Canadian Patents Database / Patent 2511267 Summary

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(12) Patent: (11) CA 2511267
(54) English Title: ROTARY ENGINE WITH PIVOTING BLADES
(54) French Title: MOTEUR ROTATIF AVEC LAMES PIVOTANTES
(51) International Patent Classification (IPC):
  • F01C 1/44 (2006.01)
(72) Inventors (Country):
  • SAINT-HILAIRE, GILLES (Canada)
  • SAINT-HILAIRE, ROXAN (Canada)
  • SAINT-HILAIRE, YLIAN (Canada)
  • SAINT-HILAIRE, FRANCOISE (Canada)
(73) Owners (Country):
  • SAINT-HILAIRE, GILLES (Canada)
  • SAINT-HILAIRE, ROXAN (Canada)
  • SAINT-HILAIRE, YLIAN (Canada)
  • SAINT-HILAIRE, FRANCOISE (Canada)
(71) Applicants (Country):
  • SAINT-HILAIRE, GILLES (Canada)
  • SAINT-HILAIRE, ROXAN (Canada)
  • SAINT-HILAIRE, YLIAN (Canada)
  • SAINT-HILAIRE, FRANCOISE (Canada)
(74) Agent: NA
(45) Issued: 2008-07-08
(86) PCT Filing Date: 2003-02-10
(87) PCT Publication Date: 2004-08-19
Examination requested: 2005-06-20
(30) Availability of licence: N/A
(30) Language of filing: English

English Abstract





The Quasiturbine uses a rotor arrangement peripherally supported by four
rolling carriages,
the carriages taking the pivoting blade pressure-load, of the blades forming
the rotor, and
transferring the load to the opposite contoured housing wall. The present
invention discloses a
central, annular, rotor support for the rotor geometry defined by the pivoting
blades and
associated wheelbearings, while still maintaining the important center-free
engine
characteristic. The pressure-load on each pivoting blade is taken either by
its own set of wheel
bearings rolling on annular tracks part of the casing, or is cancelled out in
symmetrically
pressurized fluid energy converter mode through the central holding action of
annular power
sleeves. This central, annular, rotor support could generally apply to all the
family of
Quasiturbine rotor arrangements and particularly to the limit case here
considered, where the
previous carriage design is replaced by a cylindrical pivoting blade joint as
developed in the
present patent, and for which an efficient solution of the five bodies rotary
engine sealing
problem is given.


French Abstract

L'invention concerne une Quasiturbine (abrégé en Qurbine) qui fait intervenir un dispositif de rotor supporté sur sa périphérie par quatre chariots roulants, ces chariots supportant la charge de pressurisation de la lame pivotante des lames qui forment le rotor et transférant la charge sur la paroi profilée opposée du logement. L'invention décrit une embase de rotor centrale annulaire pour la configuration géométrique définie par les lames pivotantes et les roulements de roues associés, tout en conservant la caractéristique importante d'un moteur exempt de centre. La charge de pressurisation sur chaque lame pivotante est soit supportée par l'ensemble de roulements de roues respectif de chaque lame pivotante roulant sur des pistes annulaires fixées sur la zone centrale de couvercles latéraux faisant partie du carter, soit neutralisée dans un mode de conversion de l'énergie du fluide pressurisé symétriquement sous l'action centrale de retenue de manchons de puissance annulaires. Cette embase de rotor centrale annulaire peut généralement être appliquée à toute la famille des dispositifs de rotor Quasiturbine, et particulièrement au cas limite considéré ici, dans lequel la conception antérieure de chariot est remplacée par une lame pivotante cylindrique développée dans le présent brevet, et pour lequel une solution efficace est apportée au problème du scellement du moteur rotatif à cinq corps.


Note: Claims are shown in the official language in which they were submitted.




