Note: Descriptions are shown in the official language in which they were submitted.
CA 0223~732 1998-0~-13 ll-,
1 3449P W0/CMJ0
PCT/EP96/04976
Rotary distributor rotating apparatus for handling of objects, in particular
containers, with a revolving joint for the transport of fluid between a
stationary assembly and a rotating assembly
Description
The present invention concerns a rotating apparatus for handling of
objects, in particular of containers such as bottles, in particular for at leastone of cleaning and filling and closing and labelling and singling and sorting
and aligning the containers or objects, comprising a stationary assembly, a
rotating assembly driven by a rotary drive and rotatable with respect to the
stationary assembly, receptacles for the objects and associated to the
circumference of said rotating assembly, handling devices for the handling
of the objects and a shielding wall which at least partially encloses the
rotating assembly and which is stationary during driving the rotating
assembly for rotation.
For such rotating apparatus it is often necessary to regularly clean the
inner side of the shielding wall which is directed towards the rotating
assembly. The shielding wall can be a protecting wall which shall give
protection against touching of the rotating element, the handling devices or
other components, which shall protect against noise (acoustic protection),
which shall give sight protection or which shall protect against
contamination. In case of protection against contamination it is possible,
for example, that the rotating assembly or the handling devices are
protected against contamination from the outside, for example, if the
rotating apparatus is placed in a dusty atmosphere or it is possible that the
surrounding of the rotating apparatus is protected against contamination
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which is caused by the handling of the objects. As an example reference is
made to a rotating apparatus in the form of a filling apparatus for bottles,
in which bottles are filled with a filling medium, for example a beverage.
During the filling it can happen that certain amounts of the filling medium
are splattered or splashed during the bottling. The shielding wall prevents
the surrounding of the filling apparatus for bottles from being contaminated
by the filling medium.
In conventional rotating apparatus of the mentioned type the shielding wall
and possibly other stationary components so far were cleaned manually,
for example by hosing down with a hose provided that the shielding wall
has corresponding openings or encloses the rotating assembly only
partially. For particularly high requirements with respect to the cleanness,
or if no cleaning openings are provided in a shielding wall which
completely encloses the rotating assembly one could dismantle the
shielding wall at least partially to allow cleaning of the shielding wall and
possibly the other stationary components.
In particular recently there have been increased efforts to increase the
productivity. Before this background the ways of cleaning as described are
no longer satisfactory for beverage filling apparatus as well as generally for
rotating apparatus for handling of objects. In the special case of beverage
filling apparatus one can foresee that at least in the long run the cleaning
possibilities as described will not be sufficient any more because of the
hygienic standards which will increase significantly in the future.
In view of the foregoing it is an object of the invention to provide a
rotating apparatus of the kind mentioned which allows a simple and reliable
cleaning of the shielding wall from the inside and possibly of other
stationary components of the apparatus. For solving this object it is
suggested that there is arranged at least one discharge opening at the
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rotating assembly for discharge of a cleaning fluid, in particular a cleaning
liquid, for cleaning of said shielding wall and possibly of other stationary
components of the apparatus, and that said at least one discharge opening
is connected with a stationary cleaning fluid supply via a revolving joint.
Because there is provided at least one discharge opening, preferrably
several discharge openings, on the rotating assembly, the shielding wall
can be cleaned simply and reliably from the inside. To this end the cleaning
fluid, in particular the cleaning liquid, is supplied to the at least one
discharge opening via the revolving joint and is directed against the inner
surface of the shielding wall and possibly onto the other stationary
components. While doing so, the rotating assembly can be rotated so that
the cleaning medium reaches the complete inner surface of the shielding
wall and all other stationary components to be cleaned. The rotating
assembly can rotate continuously during the cleaning operation or can also
be stopped at certain rotary positions, for example for the cleaning of
heavily soiled regions of the shielding wall or for the cleaning of heavily
soiled stationary components. Preferably, the discharge openings are
formed as nozzles which direct a cleaning fluid jet onto the shielding wall
or the other components to be cleaned. To this end, the cleaning fluid can
be supplied to the nozzles with a pressure which is substantially higher
than normal pressure, so that a high pressure cleaning effect is achieved
as in the case of a high pressure cleaning device. If the cleaning fluid is
steam, for example, a steam jet cleaning effect results like the effect
achieved with a steam jet cleaning device.
Besides water, possibly with cleaning additives, also special liquid cleaning
chemicals are a possibility to be used as cleaning liquids. It is clear that
after the application of a special liquid cleaning chemical one can
subsequently clean with water in a final cleaning step, if necessary, to
remove the residues of the cleaning chemical.
CA 0223~732 1998-0~-13
}
In all cases the cleaning can be effected substantially mechanized without
the need to remove the shielding wall or parts of the shielding wall. There
is further no need for the shielding wall to have openings for cleaning
purposes, since a manual cleaning by means of hosing with a hose or the
like can be left out. Additionally to the at least one discharge opening
arranged on the rotating assembly, there can be provided one or several
stationary discharge openings for example on the shielding wall which
allow a mechanized cleaning of the rotating assembly.
The invention is particularly advantageous in the case of a beverage filling
apparatus, since highest hygienic standards can be fulfilled if the invention
is applied. Beverage which sticks to the inner surface of the shielding wall
or to other stationary components and which is possibly dried can be
reliably removed. For the removal special cleaning chemicals or also steam
can be used. If steam is used, also a heat sterilization effect is achieved
besides the cleaning effect.
The invention offers the possibility that cleaning operation phases areeffected automatically in certain time intervals. Normally, for the cleaning
the working operation of the rotating apparatus, in particular the filling
operation of the beverage filling apparatus, will be interrupted for the
respective cleaning operation phase. However, it cannot be ruled out that
for special applications the working operation of the rotating apparatus will
be continued during the respective cleaning operation phase.
As can be seen from the foregoing remarks, the invention cannot only besuitably applied to beverage filling apparatus or bottling apparatus. The
rotating apparatus, as has already been mentioned in the introduction, can
also be an apparatus for at least one of singling, sorting and aligning of
objects, for example containers such as bottles, or also of lids for the
closing of containers. For example, these objects (containers or lids) can
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be supplied to the rotating apparatus in groups comprising a plurality of
objects with the objects being disordered within the groups. The objects
will then be singled, possibly sorted or sorted out and possibly aligned
within the rotating apparatus. One has also to consider other applications,
in particular in the production and processing technology, for example
automatic milling machines, automatic turning machines, automatic drilling
machines, other automatic forming machines and the like.
With respect to the construction of the revolving joint it is suggested that
the revolving joint comprises a revolving joint stationary unit which is fixed
or fixable to the stationary assembly to prevent rotation, and a revolving
joint rotating unit which is connectable or connected with the rotating
assembly for rotating together, wherein these two revolving joint
components are rotatably supported at each other by axially directed
sliding surfaces.
Sliding surfaces which are axially directed can be processed relativelyeasily and, with respect to sliding surfaces which are radially directed, less
severe manufacturing tolerances are possible. It is even preferred that the
two revolving joint components have radial play with respect to each
other. In this case, the revolving joint can be manufactured very
economically, since only relatively rough manufacturing tolerances with
respect to the radial dimensions must be fulfilled. Also with respect to the
mounting of the revolving joint on the rotating apparatus there are high
cost advantages, since also for this mounting there are no particularly high
tolerances which have to be met. For example, by means of the radial play
a certain deviation between the rotary axis of the revolving joint rotating
unit and the rotary axis of the rotating assembly can be accommodated. It
is not necessary that the two rotary axes are completely coaxial with
respect to each other. It is sufficient if the two axes are substantially
parallel with respect to each other and have such distance from each other
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that this distance can be accommodated by the radial play. This viewpoint
is of importance in particular when the revolving joint is replaced or when
the revolving joint together with the at least one discharge opening (on
corresponding pipelines or the like) is retrofitted on a conventional rotating
apparatus.
