Machine tools abstract
In a spindle assembly for machine tools, the axial length .lambda.
of the collar of a spring collet is determined as a function of
the axial course length c of a clamping sleeve operating spring
collet. This axial length .lambda. is preferably retained within
an interval ranging between 3 mm and 9 mm. A tapering surface of
the collar presents an inclined profile, which is straight, curved,
or at least partially curved. The angle of inclination formed by
the tapering surface with the axis of the spring collet is advantageously
of the order of 45.degree.. The spring collet has grooves, the number
whereof is at least two, but also greater than three. The gap between
these grooves may be determined in such a way that, when the spring
collet is in the closed position, then the workpiece is gripped
with a predetermined clamping force, and the two mutually opposing
faces of each groove portion abut against each other.
Machine tools claims
1. Spring collet for use within a spindle assembly of machine tools,
and particularly automatic lathes, wherein: the spring collet has
an axis and concentrically aligned thereto, a variable central axial
opening amenable to a first open position and to a second closed
position, for respectively, releasing and clamping a workpiece,
and vice versa, the spring collet having at least two grooves, where
each one of the two grooves has two mutually opposite faces, and
a collar extending concentrically outward from the spring collet,
and having a tapering surface against which rests a corresponding
face of a sleeve operable for translating forth and back along a
limited axial course length c, to reversibly dispose the variable
central axial opening, respectively, in the open and in the closed
position, comprising: an axial length .lambda. of the collar being
retained within a length interval whose lower and upper limits are
about, respectively, twice and five times the axial course length
c, and the tapering surface being inclined by more than 15.degree.
relative to the axis of the spring collet.
2. Spring collet according to claim 1 wherein: the axial length
.lambda. of the collar is selected within an interval ranging between
2 mm and 15 mm, and the length of the axial course c is retained
between 1 mm and 3 mm.
3. Spring collet according to claim 1 wherein: the axial length
.lambda. of the collar is selected within an interval ranging between
3 mm and 9 mm, and the length of the axial course is retained between
1.5 mm and 1.8 mm.
4. Spring collet according to claim 1 wherein: the tapering surface
of the collar is inclined by some 45.degree. relative to the axis
of the spring collet.
5. Spring collet according to claim 1 wherein: the tapering surface
of the collar has a profile that is selected from the group of profiles
consisting of a straight profile, a curved profile, and an at least
partially curved profile.
6. Spring collet according to claim 1 wherein: the spring collet
has more than three grooves.
7. Spring collet according to claim 1 wherein: the variable central
axial opening has a diameter, and the difference in diameter between
the open and the closed position of the variable central axial opening
is greater than 0.30 mm.
8. Spring collet according to claim 1 wherein: at least a portion
of two mutually opposite faces of the at least two grooves abut
against each other when the spring collet is in the closed position
and grips the workpiece with a predetermined clamping force.
9. Spring collet for use within a within a spindle assembly of
machine tools, and particularly automatic lathes, wherein: the spring
collet has an axis and concentrically aligned thereto, a variable
central axial opening amenable to a first open position and to a
second closed position, for respectively, releasing and clamping
a workpiece, and vice versa, the spring collet having at least two
grooves, where each one of the two grooves has two mutually opposite
faces, and a collar extending concentrically outward from the spring
collet, and having a tapering surface against which rests a corresponding
face of a sleeve operable for translating forth and back along a
limited axial course length, for reversibly dispose the variable
central axial opening, respectively, in the open and in the closed
position, comprising: at least one portion of each one of the two
grooves having a gap opening when the spring collet is in the open
position, and at least a portion of two mutually opposite faces
of the at least two grooves abut against each other when the spring
collet is in the closed position and grips the workpiece with a
predetermined clamping force.
10. Spring collet according to claim 9 wherein: an axial length
.lambda. of the collar being retained within a length interval whose
lower and upper limits are about, respectively, twice and five times
the axial course length, and the tapering surface being inclined
by more than 15.degree. relative to the axis of the spring collet.
