Note: Descriptions are shown in the official language in which they were submitted.
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Description
Barrel motor
Field of the invention
The invention relates to a barrel motor drive unit, to a barrel motor and to a
drift
conveyer having a barrel motor such as this.
Background to the invention and prior art
Various conveyer installations exist on which material being conveyed is
transported on conveyer rollers. Some of the conveyer rollers such as these
are
driven.
Driven conveyer rollers such as these are described, for example, in US
6,402,653
B1 and EP 0 752 970 Bl.
In general, conveyer rollers such as these have a continuous axle which
comprises
one or more parts and extends beyond the conveyer rollers at their ends. The
conveyer rollers are mounted in the conveyer installation via the ends of an
axle
such as this.
Drives which are contained in such conveyor rollers are in general arranged
concentrically about an axle such as this, that is to say the axle passes
through the
drive from one end to the other end. The known driven conveyer rollers
generally
have an element by means of which the drive force from the drive unit is
transmitted circumferentially to the rotatable tube of the conveyer roller on
which
the material being conveyed runs.
In some cases, conveyer rollers such as these have a transmission which must
be
lubricated during operation. In order to ensure such lubrication, the interior
of a
conveyor roller such as this is filled, for example, with oil up to a specific
height.
Object
One object of the invention is to provide a drift conveyor having a barrel
motor, a
barrel motor such as this and a barrel motor drive unit for a barrel motor
such as
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this, which can be produced easily and cheaply, and which can be maintained
easily and at low cost during operation.
Achievement of the object
The object is achieved by the apparatuses and the method as claimed in the
independent claims. Advantageous embodiments are disclosed in the dependent
claims.
One aspect of the invention relates to a barrel motor comprising a barrel
casing, a
barrel motor drive unit, a first mounting element and a second mounting
element
for mounting the barrel motor in a conveyer frame, wherein the barrel casing
is
rotatably supported about a barrel axis at least relative to the first
mounting
element, wherein the barrel motor drive unit comprises an electric motor
having a
stator and a rotor, and is arranged within the barrel casing, wherein the
stator of the
electric motor is connected to the first mounting element in a torque-proof
manner,
wherein the rotor of the electric motor is connected to the barrel casing via
an
output drive element, such that the barrel casing can be driven via the output
drive
element at least relative to the first mounting element such that it can
rotate about
the barrel axis, wherein the output drive element is arranged on the same side
of
the barrel motor drive unit as the first mounting element, with respect to the
barrel
axis, and wherein the rotation axis of the output drive element is not
identical to
the rotation axis of the rotor. This design has the advantage that all the
parts of the
barrel motor drive unit which have to transmit a torque can be arranged on one
side
of the barrel motor drive unit and that the output drive element need not rest
circumferentially on the inner wall of the barrel casing but can specifically
transmit
a drive force to individual points on the barrel casing. This may be
advantageous,
for example, when a tooth system is provided between the barrel casing and the
drive unit. Furthermore, a barrel motor such as this is simple to install,
since the
barrel motor drive unit can be introduced into the barrel casing from one side
of the
barrel casing such that, for example, the other side of the barrel motor can
be
provided in an already completely assembled form. For the purposes of this
claim,
the expression "in a torque-proof manner" means that a torque can be
transmitted
via a torque-proof connection such as this in which the elements cannot rotate
with
respect to one another, and in which case the parts which are connected to one
another essentially do not rotate with respect to one another. However, the
expression is also intended to cover connections which, for example, have
damping
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elements which allow the parts which are connected to one another to rotate
through a few degrees.
A further advantageous embodiment relates to a barrel motor in which the
rotation
axis of the output drive element is not identical to the barrel axis. A barrel
motor
such as this has essentially the same advantages as the abovementioned barrel
motor. Depending on the configuration of the barrel motor, it may be possible
for
the barrel axis not to correspond to the rotation axis of the rotor.