ROTARY ENGINE WITH PIVOTING BLADES


WE CLAIM:



1. A rotary apparatus producing mechanical energy from hydraulic, steam, and
pneumatic
pressurized fluid flow, and from Stirling cycle, Brayton cycle, Otto and
Diesel internal
combustion cycles and to pump, make vacuum and compress, generally referred to
as a
Quasiturbine, and comprising:
- a stator casing having an internal contoured housing wall, including two
lateral side covers;
- pivoting blades consecutively pivoted one to the other at their ends, and
pivot axes being
parallel; wherein each of said pivoting blades carrying an inwardly directed
power transfer
slot with wheel bearing axes;
- an assembly of said pivoting blades and joints forming a X, Y, .theta.
variable-shape rotor rolling
inside said internal contoured housing wall about a central axis, with
deformation from square
configuration rotor to diamond configuration rotor;
- a family profile of curves being calculated for said internal contoured
housing wall, and a
criteria being selected to meet the pressure volume engine PV diagram;
- each of said lateral side covers carrying an annular track on an inner
surface;
- a set of contour seals in contact with said internal contoured housing wall,
and a system of
lateral seals in contact with said lateral side covers;
- variable volume chambers, each of said variable volume chambers limited by
two successive
contour seals, and extending along the inner surface of the internal contoured
housing wall,
and the outer surface of said pivoting blades, limiting two compression
housing sections
located symmetrically to the center as the two opposed expansion housing
sections;
- each of said pivoting blades carrying a combustion chamber cavity;
- a set of ports in said casing for intakes and exhausts;
- a set of ports in said lateral side covers for intakes and exhausts;
- a set of ports through said pivoting blades, connecting said variable volume
chamber to the
central area;
- an ignition flame transfer slot-cavity;
- a spark plug
- a compression ratio tuner;
- a check valve port,



18




- a set of clutch centrifuge weights inside a rotor;
- a set of annular power sleeves located inside said rotor;
- a modulated Inner Rotor Volume (MIRV) within said rotor;
- a set of differential washers linking said annular power sleeves to a power
disk and a power
shaft;
- wherein all consecutive compressions housing sections are occurring
repetitively in the same
housing section, and all consecutive expansions are also occurring
repetitively at different
intermediate housing sections;
- wherein the two compression housing sections are located symmetrically to
the center, as
the two opposed expansion housing sections;
- wherein each successive compression stroke and expansion stroke start and
end
simultaneously;
- wherein the distance between two consecutive contour seals stays almost
constant during a
revolution of said rotor;
- wherein the contour seals stay almost perpendicular to said internal
contoured housing wall
at all times;
- wherein said differential washers prevents the wheel bearings axes
rotational harmonic to
reach said power shaft;
- wherein said rotor and said differential washers linking centers of mass are
immobile during
rotation;
- wherein said variable volume chambers are asymmetric from mid-value, and the
pressure
pulse is short and increases and decreases linearly near the top dead center;
- wherein a Quasiturbine Internal Combustion cycle (QTIC) results from said
pressure pulse
characteristics;
- wherein said Modulated Inner Rotor Volume (MIRV) is 45 degrees out of phase
with
outward rotor chambers; and
- wherein said Modulated Inner Rotor Volume (MIRV) is alternately pressurized
to make an
Inward Rotor Engine Quasiturbine (IREQ), driving said rotor from the interior;
- wherein the direction of rotation is reversed, reversing the direction of
the flow.


2. The rotary apparatus as defined in claim 1, wherein said internal contoured
housing wall is
a rounded corner parallelepiped shape, with four areas of maximum curvature
and four
intermediate areas of minimum curvature, and wherein the complexity of the
internal
contoured housing wall makes the radius of curvature to slightly fluctuate
within one single
quadrant.


3. The rotary apparatus as defined in claim 1, wherein to permit higher
eccentricity of said


19




rotor, the calculated internal contoured housing wall is lobed shaped, with
six areas of
maximum curvature and six intermediate areas of minimum curvature.