11. Spring collet according to claim 9 wherein: the axial length
.lambda. of the collar is selected within an interval ranging between
2 mm and 15 mm, and the length of the axial course is retained between,
approximately 1 mm and 3 mm.
12. Spring collet according to claim 9 wherein: the axial length
.lambda. of the collar is selected within an interval ranging between
3 mm and 9 mm, and the length of the axial course is retained between
1.5 mm and 1.8 mm.
13. Spring collet according to claim 9 wherein: the tapering surface
of the collar is inclined by some 45.degree. relative to the axis
of the spring collet.
14. Spring collet according to claim 9 wherein: the tapering surface
of the collar has a profile that is selected from the group of profiles
consisting of a straight profile, a curved profile, and an at least
partially curved profile.
15. Spring collet according to claim 9 wherein: the spring collet
has more than three grooves.
16. Spring collet according to claim 9 wherein: the variable central
axial opening has a diameter, and the difference in diameter between
the open and the closed position of the variable central axial opening
is greater that 0.30 mm.
Machine tools description
TECHNICAL FIELD
[0001] The present invention relates to spindle assemblies for
machine tools, namely for automatic lathes, and in particular, to
a spring collet for use with spindle assemblies.
DISCLOSURE
[0002] The user of a machine tool for the production of high-precision
parts, possesses an entire set of existing collets from which he
will select one for mounting, for example, within a rework spindle
or within an indexing attachment. The selected existing collet is
chosen with a diameter suitable to that of the workpiece to be machined
(with a diameter ranging approximately from 1 mm to 10 mm). When
closed, the clamping jaws are able to grip the diameter of the workpiece
as long as there is a gap between the mutually opposing faces of
each groove. As known from the prior art, existing collets, operating
in spindle assemblies of machine tools, usually have three grooves
that form the clamping jaws for retaining and releasing a workpiece.
The portion with the grooves has the shape of a truncated cone that
is relatively long, namely with the cone having a vertex angle of
the order of 30.degree..
[0003] The problem is that existing collets, used for the production
of high-accuracy machine parts, are subject to a double disadvantage,
in view of the diversity of workpieces for the machining of which
they are used.
[0004] In a first instance, or first problem, various diameters
have often to be machined along the length of the workpiece. With
existing collets, the difference between the diameters of the variable
opening of these collets when in the open position (maximum opening)
and in the closed position (that is, clamped onto the workpiece),
is very small, namely of the order of 0.30 mm in the best case,
which is often smaller than the difference between the diameters
to be processed on the workpiece. Accordingly, with a workpiece
which has a general diameter D, and presents a diameter of D+0.40
mm over a certain portion of its length, there is selected an appropriate
existing collet for the diameter D. However, when the clamping jaws
of the selected existing collet (which is intended to clamp a workpiece
of diameter D) are in the maximum opening position, thus at opening
diameter D+0.30 the passage of the workpiece, with maximum diameter
of D+0.40 mm is evidently hindered. In such a first instance situation,
it is necessary to proceed in several successive machining stages
to perform the machining of the workpiece along its entire length.
This may involve, for example, reworking the workpiece by means
of an adaptation sleeve, counter-operations, etc., all resulting
in a considerable increase of manufacturing costs.
[0005] In a second instance, or second problem, manufacturers are
often confronted with the risk of crushing the workpiece when it
is clamped in an existing collet. This is due to specific parameters
which characterize the workpiece or which relate to the machining
data, amongst others: workpiece made of relatively soft material,
clamping on a screw thread, thin walls, workpiece in tubular form,
diameter of the workpiece at the clamping location, force applied
to the workpiece by the cutting tool. The means presently used in
order to limit the clamping force (such as the machining of a limit
stop at a certain point, in view of limiting the course of the sleeve
within which the collet is disposed) are quite unsatisfactory. This
second instance inability to control the clamping force is another
source of increased manufacturing costs, causing a large number
of rejects and providing rather inconsistent machining quality.
