Note: Descriptions are shown in the official language in which they were submitted.
CA 02550348 2006-06-16
A Drive Device for Rotating Tools Operating with
Oscillation Superimposition and a Tool Equipped Therewith
The invention relates to a drive device for
rotating tools operating with oscillation superimposition
exhibiting a drive housing, a carrier sleeve mounted
rotatably in the drive housing, a drive shaft mounted
rotatably in the carrier sleeve, a tool carrier to receive
working tools and an oscillation-generating arrangement
for producing the oscillation superimposition for the tool
carrier.
In the drive devices of the kind in question with
impact superimposition, activation of the impact impulse
takes place by means of appropriate striking mechanisms,
imbalance generators and, in particular, eccentric shafts,
which carry freely rotating or driven working tools. Tools
operating with impact superimposition are used in
particular in mining, in tunnel construction and in road
building, for example when hard rock or other mineral-
bearing rock must be loosened, cut or worked in some other
way. Impact superimposition permits the necessary pressing
forces to be applied to the material intended for
loosening or excavation to be reduced to as little as 1/10
of the pressing forces that are necessary without impact
superimposition, which permits the use of lighter and
smaller tools and machines and, at the same time,
increases the extraction performance or daily headway of
the tools.
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Drive devices of the kind in question for tools on
which impacts are superimposed are previously disclosed in
EP 329 915 A1 and EP 455 994 B1. The drive devices of the
kind in question each comprise a carrier sleeve that is
rotatably mounted and is driven by a carrier sleeve drive
with an eccentrically arranged internal bore, in which a
shaft is rigidly connected to the tool carrier, which
shaft is designated in the prior art as an eccentric
shaft. The carrier sleeve is provided with counterweights
for the dynamic balancing of the drive device, and the
eccentric shaft is driven by means of a second drive,
which can consist of a separate drive or a reduction
drive. In a reduction drive, the speed ratio between the
speed of the eccentric shaft and the speed of the carrier
sleeve is fixed; in drive devices with a separate drive
for the eccentric shaft, the speed ratio is variable
within limits. The offset of the eccentric shaft in the
carrier sleeve can be 5 mm, for example, and the speed
ratio of the faster-rotating eccentric shaft to the more
slowly-rotating carrier sleeve can be in the order of
30:1, so that the working tools mounted on the tool
carrier strike the material or rock to be mined or worked
with a large number of radial impacts. The loosening or
mining performance achieved in the case of the tools with
impact superimposition of the kind in question is already
many times higher than in conventional drive devices
without impact superimposition.
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However, the considerable vibrations that are
introduced into the drive housing and tool housing, the
imbalance masses that are required in particular for
dynamic balancing, and the service life of the seals and
bearings for the eccentric shaft and the carrier sleeve,
continue to be problematical in eccentric-induced drive
devices with impact superimposition of the kind in
question.
The object of the invention is to make available a
drive device for rotating tools operating with impact
superimposition, in which the bearing and sealing of the
drive shaft and carrier sleeve are improved in order to
increase the service life of the drive devices and, in
particular, of the tools equipped with these.
This and further objects are achieved in
accordance with the invention in that the generating
device for the impact superimposition is an oscillation-
generating arrangement, which exhibits at least two
intermediate shafts for each tool carrier, which shafts
are connected in each case to the tool carrier via an
eccentric component part and are capable of being driven
in a synchronous fashion. In terms of their construction,
the drive devices in accordance with the invention exhibit
a fundamentally different design from that of the drive
devices of the kind in question with impact
superimposition. The impact induction, which is referred
to as oscillation in the invention in order to distinguish
it from the state of the art, no longer takes place by
CA 02550348 2006-06-16
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means of a single, eccentrically mounted and arranged
eccentric shaft, but by means of at least two intermediate
shafts, which are connected to the tool carrier in an
appropriate manner eccentrically via an eccentric
component part and are capable of being driven in a
synchronous fashion. Since at least two intermediate
shafts are assigned to the one tool carrier, or to each
tool carrier, these can have significantly smaller
dimensions than in the state of the art, as a consequence
of which the sealing of the shafts and the support of the
intermediate shafts in bearings are greatly simplified.
Also dispensed with at the same time is a carrier sleeve
of similar large dimensions, to which a counterweight of
correspondingly large dimensions had to be allocated in
the state of the art . This is no longer necessary, on the
other hand, in the construction in accordance with the
invention with a plurality of smaller intermediate shafts.
