Note: Descriptions are shown in the official language in which they were submitted.
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BLADE SUPPORT IN A QUASITURBINE PUMP
TECHNICAL FIELD
The present invention relates to a rotary pump. More specifically, but not
exclusively, the present invention relates to pistonless rotary pump,
compressor
or engine.
BACKGROUND
The Quasiturbine or Qurbine engine is a pistonless rotary engine or pump using
a rhomboidal rotor whose sides are hinged at the vertices. The volume enclosed
between the sides of the rotor and the rotor casing provide compression and
expansion in a fashion similar to Wankel engine, but the hinging at the edges
allows the volume ratio to increase. The Quasiturbine is proposed as a
Stirling
engine, a pneumatic engine using stored compressed air, and as a steam
engine.
Drawbacks with the Quasiturbine include the high amount of friction between
the
hinged vertices and sides of the rhomboidal rotor and the inner wall of the
casing
as well as the inner sides of the lateral covers, which results in energy loss
as
well as damage. Furthermore, the friction between the rhomboidal rotor of the
Quasiturbine and the inner wall of the casing does not provide for using this
apparatus in the turbine mode with a gaseous fluid since the gas will escape
between the pressurized compartments within the pump. As such, the
Quasiturbine requires a starter.
There thus remains a need from improvements with regards to pistonless rotary
engines or pumps.
OBJECTS
An object of the present disclosure is to provide rotary pump.
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SUMMARY OF ILLUSTRATIVE EMBODIMENTS
In accordance with an aspect of the disclosure, there is provided a pump
comprising: a housing having an inner contour and defining an ovaloidal
chamber; a rhomboidal rotor assembly positioned within said ovaloidal chamber
and being configured to rotate; a movement imparting assembly for imparting a
rotation movement to said rhomboidal rotor assembly; and intake and exhaust
ports in communication with said chamber providing for intake of fluid therein
and
exhaust of fluid therefrom.
In an embodiment, said rhomboidal rotor assembly comprises a plurality of
blades adjoined together at joint, wherein said joint comprises a rotating
member.
In an embodiment, said rotating member is interposed between said two blades
and space therefrom. In an embodiment, two adjacent blades comprise
respective ends circumscribing a rotating member and being spaced therefrom.
In an embodiment, said rhomboidal rotor assembly comprises adjacent blades
with rotating cylinders interposed therebetween. In an embodiment, said
cylinders rotate about their longitudinal axis. In an embodiment, a pair of
adjacent
said blades comprise respective longitudinal ends, a given said cylinder being
provided to rotate between said two ends of said adjacent blades. In an
embodiment, said two ends comprise respective concave configuration. In an
embodiment, said longitudinal ends comprise a respective bearing. In an
embodiment, a said bearing is outwardly biased relative to a said longitudinal
end. In an embodiment, said bearing and said cylinder are so positioned as to
be
spaced apart. In an embodiment, said chamber comprises a lubricant therein
positioned between a pair of adjacent said blades and said cylinders.
In an embodiment, said the blades are moved away from said contour during
rotation. In an embodiment, said blades comprise respective arched
configurations. In an embodiment, said rhomboidal rotor assembly comprises
four said blades.
In an embodiment, said chamber comprises a lubricating fluid, said rhomboidal
rotor assembly rotating about said lubricating fluid. In an embodiment, said
housing comprises a central protrusion, said chamber being defined between
said inner contour and said central protrusion, said rhomboidal rotor assembly
being provided to rotate about said central protrusion.
In an embodiment, said pump further comprises a support assembly for
supporting said rhomboidal rotor assembly.
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In an embodiment, said pump further comprising a bracket assembly for
supporting said blades. In an embodiment, said bracket assembly is pivotally
mounted to said blades. In an embodiment, said bracket assembly comprises
elongated members pivotally interconnected.
In an embodiment, said pump further comprises a blade support assembly
comprising a pair of support members for each said blade, each pair of support
members receiving a respective blade therebetween. In an embodiment, said
support members comprise a larger respective surface area than that of said
blade. In an embodiment, two adjacent said pairs of support members of two
adjacent blades are hinged together at a joint therebetween. In an embodiment,
said rotatable member is pivotally mounted to said joint between said adjacent
pair of support members. In an embodiment, said cylinder is pivotally mounted
to
said joint. In an embodiment, said support members comprise magnets. In an
embodiment, a said support member comprises an external surface thereof
opposite an internal surface thereof for engaging said blade, said external
surface comprising recesses for receiving said magnets.