[0006] It is an object of the embodiments of the present invention
to provide a spring collet for use within the spindle of existing
and of new machine tools, for high-precision machining that overcomes
the two disadvantages, or problems described above. That is, for
example, the too limited range of diameters of the variable central
axial opening of all the existing collets in a set, and the risk
of crushing portions of the workpiece or, at the very least, to
surmount one or the other of both problems, according to the type
of workpiece to be machined, when either one or both of these disadvantages
is present.
[0007] As a solution to the problems mentioned above, a spring
collet is designed, to be mounted within the spindle of a machine
tool in replacement of an existing collet. The problem-solving spring
collet permits machining of high-precision cylindrical workpieces
with a wider range of diameters than the existing collets, for a
broad variety of applications. By way of illustration only, the
spring collet may be used for the machining of shafts for prostheses
used in osteopathy, or shafts for micro-motors. The front end of
the spring collet has a portion shaped as a truncated cone extended
by a nose and presents, along a defined length, at least two grooves
opening onto the front end, forming at least two clamping jaws around
the variable central axial opening, enabling the clamping of the
workpiece to be machined, so that the plane of symmetry of each
groove passes through the axis of rotation of the spring collet.
[0008] To this end there is provided a spring collet with a particularly
dimensioned collar. A tapering surface of the collar, in the general
shape of a truncated cone, has a maximal collar root width, defined
as an axial length .lambda., which is selected as a function of
an interval limited by specific multiples of the axial course length
c. That axial course length c is the length of translation of the
clamping sleeve of the spindle operating on the spring collet to
clamp or release the workpiece. The function defines that the axial
length .lambda. is to be retained within the interval limited by
about twice and five times the axial course length c. Furthermore,
the angle between the tapering surface of the collar and the axis
of the spring collet is chosen to be greater than 15.degree., and
preferably, about 45.degree..
BACKGROUND ART
[0009] DE Patent No. 434583 to Seidemann discloses a chuck assembly.
A free translation of lines 1 to 3 in column 1 recites: "The
invention relates to a chuck for which the gripping is achieved
by means of rolling elements". This is achieved by using a
plurality of sequentially arranged rolling members, rolling on each
other, to axially transfer the force required for clamping a workpiece.
Abb. 1 (FIG. 1) shows the chuck when open, while Abb. 2 (FIG. 2)
depicts the same chuck when closed. Seidemann thus discloses a system
for opening and for closing a chuck for gripping a workpiece.
[0010] When FIGS. 1 and 2 provided by Seidemann are enlarged and
measured, the axial length .lambda. of the existing collar is found
to be ten times that of the axial course length c, thus exceeding
by far the upper limit of five times c recited in claim 1 hereinbelow.
[0011] In DE Patent No. 974660 to Shoenenberger, the translation
of the title reads: "Means for fast gripping", and discloses
a chuck mechanism for gripping a workpiece by operating a handle
e to push, or pull, or internally operate, the gripping of a workpiece.
Shoenenberger claims the invention of a chuck, namely a fast operating
chuck, and not of a spring collet. Moreover, when FIG. 1 provided
by Shoenenberger is enlarged and measured, the axial length .lambda.
of the existing collar is found to be as large as 9.5 times that
of the axial course length c, thus far above the upper limit of
five times c recited in claim 1 hereinbelow.
[0012] JP Patent No. 01-11701 to Suganuma is an invention for a
"Method of automatically inserting [a bar of stock having a]
profile into [an] automatic lathe and device therefore". As
stated in the Purpose paragraph, Suganuma's teaches means: "To
surely and automatically insert and grip a profile in one motion
by stopping and setting the profile opening of a collet chuck with
the use of a rotational angle position stopping function so that
the profile opening coincides with the cross-sectional posture of
the profile on a material supply pass in an automatic material feeder".
In other words, the disclosure of Suganuma serves the purpose of
automatically positioning stock for loading into a processing machine,
thus for gripping stock having a male profile in correct angular
position relative to a collet having a matching female opening.