The drive device in accordance with the invention can thus
be used to drive tools which operate with oscillation
superimposition, which tools can be of a significantly
larger size and more versatile than in the state of the
art, but without the bearing or the shaft sealing of the
intermediate shafts, the carrier sleeve and/or the drive
shaft being problematical. A further advantage, in
accordance with the invention, is that the entire part on
the drive side is not subjected to the oscillations of the
tool carriers produced by the oscillation-generating
arrangements.
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In a particularly advantageous embodiment of the
invention, all the intermediate shafts are supported in
bearings concentrically to the axis of rotation of the
drive shaft in the carrier sleeve. In this construction,
therefore, not only the drive shaft is supported in
bearings concentrically to the carrier sleeve, but also
all the intermediate shafts are supported in bearings
concentrically to their common axis of rotation. The
plurality of intermediate shafts can then be distributed
in particular symmetrically, and can be arranged and
supported in bearings around the axis of rotation of the
drive shaft arranged on a peripheral circle. In this
construction, the driving of the drive shaft and the
driving of the carrier sleeve can take place in a
particularly simple manner, since both the carrier sleeve
and the drive shaft rotate concentrically about a common
axis of rotation.
In a further preferred embodiment of the drive
device, the intermediate shafts can be connected to the
drive shaft via a gear mechanism, and particularly
advantageously via a toothed gear mechanism. The use of a
toothed gear mechanism is made possible by the fact that
the axes of rotation of the intermediate shafts exhibit a
constant distance to the common axis of rotation of the
drive shaft and the carrier sleeve, regardless of their
instantaneous position.
In accordance with one advantageous embodiment,
the toothed gear mechanism can exhibit a central toothed
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wheel that is rigidly connected to the drive shaft and
planet wheels that are each rigidly connected to the
intermediate shafts and are in toothed engagement with the
central wheel. In an alternative embodiment, the toothed
gear mechanism can exhibit a central toothed wheel that is
rigidly attached to the drive shaft and planet wheels that
are each rigidly attached to the intermediate shafts, in
conjunction with which intermediate toothed wheels are
arranged additionally between the central toothed wheel
and the planet wheels, which intermediate toothed wheels
are supported in bearings in the carrier sleeve in such a
way that they are free to rotate. In the case of planet
wheels that are connected directly to the central toothed
wheel, relatively high speeds of rotation can be achieved
for the intermediate shafts, whereas in the construction
with intermediate toothed wheels, the speed of the
intermediate shafts can correspond essentially or
precisely to the speed of the drive shaft. The latter is
particularly advantageous if a balancing weight that is
rigidly connected to the drive shaft is allocated to an
individual tool carrier. It will be obvious in this case
to a person skilled in the art that the multiplication
ratio or the reduction ratio depends on the constructive
layout of the individual toothed wheels.
A further major advantage of the solution in
accordance with the invention is that the eccentricity is
formed directly between the tool carrier and the
intermediate shafts and is achieved by means of the
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eccentric component parts. In an embodiment in accordance
with the invention, the eccentric component parts can be
constituent parts of the intermediate shafts and can be
constituted by an eccentric pin arranged eccentrically to
the central axis of the intermediate shaft. One-piece
intermediate shafts, on which the eccentric pin is
integrally formed, are provided in this embodiment,
therefore. In an alternative construction, the eccentric
component parts can be shaft prolongations arranged
eccentrically to the central axis of the intermediate
shaft, which are attached to the intermediate shaft in a
detachable fashion. In the construction with detachable
shaft prolongations, it is particularly advantageous if
the intermediate shafts and the shaft prolongations are
connected via a conical taper prolongation, which engages
in a conical depression in the second part. Since the
intermediate shafts normally exhibit a greater diameter
than the shaft prolongations, the depression can
preferably be executed in the intermediate shaft. The
reverse arrangement is also possible, however. It is then
particularly advantageous if the rigid connection between
the taper prolongation and the depression is secured by
means of a securing means.
As a further alternative, instead of intermediate
shafts with eccentric shaft prolongations, intermediate
shafts with concentric shaft pins can also be used, in
conjunction with which the eccentric component parts are
then formed by means of sleeves with an eccentric shaft
CA 02550348 2006-06-16
seat. The shaft pins in this case engage in the shaft
seats, whereby the eccentric arrangement between the
intermediate shafts and the tool carriers is formed. In
this case, too, it is advantageous if the shaft seat and
the shaft pin are of conical execution and engage rigidly
into one another, in conjunction with which the rigid
connection is preferably secured with the help of a
securing means. A connection with conical parts
facilitates the dismantling of the one or mote tool
carriers from the component part on the drive side, which
comprises the carrier sleeve, the drive shaft and the
bearing for the intermediate shafts. As an alternative to
screwed connections as a securing means, the rigid
connection between the conical parts can also consist of
an oil press fit connection or a press fit that can be
released by subjecting it to pressure with hydraulic
means. Assembly is then effected by means of a pressing-on
process, in conjunction with which oil or some other
hydraulic means is forced into the joint gap between the
conical parts in order to dilate the external part for
assembly. The necessary pressing force can be achieved
with a multiplier or a hydraulic press, for example. It
goes without saying that dilation of the outer conical
part by means of the hydraulic means must also take place
for the purposes of dismantling.
