Title of Invention

COMBINATION ASSEMBLY FOR MANAGING A HOUSE OR LIKE ALASTIC PUMP TUBE IN A POSITIVE DISPLACEMENT PUMP

Abstract Acombination assembly is dicclosed for managing a hose or like elastic pump tube or pump channel such that paticularly is used in a peristaltic pump.The invention is chracterictic by having the jump equiped with in assembly for the adjustment of the pump pressure and/or compression imposed on the house/tube the assembly comprising a aeplessly adjustable accentric adjustment mechanism.
Full Text WO 2004/076861 PCT/FI2004/000106
Combination assembly for managing a hose or like elastic pump tube in a
positive displacement pump
The present invention relates to a combination assembly according to the
preamble of claim 1 for managing a hose or like elastic pump tube or pump
channel such that particularly is used in a positive displacement pump.
Positive displacement pumps, in which peristaltic pumps form a subclass, are
employed for pumping problematic substances in particular, such as abra-
sive, corrosive, slunied or high-viscosity liquids and liquid-suspended solids.
Peristaltic pumps are also preferred when pumping as a primary function
must be complemented with accurate metering, high hygienic standard and
leakproofness. Peristaltic pumps are used widely, e.g., in the manufacture of
foodstuffs, drugs, oil and chemical products. In heavy industries, peristaltic
pumps serve to pump, i.a., such materials as liquids and ore/mineral
suspensions.
To operate properly, a peristaltic pump must be capable of forcing a volume
of a fluid medium to move along a hose/tube by way of peristaltically com-
pressing the hose from end to end during one turn of the pump rotor while
simultaneously the next fluid volume is already filling the hose. Conventional-
ly, this pumping sequence is implemented by rotating a nonrotary shoe or
pressing roller, whereby the hose is subjected to progressive compression in
the nip between the shoe/roller and the peripheral wall of the pump head.
Furthermore, the hose/tube/tubing is selected to be sufficiently elastic and
reinforces such that the hose resumes its circular profile immediately after
the compression thereby creating a vacuum in its lumen thus inducing the
entry of the next volume of the fluid medium into the hose.
Most generally, this pump construction is implemented by way of flexing a
straight hose/tube into a semicircle adapted into the pump head cavity
wherein the hose is compressed radially by two diametrically opposite shoes
or rollers. This kind of pump embodiment is characterized in that the shoe or
roller applies a compressive force against the hose at all times and that the
pump is typically half filled with a lubricant (e.g., glycerin) serving both to

WO 2004/076861 PCT/FI2004/000106
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transfer frictional heat to the pump's external housing structures and
therefrom out from the pump as well as to reduce sliding or rolling friction
occurring in the compression of the hose. However, at higher rotor speeds or
operation against a high head, the pump heats up so much that it must be
stopped at regular intervals for cooling down. If the pump is specified for
continuous operation, the pump as well as the drive motor/gear must be
overdimensioned resulting in substantial investment and operating costs.
Additional costs are also incurred during service and adjustment of the pump
inasmuch as the lubricant must be drained and replaced at the same time as
the seals of the pump housing and shaft are replaced.
Moreover, in this kind of prior art construction, both ones of the rotor
shoes/rollers begin to compress the hose at its suction end thus imparting a
transient force impulse on both the stationary hose fixture and the hose itself.
Such an impulse occurring twice during a single turn of the pump rotor
imposes strong stresses on the hose and particularly the captive fittings of
the hose ends.
In some pump constructions, attempts have been made to reduce the high
abrasive friction and rapid pulsation by way of using compressing wheel
rollingly running in bearings along an orbital trajectory. Herein, the hose may
be bent into a full circle or even more, whereby the hose suction and dis-
charge ends overlap. This kind of a single-contact rolling wheel minimizes the
friction between the compressing wheel and the hose thus needing substan-
tially less lubrication. Moreover, the single-contact pump rotor running over a
full circle of the hose halves the number of pumping pulses, that is, only one
fluid pulse instead of two is ejected from the pump per one turn of the rotor.
Fluid pulsation also remains less aggressive due to the larger compressive
area of the rotor that closes the lumen of the hose at a respectively slower
speed resulting in slower onset/fall of the fluid pulse than in double-contact
pumps. This kind of construction also has less friction and, hence, generates
less heat thus facilitating continuous operation at a higher rotor speed,
whereby the desired volumetric flow rate can be produced with a smaller
pump, gear train and motor.
However, continuous operation at a high speed is strenuous to both the hose