Furthermore, in one preferred embodiment of the barrel motor, the output drive
element is a pinion which engages with an internal tooth system which is
provided
on the internal circumference of the barrel casing in a torque-proof manner.
This
has the advantage that higher drive forces can be transmitted via a tooth
system
than is the case with friction-locking connections. Furthermore, a tooth
system can
be arranged in a more space-saving manner, and is easier to assemble.
Furthermore, a barrel motor such as this preferably has a design in which a
first
roller bearing and/or a first fluid seal are/is provided between the barrel
casing and
the first mounting element. Preferred fluid seals are slide ring seals or
shaft sealing
rings which are available, for example, under the Simrit trademark.
Further advantageous aspects of an embodiment such as this may lie in a barrel
motor in which the external radius of the first roller bearing and/or the
external
radius of the first fluid seal are/is essentially equal to or greater than a
radius which
extends from the barrel axis to the rotation axis of the output drive element,
and/or
is equal to or greater than the radius of the root circle of the internal
tooth system,
which is provided on the internal circumference of the barrel casing in a
torque-
proof manner. One advantage of this design is that roller bearings having a
relatively large diameter can also absorb more load, as a result of which
heavier
loads can be transported on a barrel motor such as this, and/or that a barrel
motor
such as this can also be used in conjunction with a belt, since bearings
designed in
this way can also absorb a belt stress. It should also be noted that, when
roller
bearings are chosen in this way, the internal diameter is also relatively
large. The
first mounting element in the case of an embodiment which is designed
advantageously in this way therefore preferably has a relatively large
external
diameter which corresponds to the internal diameter of a roller bearing such
as this.
A relatively large diameter such as this of the first mounting element makes
it
possible to provide different functional elements in the radial cross section
of the
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mounting element, for example cables with relatively large cross sections,
more
cables than normal, specifically for example for open-loop and closed-loop
control
of additional functions (for example brakes, rotation sensors etc.), plug
sockets for
connection, which are preferably sealed, oil filling holes, threaded holes for
mounting the mounting element on an adjacent frame of a drift conveyer. It is
also
possible for a first mounting element such as this to be designed such that it
ends
essentially flush with the axial rim of the barrel casing, or projects only
slightly
beyond the axial rim of the barrel casing. This allows the barrel motor to
have a
compact form. The installed length of the barrel motor can thus be reduced to
a
minimum. The barrel motor can be fitted in a sheet-metal conveyer frame using
standard parts by means of the threaded holes, which can be incorporated
easily.
This preferred embodiment ensures optimized assembly and dismantling in the
conveyer, and there is no restriction to the connection options.
A barrel motor such as this is preferable, in which the first roller bearing
has an
external diameter which is essentially equal to or greater than the diameter
of the
barrel motor drive unit. The advantage in this case is that the barrel motor
drive
unit can be pushed into the barrel casing with the roller bearing and/or the
fluid
seal removed. In this context, it is likewise preferable for the crown circle
of the
tooth system therefore to have a diameter, which is formed by the uppermost
peaks
of the internal tooth system, which is likewise equal to or greater than the
external
diameter of the barrel drive unit. In another preferred embodiment, the barrel
motor drive unit has an external diameter which is slightly smaller than the
internal
diameter of the barrel casing in the area in which the barrel motor drive unit
is
arranged in the barrel casing when in the assembled state. The external
diameter of
the barrel motor drive unit is preferably about one to two millimeters less
than the
internal diameter of the barrel casing. In this design, the internal area in
the barrel
casing could be optimally utilized, thus making it possible to use a barrel
motor
drive unit of maximum power. In this case, a first bearing unit, which
comprises
the internal tooth system, the first roller bearing and the first fluid seal,
could be
installed together with the barrel motor drive unit.