In an embodiment, said pump further comprises magnets operatively
communicating with at least one said blade. In an embodiment, said magnets are
imbedded in said blade. In an embodiment, said magnets are mounted to the
surface of said blade. In an embodiment, said pump further comprising a plaque
mountable to said blade for mounting said magnets therebetween.
In an embodiment, at least one said blade comprises a squirrel-cage, said
movement imparting assembly providing an electrical current to said squirrel-
cage for rotation of said rhomboidal rotor assembly. In an embodiment, at
least
one said blade comprises laminations, said movement imparting assembly
providing an electrical current to said laminations for rotation of said
rhomboidal
rotor assembly. said blades are spaced apart from said inner contour during
rotation of said rhomboidal rotor assembly.
In an embodiment, said movement imparting assembly provides for an
electromagnetic flux for actuating said rhomboidal rotor assembly. In an
embodiment, said movement imparting assembly comprises a stator mounted
within said housing.
In an embodiment, there is provided a pump comprising: a housing defining an
ovaloidal chamber; a rhomboidal rotor positioned within said ovaloidal chamber
and being configured to rotate about a central lubricating liquid fluid; and
intake
and exhaust ports for intake of fluid into the chamber and exhaust of fluid
from
the chamber.
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In an embodiment, the chamber is circumscribed by a contour wall, the
rhomboidal rotor comprises adjoined blades, the blades are moved away from
the wall during rotation.
In an embodiment, the rhomboidal rotor comprises blades, with each pair of
adjacent blades being adjoined about a cylinder. In an embodiment the
cylinders
are rotatable about their axis.
In an embodiment, the housing comprises at least one lateral side cover, the
at
least one lateral side cover comprises electromagnetic elements, the
rhomboidal
rotor comprises complementary electromagnetic elements embedded therein.
In an embodiment, there is provided a pump comprises a housing having an
inner contour and defining an ovaloidal chamber with a rhomboidal rotor
assembly positioned therein and being configured to rotate. The housing
includes
intake and exhaust ports in communication with the chamber providing for
intake
of fluid therein and exhaust of fluid therefrom. A movement imparting assembly
imparts a rotational movement to the rhomboidal rotor assembly. The rhomboidal
rotor assembly comprises four blades, adjoined at four joints comprising
rotatable
members spaced interposed between two adjacent blades and being spaced
therefrom. The pump can be a compressor or and engines and can be used in a
variety of fields.
In accordance with a general aspect, there is provided a pump comprising: a
housing having an inner contour and defining an ovaloidal chamber; a
rhomboidal rotor assembly positioned within said ovaloidal chamber and being
configured to rotate in said ovaloidal chamber, said rhomboidal rotor assembly
comprising a plurality of blades adjoined together at joints, each one of the
joints
comprising a rotating cylinder rotatable about a longitudinal axis thereof
upon
rotation of the rhomboidal rotor assembly in said ovaloidal chamber; a
movement
imparting assembly comprising a stator and configured to impart a rotational
movement to said rhomboidal rotor assembly; and intake and exhaust ports in
fluid communication with said ovaloidal chamber, said intake ports allowing
intake of a fluid therein and said exhaust ports allowing exhaust of the fluid
therefrom.