4. The rotary apparatus as defined in claim 1, wherein the mathematical
contour profile of the
said internal contoured housing wall is one of a family of curves requiring
only symmetry
about the center of the internal contoured housing wall and not through the x-
or y- axis, and
the method for calculating the said internal contoured housing wall profile,
including lobed
and eccentricity limit solutions, referred to a calculation comprising steps:
- selecting a diamond-shaped rotor eccentricity which imposes and defines at
design the x-
and y- axes blade pivot profile coordinates, while the said square
configuration rotor defines
the 45 degrees pivot profile coordinates;
- calculating a set of blade pivots profile;
- linearly assuming empirical blade pivots profile radius in the 0 - 45
degrees interval, and
modulating said empirical blade pivots profiles radius based on at least a two-
parameters
function which does not change the 0 and 90 degree area tangentiality;
- performing oblique lozenge mapping; and a simple Pythagoras Diamond-diamond
mapping
of the 0 - 45 degrees interval, with slope continuity in the 45 degrees area,
in the case of the
perpendicular x- and y- axes of the 45-90 degrees interval;
- obtaining a corresponding set of said internal contoured housing wall by
enlarging said
blade pivots profile by one pivot radius all around;
- wherein from the set of said internal contoured housing walls, selecting of
an optimum
engine application internal contoured housing wall is done, wherein the final
said chamber
expansion volume equals the volume generated by the movement of the tangential
surface of
push, which pressure-volume characteristics meets the standard engine PV
diagram; and
- wherein the calculation method applies for all values, including of positive
values, negative
values and null values of the eccentricity, the pivot diameters, and the x-
and y- arbitrary axes
angle.


5. The rotary apparatus as defined in claim 1, wherein the lateral side covers
have:
- multiple notches on the periphery for thermal fins;
- an annular track on the inner surface for the pivoting blade wheel bearings,
the tracks not
necessarily circular except if the pivoting blade wheel bearings are located
on the axis of two
successive pivots;
- a bearing holder on the engine axis for the power shaft;
- a large aperture on one lateral side cover on the engine axis, permitting
the power disk and
the power shaft to slide in-and-out the casing without dismantling the engine;
- a bearing-cap fitting the large aperture, and holding a bearing and the
power shaft; and



20




- volume modulator ports outside the periphery of the annular track, for the
Modulated Inner
Rotor Volumes (MIRV).


6. The rotary apparatus as defined in claim 1, wherein the pivoting blade
comprises:
- an outward surface shaped to insure free rotation of the rotor within the
internal contoured
housing wall for all angles of rotation;
- an outward surface being cave-cut to enlarge the combustion chamber when
required;
- a check valve port made radially through said pivoting blade, and linking
the said
combustion chambers to the central engine area;
- said check valve port allowing chamber intake enhancement by centrifuge
force;
- a power transfer slot extending inwardly toward the central rotor area;
- a receptacle space within the said Modulated Inner Rotor Volumes (MIRV), on
both side of
said transfer slot, to locate the clutch centrifuge weights; and
- an axial strong pivoting joint at said pivoting blades ends.


7. The rotary apparatus as defined in claim 1, wherein said ports are radial
housing ports for a
spark plug, a compression ratio tuner, and for intake and exhaust ports
located near where the
contour seals stand at top dead center.


8. The rotary apparatus as defined in claim 1, wherein said ports are lateral
side cover ports
for a spark plug, a compression ratio tuner, and for intake and exhaust ports
located on the
pivoting blade pivot path, near the blade pivot positions when at top dead
center.


9. The rotary apparatus as defined in claim 1, wherein said intake and exhaust
ports comprise:
- several removable intake and exhaust plugs, which are used to convert the
two parallel
compression and expansion circuits into a sole serial circuit;
- two quasi-independent circuits used in parallel with all plugs removed for
operation as a two
stroke rotary internal combustion engine, a fluid energy converter, a
compressor, a vacuum
pump and a flow meter; and
- two quasi-independent circuits used in serial by plugging intermediate
ports, to make a four
stroke internal combustion rotary engine.