A barrel motor such as this preferably has a design in which an axle element
which
is essentially concentric with the barrel axis is provided between the barrel
motor
drive unit and the mounting element and fixes the stator of the electric motor
by
means of the mounting element in a blind hole of the mounting element in a
torque-proof manner. A concentric axle element such as this is preferably
formed
like a pin and/or to be cylindrical, and preferably has a diameter which is
equal to
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or less than the difference between the length of a radius from the barrel
axis to the
rotation axis of the output drive element and the radius of the output drive
element,
that is to say in the case of a pinion its crown circle. A design such as this
allows
the concentric axle element and the output drive element to be provided
alongside
one another without the rotating output drive element sliding on the axle
element.
A cylindrical axle element such as this can easily be fixed in or connected in
the
blind hole of the first mounting element. A torque-proof connection can be
provided via any desired shaft-hub connections, preferably for example via an
adjusting spring.
A further advantageous embodiment relates to a barrel motor in which a cable
opening, in particular for the electrical supply for the electric motor,
and/or a plug
socket and/or an oil filling opening are/is provided in the mounting element.
A
design such as this has the advantage that a barrel motor such as this can
easily be
assembled and maintained since not only is it possible to easily produce a
plug
connection, but the accessibility to the oil filling opening is also ensured.
In a further preferred embodiment of the barrel motor, the barrel drive unit
and the
barrel casing are supported via a first bearing and a center bearing such that
they
can rotate with respect to one another and cannot tilt with respect to one
another,
wherein the center bearing is at a distance from the first bearing in the
direction of
the barrel axis, wherein, viewed from the first bearing in the direction of
the barrel
axis, a second bearing is provided behind the center bearing, via which second
bearing the barrel casing is rotatably supported with respect to a conveyer
frame,
which is adjacent to the barrel motor, wherein the barrel drive unit is
supported
with respect to the barrel casing independently of the second bearing. A
bearing
such as this has the advantage that there is no need to provide an axle which
extends from one end of the barrel motor to the other end and bears the barrel
motor drive unit within the barrel casing. Furthermore, this design has the
advantage that slight bending of the barrel casing under load does not lead to
tilting
of the barrel motor drive unit with respect to the barrel casing. A further
advantage
is that center bearing such as this leads to the barrel casing being
reinforced and
made robust.
Furthermore, a barrel motor such as this preferably has a design in which the
first
bearing comprises the first roller bearing. A design such as this renders an
additional bearing superfluous.
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Further advantageous aspects of an embodiment such as this may lie in a barrel
motor in which the second bearing comprises a second roller bearing in the
area of
the second mounting element.
A barrel motor such as this in which a center seal is provided between the
first
fluid seal and the second bearing such that a fluid-tight space, which
accommodates at least a portion of the barrel motor drive unit, is formed
between
the first seal and the second bearing in the interior of the barrel motor is
preferred.
This design results in an advantageous configuration in which different barrel
motors with different barrel casing lengths have a fluid-tight space on sides
of the
barrel motor drive unit, which area is essentially of the same size in all the
different barrel motors. If oil lubrication is required in a barrel motor such
as this,
this would ensure that the same amount of oil would be required to fill the
fluid-
tight space in each of the different barrel motors. The required amount of oil
is less
for barrel motors with longer physical lengths than in the case of
conventional
barrel motors, which means that oil can be saved.
A barrel motor such as this preferably has a design in which the center seal
comprises a sealing trough whose rim is formed by a tubular section which is
cylindrical in places and whose external diameter corresponds essentially to
the
internal diameter of the barrel casing. A center seal such as this could
preferably
have a circumferential groove on the outside of the cylindrical tubular
section, in
which groove an 0-ring is inserted which provides a seal between the sealing
trough and the barrel casing. Alternatively, an interference fit could also be
provided between the barrel casing and the sealing trough, designed and/or of
such
a size that, at the same time, it has a sealing and power-transmitting
function. As
an alternative to the sealing trough, it would also be possible to provide a
sealing
roller bearing, for example a grooved ball bearing, whose outer ring is fitted
into
the barrel casing. It is also feasible for a shaft sealing ring or a similar
sealing
element to be provided in addition to a grooved ball bearing. In comparison to
these alternative solutions, the solution with the sealing trough has the
advantage
that the sealing trough can be produced easily, for example by the injection-
molding process. Furthermore, a sealing trough such as this serves to
reinforce the
barrel casing in the internal area.