For the sealing of the revolving joint separate sealing lips, sealing rings or
the like may be provided in particular neighboring to the sealing surfaces.
However, not only because of the costs it is particularly advantageous if
the sliding surfaces are simultaneously formed as sealing surfaces. Sealing
elements such as sealing lips, sealing rings and the like are usually
manufactured from materials which are softer and less abrasion-proof than
usual materials of sliding surfaces. Such sealing elements may accordingly
wear with time and then they have to be replaced. The sliding surfaces
which, according to the preferred embodiment, are simultaneously
designed as sealing surfaces may be of such nature that they have
sufficient sealing effect for the complete service life of the rotating
apparatus, so that a reduced effort for maintenance and servicing results.
There may be provided setting means which are mounted on at least one
of the two revolving joint components and which are axially effective and
adapted to hold the two revolving joint components in sealing abutment
with respect to each other. The setting means may be provided to
compensate for a certain abrasion on the sealing surfaces so that despite
the abrasion the sealing effect is maintained. The setting means may,
however, also be provided, so that the two revolving joint components
need not be permanently maintained in sealing abutment with respect to
each other. The latter design is preferred in the case that the cleaning of
the shielding wall and possibly the other stationary components is effected
only phase-wise, i.e. not permanently during the working operation of the
rotating apparatus. Since the revolving joint rotating unit rotates together
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with the rotating assembly during working operation, the sliding surfaces
and possibly the whole revolving joint may be heated up because of the
friction which occurs between the sliding surfaces. Such a heating up may
in particular happen in the case when the sliding surfaces are maintained in
sealing abutment with respect to each other.
During a cleaning operation phase an excessive warming up or heating upof the sliding surfaces or the whole revolving joint is prevented because
the heat generated by friction will be transported away by the cleaning
fluid (provided the fluid flow is greater than a certain minimal fluid flow).
During a pure working operation without simultaneous cleaning operation
phase such a removal of friction heat by the cleaning fluid is not possible.
If the sliding surfaces are not in sealing abutment during the pure working
operation, the friction between the sliding surfaces is reduced or possibly
substantially cancelled, so that there develops only minor or virtually no
friction heat. Then there is no danger that during pure working operation
the sliding surfaces or the revolving joint may overheat and possibly be
damaged thereby.
One of the two revolving joint components may be formed with sliding
surfaces facing each other and the respective other of the two revolving
joint components may be formed with sliding surfaces turned away from
each other. Preferably, the two revolving joint components together form a
ring chamber for the fluid distribution, i.e. for the distribution of the
cleaning fluid with the ring chamber being sealed or being sealable
particularly in the region of the sliding surfaces. By the provision of the
ring chamber, a uniform fluid distribution with pressure conditions which
substantially remain constant, is possible. The ring chamber may also be
intended to mix within the ring chamber several fluids supplied to the ring
chamber via corresponding supply openings so that a fluid mixture
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emerges from the ring chamber via one or several corresponding discharge
openings .
One of the two revolving joint components may form an annular groove
which is radially open and in which the respective other revolving joint
component is received with its sliding surfaces. In this case the revolving
joint may be manufactured relatively simply and economically and the
manufacturing costs of the whole rotating apparatus as well are thus
correspondingly reduced. The fact that the revolving joint can be
manufactured at a reasonable price is of importance particularly in the case
of revolving joints intended for retrofitting since in this case the persons
deciding over the retrofitting may be convinced more easily that a
retrofitting is worthwhile.
The ring chamber may be limited radially between a bottom of the annular
groove of said one revolving joint component and a circumferential surface
of said other revolving joint component. The annular groove may be open
radially inwardly or outwardly. If there is sufficient space available in radialdirection, the variant with the annular groove which is radially outwardly
open is preferred. In this case the revolving joint may be mounted
particularly easily and there can be conduits or the like for the supply or
withdrawal of fluid which extend radially outwardly from the revolving joint
component received with its sliding surfaces within the annular groove.
Said one revolving joint component may comprise two partial components
which are combined in a dividing plane disposed between its two sliding
surfaces facing each other. In this case, the two revolving joint
components can be assembled easily to form the revolving joint. In
particular, the revolving joint component which has to be received with its
sliding surfaces in the annular groove can be inserted between the two
partial components like a sandwich.
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At least one of the two sliding surfaces facing each other may be arranged
on a flange of said one revolving joint component which flange is movable
axially. Preferably this flange is exposed to the influence of setting means
which are axially effective and disposed on said one revolving joint
component. The results are the advantages which were already mentioned
in connection with the setting means, with the embodiment set forth now
can be realized without large constructive and manufacturing expenditure.
It is of major advantage if the setting means which are axially effective are
formed by an inflating tube which is supported or supportable on a
supporting surface of said one revolving joint component which supporting
surface is neighboring to the flange. By use of an inflating tube as setting
means, an uniform exerting of force onto the flange is possible over the
hole length of the flexible tube in case of an inflated tube. Preferably the
inflating tube is ring-shaped, i.e. formed as an annular tube, so that the
sliding surfaces may be uniformly loaded for the sealing abutment over the
hole respective annular surface.
Because of its simple construction, setting means in the form of an
inflating tube result also in a particularly high reliability (safety against
failure, low susceptibility to be in need of repairs) and the constructive and
manufacturing expenditure is extremely low, so that there are major cost
advantages with respect to other setting means, such as setting motors or
the like. The inflating tube can be inflated by means of a gas, in particular
by means of air or also by means of a suitable liquid for the exerting of
pressure onto the sliding surfaces via the flange.
The inflating tube may be received in an annular groove of a supportingplate of said one revolving joint component which plate abuts against the
flange. The manufacturing expenditure for such an annular groove is low.
The supporting plate may be connected sandwich-like with said one
revolving joint component by tension rods, for example screws, wherein in
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1 0
the case of the division of said one revolving joint component in partial
components these tension rods - if desired - also hold these partial
components together.
One revolving joint component of the two revolving joint components maybe manufactured from metal, in particular stainless steel, and the other
revolving joint component may be manufactured from plastic. For the
manufacture of the revolving joint component made of plastic, one may
use polyethylen in particular. However, also other plastics materials are a
possibility.
In case of construction of said one revolving joint component with a flange
which is axially movable, this revolving joint component is preferably
manufactured from plastic and - if desired - is constructed with at least one
weakening recess which favors the axial deflectability of the flange. The
respective revolving joint component may be manufactured easily in this
case and, in case of a resilient plastic, the flange is resilient to either exert
a desired pressing force onto the sliding surfaces or- in the case of setting
means, in particular of the inflating tube (when the flexible tube is not
inflated) - to provide a restoring force which is adapted to relieve the
sliding surfaces. By means of corresponding dimensioning of said at least
one weakening recess, the force exerted to the sliding surfaces or the
restoring force, respectively, may be adjusted. In the latter case it is
possible that the setting means may only nead to apply a relatively weak
force for the movement of the flange.
The revolving joint stationary unit may be mounted on the shielding wall or
also on a separate support setup on which the shielding wall possibly is
fastened. Preferably, at least one entrainment means of the rotating
assembly is provided for the driving of the revolving joint rotating unit. The
entrainment means may engage directly with the revolving joint rotating
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1 1
unit or also with a fluid transport pipe or the like which is fixed at the
revolving joint rotating unit and possibly is connected with the ring
chamber.