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and, in particular, the captive fittings of the hose ends. Hence, a typical prob-
lem in prior-art positive displacement pumps of the peristaltic type is asso-
ciated with the captive securing of the hose ends to the pump housing. The
hose is conventionally fixed with hose damps/inserts to a support flange
mounted to the external side of the pump housing. The captive securing of
the hose ends must take the line pressure imposed on the pump, seal the
hose feedthrough opening so that the medium serving as hose lubricant in
the pump does not leak out from the pump housing and, simultaneously, fix
the hose to the pump housing so tightly that the forces imposed by the rotor
on the hose cannot pull/push the hose end free.
The state of the art is represented, e.g., by patent publication FR-1114877
disclosing a construction in which a roll is adapted orbitally rotatable in the
pump cavity by means of a crankshaft. The pump structure is illustrated in
FIG. 2 of cited reference publication. It must be noted that the elastic pump
flow channel does not cover a full 360° circle in the pump cavity.
In patent publication AU-19971675, "Orbital peristaltic pump with dynamic
pump tube," is disclosed an oscillatory compressive ring adapted rotatable in
the pump cavity by alternative drive means. The tube is passed a full 360°
circle atong the inner periphery of the pump cavity and the suction/discharge
ends of the tube enter/leave the pump cavity in a tangential fashion relative
to the pump housing. The cross section of the tube is shown in FIG. 6 of cited
reference publication.
A crucial problem hampering prior-art constructions is the total lack of an
adjustment mechanism for setting the compressive force. More specifically,
no facility is provided for setting the compression applied on the pump hose
or like elastic flow channel, whereby the distance between the rotor and the
pump cavity cannot be varied from a constant value. In addition to the short-
comings listed above, conventional embodiments of the captive fitting of the
hose to the pump housing are often implemented in an extremely awkward
fashion. In other words, the technical implementation in regard to its
practicable functionality and everyday servicing has mostly been neglected
entirely.

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Almost invariably, the above-mentioned problems are associated with each
other and often in an intimate causal relation to each other. Hence, it appears
to be extremely essential for efficient and service-friendly operation of a peri-
staltic pump that further attempts are made to develop a system featuring
simple and reliable captive fitting of the hose as well as an adjustment
mechanism of the hose compression.
It is an object of the present invention to overcome the above disadvantages.
The goal of the invention is attained by means of a combination assembly for
managing a hose or like elastic pump tube or pump channel, in particular
such a hose/tube that is used in a positive displacement pump.
The specifications of an assembly according to the invention are disclosed in
the characterizing parts of appended claims. The invention differs from the
prior art by virtue of having the pump equipped with an assembly suited for
the adjustment of the pump pressure and/or compression imposed on the
hose/tube, the assembly featuring a mechanism with steplessly adjustable
eccentricity. In addition to this feature, the invention is characterized in that
the peristaltic pump is adaptable to use, either alone or in conjunction with
the eccentric adjustment mechanism, a captive hose fitting system for
managing the pressure imposed on the pump hose/tube.
In the following, the invention is described in more detail by making reference
to the appended drawings in which
FIG. 1 is an illustration of an embodiment of a peristaltic hose pump;
FIG, 2 is a cross-sectional side elevation view of an eccentric adjustment
mechanism according to the invention adapted to a peristaltic pump;
FIG. 3 is a cross-sectional front elevation view of- an eccentric adjustment
mechanism according to the invention set into its uppermost position;
FIG 4 is a cross-sectional front elevation view of an eccentric adjustment
mechanism according to the invention set into its lowermost position;