A further advantageous embodiment relates to a barrel motor in which the
center
bearing comprises a central roller bearing which is arranged between the
barrel
motor drive unit and the barrel casing, in particular between the barrel motor
drive
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unit and an inner surface of the cylindrical tubular section of the sealing
trough. A
design such as this makes it easier to assemble the barrel motor drive unit
together
with a roller bearing and the sealing trough in the barrel motor. Furthermore,
a
bearing surface can be produced more easily on the inner surface of the
sealing
trough than in the internal area of the barrel casing.
A further aspect of the invention relates to a barrel motor comprising a
barrel
casing, a barrel motor drive unit, a first mounting element and a second
mounting
element for mounting the barrel motor in a conveyer frame, wherein the barrel
casing is rotatably supported about a barrel axis at least relative to the
first
mounting element, wherein the barrel motor drive unit comprises an electric
motor
having a stator and a rotor, and is arranged within the barrel casing, wherein
the
stator of the electric motor is connected to the first mounting element in a
torque-
proof manner, wherein the barrel drive unit and the barrel casing are
supported via
a first bearing and a center bearing such that they can rotate with respect to
one
another and cannot tilt with respect to one another, wherein the center
bearing is at
a distance from the first bearing in the direction of the barrel axis,
wherein, viewed
from the first bearing in the direction of the barrel axis, a second bearing
is
provided behind the center bearing, via which second bearing the barrel casing
is
rotatably supported with respect to a conveyer frame, which is adjacent to the
barrel motor, and wherein the barrel drive unit is supported with respect to
the
barrel casing independently of the second bearing. The statements that have
been
made above with respect to the first aspect of the invention apply essentially
to this
further aspect of the invention. As above as well, the bearing of the barrel
motor
drive unit in the barrel casing on the side of the unit facing away from the
first
mounting element has the advantage that, even if the second bearing were to be
removed, the barrel motor drive unit would still be supported such that it
cannot tilt
with respect to the barrel casing. There is therefore no need for any
additional
bearing for the barrel motor drive unit, for example via a continuous axle or
an
axle of the barrel motor drive unit, which also extends on the side of the
barrel
motor drive unit facing away from the first mounting element. Inter alia, this
also
has the advantage that a continuous axle such as this, which would be
dependent
on the length of the barrel casing and would therefore have to be manufactured
as
an extra item for each barrel length, is not required. The alternatives and
advantages mentioned with reference to the embodiments described above also
apply to the advantageous embodiments described in the following text.
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Furthermore, in one preferred embodiment of the barrel motor, the first
bearing is
arranged between the first mounting element and the barrel casing and
comprises a
first roller bearing and/or a first fluid seal.
Furthermore, a barrel motor such as this preferably has a design in which the
second bearing is arranged between the second mounting element and the barrel
casing, and comprises a second roller bearing and/or a second fluid seal.
Further advantageous aspects of an embodiment such as this may lie in a barrel
motor in which a center seal is provided between the first fluid seal and the
second
bearing such that a fluid-tight space, which accommodates at least a portion
of the
barrel motor drive, is formed between the first seal and the second bearing in
the
interior of the barrel motor.
A barrel motor such as this is preferable in which the center seal comprises a
sealing trough whose rim is formed by a tubular section which is cylindrical
in
places and whose external diameter corresponds essentially to the internal
diameter
of the barrel casing.
A barrel motor such as this preferably has a design in which the rotor of the
electric motor is connected to the barrel casing via an output drive element,
such
that the barrel casing can be driven via the output drive element at least
relative to
the first mounting element, such that it can rotate about the barrel axis,
wherein the
output drive element is arranged on the same side of the barrel motor drive
unit as
the first mounting element with respect to the barrel axis, and wherein the
rotation
axis of the output drive element is not identical to the rotation axis of the
rotor.