[0013] When FIGS. 2 and 3 provided by Suganuma are enlarged and
measured, the axial length .lambda. of the existing collar is found
to be as large as 7.35 times that of the axial course length c,
thus above the upper limit of five times c recited in claim 1 hereinbelow.
[0014] U.S. Pat. No. 24755197 to Robichaud is entitled: "A
chucking apparatus", which recites, as by column 1 lines 10
to 18: " . . . characterized by a chucking mechanism adapted
for gripping and releasing a bar of stock while the spindle is in
rotation. The mechanism is constructed in such a way that bar gripping
means operates when released to instantly expand to effect a quick
release of the bar while at the same time the bar gripping means
is easily and readily operated for gripping a bar." In other
words, Robichaud teaches a mechanism for opening and for closing
a chuck.
[0015] When FIG. 1 provided by Robichaud is enlarged and measured,
the axial length .lambda. of the existing collar is found to be
as large as 6.4 times that of the axial course length c, thus above
the upper limit of five times c recited in claim 1 hereinbelow.
[0016] Seidemann, Shoenenberger, Suganuma, and Robichaud fail to
mention a particular spring collet with a collar designed for widening
the range of workpiece diameters able to be processed at high-precision
in one manufacturing step, and also fail to mention the use of only
but the spring collet itself for limiting the clamping force applied
to the workpiece when gripped. Moreover, the prior art does not
teach a function relating the axial length .lambda. and the axial
course length c. The prior art thus does not disclose, teach, or
suggest neither the spring collet nor the embodiments of the present
invention.
[0017] The embodiments of the present invention deal with a distinct
structure for a particular spring collet, for use with high-precision
manufacturing, operative in replacement of existing collets present
in a variety of spindles pertaining to machine tools, namely turning
lathes and indexing devices, and providing either one and both wider
workpiece diameter single-pass processing capability and workpiece
clamping force control.
[0018] A spring collet openable and adaptable to a wide range of
workpiece diameters was always desired in the uppermost high-precision
industry, but expectations were delayed until a solution was found
for the practical implementation as a suitable product. Presently,
the spring collet is openly approved by the experts and well received
on the market.
SUMMARY
[0019] It is an object of the present invention to provide a spring
collet for use within a spindle assembly of machine tools, and particularly
for automatic lathes. The spring collet has an axis and concentrically
aligned thereto, a variable central axial opening amenable to a
first open position and to a second closed position, for respectively,
releasing and clamping a workpiece, and vice versa. The spring collet
has at least two grooves, where each one of the two grooves has
two mutually opposite faces, and a collar extending concentrically
outward from the spring collet, and having a tapering surface against
which rests a corresponding face of a sleeve. The sleeve is operable
for translating forth and back along a limited axial course length
c, to reversibly dispose the opening, respectively, in the open
and in the closed position. The spring collet comprises an axial
length .lambda. of the collar being retained within a length interval
whose lower and upper limits are about, respectively, twice and
five times the axial course length c, and the tapering surface being
inclined by more than 15.degree. relative to the axis of the spring
collet.
[0020] One embodiment of the present invention provides a spring
collet wherein the axial length .lambda. of the collar is selected
within an interval ranging between approximately 2 mm and 15 mm,
and the length of the axial course c is retained between, approximately
1 mm and 3 mm. In another embodiment, the axial length .lambda.
of the collar is possibly selected within an interval ranging between
approximately 3 mm and 9 mm, and the length of the axial course
is retained between, approximately 1.5 mm and 1.8 mm.
[0021] It is a further object of the present invention to provide
a spring collet wherein the tapering surface of the collar is inclined
by some 45.degree. relative to the axis of the spring collet, and
if desired, the tapering surface of the collar has a profile that
is selected from the group of profiles consisting of a straight
profile, a curved profile, and an at least partially curved profile.