One pivot bearing and, in the case of tool
carriers with larger dimensions or depths, two or more
pivot bearings, is/are appropriately arranged in each case
CA 02550348 2006-06-16
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between the eccentric component part and the tool carrier.
Only these pivot bearings are required to handle the
eccentric rotation of the shaft prolongations or the shaft
pins on the intermediate shafts. However, since the
dimensions of the sleeves, the shaft pins or the shaft
prolongations are relatively small because of the
plurality of intermediate shafts, the service life of the
bearings and the shaft seals presents no problems in spite
of the eccentricity.
The drive device or a tool with the drive device
can be executed in numerous different ways. According to
one preferred embodiment, the drive device or the tool
exhibits a plurality of tool carriers, in conjunction with
which at least two intermediate shafts are connected to
each tool carrier. In one embodiment with a plurality of
tool carriers, it is particularly advantageous if the
vibration produced by the oscillation-generating
arrangement for the first tool carrier is out-of-phase in
relation to the one or more vibrations produced by the one
or more additional oscillation-generating arrangements. In
this embodiment, therefore, it is possible for the dynamic
balancing of a tool carrier to take place exclusively via
a phase-displaced oscillation of at least one additional
tool carrier.
According to a particularly advantageous
embodiment, an even number of tool carriers can be
provided, in conjunction with which in each case the
mutually opposing tool carriers are superimposed with an
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oscillation impulse having a phase displaced by 180°
through the arrangement of the eccentric component parts
of the intermediate shafts of the associated oscillation-
generating arrangements. In the case of two tool carriers,
for example, these tool carriers are superimposed with an
oscillation impulse having a phase displaced by 180°, and
the oscillation impulse is directed either to the outside
or to the inside at a set time, for example in the case of
both tool carriers. Two pairs are produced in each case,
for example, in the case of four tool carriers, in
conjunction with which, within one pair, two tool carriers
are superimposed with an oscillation impulse having a
phase displaced by 180° and, particularly advantageously,
a phase displacement of 90 ° exists between the pairs . All
four tool carriers can be arranged in a single plane in
this case. According to a second advantageous embodiment,
three tool carriers are provided, in conjunction with
which the individual tool carriers are superimposed with
an oscillation impulse having a phase displaced by 120°,
through the arrangement of the eccentric component parts
of the intermediate shafts of the associated oscillation-
generating arrangements. In this case, too, the dynamic
balancing takes place exclusively through the phase-
displaced superimposition of the oscillation impulses of
the three other tool carriers, without the need for
additional balance weights.
According to a further, alternative embodiment,
two tool carriers arranged in different planes can be
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provided, which are superimposed with an oscillation
impulse having a phase displaced by 180° through the
arrangement of the eccentric component parts of the
intermediate shafts of the associated oscillation-
s generating arrangements. The embodiment with tool carriers
arranged in different planes has the advantage, to the
extent that the working tools attached to it also lie in
different planes, that the pressing forces, which are
applied by a feed drive mechanism, for example, are
further reduced, since the individual tool carriers ire
not in simultaneous engagement with the rock to be
excavated at any time. Especially in the case of the last-
mentioned embodiment, it is particularly advantageous if
three intermediate shafts are allocated to each tool
carrier, which shafts are distributed alternately around
the periphery. In order to permit the arrangement in two
different planes, the associated tool carriers can be of a
spade-shaped, propeller-shaped or star-shaped execution in
particular. An arrangement with three intermediate shafts
can also be effected, however, in the case of drive
devices and tools with only two tool carriers, or even
with only a single tool carrier, and/or in the case of
spade-shaped or propeller-shaped tool carriers, the
location areas for the working tools can also be executed
on the tool carriers by means of interleaving or off-
setting in such a way that the working tools lie and act
in a single plane.