A further advantageous embodiment relates to a barrel motor in which the
rotation
axis of the output drive element is not identical to the barrel axis.
In a further preferred embodiment of the barrel motor, the output drive
element is a
pinion which engages with an internal tooth system which is provided on the
internal circumference of the barrel casing in a torque-proof manner.
Furthermore, a barrel motor such as this preferably has a design in which the
external radius of the first roller bearing and/or the external radius of the
first fluid
seal are/is essentially equal to or greater than a radius which extends from
the
barrel axis to the rotation axis of the output drive element, and/or is equal
to or
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greater than the radius of the root circle of the internal tooth system, which
is
provided on the internal circumference of the barrel casing in a torque-proof
manner.
Further advantageous aspects of an embodiment such as this may lie in a barrel
motor in which the first roller bearing has an external diameter which is
essentially
equal to or greater than the diameter of the barrel motor drive unit
In one preferred barrel motor such as this, an axle element which is
essentially
concentric with the barrel axis is provided between the barrel motor drive
unit and
the mounting element and fixes or connects the stator of the electric motor by
means of the mounting element in a blind hole of the mounting element in a
torque-proof manner.
A barrel motor such as this preferably has a design in which a cable opening,
in
particular for the electrical supply for the electric motor, and/or a plug
socket
and/or an oil filling opening areilis provided in the mounting element.
A further advantageous embodiment relates to a barrel motor in which the
center
bearing comprises a central roller bearing which is arranged between the
barrel
motor drive unit and the barrel casing, in particular between the barrel motor
drive
unit and an inner surface of the cylindrical tubular section of the sealing
trough.
A further aspect of the invention relates to a drift conveyer having a barrel
motor
95 according to the present invention.
A further aspect of the invention relates to a barrel motor drive unit
comprising an
axle element, an electric motor having a stator and a rotor, a transmission
having a
drive element and having an output drive element, wherein the axle element is
arranged with respect to the stator of the electric motor in a torque-proof
manner
and is passed out of the barrel motor drive unit on a first side of the barrel
motor
drive unit, wherein the output drive element is passed out of the barrel motor
drive
unit on the side of the axle element, and wherein the rotation axis of the
output
drive element is arranged offset with respect to the axle element.
A further aspect of the invention relates to a barrel motor comprising a
barrel
casing, a barrel motor drive unit, a first mounting element and a second
mounting
element for mounting the barrel motor in a conveyer frame, a bearing for
mounting
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the barrel casing on the mounting elements, and at least one axle element
which is used
as a connecting element between the barrel motor drive unit and at least one
of the
mounting elements, wherein all said components of the barrel motor apart from
the barrel
casing are designed such that they can be used in an identical manner in
barrel motors
with different casing lengths, in such a way that the only length-dependent
part of the
barrel motor is the barrel casing. Only the most important parts which a
barrel motor such
as this comprises have been mentioned in this context. It is feasible for a
barrel motor
such as this to comprise further parts, in particular those parts that have
been described
with reference to the other aspects of the invention. In particular, parts
such as these may
also be "said components" in the sense of this aspect of the invention. A
barrel motor
such as this has the advantage that barrel motors of different lengths can be
produced
easily, since most of the components for barrel motors, which each have
different lengths,
are identical. It is particularly preferable for only a single part, in
particular the barrel
casing, to have to be produced as a function of the length in a barrel motor
such as this.