10. The rotary apparatus as defined in claim 1, wherein said intake and
exhaust ports have
different angular locations for different applications, and wherein:
- symmetrically opposed said ports with respect to engine center are used for
fluid energy
converter, compressor and two stroke engine applications;
- said symmetrically opposed ports are slightly moved toward the high-pressure
zone, to take


21




advantage of the pivoting blade port obstruction during port-seal crossing,
preventing
momentarily free intake-to-exhaust flow;
- said intake port for internal combustion engine is an arc-shaped like
opening in an angular
suction zone in relation to the forward contour seal, and extending further to
account for fluid
flow time delay;
- said check valve port made radially through said pivoting blade, permits
chamber central
intake enhancement by the centrifuge force;
- said exhaust port for internal combustion engine is shaped as an elongated
angular opening,
extending to account for fluid flow time delay and inertial exhausting; and
- said spark plug and compression ratio tuner are located in the high-pressure
zone, anywhere
in between the pivoting blade contour seals when at top dead center horizontal
position,
extending further to account for fluid flow time delay.


11. The rotary apparatus as defined in claim 1, wherein a pivoting blade joint
comprises:
- a male and a female part at the respective ends of said pivoting blade;
- two female parts at both ends of the same said pivoting blades, while said
male parts are at
both ends of the two complementary pivoting blades of said rotor;
- the male part made cylindrical with two different radiuses of curvature,
having an
underneath holding finger so that four and more pivoting blades can be firmly
assembled
together;
- the male part acting as a rubbing pad against the internal contoured housing
wall to guide
the rotor deformation into proper diamond shape, having provision for hard
surface sleeves
insert to allow for material of plastic, ceramic and glass;
- the female part having an arm extension also holding two different radiuses
of curvature;
- an in-joint seal within a groove located in and along said female part; and
- the joint having a provision for an in-joint bearing, linking friction-free
the cylindrical male
part to the female part.


12. The rotary apparatus as defined in claim 1, wherein said transfer slot
comprises:
- a pivoting blade wheel bearings shaft parallel to the engine axis, near mid-
way between said
blade pivots;
- a cylindrical wheel bearings shaft holder fitting tightly with the wheel
bearings shaft and the
transfer slot;
- the extremities of said wheel bearings shaft each carrying one wheel
bearings rolling on said
lateral side cover annular track; and
- an attachment space on said wheel bearings shaft for one of the said annular
power sleeves
bearing ears, allowing driving of the central power disk and power shaft.



22




13. The rotary apparatus as defined in claim 1, having a set of contour seals
each located in a
linear groove extending along the engine axis within said pivoting blade male
joint and
comprising:
- a gate type seal being a back spring-loaded sliding;
- a gate type seal being a back spring-loaded sliding in fit contact
simultaneously with the
internal contoured housing contour wall and the lateral side covers; and
- a contour seal damper made of a rubber band lying in the bottom of the
groove on which
said contour seal and spring are sited.


14. The rotary apparatus as defined in claim 1, having a system of lateral
seals carried by said
pivoting blades and comprising:
- a curved groove and a curved seal in contact with said lateral side covers;
and
- a moon-like shaped groove and pellet seal on each side of said male joint.


15. The rotary apparatus as defined in claim 1, wherein said lateral seals
include:
- a moon-like shaped groove and pellet seal on each side of said male joint;
and
- an almost elliptic pivots path groove and static back-pressured ring in each
side cover, which
by design is in permanent contact with the rotor.


16. The rotary apparatus as defined in claim 1, wherein lubrication needs are
suppressed, and
comprising:
- a favorable geometry where lubricant is not needed for cooling;
- a favorable geometry where no internal parallax forces exist;
- a favorable geometry where no seal is under internal stress, and subject to
hydrogen
combustion; and
- said contour seals and lateral seals system made of very hard material for
operation without
lubricant.