As already mentioned above, the sliding surfaces may be arranged
opposite each other substantially without sealing force during working
operation of the rotating apparatus and are adapted to be sealingly pressed
against each other for cleaning operation phases. If during the working
operation of the rotating apparatus there is no simultaneous cleaning, i.e. if
there occurs a "dry operation" of the revolving joint, a detrimental warming
up or heating up of the sliding surfaces or the revolving joint because of
friction head is avoided.
The revolving joint stationary unit may be formed U-shaped with a radially
outwardly open annular groove in a cross section containing the axis, the
revolving joint rotating unit preferably being formed as a ring body which is
received in the groove and has a radial fluid connection.
The revolving joint may be formed annular and - if desired - may enclose a
part of the rotating assembly. In case that the rotating assembly is, for
example, a filling apparatus for the filling of containers, in particular a
beverage filling apparatus, the filling medium (in particular the beverage)
can be supplied to the rotating assembly via conventional rotary
distributors having an axial supply of filling medium, whereas the cleaning
fluid is supplied to the rotating assembly non-axially. The terms "axial" and
"non-axial" refer to the rotational axes of the rotating assembly and the
revolving joint rotating unit which substantially coincide or are neighboring
closely. Axial supply means that the filling medium is substantially supplied
along the rotational axis of the rotating assembly and non-axial supply
means that the fluid is not supplied along the rotational axis to the rotary
distributor. By means of the annular construction of the revolving joint,
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1 2
many conventional rotating apparatus may be retrofitted with the revolving
joint and a corresponding conduit system having at least one discharge
opening .
There may be provided holding means for the objects, in particular
containers, on the rotating assembly. The handling devices may be
arranged stationary or may be connected with the rotating assembly for
common rotation. The shielding wall may have passing-through openings
for object conveying means, in particular container conveying means,
which supply objects, in particular the containers, to the rotating assembly
or remove the same from the rotating assembly. Preferably, the revolving
joint is disposed in an upper region of the rotating assembly or above the
same .
As has already been indicated in the foregoing discussion, the rotatingapparatus may have a conduit system comprising the at least one
discharge opening. At least one of the conduit system having the at least
one discharge opening and the revolving joint may be adapted for
retrofitting to the rotating apparatus which is substantially ready for
operation. Accordingly, conventional rotating apparatus may be retrofitted
or changed over to a rotating apparatus according to the present invention.
According to another aspect, the invention concerns a revolving joint for
the transport of fluid between a stationary assembly and a rotating
assembly, in particular in a rotating apparatus as described in the
foregoing. The revolving joint comprises a revolving joint stationary unit
which is fixed or fixable to the stationary assembly to prevent rotation, and
a revolving joint rotating unit which is connectable or connected with the
rotating assembly for rotating together, wherein these two revolving joint
components are rotatably supported at each other by axially directed
sliding surfaces. The revolving joint further may have at least one further
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1 3
feature of the revolving joint olF a rotating apparatus according to the
invention as described in the foregoing.
In particular, it is pointed to the construction of the revolving joint having
radial play between the revolving joint stationary unit and the revolving
joint rotating unit, the annular construction of the revolving joint as well as
the possibility that the sliding surfaces may be formed as sealing surfaces,
with the sliding surfaces possibly not permanently being held in sealing
abutment against each other. The advantages explained above are
achieved .
The invention will be explained in more detail in the following with
reference to an embodiment shown in figures 1 to 5.
Figure 1 shows an embodiment of a rotating apparatus according to
the invention in the form of a bottling apparatus in a view
from the side with the shielding wall being depicted
sectionally.
Figure 2 shows an enlargernent of a detail of figure 1, with the
revolving joint of ~he bottling apparatus being depicted
sectionally.
Figure 3 shows a top view onto or a view into the bottling apparatus
being open upwardly.
Figure 4 shows the revolving joint of the bottling apparatus in a
partially sectional top view with a section according to line IV-
IV in figure 5a.
Figure 5 shows in figures 5a and 5b a section according to VAB-VAB
of figure 4 in two different operation conditions of the
revolving joint and in figure 5c a section according to line VC-
VC in figure 4 in the operation condition of the revolving joint
corresponding to figure 5b.
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14
The bottling apparatus 1 for example for the bottling of beverages which is
shown in the figures comprises a stationary assembly 10 being of the type
of a base cabinet and a rotating assembly 14 which is rotatably supported
with respect to the stationary assembly 10. The rotating assembly is
substantially supported in overhung position or is supported in the
stationary assembly 10 and at a support assembly 12. The support
assembly comprises vertical beams 1 2a extending in vertical direction from
the upper surface of the stationary assembly 10 and being fastened on the
same and horizontal beams 1 2b which are fastened to the upper ends of
the vertical beams 1 2a and extend above the rotating assembly 14.
Accordingly, the rotating assembly is disposed between the stationary
assembly 10 and the horizontal beams 12b.
With respect to the structure of the support assembly different variants are
conceivable with figure 1 and figure 3 showing variants differing slightly
from each other. According to the embodiment of figure 3, there are
provided three horizontal beams 1 2b and correspondingly three vertical
beams 1 2a with two neighboring horizontal beams enclosing an angle of
about 120~ between them. Further deviations between figure 1 and figure
3 are due to the fact that in figure 3 not all of the components shown in
figure 1 are depicted and that the figures concern embodiments which
differ slightly from each other. For the explanation of the invention, these
deviations are without any relevance so that these deviations need not be
considered in the following.
The rotating assembly 14 has a conveying and bottling rotating unit 16
which in short also will be denoted in the following only as conveying
rotating unit 16. The conveying rotating unit 16 is rotatably supported
around a vertical rotary axis at a stationary rotating shaft structure 18
which extends vertically. The upper end of the rotating shaft structure 18
is fastened to the vertical beams 1 2a.
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k ., . ~ ~ ~
1 5
The conveying and bottling rotating unit 16 is drivable by means of a
rotational drive unit which is disposed within the stationary assembly 10
and which can drive the conveying rotating unit 16 for rotation in at least
one operation of continuous operation and fixed-cycle operation. If the
conveying and bottling rotating unit 16 rotates continuously during the
filling of the bottles 20 shown in figure 1, a particularly high bottling
efficiency (number of bottles filled per time unit) can be reached.
The conveying and bottling rotating unit 16 is enclosed by a shielding wall
22 in a manner like a circular cylindrical shell which is coaxial with respect
to the rotational axis of the conveying rotating unit. This can be seen
particularly well from figure 3. The shielding wall extends from the upper
side of the stationary assembly up to the upper end of the vertical beams.
To completely enclose the rotating assembly the shielding wall 22 may
comprise additionally a wall section formed as a plate and having a circular
circumference which is disposed in a horizontal plane and links up to the
upper edge of the circular cylindrical shell section of the shielding wall 22.
The rotating assembly 14 would be completely enclosed by the shielding
wall 22 and the stationary assembly 10 in this case.
The bottling apparatus 1 is shown in figures 1 to 3 only insofar in detail as
it is necessary for the understanding of the invention. With respect to the
general setup of bottling apparatus, numerous variants are well known. As
far as that goes, figures 1 to 3 depict the bottling apparatus only
schematically. For example, the shielding wall 22 of course has passing-
throught openings for the bottles and there are provided bottle conveying
means which supply the bottles 20 to the conveying and bottling rotating
unit 16 in an appropriate manner and remove the same from the bottling
and conveying rotating unit again.