Other objects, advantages and features of the disclosure will become more
apparent upon reading of the following non-restrictive description of
non-limiting illustrative embodiments thereof, given by way of example only
with
reference to the accompanying drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
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In the appended drawings, where like reference numerals denote like elements
throughout and in where:
Figure 1 is a schematic perspective view of the pump in accordance with a non-
restrictive illustrative embodiment of the present disclosure;
5 Figure 2 is a lateral side view of the pump of Figure 1 showing the
contents
thereof in stippled lines;
Figures 3, 4, 7 and 14 are lateral side sectional views of the pump of Figure
1;
Figure 5 is a sectional view of the pump of Figure 3;
Figure 6 is a schematic perspective view of the cylinder of the rotor assembly
in
accordance with a non-restrictive illustrative embodiment of the present
disclosure;
Figure 8 is a top view of a portion of the rotor assembly accordance with a
non-
restrictive illustrative embodiment of the present disclosure;
Figure 9 is a sectional view of the portion of the rotor assembly of Figure 8
along
line 9-9;
Figure 10 is a schematic perspective partially exploded view of the blade
bearing
assembly in accordance with a non-restrictive illustrative embodiment of the
present disclosure;
Figure 11 is a schematic perspective view of the pump in accordance with
another non-restrictive illustrative embodiment of the present disclosure;
Figure 12 is a lateral side view of the pump of Figure 11 showing the contents
thereof in stippled lines;
Figure 13 is a schematic top view of a portion of the rotor assembly in
accordance with another non-restrictive illustrative embodiment of the present
disclosure;
Figure 15 is a schematic top view of the cylinder during rotation of the rotor
assembly in accordance with a non-restrictive illustrative embodiment of the
present disclosure;
Figure 16 is front elevation view of a pump in accordance a non- restrictive
illustrative embodiment of the present disclosure;
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Figure 17 is a section view of the pump of Figure 16 taken along line A-A';
Figure 18 is a perspective exploded view of the pump of Figure 16;
Figure 19 is perspective exploded view of the pump of Figure 16 opposite the
view of Figure 18;
Figure 20 is an exploded perspective view of a rotor blade in accordance a non-
restrictive illustrative embodiment of the present disclosure;
Figure 21 is an exploded perspective view of a rotor blade in accordance a non-
restrictive illustrative embodiment of the present disclosure;
Figure 22 is a perspective view of a rotor blade in accordance a non-
restrictive
illustrative embodiment of the present disclosure;
Figure 23 is a perspective view of a squirrel cage for a blade in accordance a
non-restrictive illustrative embodiment of the present disclosure;
Figure 24 is front elevational view of the bracket assembly from the blades of
the
rhomboidal rotor assembly in accordance a non-restrictive illustrative
embodiment of the present disclosure;
Figure 25 is a perspective view of a pump in accordance a non-restrictive
illustrative embodiment of the present disclosure;
Figure 26 is front elevational view of the pump of Figure 25;
Figure 27 is a section view of the pump of Figure 25 taken along line A-A of
Figure 26;
Figure 28 is an exploded perspective view of the pump of Figure 25;
Figure 29 is perspective view of the cylinder of the rhomboidal rotor assembly
of
the pump of Figure 25;
Figure 30 is a perspective view of the blade assembly of the rhomboidal rotor
assembly of the pump of Figure 25;
Figure 31 is an exploded view the blade assembly of Figure 30;
Figure 32 is a partial perspective view the rhomboidal rotor assembly of the
pump
of Figure 25;
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Figure 33 is an exploded perspective view of the rhomboidal rotor assembly of
Figure 32; and
Figure 34 shows TABLE 1 which represents the position of points on the X and Y
axis of the profile of the rotor blade.
DETAILED DESCRIPTION OF ILLUSTRATIVE EMBODIMENTS
Generally stated and in accordance with an illustrative embodiment of the
present disclosure, there is provided a pistonless rotary pump, compressor or
engine. The pump comprises a housing defining an ovaloidal chamber for
housing a rhomboidal rotor. The rhomboidal rotor comprises four blades,
adjoined at four joints. The joints comprise a respective rotating member in
the
form of a rotatable cylinder. The rotor actuates intake and outtake of fluid.
The
blades rotate about a central lubricating liquid fluid. In an embodiment, the
housing comprises covers with electromagnetic elements, the blades having
complementary electromagnetic elements embedded therein, mounted thereto,
or otherwise operatively communicating therewith. The rotary pumps disclosed
herein can be compressor or engines and can be used in a variety of fields.
With reference to the appended drawings, non-restrictive illustrative
embodiments will be described so as to provide examples and not limit the
scope
of the disclosure.
Figures 1 to 4 show the pump 10 comprising a main body 12 including a stator
casing 14 and lateral side covers 16. The stator casing 14 includes an
internal
wall contour 18 defining along with the inner surface 17 (see Figure 5) of the
covers 16 an ovaloidal chamber 20. Radial intake ports 22 and outtake ports 24
are formed through the stator casing 14 and are in fluid communication with
the
chamber 20. A rhomboidal rotor assembly 26 is housed within the chamber 20.
The rhomboidal rotor assembly 26 comprises four blades 28 as well as four
cylinders 30.
With respect to Figures 2 and 7, each blade 28, comprises a slightly arched
body
32 having concave longitudinal ends 34. Turning to Figure 5, each blade 28 has
an outer surface 36 and a tapered inner surface 38 as well as generally flat
lateral sides 40.