17. The rotary apparatus as defined in claim 1, wherein said annular power
sleeves comprises:
- an empty annular ring concentric with the engine axis, with an interior
receptacle for said
differential washers linking the power disk;
- two opposed small bearing-rings, each linked to a pivoting blade wheel
bearings axes;
- multiple grooves on the inner surface of said empty annular ring, for
tangential torque
transfer to said differential washers;
- a set of seals carried by said empty annular ring, to leak proof the inner
area from the outer
area;



23


- wherein the two said annular power sleeves are inserted co-linearly 90
degrees apart within
the Quasiturbine, each one making a relative back and forth rotation not at
constant angular
speed; and
- wherein the load-pressure on two opposed said pivoting blades when in the
fluid energy
converter mode is canceled out by the annular power sleeves, generally
suppressing the need
for the said wheel bearings and the annular track.


18. The rotary apparatus as defined in claim 1, wherein said clutch centrifuge
weights
comprise:
- a plurality of said clutch centrifuge weights located in-between said
pivoting blade and the
annular power sleeves;
- said clutch centrifuge weights pivoting around the closest wheel bearings
axes;
- a plurality of friction clutch pads located on the outer surface of the
annular power sleeves,
where the rotation is not at constant angular speed;
- a plurality of friction clutch pads located on the inside surfaces of the
said annular power
sleeves, where the rotation is not at constant angular speed;
- a plurality of friction clutch pads located on the surface of said power
disk, where the
rotation is at constant angular speed;
- a plurality of friction clutch pads located outside the Quasiturbine engine,
but driven by the
centrifuge weights inside said clutch; and
- a clutch pad-locking mechanism to permit to crank the engine by the said
power shaft for
starting.


19. The rotary apparatus as defined in claim 1, wherein said Modulated Inner
Rotor Volume
(MIRV) comprises:
- a triangular shaped chamber defined by the inward joint of two successive
said pivoting
blades and the outer surface of the annular power sleeves, and extending from
one respective
pivoting blade wheel bearings axes to the other;
- wherein the Modulated Inner Rotor Volumes (MIRV) are 45 degrees out of phase
with said
outward rotor chambers;
- wherein said triangular shaped-like chamber has a minimum volume at open
diamond corner
angles and a maximum volume at closed angles;
- wherein the rotation of said rotor expels the gas-liquid enclosed in the
maximum volume,
and intakes similar content from the minimum volume configuration;
- wherein said Modulated Inner Rotor Volumes (MIRV) act as a compressor-
ventilator, and as
a second stage low-flow high-pressure compressor mode;
- wherein said Modulated Inner Rotor Volumes (MIRV) ventilate the rotor inside
area

24


through two independent top and bottom circuits by either pulsing, parallel
and counter flow
directions;
- wherein the said Modulated Inner Rotor Volumes (MIRV) circulate air-liquid
coolant
through the engine block and in the rotor central area, providing an integral
cooling active
circuit;
- wherein said Modulated Inner Rotor Volumes (MIRV) provide the pressure
fluctuation
required to operate a standard carburetor fuel diaphragm pump;
- wherein said Modulated Inner Rotor Volumes (MIRV) work in both directions of
rotation,
upon reversing the direction of the flow; and
- wherein very high-pressure is obtained from the pivoting blades scissor-
effect, to drive a
Diesel fuel pump and other device.


20. The rotary apparatus as defined in claim 1, wherein said Modulated Inner
Rotor Volumes
(MIRV) work as a compressor, a pump and an oscillating engine, without
rotation but simply
by successive oscillating deformation of said diamond shaped rotor, by using
an alternating
piston, external fluid pressure.


21. The rotary apparatus as defined in claim 1, wherein said pivoting blade
Modulated Inner
Rotor Volumes (MIRV) act as an Inward Rotor Engine Quasiturbine (IREQ), and
comprises:
- a triangular shaped-like chamber defined by the inward joint of two
successive said pivoting
blades and the outward surface of the annular power sleeves, and extending
from one
respective pivoting blade wheel bearings axes to the other;
- wherein the said triangular shaped-like chamber has a minimum volume at open
diamond
corner angles, and maximum volume at closed angles;
- wherein a pressure in the minimum volume configuration of said chamber
provokes the said
rotor to rotate 90 degrees toward a maximum volume configuration;
- wherein successive said triangular shaped-like chamber pressurizations
continuously drive
said rotor in an engine mode; and
- wherein the said Inward Rotor Engine Quasiturbine (IREQ) mode leaves the
rotor outward
areas free for compressor, pump and other uses.