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FIG 5 is a cross-sectional view of an eccentric adjustment mechanism
according to the invention;
FIG. 6 is a longitudinally sectional view of a captive hose fitting system
according to the invention adapted to a peristaltic pump; and
FIG. 7 is a cross-sectional view of a captive hose fitting system according to
the invention adapted to a peristaltic pump.
Referring to FIGL 1, therein are shown the main components of a peristaltic
pump. The pump comprises a pump body 1, a hose 2 and a rotor 3 mounted
freely rotatable on bearings mounted onto an eccentric adjustment bushing 5.
The eccentric adjustment bushing in turn is mounted on a crankshaft pin
denoted by reference numeral 10 of FIG, 2. The crankshaft is mounted on
bearings on the rear wall of pump body 1, centrally in regard to the pump
cavity 34. The hose or like elastic pump tube or pump channel is inserted into
the pump cavity with the rotor housed therein, whereby the hose rests
against the pump cavity inner perimeter so as to cover a full circle. The hose
ends are captively fitted in feedthrough openings 8 of the pump body. Actuat-
ed by the drive means, the crankshaft forces the rotor to rotate in the pump
cavity at si given distance from the interior perimeter of the purnp cavity. This
distance is set smaller than the two-fold thickness of the hose/tube wall.
Hereby, the rotor compresses the hose inserted in the pump cavity so that,
with the rotation of the rotor, the volume of fluid medium being pumped and
contained in the hose in front of the rotor is prevented from leaking in the
reverse direction past the point of the hose compressed by the rotor. With the
rotation of the rotor in the pump cavity, it rolls over the hose surface thus
propelling the bulk of fluid medium contained in the hose. With the rotary
progressive motion of the rotor and the hose recovering its circular profile
immediately after the point of rotor compression, the hose creates a vacuum
that causes the hose to become refilled with the fluid medium being pumped.
In FIGS. 2, 3 and 4 is shown an eccentric adjustment mechanism comprising
an eccentric adjustment bushing 5, a worm gear 6, a spur gear 9, a lockcover
4, lockpins 11 and locking bolt(s) 12. The eccentric adjustment mechanism
serves to adjust the gap 23 shown in FIG. 4 between the rotor outer surface

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and the pump cavity inner periphery that determines the compressive force
imposed on the hose. The rotor gap is adjusted by rotation of the eccentric
bushing 5 mounted on the crankshaft pin 10. The rotor in turn is mounted on
a bearing on the outer periphery of the eccentric bushing. The eccentricity 19
of the adjustment bushing illustrated in FIG. 3 is accomplished by drilling the
bore of the bushing eccentrically in regard to the outer periphery of the
bushing.
The rotation of the eccentric adjustment bushing takes place with the help of
a reduction gear such as a worm gear adapted between the eccentric
bushing and the crankshaft. The reduction gear is constructed by adapting
the worm 6, i.e., the driving shaft of the reduction gear, into the solid body
part of the eccentric bushing. The spur gear 9, i.e., the driven gear, is
mounted to the end of the crankshaft pin. Alternatively, the driven spur gear 9
may also be machined directly to the end of the crankshaft pin. With the rota-
tion of the driving shaft, the eccentric bushing turns on the crankshaft pin,
whereby the distance 23 between the rotor outer periphery and the pump
cavity inner periphery changes as shown in FIG. 4. The maximum possible
span of pump rotor-to-body distance adjustment is equal to the difference
between wall thicknesses 20 and 21 of bushing 5 as shown in FIG. 3.
A worm gear or like self-locking gear is advantageously used as the reduc-
tion gear. This allows the rotor gap adjustment to be carried out accurately
and easily by a single operator, since the compressive force applied to the
hose cannot rotate the bushing backward inasmuch as the self-locking reduc-
tion gear prevents uncontrolled rotation of the bushing. Based on the use of a
toothed reduction gear, the rotor gap adjustment can be performed without
the need for any special tools or adjustment shims.
In a running pump, the eccentric adjustment bushing is continually subjected
to forces that tend to rotate the eccentric bushing. With the help of lockcover
4, the eccentric bushing is locked to the crankshaft pin so that the reduction
gear need not take all the rotational forces directed to the eccentric bushing
during the operation of the pump. The lockcover is clamped against a conical
surface 14 of the eccentric bushing with a bolt 12 illustrated in FIG. 2 to pass
through the lockcover and fit into a threaded hole 22 of the crankshaft end