Each cylinder 30 is positioned between the respective adjacent concave ends 34
of two adjacent blades 28. Turning now to Figure 6, each cylinder 30 comprises
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an elongated cylindrical body 42 with lateral sides 44. The lateral sides 44
may
include openings 46 leading to an elongated bore 48 throughout the body 42.
With respect to Figures 8, 9 and 10, the concave ends 34 of the blade 28
include
bearing assemblies 50. Each bearing assembly 50 includes a shaft 52 mounted
within the body 32 of the blade 28, for providing a ball bearing 54 to rotate
thereon. The shaft 52 defines the axis of rotation of the ball bearing 54. An
opening 56 formed within the concave end 34 provides for the ball bearing 54
to
slightly protrude therefrom.
As shown in the Figure 7, each cylinder 30 is partially circumscribed by a
pair of
adjacent concave ends 34 and separated therefrom a by gap 58 (during high
velocity rotation as will be describe herein). The cylinders 30 form part of a
joint
60 between a pair of adjacent concave ends 34.
Figures 11, 12 and 13 show another embodiment of the pump, denoted here as
10' with electromagnets 68 positioned on the outer side 70 of the lateral side
cover 16' to interact with the blades 28'. The blade 28' comprise a squirrel-
cage
72 embedded within body 32'.
With regards to Figures 3, 4 and 14, the rotor assembly 26 is suspended within
a
central lubricating liquid fluid L in chamber 20.
In operation, the rhomboidal rotor assembly 26 rotates causing fluid (gaseous
or
liquid) to be pumped into the chamber 20 via the intake ports 22 and out of
the
chamber 20 via the outtake ports 24. The lubricating fluid L within the
ovaloidal
chamber 20 rotates in the direction C. In this way, the rhomboidal rotor
assembly
26 rotates about the fluid L. Figures 3 and 4 show the rotor assembly 26
effectuating a 45 degree rotation.
The ovaloidal configuration of the chamber 20 forces the rhomboidal rotor
assembly 26 to move from a generally square configuration shown in Figure 2 to
a rhomb configuration shown in Figure 1. Therefore, during rotation of the
rotor
assembly 26 the volume between the periphery of the rotor assembly 26 and the
wall contour 18 is modified, thereby changing between expansion, which causes
suctioning during fluid intake, and compression which causes propulsion during
fluid outtake.
Since the fluid causes the blades 28 to move inwardly, friction between the
rotor
assembly 26 and the wall contour 18 and wall 17 is minimized. The gap between
the rotor assembly 26 and the contour 18 is variable whereas the small gap
with
the wall 17 is almost constant. Nevertheless, while avoiding direct contact,
the
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blades 28 brush along the wall contour 18 thereby providing viscous friction
between the blades 28 and the wall contour 18. The lubricating liquid fluid L
gets
trapped between the periphery of the rotor assembly 26 and wall contour 18
thereby minimizing friction. Moreover, during rotation, each cylinder 30 also
rotates about its longitudinal axis (see Figure 6) and thus rollingly engages
the
wall contour 18. Again, there is at least a film of fluid between each
cylinder 30
and the wall contour 18 further minimizing friction during the wall-cylinder
engagement.
During high velocity rotation, the cylinders 30 are submitted to a centripetal
force
F1 (see Figures 14 and 15), furthermore, the lubricating liquid fluid L is
also
rotating along with the rotor assembly 26 and this produces a centripetal
force on
the blades 28. The foregoing produces a gap 58 between each cylinders 30 and
the adjacent concave ends 34 and as such there is almost no friction between
the blades 28 and the cylinders 30. It should also be noted that as the
cylinder 30
rotates about its longitudinal axis (see Figure 6) it causes the lubricating
liquid
fluid L within the gap 58 to rotate along with the cylinder 30. This rotation
of the
liquid L within gap 58 is assisted by the ball bearings 54 of the concave ends
34
(see Figures 8,9 and 10).
In another embodiment, shown in Figures 11, 12 and 13 the rotation of the
rotor
assembly 26' is provided electromagnetically as is known in the art.
Figures 16 to 19 show a pump 100 which can be a compressor, a turbine or an
engine.
The pump 100 includes a housing 101 having a first and second housing
assemblies 102 (only one assembly shown here) mounted to each lateral side of
a plate 103.