[0022] It is another object of the present invention to provide
a spring collet wherein the spring collet has more than three grooves,
and the difference in diameter between the open and the closed position
of the variable central axial opening is greater than 0.30 mm.
[0023] It is yet another object of the present invention to provide
a spring collet wherein the spring collet has at least a portion
of two mutually opposite faces of the at least two grooves that
abut against each other when the spring collet is in the closed
position and grips the workpiece with a predetermined clamping force.
BRIEF DESCRIPTION OF THE DRAWINGS
[0024] In order to understand the invention and to see how it may
be carried out in practice, preferred embodiments will now be described,
by way of non-limiting example only, with reference to the accompanying
drawings, in which:
[0025] FIG. 1 is an axial longitudinal section of an assembly within
which the spring collet is mounted, the spring collet being shown
in closed position,
[0026] FIG. 2 is an axial longitudinal section similar to that
shown in FIG. 1 the spring collet being shown in open position,
[0027] FIG. 3 is an axial longitudinal section of the spring collet
only,
[0028] FIG. 4 is a front view of the spring collet (in open position),
showing the grooves according to one embodiment,
[0029] FIGS. 5 and 6 are front views of the spring collet (in closed
position), showing the form of the grooves according to another
embodiment, and
[0030] FIGS. 7 and 8 show profile variants of an element of the
spring collet.
[0031] It is noted that the scale of representation of the various
Figures is not uniform.
DETAILED DESCRIPTION OF THE INVENTION
[0032] FIGS. 1 and 2 show a spring collet 1 integrated within a
spindle assembly 100 which is part of a rework spindle, including
a clamping sleeve 20 connected to a clamping piston 40 on the right
of the Figs., indicating the rear, that is, rearward of the spring
collet 1 a fixed sleeve 60 on which are mounted roller bearings
70 a clamping nut 30 on the left of the Figs., indicating the
front, that is, to the front with the spring collet 1 and an elastic
organ 50. The elastic organ 50 rests, on one side, against a face
(not shown) of the sleeve 20 and, on the other side, against the
rear face 19 (shown in FIG. 3) of the spring collet 1. After introducing
the spring collet 1 into the spindle assembly 100 the nut 30 is
screwed onto a threaded portion 61 of the sleeve 60. A collar 2
of the spring collet 1 is caught between an interior face 33 of
a corner 31 of the nut 30 and a front face 21 of the sleeve 20
and an interior face 32 of said nut 30 abuts against a front face
62 of the sleeve 60. Thereby, the spring collet 1 constitutes an
integral portion of the spindle assembly 100.
[0033] The spring collet 1 with a central longitudinal axis designated
as 1A in the Figs., is generally tubular in form, in the sense that
it consists of a hollow body forming a hollow internal space, as
represented in an axial section, and in a closed position, in FIG.
3. According to the example shown, and extending radially outward
from the collar 2 that has a frusto-conical shape, there is a base
3 (oriented toward the front) and a lateral tapering surface 4
with respectively, on one side a nose 5 and on the other side,
a span 6. A rear portion 6A of the span 6 remains guided by the
clamping sleeve 20 (see also FIGS. 1 and 2). The outside diameter
of the span 6 extends, according to the construction thereof, over
a range of several millimeters, more or less, like the diameter
of the nose 5. The hollow internal space is essentially composed
of a variable central axial opening 7 and a relief 8. The periphery
of the variable central axial opening 7 is provided, according to
the example, with a carbide insert 9 which is applied to the workpiece
10 (FIGS. 1 and 2). The spring collet 1 according to the example,
has three blind grooves 11; 12 where the grooves 11 (FIG. 4) and
12 (FIGS. 5 and 6) correspond respectively to two different embodiments.
Each pair of median planes 11 P; 12 P of the grooves 11; 12 forms
an angle of 120.degree. (shown only once, in FIG. 4). These grooves
11; 12 open, to the front, onto a face 18 of the spring collet 1
and end in the formation of three clamping jaws 14; 15--or, more
generally, of as many clamping jaws as there are grooves, whereby
the clamping jaws are capable of opening and of closing by virtue
of their elasticity. At the opposite end, the grooves 11; 12 open
into hollows 13 which enable improved elasticity.