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In an embodiment in accordance with the invention
with only a single tool carrier, this can also be driven
with a higher number, for example six, of synchronously
rotating intermediate shafts. In the embodiment with only
a single tool carrier, there is then actually a
requirement for a balance weight, which preferably rotates
in the same direction about the drive axis of the drive
shaft with a phase displacement of 180° in relation to the
oscillation impulse generated by means of the eccentric
components of all the intermediate shafts.
The tools can be attached directly to the tool
carrier. It is particularly advantageous, however, if
single-component or multiple-component tool holders in the
form of an annular segment are attached to each tool
carrier with attachment devices for a plurality of working
tools. The drive device in accordance with the invention
can be used for boring, cutting or the excavation of rock
and minerals. The working tools used can consist in
particular of self-sharpening round chisel bits, flat
chisel bits, discs or cross roller bits. It is also
advantageous if the carrier sleeve is driven during
operation at a considerably slower speed than the
intermediate shafts, in conjunction with which the speed
ratio preferably lies between the speed NZ of the
intermediate shafts and the speed NT of the carrier sleeves
>22 and in particular between 25:1 and about 31:1,
depending on the nature of the rock to be excavated and
the number of working tools, etc. The carrier sleeves can
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preferably also be driven with a carrier sleeve drive, and
the intermediate shafts with an intermediate shaft drive
allocated to the drive shaft, and a feed speed for the
drive device is adjustable via a feed drive mechanism, in
conjunction with which a control device controls the
carrier sleeve drive and the feed drive depending on the
intermediate shaft drive and thus on the drive for the
drive shaft. The connection between the intermediate shaft
drive and the carrier sleeve drive can also be effected by
means of a gear mechanism with a fixed multiplication
ratio.
Further advantages and embodiments of the
invention can be appreciated from the following
description of illustrative embodiments represented
schematically in the drawing of drive devices in
accordance with the invention and of tools on which
impacts are superimposed having drive devices in
accordance with the invention. In the drawing:
Fig. 1 is a schematic representation as a side
view of a drive device in accordance with
the invention equipped with working tools;
Fig. 2 is a view from the front of the tool
carrier illustrated in Fig. 1 equipped with
working tools;
Fig. 3 is a vertical section through a drive
device in accordance with the invention
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according to a first illustrative
embodiment;
Fig. 4 is a view from the front of the tool
carrier of the drive device illustrated in
Fig. 3;
Fig. 5 is a drive device in accordance with the
invention according to a second
illustrative embodiment shown in a vertical
section according to Fig. 3;
Figs. 6A 6D illustrate schematically the sequence of
-
the movements of the tool carriers in a
drive device according to a third
illustrative embodiment;
Figs. 7A - 7D illustrate schematically the sequence of
the movements of the tool carriers in a
drive device according to a fourth
illustrative embodiment;
Figs. 8A - 8D illustrate schematically the sequence of
the movements of the tool carriers in a
drive device according to a fifth
illustrative embodiment;
Fig. 9 illustrates a drive device according to a
sixth illustrative embodiment as a front
view of the tool carriers;
Fig. 10 illustrates a drive device according to a
seventh illustrative embodiment as a front
view of the tool carriers;
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Fig. 11 illustrates a drive device according to an
eighth illustrative embodiment as a
vertical section; and
Fig. 12 illustrates a view of the tool carriers in
the drive device shown in Fig. 11.
Represented in Figs. 1 and 2 is only a single
drive device 10 for producing or causing the impact
superimposition of a tool operating with impact
superimposition and generally designated by the reference
designation 1, which exhibits a drive housing 11, a drive
shaft 13 capable of being driven via a toothed wheel 12, a
carrier sleeve (15, Fig. 3) capable of being driven via a
toothed wheel 14 and mounted rotatably inside the drive
housing 11, shown here together with two tool carriers
16A, 16B in the form of half discs. The drives connected
to the toothed wheels 12, 14 and other component parts of
the tool are not illustrated. Detachably attached to each
tool carrier is a semi-annular-shaped tool holder 17A,
17B, which are equipped here in each case with six round
shaft chisel bits 3 as working tools arranged in tool
holding fixtures 2. The two tool holders 17A, 17B are
executed in the form of annular segments, lie against the
edges of the tool carriers 16A, 16B with positive
engagement, and are detachably attached there by means of
screwed connections 4. When the tool 1 is being used at a
working face 5 with rock to be excavated, in particular
hard rock, the tips of the chisel bits of the working
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tools 3 are in engagement and remove lumps of material at
the working face 5 as the tool 1 is caused to advance in
the direction of the arrow V in Fig. 1. During operation,
the toothed wheel 14 that is connected to the carrier
sleeve in such a way as to be incapable of rotation is
driven via the carrier sleeve drive, not illustrated here,
as a consequence of which the tool carriers 16A, 16B are
jointly caused to rotate in the direction of the arrow R
in Fig. 2. In addition to the rotation in the direction of
the arrow R, the two tool holders 16A, 16B move
eccentrically about axes of rotation of intermediate
shafts, which, as will be explained below, are driven by
means of the drive shaft 13 and an intermediate shaft
drive attached to the toothed wheel 12, as a consequence
of which the working tools 3 are also subjected to an
impact pulse in addition to the rotation, which impact
pulse significantly improves the removal of the rock at
the working face 5, as is already familiar for tools
operating with impact superimposition. The intermediate
shafts, by means of which the tool carriers 16A, 16B are
subjected to the impact superimposition, referred to below
as oscillation superimposition, are accessible in each
case from the front side of the tool 1 or the tool carrier
16A, 16B via hatch covers 6. In the illustrative
embodiment according to Figs. 1 to 4, three intermediate
shafts are thus provided in each case for each tool
carrier 16A, 16B.