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16
The conveying and bottling rotating unit 16 comprises an upper circularcylindrical section 16a and a lower circular cylindrical section 16b. To the
circular cylindrical section 16b there are attached holding means for the
bottles to be filled which holding means are diposed directly above the
stationary assembly 10. The holding means are distributed over the
circumference of the conveying rotating unit 16 and neighboring holding
means are spaced equally in the circumferential direction. Of the holding
means there are shown in figures 1 and 3 only holding trays 24 on which
the bottles 20 are placed. Additionally to the holding trays 24, there are
provided holding means not shown which secure the bottles 20 against
slipping off the holding trays 24 under the influence of centrifugal force in
particular.
Each holding tray 24 has associated a handling device in the form of a
filling device 26. Specifically, there is above each holding tray 24 (with
respect to the holding tray offset in vertical direction) a respective filling
device 26 which is attached to the upper circular cylindrical section 16a of
the conveying and bottling rotating unit 16. The filling devices 26 as well
as the holding trays 24 are connected with the conveying and bottling
rotating unit 16 for common rotation. Each filling device 26 comprises an
axially stationary section 26a which is connected with the conveying
rotating unit section 16a via a crosspiece 28 and a lower section 26b
which is received telescopically in the stationary section 26a and is
movable in axial, i.e. vertical, direction. The lower section 26b has a
charging piece and can be lowered with the charging piece onto to the
bottle 20 disposed on the associated holding tray 24 to fill the same with a
filling medium, in particular a beverage. The lower section 26b has at the
lower end a filling sleeve 26c which surrounds the charging piece and the
uppermost section of the bottle neck during the filling of the respective
bottle to avoid splashing of the filling medium as far as possible.
Nevertheless, a contamination of the interior of the bottling apparatus
CA 0223~732 1998-0~-13
~. . . C ~ '
1 7
within the shielding wall 22, in particular of the inner surface of the
shielding wall 22 and other components of the bottling apparatus disposed
in this interior cannot be prevented completely.
The filling medium is supplied to the filling device from the interior of the
conveying and bottling rotating unit 16. However, flexible conveying tubes
and the like provided for this purpose are not shown in figures 1 to 3 for
simplicity. The filling medium is supplied to the conveying and bottling
rotating unit 16 via the rotational shaft structure 18 either from below
through the stationary assembly 10 or from above through at least one of
the vertical beams 1 2b. As can be seen in figure 2, a horizontal beam 1 2b
is formed as a tube. The rotating assembly 14 accordingly comprises a
supply tube for the filling medium. The supply tube extends co-axially to
the rotational axis of the conveying and bottling rotating unit 16 and a
conventionally well-known revolving joint- also denoted as rotary
distributor - is provided, which connects the supply tube with
corresponding tubes of the conveying and bottling rotating unit 16 leading
to the filling devices 26.
For the control of the filling devices 26 and of the holding means
associated to the holding trays 24, there are attached to the vertical beams
1 2a two circular ring-shaped cams 30 which are co-axial to the rotational
axis of the conveying rotating unit 16. I.e., the circular ring-shaped cams
30 are stationary. Each filling device 26 has associated two cam probing
struts 32 which probe the two cams by means of a probing head sliding
along the respective cam 30. The cam probing struts 32 are displaced by
the respective cam more or less radially inwardly in dependence on the
rotational position which the conveying and bottling rotating unit 16 has
reached. The resulting radial positions of the probing struts correspond to
control commands for the respective filling device and the respective
holding means. In particular, a filling medium valve of the filling device 26
CA 0223~732 1998-0~-13
18
will be operated and the lower section 26b of the filling device will be
raised and lowered, respectively, in dependence on the radial position of at
least one associated probing strut 32. The operation of the valves and of
the lower section 26b can be effected purely mechanically or, for example,
pneumatically. In the latter case, a separate pneumatic air supply has to be
provided .
As has already been mentioned, a certain contamination of the interior of
the bottling apparatus with filling medium cannot be avoided completely. In
particular in the case of beverages as filling medium hygienic problems
(settling in of germs) may arise therefrom if the interior of the bottling
apparatus including the inner surface of the shielding wall 22, the other
stationary components and of course the rotating assembly 14 itself are
not regularly cleaned thoroughly. To this end the bottling apparatus
comprises a first cleaning means 40 for cleaning the inner side of the
shielding wall 22, the cams 30 and other stationary components in the
interior 2 of the bottling apparatus which are not shown in detail. The first
cleaning means 40 comprises a revolving joint 42, which can also be
denoted as rotary distributor, and a conduit system 44, which is connected
with the conveying and bottling rotating unit 16 for common rotation. The
conduit system 44 is connected with the revolving joint 42 and has several
discharge openings 46 formed as nozzles. Further, the first cleaning means
40 comprises a supply line 48 leading from a cleaning fluid supply to the
revolving joint 42 fastened to the support assembly 12.
The conduit system 44 comprises a first section 44a and a section 44b,
which is disposed diametrically opposite the first section 44a with respect
to the rotational axis of the conveying and bottling rotating unit 16. The
two conduit system sections each comprise a tube line which firstly
extends radially outwardly from the revolving joint 42 and which then
bends down in vertical direction. There are tube line sections which branch
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1 9
off from the tube line and have nozzles 46 disposed at their ends.
According to the representation in figure 1 each conduit system section
44a and 44b has four nozzles which particularly allow to spray the circular
ring-shaped cams 30 from above and from below. Of course there may be
provided even more nozzles. If, for example, the interior 2 of the bottling
apparatus is closed upwardly as well by means of a corresponding wall
section, it is preferred that also this wall section may be sprayed by
corresponding nozzles.
In a cleaning operation phase of the bottling apparatus, the conveying and
bottling rotating unit 16 will be set into rotation and cleaning fluid, in
particular a cleaning liquid will be supplied to the discharge openings or
nozzles 46 via the supply line 48, the revolving joint 42, the conduit
system 44 rotating together with the conveying and bottling rotating unit
16. The nozzles 46 each direct a fluid jet onto a respective shielding wall
section or another stationary section of the bottling apparatus. The
cleaning fluid jet directed onto a shielding wall section moves over a
circular ring-shaped surface of the shielding wall inner side during the
rotation of the conveying and bottling rotating unit 16, so that the whole
inner circumference of the shielding wall 22 can be sprayed with the
cleanig fluid and therefore can be cleaned therewith. The same applies to
the stationary components in the interior of the bottling apparatus. After
several rotations of the conveying and bottling rotating unit 16, the whole
inner circumference of the shielding wall 22 and the stationary components
to be cleaned by means of the first cleaning means 40 are sprayed several
times with cleaning fluid. It is clear that several different cleaning fluids
may be used one after the other, for example, first a liquid cleaning
chemical, then water to remove the cleaning chemical and possibly also in
addition steam for sterilization. Therefore, extremely high cleanness and
sterile conditions can be reached.
CA 0223~732 1998-0~-13
It has to be added that the bottling apparatus, in addition to the first
cleaning means 40, may comprise a second cleaning means for the
cleaning of the rotating assembly 14. The second cleaning means
comprises preferably a stationary conduit system which is attached to the
inner side of the shielding wall 22 or to the support assembly 12 and
comprises further discharge openings preferably formed as nozzles which
direct cleaning fluid onto the rotating assembly to clean the same.
Accordingly, the whole interior of the bottling apparatus may be cleaned
thoroughly and possibly may also be sterilized.
In the following, the first cleaning means 40 will be described in moredetail in particular with respect to the construction of the revolving joint 42
(for this description reference is particularly made to figures 2, 4 and 5).
The revolving joint 42 substantially consists of two components, namely a
revolving joint stationary unit 50 manufactured from plastic (polyethylene)
and a revolving joint rotating unit 52 manufactured from stainless steel.