22. The rotary apparatus as defined in claim 1, wherein said differential
linking washers
comprises:
- a large diameter power disk concentric to, and carrying the power shaft, and
having a
plurality of radially extending pins receptacles;
- a set of differential washers carrying two washer-pins inserted into said
radially extending
pins;




- said power disk external surface shape as part of a sphere of same diameter
and the
differential washer shaped accordingly to permit perfect sitting on the power
disk spherical
surface;
- said two washer-pins of the differential washers fitting into said annular
power sleeves
interior grooves and steps;
- a play in-between said power disk external diameter and said annular power
sleeves internal
diameter to permit said differential washers to rotate slightly around said
radially extending
pins;
- a curvature of the said power disk perimeter surface along the axial
direction, to give room
for the rotation of the said differential washers;
- a design permitting the sliding in-and-out of said differential washers
linking through one of
the Quasiturbine said lateral side covers central aperture without dismantling
the engine; and
- wherein said differential linking washers prevents said pivoting blades
rotational harmonic
to reach the said power disk and power shaft.


23. The rotary apparatus as defined in claim 1, wherein said central shaft
comprises:
- a central shaft collinear with the central housing axis, crossing the two
lateral side covers
and supported by bearings in at least one of the lateral side covers;
- a central shaft coupling mechanism composed of said power disk and said
differential
linking washers;
- wherein the shaft coupling mechanism is made as a sliding plug-in unit,
easily slide in-and-
out without dismantling the engine;
- wherein said differential washers linking mechanism removes the RPM harmonic

modulation on the shaft;
- wherein the shaft gives full power takeoff at both of its ends;
- wherein said power disk and power shaft are not mandatory for engine
operation and are
removed;
- wherein the central shaft can be a very large diameter thin wall tube shaft
carrying an axial
thrust bearing at least at one end, and an engine crank starting device at
either ends, enclosing
accessories like propellers screw, electrical components, generator, gearbox
shaft and similar;
and
- wherein several Quasiturbines in different modes, are stacked side-by-side
on a single
common said power shaft through simple ratchet coupling for torque addition.


24. The rotary apparatus as defined in claim 1, wherein in engine mode, said
ignition flame
transfer slot-cavity comprises:
- a cut into the internal contoured housing wall, located nearby where the
forward contour seal

26


stands at maximum chamber pressure, to allow a flame transfer from one said
chamber to the
next following chamber, and to permit continuous combustion; and
- wherein said ignition flame transfer slot-cavity allows the injection of
high-pressure hot
burning gas into the next ready to fire chamber, producing a dynamically
enhanced
compression ratio.


25. The rotary apparatus as defined in claim 1, wherein in engine mode, the
high-tech fuel
gases and hydrogen fuel capability enable:
- multi facing said intake ports located axially one each side of the engine,
and easily
accessible to permit independent and stratified admission of fuel and air;
- multi side-by-side said intake ports located radially on the internal
contoured housing wall,
and easily accessible to permit independent and stratified admission of fuel
and air;
- said pivoting blades, wheel bearings and annular tracks made very strong;
and
- an intake chamber area kept cold, to permit direct high-tech fuel gas and
hydrogen backfire-
proof intake and engine photo-detonation mode if required.