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The construction of the drive device 10 is now
explained with reference to Figs. 3 and 4, which show a
first illustrative embodiment of the drive device 10 in
accordance with the invention. Fig. 3 shows a sectioned
view of the carrier sleeve 15 mounted rotatably on the
inside of the housing 11 via the bearings 18 and the drive
shaft 13 mounted in turn via bearings 19 in a centric
sleeve bore of the carrier sleeve 15. The drive housing 11
is provided with screw seats 7, so that the entire drive
device can be removed as a compact unit from the frame or
the housing of a tool. Unlike the tools operating with
impact superimposition and the drive devices that are
familiar from the state of the art, in the drive device 10
in accordance with the invention both the drive shaft 13
and the carrier sleeve 15 exhibit the identical axis of
rotation, designated with D, and the carrier sleeve 15 and
the drive shaft 13 therefore rotate relative to one
another without eccentricity.
The carrier sleeve 15 broadens out at one end into
a carrier sleeve head 15A, to the front side of which a
sealing disc 20 is attached, which also carries the front
bearing 19 for the drive shaft 13. Both the head 15A and
the sealing disc 20 are each provided in this case with a
total of six seats 21 for intermediate shafts 30, to which
the tool carriers 16A and 16B are attached in each case
via an eccentric component part 32. In the illustrative
embodiment according to Fig. 3, the eccentric component
part consists of a shaft prolongation 32 executed
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integrally on the intermediate shaft 30, the central axis
33 of which prolongation is arranged eccentrically to the
shaft axis 31 of the intermediate shafts 30. All the
intermediate shafts 30 are supported by the shaft bearings
22 in the seats 21 in the carrier sleeve 15 and the
sealing disc 20 in such a way that their shaft axes 31 are
arranged concentrically around the rotating shaft D. Each
intermediate shaft 30 is rigidly attached to a toothed
wheel 34, which is in toothed engagement with a central
toothed wheel 23, which is rigidly attached to the drive
shaft 13. The toothed wheels 34 allocated to the
intermediate shafts 30 thus form planet wheels, which are
driven simultaneously and synchronously by means of the
central toothed wheel 23, so that all the intermediate
shafts 30 rotate synchronously. The eccentric component
parts 32 on the intermediate shafts 30 are arranged in
such a way that all the intermediate shafts allocated to a
tool carrier 16A and 16B rotate with the same
eccentricity. This can be appreciated particularly clearly
from Fig. 4, in which each of the eccentric component
parts 32 of the three intermediate shafts that are
allocated to the tool carrier 16A are displaced downwards
in the same direction and with the same eccentricity in
relation to the shaft axis 31 of the intermediate shafts,
whereas the eccentric component parts 21 of the
intermediate shafts connected to the tool carrier 16B lie
displaced upwards in the indicated oscillation position of
the tool carriers 16A, 16B. The intermediate shafts in
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this case each rotate at the same speed in relation to one
another in the direction of the arrow Z in Fig. 4, in
conjunction with which the speed of the intermediate
shafts 30 and the eccentric component parts depends on the
drive speed of the drive shaft 13 and the multiplication
ratio of the toothed gear mechanism formed by the central
wheel 23 and the planet wheels 34. In the illustrative
embodiment with the two tool carriers 16A, 16B, the
eccentric component parts 32 are arranged in relation to
the associated intermediate shafts 30 in such a way that
an oscillation is produced in the tool carrier 16B having
a phase displacement of 180° in relation to that of the
tool carrier 16A. This has the particular advantage that
one of the tool carriers 16A in each case forms the
balance weight for the dynamic balancing of the movement
of the other tool carrier 16B. There is accordingly no
need for an additional balance weight.