In a broad aspect, moreover, the present invention provides a barrel motor
comprising a
barrel casing, a barrel motor drive unit, a first mounting element and a
second mounting
element for mounting the barrel motor in a conveyer frame, wherein the barrel
casing is
rotatably supported about a barrel axis at least relative to the first
mounting element,
wherein the barrel motor drive unit comprises an electric motor having a
stator and a
rotor, and is arranged within the barrel casing, wherein the stator of the
electric motor is
connected to the first mounting element such that they rotate together,
wherein the rotor
of the electric motor is connected to the barrel casing via an output drive
element, such
that the barrel casing can be driven via the output drive element at least
relative to the
first mounting element such that it can rotate about the barrel axis, wherein
the output
drive element is arranged on the same side of the barrel motor drive unit as
the first
mounting element, with respect to the barrel axis, wherein the rotation axis
of the output
drive element is not identical to the rotation axis of the rotor, and wherein
a first roller
bearing is provided between the barrel casing and the first mounting element,
characterized in that the first roller bearing has an external diameter which
is essentially
equal to or greater than the diameter of the barrel motor drive unit.
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In another broad aspect, the present invention a barrel motor drive unit
comprising an
axle element, an electric motor having a stator and a rotor, a transmission
having a drive
element and having an output drive element, wherein the axle element is
arranged with
respect to the stator of the electric motor in a torque-proof manner and is
passed out of
the barrel motor drive unit on a first side of the barrel motor drive unit,
wherein the
output drive element is passed out of the barrel motor drive unit on the side
of the axle
element, and wherein the rotation axis of the output drive element is arranged
offset with
respect to the axle element.
In another broad aspect, the present invention provides a barrel motor
comprising a barrel
casing, a barrel motor drive unit, a first mounting element and a second
mounting
element for mounting the barrel motor in a conveyer frame, a bearing for
supporting the
barrel casing on the mounting elements, and at least one axle element which is
used as a
connecting element between the barrel motor drive unit and at least one of the
mounting
elements, wherein the only part of the barrel motor having variable length is
the barrel
casing, whereby all other components of the barrel motor are interchangeable
between
motors of differing casing lengths.
Individual particularly preferred embodiments of the invention will be
described by way
of example in the following text. In this case, the individual described
embodiments in
some cases have features which are not absolutely essential in order to
implement the
present invention but which are in general considered to be preferable. For
example,
embodiments which do not have all the features of the embodiments described in
the
following text are also considered to have been disclosed within the teaching
of the
invention. It is likewise feasible for features which are described with
reference to
different embodiments to be selectively combined with one another.
Brief description of the drawings
In the figures:
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Figure 1 shows a longitudinal section through one preferred embodiment of a
barrel
motor according to the invention, and a side view of the barrel motor, and
Figure 2a and figure 2b
show enlargements of details from the longitudinal section from figure 1.
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Detailed description of the drawing
Figure 1 shows a longitudinal section through one preferred embodiment of a
barrel motor according to the invention, and a side view of the barrel motor.
The figure shows a barrel motor 1 which has a barrel casing 10, a first
mounting
element 13, a second mounting element 14 and a barrel motor drive unit 12.
The barrel casing 10 can rotate about the mounting elements 13, 14. This is
ensured by means of a first roller bearing 136 in the area of a first bearing
135, and
by means of a second roller bearing 142 in the area of a second bearing 141,
which
bearings bear the barrel casing on the first mounting element 13 and the
second
mounting element 14. The first bearing 135 furthermore comprises a first fluid
seal
137, and the second bearing 141 furthermore comprises a second fluid seal 143.
These fluid seals ensure that no moisture can enter the barrel motor 1 from
the
outside. On the other hand, the fluid seal 137 ensures that oil which is
located in a
fluid-tight space 16 cannot escape out of the barrel motor to the outside.
The oil level HO in the internal area 16 is designed on the one hand to ensure
lubrication of the first roller bearing and of the central roller bearing, and
on the
other hand to ensure adequate cooling of the barrel motor drive unit. This is
a
further advantage of the design with roller bearings with a large diameter, on
the
basis of which a relatively low filling height of the oil, that is to say a
low oil level
HO, is sufficient to lubricate the roller bearings.