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shown in FIG. 3. In addition to providing the locking force of the conical fit,
the tightened bolt presses a sealing O-ring 15 placed between the lockcover
flange and the eccentric bushing in order to prevent the hose lubricant or
other contamination from entering into the reduction gear and the interface
between the eccentric bushing and the crankshaft pin. Thus, the screws
passing through the lockcover only serve to provide the clamping force that
keeps the lockcover tight against the conical surface 13. The force, which
tends to rotate the eccentric bushing and is transmitted via the conical inter-
face between the lockcover and the eccentric bushing, is transmitted further
to the crankshaft end via the locking between the crankshaft and the
lockcover. This locking is accomplished with the help of lockpins 11 sunken
in the crankshaft end or a key slot The lockcover is respectively provided
with recesses 13 mating with the lockpins or key.
By virtue of the lockcover, also the inner races of the bearings mounted on
the eccentric bushing can be damped axially between a shoulder 17 of the
eccentric bushing and a shoulder 16 of the crankshaft. This is necessary to
clamp the inner races of the bearings in a stationary and tight fit between the
shoulders of the eccentric bushing and the crankshaft thus preventing the
bearings from having a play in regard to the eccentric bushing.
A characteristic property of a peristaltic pump based on positive displacement
is that the inner surface of the hose/tube erodes during pumping. This
process reduces the hose wall thickness and, thence, the compression of the
hose in the gap between the pump rotor and body. Hence, the hose com-
pression must be adjusted during the life of the hose. During continuous use,
the known wall thickness of the hose wears down to an unknown value. In
such a situation, it is very difficult to establish valid rules to be applied in
conventional techniques of correct adjustment of hose compression. Invalid
adjustment rules must be complemented with practical operating experience
that frequently invokes serious overcompression and pump damage
situations. In contrast, the eccentric adjustment assembly disclosed in the
present application allows runtime adjustment of hose compression to be
carried out simply with a calibrated torque wrench. The end 18 of the worm is
so shaped as to be rotatable by means of the torque wrench. As the worm is
thus turned with the torque wrench, an accurately set torque can be applied

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during rotation of the worm. With the applied torque thus being always con-
stant, also the compressive force imposed on the hose becomes sufficiently
accurately set to a constant value. In the adjustment of hose compression, it
is important to apply a constant tightening torque at all times in order to com-
pensate for slackening compression due to the wear of the hose.
In FIG. 3 the eccentric adjustment is shown set into its minimum compression
gap position. In FIG. 4 respectively, the eccentric adjustment is shown set
into a position wherein the compression gap 23 is set to its maximum value.
In FIG. 5 is shown an alternative embodiment of the eccentric adjustment
assembly according to the invention. This modification of the adjustment
assembly is suited for setting the hose compression particularly in small-size
pumps in which the adoption of the above-described reduction-gear-based
adjustment arrangement is not economically or physically viable.
The eccentric adjustment assembly of FIG. 5 comprises a locknut 25 at the
crankshaft end, a lockcone 27 and an eccentric bushing 5. In this embodi-
ment, the hose compression adjustment is based on the same eccentric
adjustment concept as described above and illustrated in FIG. 2. The princi-
pal differences between these two embodiments are seen in the technique of
providing the torque for rotating the cone bushing and in the arrangement for
locking the eccentric bushing in place. Rotation of the eccentric bushing on
the crankshaft pin takes place by turning the bushing by the keyhead of its
flange with a conventional wrench or tongs. The eccentric bushing is locked
into the desired adjustment position by the lockcone 27. The lockcone is
pressed home by way of tightening the locknut 25 onto an outer thread 26
made on the crankshaft end. The locknut is secured to the shaft with a tab
washer. The lockcone is detached with the help of extractor threads 24 made
on the flange of the lockcone. To this end, the lockcone flange is provided
with two threaded holes 24 wherein extractor bolts can be fitted to remove
the lockcone. The bolts are tightened until their tips meet an inner shoulder of
the eccentric bushing, whereby they force the eccentric bushing off from its
place. For precise hose compression adjustment, between the tab wafer and
the eccentric bushing may be placed a dial plate with a graduation needed in
the adjustment. The dial plate is secured to the shaft with the help of the