In the drive device 10 in accordance with the
invention, neither the shaft seals 24 between the drive
housing 11 and the carrier sleeve 15 nor the shaft seals
on the seats 21 in the sealing disc 20, nor the shaft
seals 26 between the eccentric component parts 32 and the
tool carriers 16A, 16H are subjected to eccentric
movements. Every tool carrier 16A, 16B is rotatably
25 connected to the intermediate shafts 30 by means of a
plurality of, in this case three, eccentric component
parts 32 and associated bearings 35 for the eccentric
component parts, so that the bearings 18, 22 and 35 are
CA 02550348 2006-06-16
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also not exposed to any excessive impact loadings, which
are produced with the oscillation superimposition in the
drive device l0.
Fig. 5 shows a second illustrative embodiment of a
drive device 110 in accordance with the invention.
Structurally and functionally identical components to
those in the first illustrative embodiment are provided
with identical reference designations, and a carrier
sleeve 15 and a drive shaft 13 are also supported
concentrically in bearings about the axis of rotation D in
a drive housing 11 in drive device 110. On the other hand,
in the drive device 110, two tool carriers 116A, 116B are
connected to intermediate shafts 130 via an eccentric
component part in such a way that an oscillation-
generating arrangement for each tool carrier 116A, 116B is
formed with the intermediate shafts 130. Both of the half-
disc-shaped tool carriers 116A, 116B lying in a single
plane are connected in each case to the eccentric
component parts 132 of three intermediate shafts 130, and
the intermediate shafts 130 of every tool carrier 116A,
116B are synchronously driven. The rotating drive for the
intermediate shafts 130, on the other hand, consists of a
central toothed wheel 23 rigidly connected to the drive
shaft 13 and planet wheels 34 rigidly connected to the
intermediate shafts 130. Unlike the first illustrative
embodiment, however, the intermediate shafts 130 exhibit a
shaft pin 132 executed concentrically to the shaft axis
131 and projecting into a bearing seat 137 in the tool
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carriers 116A, 116B, which pin is executed as cone and is
attached to one sleeve 140 with eccentrically arranged
shaft seats 141. The central axis 143 of the sleeves 140,
which corresponds to the central axis of the bearings 135,
is indicated schematically in Fig. 5. Because of the
bearings 135 arranged between the sleeves 140 and the tool
carriers 116A and 116B, as in the first illustrative
embodiment, the tool carriers 116A and 116B in each case
can still move additionally to the rotation of the carrier
sleeve 15 about the axes 131 of the intermediate shafts
130 in an oscillation movement, as a consequence of which,
on the other hand, a tool equipped with the drive device
IIO receives an impact superimposition or an oscillation
superimposition for the working tools. The shaft seat 141
in the sleeve 140 is adapted to the shaft pins 143, which
are also conical, in order to be able to separate the
sleeve 140 and the intermediate shaft 130 easily from one
another. The eccentric component parts, that is to say the
sleeves 140 in this case, are also arranged in such a way
in the drive device 110 that all of the sleeves 140
allocated to the tool carrier 116A and all of the sleeves
140 allocated to the tool carrier 116B together exhibit an
eccentric displacement in the same direction and of the
same order of magnitude, although at the same time the
tool carrier 116A relative to the tool carrier 116B
receives an oscillation superimposition having a phase
displaced through 180°, so that dynamic balancing of the
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drive device 110 by means of additional balance weights is
not necessary.
The arrangement of the tool carriers 216A, 216B
and the arrangement of the eccentric component parts 232
of the intermediate shafts are represented schematically
in Figs. 6A-6D for a drive device 210 according to a third
illustrative embodiment, in conjunction with which the
individual representations A to D in each case illustrate
the relative position of the tool carriers after a
rotation of the intermediate shafts through 90°, but
without taking into account the simultaneously occurring
rotation of the sleeve carrier, and thus both tool
carriers, about the axis of rotation D. The drive device
210, on the other hand, is provided with two semi-disc-
shaped tool carriers 216A, 216B, in conjunction with
which, however, only two intermediate shafts with
eccentric component parts 232 are allocated to each tool
carrier 216A and 216B. The axes of rotation 231 of the
intermediate shafts 230 and the axis of rotation D of the
carrier sleeve and the drive shaft are also represented in
Fig. 6A. Through the oscillation-generating arrangements
actuated by means of the eccentric component parts 232 and
the intermediate shafts, the tool carriers 216A, 216B each
experience an impulse I having a phase displaced through
180°, in conjunction with which this rotational impulse I
for the one tool carrier 216A is out-of-phase on each
occasion by 180° in relation to the impulse I for the
other tool carrier 216B, as a consequence of which the two
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tool carriers 216A, 216B are dynamically balanced in
relation to one another, as clearly illustrated by the
sequence over Figs. 6B, 6C and 6D, because the
intermediate shafts in each case have continued to rotate
through 90° between the individual representations. All of
the intermediate shafts rotate in the same direction, as
indicated by the arrows in each case.