26. The rotary apparatus as defined in claim 1, wherein said Quasiturbine
Internal
Combustion QTIC-cycle comprises:
- a fast and linear pressure-compression raising-falling Quasiturbine
characteristic near top
dead center;
- a continuous atmospheric air pressure intake without butterfly valve
restriction;
- a fuel vaporized, sprayed, and mixed directly into said continuous
atmospheric air pressure
intake without synchronization means;
- a compression of the said fuel mixture to standard pressure level, and a
uniform combustion
triggered by a spark plug;
- said compression ratio tuner made of a small adjustable threaded piston, to
replace the spark
plug at very high compression ratios;
- a compression of said fuel mixture to the Diesel-like pressure level by the
short fast raising-
falling Quasiturbine pressure pulse, and a uniform combustion driven by the
adiabatic high
temperature and radiation conditions;
- at very high-pressure, a photo-detonation engine mode made possible, where
no sparkplug
or otherwise synchronization means is needed;
- a volume variation near top dead center without said pivoting blade mass
momentum
transfer, to well resist the photo-detonation knocking; and
- a heavy construction of said pivoting rotor blades for inertial smooth-out
of the photo-
detonation knocking.


27


27. The rotary apparatus as defined in claim 1, wherein thermalization
comprises:
- said cylindrical shape male joint of the pivoting blade being in direct
mechanical contact
with said internal contoured housing wall, thereby increasing the combustion
chamber walls
thermalization, heat transportation and dissipation;
- at least one of the two lateral side covers having a large central hole
exposing the pivoting
blades central area of the rotor, thus eliminating the so called internal
engine parts, and so
improving the cooling and reducing the need for lubricant cooling; and
- a forced liquid and gas ventilation by said Modulated Inner Rotor Volumes
(MIRV) in the
area between said pivoting blades and said annular power sleeves.


28


A single figure which represents the drawing illustrating the invention.

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Admin Status

Title Date
(86) PCT Filing Date 2003-02-10
(87) PCT Publication Date 2004-08-19
(85) National Entry 2005-06-20
Examination Requested 2005-06-20
(45) Issued 2008-07-08
Lapsed 2017-02-10

Payment History

Fee Type Anniversary Year Due Date Amount Paid Paid Date
Request for Examination $400.00 2005-06-20
Filing $200.00 2005-06-20
Maintenance Fee - Application - New Act 2 2005-02-10 $50.00 2005-06-20
Maintenance Fee - Application - New Act 3 2006-02-10 $50.00 2005-06-20
Maintenance Fee - Application - New Act 4 2007-02-12 $50.00 2005-06-20
Maintenance Fee - Application - New Act 5 2008-02-11 $100.00 2005-06-20
Final $150.00 2008-04-11
Maintenance Fee - Patent - New Act 6 2009-02-10 $100.00 2008-12-22
Maintenance Fee - Patent - New Act 7 2010-02-10 $100.00 2010-01-22
Maintenance Fee - Patent - New Act 8 2011-02-10 $100.00 2010-12-08
Maintenance Fee - Patent - New Act 9 2012-02-10 $100.00 2011-11-25
Maintenance Fee - Patent - New Act 10 2013-02-11 $125.00 2012-11-26
Maintenance Fee - Patent - New Act 11 2014-02-10 $125.00 2014-01-02
Maintenance Fee - Patent - New Act 12 2015-02-10 $125.00 2014-12-01

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Description 2005-06-20 17 1,071
Representative Drawing 2005-06-20 1 59
Cover Page 2005-09-19 1 75
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Abstract 2007-04-03 1 23
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Abstract 2007-09-17 1 24
Description 2007-09-17 17 942
Claims 2007-09-17 11 489
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Cover Page 2008-06-11 1 75
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PCT 2005-06-20 2 76
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Prosecution-Amendment 2006-01-11 30 1,404
Correspondence 2006-06-28 1 60
Correspondence 2006-11-09 1 13
Prosecution-Amendment 2007-03-28 2 47
Prosecution-Amendment 2007-07-23 2 81
Prosecution-Amendment 2007-09-17 31 1,521
Correspondence 2008-04-11 1 100
Fees 2008-12-22 1 63
Fees 2010-01-22 1 56
Fees 2010-12-08 1 45
Fees 2011-11-25 1 65
Fees 2012-11-26 1 90
Fees 2014-01-02 1 127
Fees 2014-12-01 1 55