9
same key slot as is used for securing the tab washer.
A captive hose fitting system complementing the assembly according to the
invention is shown in FIG 6 and 7. The captive system comprises a rubber
flange 32 inserted to the hose end, seal gills advantageously comprising two
gills 33, and two halves of a split collet 28 and a mounting flange 7 that may
be replaced by a conventional piping flange if so desired.
The seal gills 33 project from the hose end flange 32 in a form with the dia-
metrical dimension across the outer edges of the seal gills matching the outer
diameter of the hose end flange. The seal gills are situated about the outer
perimeter of the hose, at opposite sides thereof relative to each other. The
cross section of the seal gills is made 0.5 to 1 mm thicker than the width of
the slits 34 made to the collet as it is divided into two halves.
The feedthrough opening in the pump body is of the same size or slightly
larger than the outer diameter of the hose end flange 32 inserted to the hose
end. To mount the hose into the pump cavity, the hose end is passed from
inside the cavity outward via the feedthrough opening. The length of the free
hose end projecting out from the feedthrough opening is trimmed to about
twice the hose thickness. The split collet 26 is placed about the hose end,
behind the hose end flange 32, so that the seal gills 33 remain trapped
between the split collet halves. Next, the flange of the split collet is fitted
against the hose end flange already inserted to the hose end. To the rear
side of the flange of the split collet is placed an O-ring 29. Finally, the hose
end is pushed back into the pump cavity so deep that the flange of the split
collet remains resting against the pump body 1. Then, the O-ring placed on
the split collet remains compressed in the gap between the flange of the split
collet and a bevel 30 made to the edge of the feedthrough opening of the
30 pump body thus exerting a force that presses the halves of the split collet
against the seal gills. Resultingly, a seal is established between the perimeter
of the split collet and the pump cavity, The captive fitting set comprising the
hose end flange, the split collet and the O-ring is tightened with the help of
mounting screws 7 against the rim of the feedthrough opening made on the
35 pump body. To accommodate the hose end flange, the mounting flange has
a sunken shoulder 31 made thereon serving to prevent overtightening of the

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hose end flange. The depth of the sunken shoulder is dimensioned such that
the mounting flange meets the flange of the split collet at a depth where the
compression of the hose end flange at the hose end is about 30%. This
amount of compression is sufficient to keep the hose end firmly clamped.
Excessive compression of the hose end flange damages the hose end flange
thus impairing the strength of the flange. In certain cases, the fixing holes of
the mounting flange can be drilled into the same positions as those of a
standardized piping flange corresponding to the nominal size and pressure
specifications of the pump. Then, the mounting flange can be replaced by a
conventional piping flange if so desired.
A steel ring embedded in the hose end flange further assures that the hose
end flange retains its shape and the flange cannot slip off from its captive
position even under heavy mechanical stress. The seal gills, which provide
the sealing of the longitudinal gaps between the halves of the slit collet
employed in the clamping of the pump hose, also serve as indicators during
the mounting of the pump hose to verify that the pump hose is clamped
straight, not in a twisted position. The seal gills are cast such that they are in
a horizontal position when the pump hose is correctly mounted.
To a person skilled in the art it is obvious that the invention is not limited by
the above-described exemplifying embodiment, but rather may be varied
within the inventive spirit and scope of the appended claims. In addition to
those described above, more benefits are obtained by virtue of the construc-
tions implemented in the assembly of the invention. The captive hose fitting
system provides simple and pull-resistant securing of the pump hose. The
arrangement disclosed herein permits the use of a flanged hose and sealed
feedthrough of the hose. The hose fitting system also facilitates correct and
easy mounting of the hose and verification of the mounting. Additionally, it
allows the use of a standardized piping flange to be used for pump connec-
tions.
Respectively, the benefits and inventiveness of the eccentric adjustment
assembly are appreciated, i.a., in reliable and accurate setting of hose
compression force also on a worn hose. The eccentric adjustment bushing
assembly the bearing to be tightened lashless onto the eccentric bushing