The annular (circular ring-shaped) revolving joint stationary unit is
assembled sandwich-like from three partial components 50a, 50b and 50c
and is held together by tension rods in the form of screws 54a each with a
respective nut 54b. To this end, the revolving joint stationary unit 50 has a
plurality of through-bores 56 which extend throught the partial
components 50a, 50b and 50c and in which the screws 54a are
introduced from one side and tightened from the other side with a
respective nut. As can be seen in figure 4, the through-bores 56 are
arranged on a circle with equal distance in circumferential direction and
about halfway between the inner edge 58a and the outer edge 58b of the
revolving joint stationary unit 50. The number of through-bores 56 and
therefore of the tension rods or screws 45a is set such that the three
partial components 50a, 50b, and 50c will be pressed evenly against each
other along the circle defined by the through-bores 56. For this purpose,
CA 0223~732 1998-0~-13
21
the surfaces of the partical components touching each other (the underside
of the partial component 50a and the upper side of the partial component
50b as well as the underside o~ the partial component 50b and the upper
side of the partial component 50c) are formed flat.
A symmetrical axis can be associated to the revolving joint stationary unit
50. The revolving joint stationary unit 50 (not considering the through-
bores 56 and other bores) is substantially symmetrical with respect to
rotation around this axis. The through-bores extend parallel with respect to
this symmetrical axis which is orthogonal to the upper and lower sides of
the partial components.
The revolving joint stationary unit 50 is mounted in the interior 2 of the
bottling apparatus 1 above the conveying and bottling rotating unit 16
such that it encloses the rotational shaft structure 18.1.e. the rotational
shaft structure 18 extends through the ringhole 60 of the revolving joint
stationary unit 50. The revolving joint stationary unit 50 is attached below
the horizontal beams 12b by means of three fastening rods 62 on these
horizontal beams 12b. For this purpose, the revolving joint stationary unit
50 has three further through-bores 64 having a larger diameter than the
through-bores 56 with the through-bores 64 being nearer to the inner edge
58a than the through-bores 56 and being arranged in correspondence to
the arrangement of the horizontal beams 12b, so that there is associated
to each horizontal beam 12b a fastening rod 62 and a through-hole 64.
The respective fastening rod 62 is formed as a threaded bolt and extends
in vertical direction through the corresponding through-bore in the
horizontal beam 12b and the through-bore 64 through all three partial
components 50a, 50b, and 50c. The fastening rods or threaded bolts are
each fixed by means of two nuts 63 at the respective horizontal beam 12b
and the revolving joint rotating unit 52 is fixed by means of two further
CA 0223~732 1998-0~-13
22
nuts 63 at the respective fastening rod. The revolving joint rotating unit 52
is arranged such that its symmetrical axis substantially coincides with the
rotational axis of the conveying and bottling rotating unit 16.
In the outer circumferential surface of the revolving joint stationary unit 50
an annular groove 70 is formed, namely in the lower end section of the
uppermost partial component 50a and in the upper end section of the
intermediate partial component 50b, with the annular groove 70 being
radially outwardly open. The two partial components 50a and 50b abut
against each other in a horizontal divisional plane. This horizontal divisional
plane divides the annular groove 70 into an upper and a lower section
which are symmetrical with respect to each other.
The annular groove 70 comprises a radially outer section which is wider in
axial direction and a radial inner section which is less wide in axial
direction, with the sections adjoining each other stepwise. The radial outer
section is limited in axial direction by two annular surfaces 72a and 72b
which are formed as sliding surfaces and lie in a respective horizontal
plane. The two annular surfaces 72a and 72b which will be denoted as
sliding surfaces in the following, accordingly face each other.
The revolving joint rotating unit 52 is received within the radial outer
section of the annular groove 70. The revolving joint rotating unit 52 is
formed as an annular body which is symmetrical with respect to rotation
(in the arrangement described the annular body has a vertical symmetrical
axis). The revolving joint rotating unit 52 has at its upper and its lower side
a annular surface 74a and 74b, respectively, which lies in a horizontal
plane. These annular surfaces are formed as sliding surfaces as well and
will be addressed in the following as sliding surface 74a and sliding surface
74b. Of the two sliding surfaces 74a and 74b which are turned away from
each other, the sliding surface 74a is disposed opposite of the sliding
CA 0223~732 1998-0~-13
23
surface 72a and the sliding surface 74b is disposed opposite to the sliding
surface 72b.
The revolving joint stationary unit 50 and the revolving joint rotating unit
52 bear against each other via the sliding surfaces 72a, 72b and 74a, and
74b. The revolving joint rotating unit 52 has, as can be seen from figure 5,
radial play with respect to the revolving joint stationary unit 50, since a
diameter referring to the inner circumference 81 of the revolving joint
rotating unit 52 is larger than a diameter referring to the circular cylindricallimiting surface between the inner and the outer section of the annular
groove 70. At the transition between the radial inner and the radial outer
section of the annular groove 70 there is formed a circular cylindrical
annular surface 76a and 76b at the upper partial component 50a and at
the lower partial component 50b, respectively, which limit the radial play
of the revolving joint rotating unit 42 with respect to the revolving joint
stationary unit 50. These surfaces may appropriately be denoted as
abutment surfaces 76a and 76b.
Between the inner circumferential surface 81a of the revolving joint
rotating unit 52 and a bottom 80 of the annular groove 70, which bottom
is opposite to the inner circumferential surface, a ring chamber 82 is
formed. This ring chamber corresponds substantially to the radial inner
section of the annular groove 70. Two axial blind-end bores are connected
with the ring chamber 82, which extend through the partial component
50a and end in the partial component 50b. These blind-end bores 84
which are disposed diametrically opposite to each other serve as
connections for the cleaning fluid to supply the same to the ring chamber
82. The blind-end bores 84, therefore, will be denoted also as connection
bores in the following. With each connection bore 84 there is connected a
supply section 48a branching off from the supply line 48 and an end
section 78b of the supply line 48, respectively.
CA 0223~732 1998-0~-13
24
The revolving joint rotating unit 52 has two diametrically opposite, radially
extending through-bores 90a and 90b. These through-bores 90a and 90b
serve as connections as well, to which the section 44a and 44b,
respectively, of the conduit system 44 is connected. The connection is
effected via a tube section 45a or 45b of the conduit system section 54a
or 54b which tube section is fixed within the respective through-bore 90a
or 90b. The respective tube section 45a or 45b is connected substantially
rigid with the revolving joint rotating unit 52 and extends in radial
direction.
On the upper side of the conveying and bottling rotating unit 16 there are
fixed two entrainment means 92a and 92b which comprise a respective
finger section extending in radial direction. In the upper end section of the
respective finger section there is provided a through-bore through which
the tube section 45a or 45b extends. The entrainment means are only
slightly displaced radially outwardly with respect to the revolving joint
rotating unit 52, so that the entrainment means engages near the revolving
joint rotating unit 52 at the tube section 45a or 45b. During the rotation of
the conveying and bottling rotating unit 16 this conveying and bottling
rotating unit 16 entrains the revolving joint rotating unit 52 via the
entrainment means 92a and 92b and the tube sections 45a and 45b.
Because of the engagement points of the entrainment means at the tube
sections being near to the revolving joint rotating units 52, damaging, in
particular bending, of the tube sections which is caused by forces acting
on the tube sections and being increased by lever effects will be avoided.
Accordingly, the revolving joint rotating unit 52 is connected with the
conveying and bottling rotating unit 16 and, thus, with the whole rotating
assembly 14 for common rotation, whereas the revolving joint stationary
unit 50 is fixed to the stationary assembly 10 via the support assembly 12
to prevent rotation.