[0034] Returning to FIGS. 1 and 2 it is understood that, when
the piston 40 is withdrawn backward to the rear, the spring collet
1 opens and the clamping jaws 14; 15 open radially outward and away
from the axis 1A of the spring collet 1 releasing the workpiece
10 while, as described above, the spring collet 1 remains retained
between the nut 30 and the sleeve 20. Meanwhile, the elastic organ
50 exercises a force capable of retaining the collar 2 against the
internal face 33 of the corner 31 of the clamping nut 30. When the
clamping jaws 14; 15 are open, the tapering surface 4 of the collar
2 abuts against the front face 21 of the clamping sleeve 20. The
face 21 which matches with the tapering surface 4 as shown in
the example depicted in FIGS. 1 2 and 3 is itself tapered and
presents the same conicity as the tapering surface 4.
[0035] When the spring collet 1 passes from the open position (FIG.
2) to the closed position (FIG. 1) (or vice versa), the sleeve 20
translates forward (or backward) along a limited axial course length
designated in FIG. 2 by the letter c (translation of the front face
22 that is perpendicular to the axis 1A). This axial course length
c is a function of the characteristics of the machine tool within
the spindle wherein the spring collet is mounted, it being noted
that, in practice, the most customary values for the axial course
length c run between approximately 1 mm and 3 mm.
[0036] In contrast to the constraint imposed by this very limited
course length c, and in view of the configuration of the collar
of prior art collets (conicity of the order of 30.degree.--that
is, a vertex half-angle of the order of 15.degree.--and an axial
length greater than some 15 mm), the first problem described above,
or first disadvantage, is now exposed.
[0037] The first problem is solved by means pertaining to the geometric
configuration of the collar 2 which are explained further below.
[0038] The axial length of the collar 2 or collar root width 2
(indicated by the letter .lambda. in FIG. 3) is determined as a
function of the axial course length c. Accordingly, this function
is chosen so that the length .lambda. can be selected within an
interval limited by approximately twice (lower limit) and five times
(upper limit) the length of the axial course length c. Knowing that
the usual values of such axial course lengths c of sleeves 20 extend
within a range of approximately 1 mm to 3 mm, then the length .lambda.
will be selected within a range extending between approximately
2 mm and 15 mm. Experience has shown that, according to the diameter
for which the spring collet is intended, the axial length .lambda.
of the collar 2 is advantageously chosen between 3 mm and 9 mm.
[0039] The conicity of the tapering surface 4 is dictated by the
axial length .lambda. and by the diameter of the span 6 of the sleeve
20 at the intersection 2B of the tapering surface 4 with the sleeve
20 as seen in FIG. 3. There is a half-angle .alpha. and a generatrix
line disposed within a plane passing through the axis 1A and supporting
a segment 2A-2B, (the base of the cone of the collar 2 and the intersection
2B respectively). Experiments have shown that, in view of the range
of diameters of the span 6 possibly enabled for construction, the
selected angle .alpha. must always be greater than 15.degree..
[0040] Evidently, the more pronounced the conicity of the tapering
surface 4 the closer the value of the axial length .lambda. will
be to the lower limit associated with the axial course length c,
and the greater will be the force that the piston 40 must exert
on the collar 2 by means of the sleeve 20. As a result, the risk
of causing damage to the collar 2 will increase. Therefore, the
choice of the minimum value .lambda. and the maximum value of the
angle .alpha. is limited by the constraint imposed by the characteristics
of construction and constitution (material) of the collar 2. Experiments
have shown that it is preferable for the angle .alpha. not to exceed
75.degree., whereas the prohibitive nature becomes stronger as the
angle .alpha. approaches 90.degree.. In compliance with the embodiment
represented by FIGS. 1 2 and 3 the angle .alpha. of the tapering
surface 4 of the collar 2 is advantageously selected as 45.degree..