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11
with the help of the lockcover and, further, locking of the eccentric bushing
and sealing of the compression adjustment gear with the help of the
lockcover. All the adjustments can be carried out by a single operator without
the need for special tools and storage of multiple spare parts separately.
The assembly according to the invention represents a substantial advance-
ment in the construction of a peristaltic pump as to its efficiency, operational
reliability and, in particular, ease of service. The invention is characterized in
that the assembly disclosed herein relates to the pumping of liquids and
slurries by way of progressively compressing an elastic hose, starting from
the hose suction end and finishing at the hose discharge end, whereby the
progressive compression transfers forward the liquid or slurry volume in front
of the compression point. Both of the mechanical constructions described
above are advantageously utilized in the assembly according to the inven-
tion. The object of the invention is particularly directed to a novel and inven-
tive approach to inserting the pump hose into the pump cavity, a captive
fixing system for the hose ends, a replacement method of the hose giving
minimiEed downtime, and an adjustment/locking mechanism of the compres-
sion applied to the hose.

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What is claimed is:
1. A combination assembly for managing a hose or like elastic pump tube or
pump channel such that particularly is used in a peristaltic pump, character-
ized in that the pump is equipped with an assembly for the adjustment of the
pump pressure and/or compression imposed on the hose/tube, the assembly
comprising a steplessly adjustable eccentric adjustment mechanism.
2. The combination assembly of claim 1, characterized in that the peristaltic
pump is adaptable to employ, either alone or in conjunction with the eccentric
adjustment mechanism, a captive hose fitting system for managing the
pressure imposed on the pump hose/tube.
3. The combination assembly of claim 1 or 2, characterized in that the
eccentric adjustment mechanism comprises an eccentric adjustment bushing
(5), a worm gear (6), a spur gear (9), a lockcover (4), lockpins (11) and at
ieast one locking bolt (12).

4. The combination assembly of any one of claims 1-3, characterized in
that the eccentric adjustment mechanism is employed to adjust the gap (23)
between the pump rotor outer surface and ths pump cavity inner periphery by
way of rotating an eccentric bushing (5) mounted on the crankshaft pin (10).
5. The combination assembly of any one of claims 1-4, characterized in
that the eccentricity (19) of the adjustment bushing is accomplished by
drilling the bore of the bushing eccentrically in regard to the outer periphery
of the bushing.
6. The combination assembly of any one of claims 1 - 5, characterized in
that the rotation of the eccentric adjustment bushing is accomplished by
means of a reduction gear such as a worm gear adapted between the
eccentric bushing and the crankshaft, the reduction gear being constructed
by adapting a worm (6) into the solid body part of the eccentric bushing,
7. The combination assembly of any one of claims 1-6, characterized in
that a spur gear (9) is mounted to the end of the crankshaft pin or, altema-

WO 2004/076861 PCT/FI2004/000106
13
tively, is machined directly to the end of the crankshaft pin.
8. The combination assembly of any one of claims 1 -7t characterized in
that the adjustment force of hose compression is controlled using a calibrated
torque wrench for rotating a worm gear (6) at its end (18).
9. The combination assembly of any one of claims 1-8, characterized in
that the eccentric adjustment bushing is locked to the crankshaft pin with the
help of the lockcover (4) that is clamped against a conical surface (14) of the
eccentric bushing with a bolt (12), whereby simultaneously the force imposed
by the tightened bolt presses a sealing O-ring (15) placed between the
lockcover flange and the eccentric bushing.

10. The combination assembly of any one of claims 1 - 9, characterized in
that the rotation of the lockcover is prevented with the help of lockpins (11)
placed between the crankshaft pin end and the lockcover.
11. The combination assembly of any one of claims 1-10, characterized in
that, by virtue of the lockcover, also the inner races of the bearings mounted
on the eccentric bushing are clamped axially between a shoulder (17) of the
eccentric bushing and a shoulder (16) of the crankshaft.
12. The combination assembly of any one of claims 1-11, characterized in
that the captive hose fitting system comprises a rubber flange (27) inserted to
the hose end, seal gills advantageously comprising two gills (33), and two
halves of a split collet (28) and, when necessary, a mounting flange (7).
13. The combination assembly of any one of claims 1-12, characterized in
that the seal gills (33) are made to project from the hose end flange in a form
with the diametrical dimension across the outer edges of the seal gills match-
ing the outer diameter of the hose end flange and the seal gills being situated
about the outer perimeter of the hose, at opposite sides thereof relative to
each other, whereby the cross section of the seal gills is made 0.5 to 1 mm
thicker than the width of the slits (34) made to the collet as it is divided into
two halves.