CA 0223~732 1998-0~-13
The revolving joint 42 has two operating modes. In a first operation mode,
which can also be denoted as "dry running operating mode", the sliding
surfaces 52a, b and 54a, b serve as sliding surfaces alone and allow for a
rotation of the revolving joint rotating unit 52 with respect to the revolving
joint stationary unit 50 with low friction. In this first operation mode, the
sliding surface 72a and 74a and the sliding surfaces 72b and 74b abut
against each other only with little exerting of force. The axial distance
between the sliding surfaces 74a and 74b of the revolving joint stationary
unit 50 may slightly exceed the distance between the sliding surfaces 74a
and 74b of the revolving joint rotating unit 52. In the first operating mode
the ring chamber 82 is not sealed radially outwardly.
In a second operation mode which may also be denoted as "operation
mode for fluid transport", the sliding surfaces 72a and 74a and the sliding
surfaces 72b and 74b are pressed against each other by setting means to
be described in more detail so that these sliding surfaces serve as sealing
surfaces as well. In this second operation mode the ring chamber 82 is
sealed radially outwardly by the sliding surfaces serving as sealing
surfaces. Because of the pressing force causing the sealing abutment of
the sliding surfaces the friction between the sliding surfaces 72a and 74a
and between the sliding surfaces 72b and 74b is now increased, however.
Then, however, the friction heat produced thereby is transported away
without further ado if fluid is flowing from the supply line 48 through the
through-bores 84, through the ring chamber 82 and through the through-
bores 90a and 90b into the conduit system 44.
To provide for the two operation modes of the revolving joint 42, the
sliding surface 72b is arranged on an axially movable flange 94 of the
intermediate partial component 50b. The flange 94 is formed with a
weakening recess in the form of an annular groove 98 which is axially
CA 0223~732 1998-0~-13
26
upwardly open, to increase the axial movablility or deflectability of the
flange 94 and therefore of the sliding surface 72b.
The setting means for the deflection of the flange 94 comprises an annular
groove 100 in the upper side of the lower partial component c. The annular
groove 100 which is semi-circular shaped in a cross section is open axially
upwardly. An inflatable ring-shaped flexible tube 102 is received within this
annular groove 28 which flexible tube can also be denoted as inflating tube
or annular tube. As tube a simple bicycle tube can be used, for example.
The flexible tube 102 comprises a connection piece 104 (in the case of a
bicycle tube the reception for the bicycle valve), which extends axially
downwardly and projects from the underside of the lower partial
component 50c. A pneumatic line 106 is connected with the connection
piece 104, so that the inflating tube 102 selectively may be put under
pressure, i.e. can be inflated, or the air within the inflating tube 102 may
be let off again. If the inflating tube 102 is inflated, it completely fills theannular groove 100 and presses against the underside of the intermediate
partial component 50b mainly in the region of the flange 94. In this manner
the inflating tube bears on the partial component 50c. This partial
component 50c accordingly can be denoted as supporting plate.
The two operating modes can be recognized well in figure 5. In figure 5a
the inflating tube 102 is not inflated or only insignificantly inflated, so thatsubstantially no pressure force is exerted on the flange 94. The revolving
joint 49 correspondingly is in the first operating mode. In figures 5b and
5c, the inflating tube is inflated and exerts a pressure force onto the flange
94, which pressure force is directed axially upwardly, so that the flange is
deflected for sealing abutment of the sliding surfaces 72a and 74a and the
sliding surfaces 72b and 74b against each other. Accordingly, the
revolving joint 42 is in the second operating mode.
CA 0223~732 1998-0~-13
27
With respect to the sealing of the ring chamber 82 it is to be added that
the ring chamber is sealed radially inwardly. For this purpose there is
provided an annular groove 110 at the underside of the uppermost partial
component 50a, which annular groove is axially downwardly open and
which receives a 0-ring 112. This 0-ring 122 is only indicated in figure 5b.
The described construction of the revolving joint 42 makes it possible that
during the bottling, i.e. during the working operation of the bottling
apparatus, the sliding surfaces 72a and 74a and the sliding surfaces 72b
and 74b are disposed opposite to each other substantially without sealing
force so that only extremely insignificant friction occurs between them.
The revolving joint 42 is brought into the first operating mode (dry running
operation modeJ for this bottling, in that no pneumatic air is applied to the
inflating tube 102 or air contained within the flexible tube is let off, so thatthe flexible tube is not inflated.
At certain time intervals, the working operation of the bottling apparatus is
interrupted for cleaning operation phases. During these cleaning operation
phases, the sliding surfaces 72a and 74a and the sliding surfaces 72b and
74b are pressed sealingly against each other, by application of pneumatic
air to the inflating tube 102 to inflate the same and to exert the pressure
forces on the flange 94, which are necessary for the pressing of the sliding
surfaces against each other. In this case, the revolving joint 42 is in the
second operation mode (operation mode for fluid transport) and cleaning
fluid is transported from the cleaning fluid supply to the nozzles 46 via the
supply line 48, the ring chamber 82, the conduit system 44. The nozzles
46 direct, as has already been described above, a respective cleaning fluid
jet, in particular cleaning liquid jet, to the inner side of the shielding wall 22
and onto other stationary components (such as the circular ring-shaped
cams 30, for example) to clean the same. After termination of the
cleaning, i.e. after termination of the cleaning operationg phase, the air is
CA 0223~732 1998-0~-13
28
let off from the inflating tube 102 again, so that the revolving joint 42
adopts the first operation mode again and the working operation of the
bottling apparatus can be continued.
Certainly it stands to reason that the revolving joint 42 may be used in all
cases in which fluid has to be transferred from a stationary assembly to a
rotating assembly. The orientation of the rotational axis of the rotating
assembly is of no concern. The rotational axis of the rotating assembly
may also be horizontal or may be inclined with respect to a horizontal
plane or a vertical plane leading to a corresponding orientation of the
rotational axis of the revolving joint rotating unit. The revolving joint
according to the invention having setting means is particularly
advantageous if the fluid does not have to be transferred permanently from
the stationary assembly to the rotating assembly. As long as no fluid has
to be transferred, the revolving joint is set into the first operation mode
(dry running operating mode), so that there is only minor friction between
the revolving joint stationary unit and the revolving joint rotating unit. The
wear and tear of the revolving joint is reduced in this way, and there is no
danger of overheating of the revolving joint because of friction heat. For
the transfer of the fluid to the rotating assembly, the revolving joint is set
into the second operating mode (operation mode for fluid transport). The
friction which is increased in this operation mode because of the sealing
abutment of the sliding surfaces is - as mentioned - harmless, since the
generated friction heat will be transported away by the fluid. The revolving
joint according to the invention having radial play between the revolving
joint stationary unit and the revolving joint rotating unit and possibly being
shaped as a ring is particularly advantageous for retrofitting purposes.
Summarizing, the invention concerns a rotating apparatus for the handling
of objects, in particular containers, for examples for the filling of said
containers. The rotating apparatus comprises a stationary assembly and a
CA 0223~732 1998-0~-13
29
rotating assembiy which is rotatable with respect to the stationary
assembly and is driven by a rotary drive. According to the invention there
is provided on the rotating assembly at least one discharge opening for the
discharge of a cleaning fluid for cleaning a shielding wall being stationary
during the rotational operation of the rotating assembly and optionally for
cleaning other stationary components. The at least one discharge opening
is connected to a stationary cleaning fluid supply via a revolving joint. For
the revolving joint it is proposed that the revolving joint comprises a
revolving joint stationary unit fixed or fixable to the stationary assembly
and a revolving joint rotating unit connectable or connected to the rotating
assembly for common rotation. Said two rotating joint components are
rotatably supported at each other by axially directed sliding surfaces.