In addition to the two said fluid seals 137, 143 in this preferred embodiment,
sealing elements are furthermore arranged axially outside the respective fluid
seals,
and each, together with the first and the second mounting element 13, 14, form
a
labyrinth seal. In this case, the sealing elements are preferably introduced
into the
barrel casing to be fluid-tight, preferably by pressing them and/or adhesively
bonding them in. This has the advantage that, when the lower edge of the
internal
diameter of the sealing element is above the oil level HO in the internal area
16, no
oil can escape from the internal area 16 even if one of the fluid seals is
leaking.
The low oil level HO which this design allows nevertheless results in a
comparatively large internal diameter of the sealing element, as a result of
which
the diameter of that area of the mounting element 13 which is passed out of
the
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sealing element can also be made large, offering sufficient space for
implementation of wiring, etc.
As can be seen in figure 1, the mounting elements 13, 14 have a relatively
large
diameter. This ensures that these mounting elements, in particular the first
mounting element 131, can provide an oil filling opening 134, a cable opening
132
which is preferably provided with a plug socket 133, and threaded holes, via
which
the mounting element can be mounted on an adjacent bearing frame.
In this embodiment, said threaded holes in particular allow a barrel motor 1
according to the invention to be easily fitted in a frame of a drift conveyer.
Other
mounting apparatuses can also be provided instead of threaded holes such as
these.
By way of example, a single threaded hole is illustrated for the second
mounting
element 14. It would also be feasible, for example, to provide a single blind
hole or
just one rest on a frame of the drift conveyer for the (second) mounting
element 14
and a fixing in the frame longitudinal direction. In this context, it is
preferable if a
fitting on the bearing frame is ensured at least on the side of the first
mounting
element 13, which fitting prevents rotation of the first mounting element,
thus
allowing the drive torque to be transmitted to the frame.
Since, in the illustrated embodiment, no torque is transmitted via the second
mounting element 14, it is not absolutely essential to provide a torque-proof
connection such as this on the side of the second mounting element. This also
applies to an oil filling opening 134, a cable opening 132 etc., in a
corresponding
manner, which can be provided on the second mounting element, but are not
required at these points for the purposes of the described embodiment.
It is preferable for at least one of the mounting elements to be designed such
that
alignment, parallelity and angle errors can be compensated for. This could be
done,
for example, by means of a rubber bearing and/or by means of elongated holes
on
the frame, by which means the barrel motor can first of all be aligned in the
frame
and can then be fixed by tightening the screws in the elongated holes.
The barrel motor drive unit 12 illustrated in figure 1 comprises an electric
motor
122 and a transmission 126. The electric motor 122 has a stator and a rotor,
which
are not illustrated in any more detail in the figures. The transmission is
connected
to the motor output drive via a drive element which is not illustrated, and
converts
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the motor rotation speed to an output drive rotation speed which is produced
on an
output drive element 128 of the transmission 126.
The output drive element 128 is in the form of a pinion in this preferred
embodiment. The pinion engages with an internal tooth system 102 which is
provided on the internal circumference of the barrel casing 10. The internal
tooth
system 102 is provided in the illustrated embodiment on a ring element, which
also
has a sealing surface for the first fluid seal 137 and a bearing surface for
the first
roller bearing 136. The ring element is pressed into the barrel casing 10 and
is
preferably produced by the injection-molding process. Where relatively high
torque levels have to be transmitted, the ring element can also be provided as
a die-
cast aluminum part. Other production methods are likewise feasible. The ring
element can be pressed, adhesively bonded and/or welded into the barrel
casing,
depending on the materials used. Other mounting methods are likewise feasible.
The crown circle, that is to say the diameter which is defined by the points
of the
internal tooth system which are located radially furthest inwards, is, in the
illustrated embodiment, equal to or greater than the diameter DT of the barrel
motor drive unit 12 at its thickest point. The barrel motor drive unit 12 can
therefore be pushed into the barrel casing once the ring element has already
been
preinstal led.