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14
14. The combination assembly of any one of claims 1-13, characterized in
that the feedthrough opening made on the pump body is of the same size or
slightly larger than the outer diameter of the hose end flange (32) inserted to
the hose end and that the split collet is placed about the hose end flange,
behind the hose end flange (32), so that the seal gills remain trapped
between the split collet halves.
15. The combination assembly of any one of claims 1-14, characterized in
that the flange of the split collet is fitted against the hose end flange inserted
to the hose end and that to the rear side of the flange of the split collet is
placed an O-ring (29), which becomes compressed in the gap between the
flange of the split collet and a bevel (30) made to the edge of the feedthrough
opening of the pump body thus exerting a force that presses the halves of the
split collet against the seal gills and seals the gap between the split collet and
the pump body.
16. The combination assembly of any one of claims 1-15, characterized in
that to the mounting flange is made a sunken shoulder (31) serving to
prevent overtightening of the hose end flange.

Acombination assembly is dicclosed for managing a hose or like elastic pump tube or pump channel such that paticularly is used in a peristaltic pump.The invention is chracterictic by having the jump equiped with in assembly for the adjustment of the pump pressure and/or compression imposed on the house/tube the assembly comprising a aeplessly adjustable accentric adjustment mechanism.

Documents:

01544-kolnp-2005-abstract.pdf

01544-kolnp-2005-claims.pdf

01544-kolnp-2005-description complete.pdf

01544-kolnp-2005-drawings.pdf

01544-kolnp-2005-form 1.pdf

01544-kolnp-2005-form 3.pdf

01544-kolnp-2005-form 5.pdf

01544-kolnp-2005-international publication.pdf

1544-KOLNP-2005-ABSTRACT.pdf

1544-KOLNP-2005-CANCELLED PAGES.pdf

1544-KOLNP-2005-CLAIMS.pdf

1544-KOLNP-2005-CORRESPONDENCE 1.2.pdf

1544-KOLNP-2005-CORRESPONDENCE-1.1.pdf

1544-KOLNP-2005-CORRESPONDENCE.pdf

1544-KOLNP-2005-DESCRIPTION (COMPLETE).pdf

1544-KOLNP-2005-DRAWINGS.pdf

1544-KOLNP-2005-FORM 1-1.1.pdf

1544-KOLNP-2005-FORM 1.pdf

1544-KOLNP-2005-FORM 2.pdf

1544-KOLNP-2005-FORM 3.pdf

1544-KOLNP-2005-FORM-27-1.pdf

1544-kolnp-2005-form-27.pdf

1544-KOLNP-2005-OTHERS 1.1.pdf

1544-KOLNP-2005-OTHERS.pdf

1544-KOLNP-2005-PETITION UNDER RULE 137.pdf

1544-KOLNP-2005-REPLY TO EXAMINATION REPORT.pdf

abstract-01544-kolnp-2005.jpg


Patent Number 243406
Indian Patent Application Number 1544/KOLNP/2005
PG Journal Number 43/2010
Publication Date 22-Oct-2010
Grant Date 13-Oct-2010
Date of Filing 04-Aug-2005
Name of Patentee LAROX FLOWSYS OY
Applicant Address PL 338, FIN-53101, LAPPEENRANTA, FINLAND.
Inventors:
# Inventor's Name Inventor's Address
1 RIIHIMAKI MATTI TAIPALSAARENTIE 16 AS 15, FIN-53900, LAPPEENRANTA, FINLAND.
PCT International Classification Number A61M 5/142
PCT International Application Number PCT/FI2004/000106
PCT International Filing date 2004-02-27
PCT Conventions:
# PCT Application Number Date of Convention Priority Country
1 20030312 2003-02-28 Finland