[0041] The profile of the tapering surface 4 of the collar 2 may
be curved (profile 4A of FIG. 7), or curved with at least one flat
portion (profile 4B of FIG. 8 the flat portion being shown by a
line 4M). The overall slope of the surfaces 4A, 4B is indicated
by the uniform reference generatrix line 4P, which supports the
right hand segment 2A-2B (same references numbers as those indicated
in FIG. 3), a generatrix which, together with the axis 1A, forms
angles .alpha..sub.A and .alpha..sub.B respectively. Obviously,
the corresponding face of the sleeve 20 (not shown in FIGS. 7 and
8) presents a similar matching profile for each case. This configuration
has the advantage of a better distribution of the force exerted
on the collar 2 whereas, in order to produce the same effect--that
is, for the same opening of the clamping jaws 14; 15--the pressure
necessary to be applied to the clamping jaws will be lower.
[0042] A second means, which can be combined with those described
above, consists of increasing the number of grooves 11; 12. The
determination of the maximum number of grooves depends on mechanical
considerations concerning construction and/or manufacture. This
increase will again enable a reduction of the force necessary to
be applied to the collar 2 in order to obtain the same opening of
the clamping jaws 14; 15. Measurements performed on the spring collets
1 provided with the means described above (even without increasing
the number of grooves) have enabled the achievement of the following
diameter differences between the open and the closed positions (by
way of illustration only): 0.60 mm with a spring collet provided
for the clamping of workpieces of 1 mm in diameter (maximum opening
1.60 mm), 1.25 mm with a spring collet for workpieces of 6.25 mm,
and 3.00 mm with a spring collet for workpieces of 10.00 mm. Assuming
a workpiece 10 (see FIGS. 1 and 2), with a clamping diameter 10A
of 1.00 mm, 6.25 mm or 10.00 mm, then the diameters 10B, 10C can
be as large as 1.60 mm, 7.50 mm or 13.00 mm respectively, without
confronting the operator with any problem of a type which would
require ancillary manipulations.
[0043] As to the second disadvantage, or second problem, it is
solved according to an embodiment of the invention, through a modification
of the geometry of the grooves (FIGS. 5 and 6). Generally, when
the spring collet 1 is in the closed position (that is, when the
workpiece is clamped), there remains a gap between the two mutually
opposite faces (not shown) of each groove 11 (FIG. 3), and an increase
of the clamping force remains possible. The modification described
above is determined, in each particular case, as a function of the
parameters detailed above (tubular workpiece, presence of threading,
etc.). In other words, for an admissible--that is, pre-calculated--clamping
force, taking into account the aforementioned parameters, the gap
between the grooves: is corrected (see FIG. 5 where the spring
collet is in the open position, and FIG. 6 where the spring collet
is in the closed position). This correction consists of providing
a gap .epsilon. over the groups 12 at least over a defined radial
distance thereof (indicated as 12R on one of the three grooves in
FIG. 5 the portions of groups 12R opening onto the variable axial
opening 7 and partially onto the relief 8 (FIG. 3)). The gap .epsilon.
is calculated so that, when the spring collet 1 is in the closed
position (FIG. 6), and is thus exerting the predetermined clamping
force on the workpiece 10 to be machined, then the mutually opposite
faces of the portions of the grooves 12R abut against each other,
thus making impossible any increase in clamping force. The workpiece
10 will thus be protected from any damage due to unintentional crushing.
[0044] It will be appreciated by persons skilled in the art, that
the embodiments of the present invention are not limited to what
has been particularly shown and described hereinabove. For example,
the spring collet 1 may retain the workpiece 10 with any appropriate
insert, or without the intermediary of any insert, and thus without
the intermediary of a carbide insert 9. Rather, the scope of the
present invention is defined by the appended claims and includes
both combinations and subcombinations of the various features described
hereinabove as well as variations and modifications thereof which
would occur to persons skilled in the art upon reading the foregoing
description.
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