Besides the designs of the rotating apparatus according to the invention
proposed above (in which - in deviation of the statements in the beginning
- a shielding wall which at least partially encloses the rotating assembly
~ and which is stationary during the rotational operation of the rotating
assembly may be omitted and in which there is arranged on the rotating
assembly at least one discharge opening for the discharge of a cleaning
fluid for cleaning at least one of the shielding wall and other stationary
components of the rotating apparatus) and of the revolving joint according
to the invention, other advantageous designs are possible. As a particularly
advantageous design it is proposed that at least one sliding surface of at
least one of the two revolving joint components is formed on a ring plate
which is elastically deformable and that this ring plate has a loading zone
in radial distance from the sliding surface for loading by an axially directed
setting force. In a further ring zone, in particular in an intermediate zone
between the sliding surface and the loading zone, a supporting zone for
the ring plate is provided so that by loading of the loading zone with
setting force an axial movement of the sliding surface is introduced, in
=
CA 0223~732 1998-0~-13
particular an axial movement, which is opposed to the direction of the
loading with the setting force.
According to this suggestion a particularly simple design of the revolving
joint according to the invention is achieved keeping the manufacturing
costs low. According to this suggestion, the revolving joint according to
the invention may have a particularly low height in axial direction, for
example achieved in such a way that setting means which are possibly
provided are displaced primarily in radial direction with respect to the
sliding surfaces and at the most only insignificantly in axial direction, so
that they are disposed substantially in the same axial region of the
revolving joint as the sliding surfaces. For the low overall height of the
revolving joint in axial direction, a further contribution is obtained if the
elastically deformable ring plate is made from metal, for example, stainless
steel, so that particularly low dimensions of the ring plate in axial direction
are possible.
The elastically deformable ring plate preferably forms with its slidingsurface a limiting wall of an ring-shaped radially open annular groove which
receives the respective other revolving joint component. The ring plate may
be supported on a ring plate carrier (for example made from plastic) with
formation of the supporting zone between the ring plate and the ring plate
carrier. In this context, it is proposed that there are arranged setting means
(for example in the form of at least one inflating tube) on the ring plate
carrier in the region of the loading zone, which are axially effective.
There may be arranged two ring plates on the ring plate carrier with the
sliding surfaces of the plates receiving the respective other revolving joint
component between them. This design of the rotating apparatus and the
revolving joint is preferred particularly.
-
CA 0223~732 1998-0~-13
31
In the absence of an external setting force, the sliding surface of the ring
plate is preferably out of sealing contact with an associated countersliding
surface of the respective other revolving joint component wherein the
sliding surface and the countersliding surface can be brought in sealing
contact by introduction of a setting force from the outside. Accordingly,
the sliding surfaces can lie opposite each other substantially without any
sealing force in a first operation mode of the revolving joint (working
operation of the rotating apparatus) and can be pressed sealingly against
each other for a second operation mode of the rotating apparatus (cleaning
operation phase of the rotating apparatus). Thus, in said first operation
mode, an excessive warming up or heating up of the sliding surfaces
because of friction heat is avoided despite a rotational movement of the
two revolving joint components with respect to each other, which possibly
takes place.
The setting force need only be applied for the adjustment of the secondoperation mode so that the setting means which possibly are provided for
this purpose are only put under strain in this second operation mode. In
case of an absence of the setting force, for example because of a failure of
the setting means or of a pressure medium supply for the setting means,
which is possibly provided, the first operating mode inevitably is adopted
so that the normal working operation of the rotating apparatus is not
disturbed .
To avoid an excessive warming up or heating up of the sliding surfaces or
the revolving joint also in the second operation mode in case that the
revolving joint components rotate with respect to each other, it is
suggested as being particularly advantageous that the revolving joint has
supply means for a sliding or/and heat carry-off fluid which allow the
supply of the sliding or/and heat carry-off fluid to sliding surfaces of the
revolving joint.
CA 0223~732 1998-0~-13
r
32
By corresponding supply of the sliding or/and heat carry-off fluid the
friction between the sliding surfaces can be reduced and, accordingly, the
resulting friction heat can be minimized or excessive friction heat can be
led away so that the revoiving joint may have a particularly high service
life and needs substantially no, or only minimal, maintenance.
The sliding or/and heat carry-off fluid may be formed by the cleaning fluid.
Accordingly, a sliding or/and heat carry-off fluid supply separate with
respect to the stationary cleaning fluid supply provided according to the
invention is unnecessary.
The supply of the sliding or/and heat carry-off fluid to the sliding surfaces
may be effective timewise out of cleaning periods, for examp:e by
providing that out of cleaning periods a reduced cleaning fluid flow is
supplied which only serves the purpose of reducing the friction or the
purpose of carrying off heat or that out of cleaning periods a sliding or/and
heat carry-off fluid (in particular a sliding or/and heat carry-off liquid, for
example water) separate from the cleaning fluid is supplied.
For the supply of the heat or/and heat carry-off fluid, supply means may be
provided which are independent of the conduit system of the cleaning
fluid.
With regard to the low axial overall height of the revolving joint it is
preferred that at least one connection, preferably all of the connections:
cleaning fluid connection at the revolving joint stationary unit, cleaning
fluid connection at the revolving joint rotating unit, possibly sliding or/and
heat carry-off fluid connection of the revolving joint and (in the case of
setting means) possibly pressure medium connection of the revolving joint
are formed as radial connections.
CA 0223~732 1998-0~-13
,
33
In the following, the invention will be explained in more detail by means of
a further embodiment shown in figures 6 and 7.
Figure 6 shows in figure 6a a cross-section through a revolving joint
according to the invention along line A-~ in figure 6b which
could be provided in the rotating apparatus of figure 1 in place
of the revolving joint of figures 4 and 5, and in figure 6b a top
view onto the revolving joint of figure 6a according to the
viewing direction indicated by means of arrow B.
Figure 7 shows in figure 7a a section through the revolving joint of
figure 6 along line VIIA-VIIA in figure 6b and in figure 7b a
section through this revolving joint along line VIIB-VIIB in
figure 6b.
The second embodiment of figures 6 and 7 is explained in the following
only with regard to the differences from the first embodiment of figures 1
to 5. As far as that goes, reference is made expressis verbis to the
foregoing description of the first embodiment. Components of the second
embodiment whose function corresponds to components of the first
embodiment are provided with the same reference numbers which,
however, are increased by the number 200.
The revolving joint 242 which according to figure 6a - with the exception
of deviations to be seen in figure 6 - is rotationally symmetrical to a
symmetrical axis S extending vertically comprises, as the revolving joint 42
of figures 1 to 5, a revolving joint stationary unit 50 and a revolving joint
rotating unit 252. The revolving joint stationary unit 250 comprises two
ring plates 320a and 320b which are mounted by means of tension rods
(screws 254a with nuts 254b) to the axial ends of an annular ring plate
carrier 322. The ring plates project over the ring plate carrier 322 radially
outwardly and the surfaces of the ring plates projecting radially outwardly
CA 0223~732 1998-0~-13
,c ~ r
34
beyond the ring plate carrier 322 and facing each other serve as sliding
surfaces 272a and 272b.
The ring plates 320a and 320b are manufactured from stainless steel andare resiliently deformable. By means of the tension rods 254a, 254b the
ring plates are held axially in a region of a supporting zone which lies
radially more inwardly than the sliding surfaces. The ring plates abut in the
region of the annular supporting zone and also radially more inwardly
against the ring plate carrier 322.