In the case of the illustrative embodiment of a
fourth drive device 310 in accordance with the invention
in Figs. 7A to 7D, a total of four tool carriers 316A,
316B, 316C, 316D in the form of quarter-disc segments are
connected to the eccentric component parts 332 of two
intermediate shafts in each case. The mutually opposing
tool carriers 316A and 316C and 316B, 316D in each case
form a pair and are activated with an oscillation that is
out-of-phase by 180°, so that the pair of tool carriers
316A, 316C and 316D, 316B in each case is dynamically
balanced in relation to one another. In addition, in the
illustrative embodiment shown here, a further phase
displacement of 90° is provided between the pairs, as
illustrated in each case by the different positions of the
eccentric component parts 232 relative to the shaft axes
331 of the intermediate shafts. The individual Figures in
turn illustrate a movement sequence over a 360° rotation
of the intermediate shafts, in conjunction with which each
view shows a position for the situation of the tool
carriers that is displaced through 90° in relation to the
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previous view, and the rotation of the carrier sleeve
about the axis of rotation D is not taken into account.
In the case of the fifth illustrative embodiment
of a drive device 410 shown in Figs. 8A-8D, this
illustrates three tool carriers 416A, 4168, 416C in the
form of disc segments, to which two intermediate shafts
for the oscillation superimposition rotating
concentrically about the axis of rotation D are allocated
in each case. The eccentric component parts 432 of the
intermediate shafts of the tool carrier 416A are arranged
in each case out-of-phase by 120° or rotated in relation
to the eccentric component parts 432 of the intermediate
shafts of the tool carriers 416B and 416C, so that each
tool carrier 416A receives an oscillation superimposition
having a phase displacement of 120° in relation to the two
other tool carriers 416C, 416D. In this case, too, the
phase displacement causes the three tool carriers 416A,
4168 and 416C lying in a single plane to be dynamically
balanced in relation to one another in respect of their
impact impulse.
Fig. 9 shows a sixth illustrative embodiment of a
drive device 510 in accordance with the invention with two
tool carriers 516A and 5168, in conjunction with which the
tool carrier 5168 is arranged in a plane behind the tool
carrier 516A. Three intermediate shafts with eccentric
component parts 532 are allocated in each case to each
tool carrier 516A, 5168, and the tool carrier 516A is
superimposed with an oscillation impulse, which has a
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phase displacement of 180° in relation to the oscillation
impulse for the tool carrier 516B. Both tool carriers
516A, 516B have a more or less spade-shaped contour, and
in each case an intermediate shaft allocated to the tool
carrier 516B is arranged between two intermediate shafts
that are allocated to the tool carrier 516A. The pressing
forces can be minimized during operation through the tool
carriers 516A and 516B that are present in different
planes, since the individual tool carriers 516A, 516B are
never in engagement with the rock to be excavated in the
same plane at the same time, but always attack the rock
alternately and in different planes and loosen material
there.
In the case of the seventh illustrative embodiment
of a drive device 610 in Fig. 10, on the other hand, two
tool carriers 616A, 616B are set in rotation and are
activated with oscillation superimposition. The tool
carriers can be executed essentially in the form of plates
and can be arranged with their central areas lying behind
one another, so that they and the working tools that are
capable of being attached to them lie in different planes.