On the side of the barrel motor drive unit 12 which is opposite the first
mounting
element 13, the barrel motor drive unit 12 is supported in the barrel casing
10 via a
center bearing 15. The center bearing 15 comprises a sealing trough 151 and a
central roller bearing 154. The sealing trough 151 is essentially in the form
of a
saucer. Its rim is cylindrical and is pressed into the barrel casing 10. In
the
illustrated embodiment, the fit with which the sealing trough 151 is pressed
into
the barrel casing 10 is chosen such that the sealing trough 151 and the barrel
casing
10 are sealed against fluids, in particular lubricating oil.
The central roller bearing 154 is supported on the inner surface of the
cylindrical
tubular section 152 of the sealing trough 151. The rear face of the barrel
motor
drive unit 12, which is preferably designed to be concentric with the barrel
casing
10 at least in this area, is supported via the central roller bearing 154 in
the barrel
casing 10 such that it can rotate.
As an alternative to this embodiment, it would be feasible to provide a
bearing and
a sealing surface on the surface of the barrel motor drive unit 12, in such a
way that
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the center bearing and seal are not provided at the axial end of the barrel
motor
drive unit 12, but further in the direction of the first mounting element.
Since, apart from the barrel casing 10, the same parts can be used in every
barrel
motor 1, depending on the dimensions of the barrel motor drive unit 12, these
parts
can be produced particularly advantageously. Furthermore, the fluid-tight
space 16
which is formed between the first mounting element 13, the sealing trough 151
and
the barrel casing 10 is always of the same size in barrel motors such as
these. In
consequence, the same amount of oil is always required, and is introduced in
order
to lubricate the pinion and internal tooth system, and/or transmission 126.
The oil
filling level in figure 2a is indicated by the reference symbol HO.
Figures 2a and 2b show enlargements of details from the longitudinal section
from
figure 1.
Figure 2a shows an enlargement of the area of the barrel motor 1, in the area
of the
first mounting element 13. Those parts which revolve around the barrel axis
101
are indicated by cross-shading. The illustration shows, inter alia, various
radii and
diameters. The reference symbol RF denotes the radius between the barrel axis
101
and the root circle of the internal tooth system 102. The root circle is the
circle of a
tooth system which runs through the deepest points at the tooth base between
in
each case two teeth.
The radius which extends from the barrel axis 101 to the rotation axis of the
output
drive element 129 is annotated with the reference symbol RA. Since the output
drive element 128 can be located behind the plane of the drawing in the
illustrated
embodiment, this radius may be greater than that illustrated in the
projection.
Figure 2b shows an enlargement of the area of the center bearing 15 from
figure 1.
This shows well that the barrel casing is formed with different diameters
which
form a step in the area of the center bearing. The sealing trough 151 is
pushed onto
this step and is fixed thereby axially in the direction of the second mounting
element.
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List of reference symbols
1 Barrel motor
10 Barrel casing
101 Barrel axis
102 Internal tooth system
12 Barrel motor drive unit
121 Concentric axle element
122 Electric motor
125 Rotation axis of the rotor
126 Transmission
128 Output drive element
129 Rotation axis of the output drive element
13 First mounting element
131 Blind hole
132 Cable opening
133 Plug socket
134 Oil filling opening
135 First bearing
136 First roller bearing
137 First fluid seal
14 Second mounting element
141 Second bearing
142 Second roller bearing
143 Second fluid seal
15 Center bearing
151 Sealing trough
152 Cylindrical tubular section
153 Inner surface of the cylindrical tubular section of the sealing trough
154 Central roller bearing
155 Center seal
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16 Fluid-tight space
2 Conveyer frame
R1 External radius of the first roller bearing
RA Radius which extends from the barrel axis to the rotation axis of
the
output drive element
RF Radius of the root circle of the internal tooth system
RT Radius of the barrel motor drive unit
DT Diameter of the barrel motor drive unit
HO Oil level