Radially outwardly of the supporting zone defined by the tension rods
254a, 254b, the axial dimension of the ring plate carrier 122 is somewhat
reduced, as can be seen in figure 7, so that the axial distance between the
sliding surfaces 272a and 272b can be reduced under corresponding
elastic deformation of the ring plates 320a, 320b and also (to a certain
amount) of the tension rods by exerting of a corresponding setting force
onto the ring plates in a region which lies radially more inwardly with
respect to the supporting zone. For this purpose there are provided setting
means in the form of two inflating tubes 302a and 302b which are
disposed radially more inwardly than the supporting zone.
The inflating tubes 302a and 302b are disposed respectively in an annular
groove 300a or 300b of the ring plate carrier 322 preferably being
manufactured from plastic, with the annular groove being open in axial
direction and being covered by a ring section of the ring plate 320a or
320b which lies radially inwardly. The inflating tubes serve for loading the
axially opposite ring section of the respective ring plate 320a or 320b with
a setting force which is axially directed, to obtain an axial movement of the
sliding surface 274a and 274b opposite to the direction of the loading with
the setting force, if the sliding surfaces 274a and 274b have to be brought
into sealing contact or sealing engagement (second operation mode of the
CA 0223~732 1998-0~-13
revolving joint 242) with the respectively associated axially opposite sliding
surface 274a or 274b of the revolving joint rotating unit 252, which to the
greater part (also in the region of the sliding surfaces 274a and 274b) is
manufactured from plastic.
For exerting the axially directed setting forces onto the ring plates 320a,
320b the flexible pressure tubes 302a and 302b, which define a loading
zone, are inflated by introduction of a pressure medium via lines 306a,
306b for the pressure medium. To bring the revolving joint 242 from the
second operation mode (operation mode for fluid transport) again into the
first operation mode (dry running operation mode) the pressure medium (in
particular pneumatic air) will again be let off from the inflating tubes, so
that an elastic restoring force arising from the elastic deformation of the
ring plates 320a and 320b displaces the sliding surfaces 274a, 274b
axially from each other and accordingly brings the same out of sealing
engagement with the sliding surfaces 274a and 274b of the revolving joint
rotating unit 252.
For the sealing of the ring chamber 282 radially inwardly for the operating
mode for fluid transport, which chamber is limited axially between the ring
plates 320a, 320b and radially between an outer circumferential surface of
the ring plate carrier 322 forming the bottom 280 of the annular groove
270 and the inner circumferential surface 281 of the ring-shaped revolving
joint rotating unit 252, there are provided two 0-rings 312a and 312b
located in a respective annular groove of the ring plate carrier 322. The 0-
rings sealingly engage radially outwardly of the tension rods 254a, 254b
on the surfaces of the ring plates 320a and 320b comprising the sliding
surfaces 272a and 272b.
To be able to reduce the friction which already is substantially reduced
because of the missing sealing engagement between the sliding surfaces
_
CA 0223~732 1998-0~-13
36
272a and 274a and 272b and 274b associated to each other, even further
in the first operation mode (dry running operation mode) or to be able to
carry off - independently of the supply of the fluid (for example cleaning
fluid in the case of the bottling apparatus 1) to be transported in the
second operation mode via the connection bores 284 to the ring chamber
282 - friction heat arising from this reduced friction and correspondingly
being reduced, the revolving joint stationary unit 250 comprises
additionally to the connecting bores 284, which are directed radially in the
described embodiment a further connection bore 330 being also directed
radially (compare figure 6). Via this connection bore 330, a fluid (sliding
or/and heat carry-off fluid, for example water) being separate from the fluid
to be transported in the second operation mode may be supplied to the
ring chamber 282 and, therefore, to the sliding surfaces 272a, 274a,
272b, 274b. This sliding or/and heat carry-off fluid will leak to a certain
extent between the sliding surfaces, since in the first operation mode there
is no sealing engagement between the sliding surfaces being associated to
each other. However, this can be accepted, in particular if the sliding
or/and heat carry-off fluid is simple water, for the benefit of the friction
being further reduced or for the benefit of an improved carrying-off of heat
in the first operation mode and, therefore, for the benefit that the service
life of the revolving joint is increased further. The amount of sealing or/and
heat carry-off fluid leaking out cannot be very large, provided that this fluid
is supplied to the ring chamber 282 under low pressure which generally
will be sufficient for a substantial reduction of the friction between the
sliding surfaces. In the second operation mode serving for the transport of
fluid, however, one will often operate with relatively high pressure so that
for this operation mode, the sealing engagement between the sliding
surfaces 272a, 274a and 272b, 274b being associated to each other and
being axially directed will generally be indispensable because of the major
loss of fluid which otherwise will occur in case of a high fluid pressure.
CA 0223~732 1998-0~-13
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37
As has already been mentioned, the connection bores 284 for the fluid
supply in the second operation mode are directed radially, so that the fluid
to be transported will be supplied to the ring chamber 282 radially from the
inner side. In figure 6b there are to be seen two threaded bores 232
neighboring to the connection bores 284, which threaded bores 232 serve
for the fastening of a connection flange of a corresponding fluid supply line
at the revolving joint stationary unit 250. Also, the supply of a pressure
medium to the inflating tubes 302a and 302b takes place radially from the
inner side (compare 7a) and the flowing off of the fluid from the ring
chamber 282 via the revolving joint rotating unit 252 takes place in radial
direction as well, namely radially outwardly (compare throughbore 290a
and tube section 245a in figure 7b). The same applies to the possible
supply of a sliding or/and heat carry-off fluid via the bore 330 in the
revolving joint stationary unit 250 which bore 330 is directed radially as
well. Because of this radial alignment of all fluid or pressure medium
connections, a particularly low overall height of the revolving joint 242 in
axial direction (axis S) results. The revolving joint 242 can therefore often
be retrofitted also in case of restricted space conditions in a rotating
apparatus (for example a bottling apparatus) which is substantially ready
for operation.
It has to be mentioned additionally for the revolving joint rotating unit 252
that this unit carries in a radially outwardly open annular groove in a ring-
shaped main rotating unit part 334 manufactured from plastic a stainless
steel ring 336, which has bores 338 aligned with the throughbores 290 for
passing through of the fluid to be transported. The tube sections 245 (tube
section 245a in figure 7b) are welded to the stainless steel ring so that a
fluid connection is established between the connection bores 284 and the
conduit system (which leads to the nozzles 46 in case of the embodiment
of figure 1) linking up with the tube sections 245 via the bores 290, 338
and the ring chamber 282. For sealing there is provided concentrically to
CA 0223~732 1998-0~-13
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38
the bore 338 in the stainless steel ring 336 a sealing ring 340 which is
sealingly effective between the main rotating unit part 334 and the
stainless steel ring 336.
A rotational entrainment of the revolving joint rotating unit 252, in case of
an application corresponding to figure 1, can be effected via the tube
sections 245 as shown in this figure. Alternatively, it is suggested to drive
the revolving joint rotating unit 252 for rotation via flexible tension
elements, for example tension cables, which engage on one side at the
rotatably driven rotating assembly and on the other side at the revolving
joint rotating unit, preferably via a safety element being effective between
one of rotating assembly and tension element on one hand and tension
element and revolving joint rotating unit on the other hand. The safety
element may be in the form of a shearing bolt. In this way, an interruption
of the operation of the rotating apparatus because of blockage of the
revolving joint rotating unit possibly because of an operating error (sealing
engagement of the sliding surfaces when the revolving joint rotating unit is
rotating without supply of fluid to be transported and without supply of
sliding or/and heat carry-off fluid) is prevented, since after response of the
safety element for disconnecting the rotational drive connection between
the rotating assembly and revolving joint rotating unit a free rotation of the
rotating assembly is possible. Such a shearing bolt, on which the tension
element engages, for example could be inserted into one or several of the
four axial bores 342 in the revolving joint rotating unit 252 which bores
can be seen in figure 6b.