However, the tool carriers 616A, 616B are preferably
provided with corresponding and appropriate interleaving,
so that the areas of both tool carriers 616A, 616B which
accept the working tools lie in a single plane and only
the central areas of both tool carriers are arranged in
planes lying one behind the other. The interleaving can be
achieved, for example, with forward-projecting off-sets on
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the rear tool carrier 616B and in addition, where
appropriate, with rearward-displaced off-sets on the front
tool carrier. Here, too, the intermediate shafts for one
tool carrier 616A are adjacent in each case to two
intermediate shafts for the other tool carrier 616B, and
the eccentric components 632 of the individual
intermediate shafts are arranged in such a way that the
two tool carriers 616A, 616B that are out-of-phase by 180°
in relation to one another are superimposed with the
IO impact impulse. Both tool carriers 616A, 616B have an
essentially star-shaped or propeller-shaped contour, and a
partially annular segment-shaped tool holder can be
attached to the screw attachments 651 on each tool carrier
616A, 616B. Every tool carrier 616A, 616B is connected to
three intermediate shafts in each case. The ends of the
individual struts of the propeller-shaped or star-shaped
tool carriers can then be provided with the off-set.
Figs. 11 and 12 show an eighth illustrative
embodiment of a drive device 710 in accordance with the
invention as a view corresponding to Figs. 3 and 4. A
drive shaft 713 and a carrier sleeve 715 are rotatably
supported about the same axis of rotation D in a drive
housing 711. The head 715A of the carrier sleeve 715 is of
a more solid execution than in the first illustrative
embodiment, and intermediate wheels 738 are supported
between the head 715A and the sealing disc 720 in addition
to a central toothed wheel 723 represented here with
relatively small dimensions and rigidly connected to the
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drive shaft 713 and the planet wheels 734 rigidly attached
to the intermediate shafts 730. A toothed gear mechanism
with a reduction ratio of 1:1 between the drive shaft 713
and the intermediate shafts 730 is achieved with the
toothed wheels 734, 738 and 723. All of the intermediate
shafts 730 exhibit an eccentric component part here, which
consists of a shaft prolongation 732 arranged
eccentrically to the shaft axis 731 of the intermediate
shafts 730, which exhibits a conical pin projection 742,
which is inserted into a similarly conical depression 743
in the intermediate shafts 730. The projection 742 and the
depression 743 are secured by means of a screw locking
means, which can be released from the front side of the
tool carrier 716 after removing the hatch covers 706. In
this way, the entire tool carrier 716 can be pulled away
from the drive housing 711 towards the front. It becomes
clear, in particular when considered together with Fig.
12, that the drive device 710 exhibits only a single tool
carrier 716, on which the impact impulse is superimposed
with a total of six intermediate shafts. A balance weight
760 is rigidly connected to the drive shaft 713 for the
purpose of balancing any dynamic imbalance, which weight
is arranged out-of-phase by 180° in relation to the
arrangement and to the eccentric offset of the eccentric
component parts and runs out-of-phase by 180° in the same
direction because of the reduction ratio of the toothed
gear mechanism, so that the balance weight 716
counterbalances the impact movement of the tool carrier
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716. The balance weight 760 in this case rotates in a
central recess 739 on the internal periphery of the tool
carrier 716.
Numerous modifications, which should fall within
the scope of the protection afforded by the dependent
claims, will be evident from the foregoing description to
a person skilled in the art. In the case of tools and
drive devices with larger dimensions, three or more
intermediate shafts can also be allocated to every tool
carrier. This embodiment also retains in full the
particular advantage that the intermediate shafts with the
eccentric component parts possess significantly smaller
dimensions than in drive devices with eccentrically broad
carrier sleeves. The possibility of connecting the drives
for the drive shafts and the drives for the carrier sleeve
directly to one another via a suitable gear arrangement is
not represented. Also not represented is the ability to
regulate the speed of the intermediate shaft drive, the
speed of the carrier sleeve drive and the rate of feed for
the tool as a whole in a way in which they are matched to
one another and in particular with reference to the speed
of the intermediate shaft drive, via a superior control
device. The eccentric offset can be 7.5 mm, for example,
for a speed of rotation of the carrier sleeve of 100-150
revolutions/min, and for an impact superimposition or
oscillation of around 3200/min, so that a speed ratio NZ
for the intermediate shafts and NT for the carrier sleeve
in the order of 20:1 to 35:1 can be obtained. The
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detachable attachment between the eccentric component
parts and the intermediate shafts can also be effected by
means of an oil press fit connection. For example, eight
working tools with an angular offset of 45° in relation to
one another can be attached to the tool carriers.
Torsionally elastic couplings can be installed between the
drive shaft and/or the carrier sleeve and their drives,
for example consisting of electric motors, which couplings
can be equipped additionally with an overload function in
order to prevent damage to the drive devices or the drives
in the event of blockages. The working tools, such as
round chisel bits, discs, flat chisel bits and the like
can also be attached directly to the tool carrier. The gap
between the segment-shaped tool carriers can be covered
with plates and the like.
