers 130.
When the control levers 134 go from the arcuate region of the
cam 92 into the depression 137 therein, the intenmediate gears
13~ also perform an additional movement relative to the gear 58,
by virtue of the tw~ holders 140 connected by the pin 141 moving
towards each other, due to the springs 142. Although that
.
additional movement results in a change in ~he speed of rotation of
the support shafts, that is however of n~ importance as in that
situation the support shafts 128 are moved away from the blank
9.
The ccntrol grooves 52 and 70 which detenmine the path of the
hlanks 9 extend as indicated by the line 15 in Figure lA or parallel
thereto, in the region covered ky the co-operating surface 1.
Outside that region, the paths of the control grooves have
deviatio~s in opposite directions, the control grooves 52 and 70
moving further apart from each other and moving towards each
other again so that in that region there is no clamping in
respect of the blanks 9 or the ~odies of revolution 9 and the
blanks ~an ~e introduced and the finished bodies of revolution
can be removed.
In the illustrated em~xxlunent, the co-operating surface 1 is of
~i45(~7
31
a curved ccnfiguratlon corresponding to the roller 12, ~ut that is
in no way ab~olutely necessary. Thus, it is also possible to
use a flat ccunterpressure su* ace over which the r~ller mcves,
in which respect it is irrele~ant whether the counterpressure
surface is moved with respect to the axis of the roller or
whether the roller is ~oved in parallel relationship with the
oounterpressure surfa oe .