More particularly, the housing assembly 102 includes a wall panel 104 with a
pair
of legs 106 mounted thereto and having a recessed portion defining a chamber
108 and a cylindrical protrusion 110 extending from the floor 112 of the
chamber
108. A stator support 114 is inserted within the chamber 108 and includes a
hole
116 for receiving the protrusion 110 therethrough. The stator support 114
includes a peripheral indentation 118 for receiving a stator 120 including a
toothed rim 122. The teeth 122 provide for winding conductive wires thereon
such as those used in double side linear inductance motors. The stator 120 and
stator support 114 are covered by cover 124 being snuggly received within the
chamber 108 and having a hole 126 to receive the protrusion 110 therethrough.
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The housing assembly 102 is mounted to one lateral side 128 of the plate 103.
The plate receives another housing assembly 102 on its opposite lateral side
130. The plate 103 includes an ovaloidal aperture 132 defining an inner
contour
136. In this way, an ovaloidal chamber 138 is defined by the inner contour 136
5 and the laterally positioned housing assembly 102. A rhomboidal rotor
assembly
140 is positioned within this chamber 138.
The rhomboidal rotor assembly 140 circumscribes the adjacent protrusions 110
or each laterally positioned housing assembly 102.
The rhomboidal rotor assembly 140 comprises four blades 142 as well as four
10 cylinders 144. The blades are interconnected by a parallelogramic
bracket
assembly 146.
Turning to Figure 24, the bracket assembly 146 includes four bracket members
148 interconnected together via rivets 150 to form a parallelogram. The
longitudinal ends of each bracket member 148 includes a hole 152 for being
mounted to a blade 142, with each pair of adjacent longitudinal ends 153A and
153B and rivet 150 therebetween providing a bracket joint that is adjacent a
respective joint 154 (see Figure 18) of the rotor assembly 140 defined by a
cylinder 144 interposed between the longitudinal ends of two adjacent blades
142.
In operation, a movement imparting assembly 321 including the stator 120
provides a rotating magnetic field, the blades 142 include magnets and thus
rotate along with this magnetic field. The bracket members 148 stabilize the
blades 142 as they rotate thereby avoiding the blades 142 from touching the
lubricated cylinders 144. The foregoing provides a synchronous rotor.
As shown in Figure 23, the blades 142 can include a squirrel-cage 156
embedded within its body for inducting an electromagnetic current provided by
the stator 120 within the blades 142 causing them to rotate. The squirrel-cage
156 includes longitudinal rods 158 interconnected by inclined bars 160.
Turning to Figure 20, each blade 142 comprises a slightly arched body 162
having concave longitudinal ends 164 within opening 165. The flat lateral
sides
166 include receiving recesses 168 for receiving respective magnets 170 which
adhere thereto via a variety of suitable adhesives. Each longitudinal end 164
includes a bearing assembly 172. Each bearing assembly 172 includes a shaft
174 mounted within the body 162 of the blade 142 via holes 176. The holes 176
are not circular but somewhat elliptical allowing the shaft 172 to slightly
move
outwardly and inwardly relative to the body 162. The shaft 172 carries a
bearing
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178 held in place via snap rings 180. Leaf springs 182 bias the shaft 172 and
bearing 178 outwardly. The bracket members 148 are mounted to the blades 142
by way of shafts 184 (see Figure 21) mounted through holes 186 (see Figure 21)
formed in the body 162 of the blade 142 and positioned through the holes 152
of
the bracket members 148.
Figure 21 shows that the blade 142 can be sandwiched between a pair of
plaques 188. In an embodiment, the plaques 188 are made of flexible and/or
resilient material. The plaques 188 are mounted to the lateral sides 166 and
thus
include holes 190 which are aligned with corresponding holes 192 formed in the
blades for receiving rivets 194. The plaques include openings 198 for the
magnets 170. Ring portions 200 are mounted to the blades 142 via their holes
202. The ring portions 200 can provide for contact with the contour 136 and
cover
124.
Figure 22 shows a blade 143 comprising laminations 204 made of thin punchings
providing a laminated core for a magnetic circuit within the blade 143. The
laminations are thin so as to minimize losses due to Eddy currents. Holes 206
allow for injecting aluminum therein.
With respect to Figures 25 to 33, a pump 300 which can be a compressor, a
turbine, or an engine will now be described.
The pump 300 includes a housing 301 having a first and second housing
assemblies 302 mounted to a plate 303 at each lateral side 303a, 303b thereof.
As better shown in Figure 25, the plate 303 includes intake and outtake ports,
305 and 307 respectively.
Each housing assembly 302 includes a wall panel 304 with a pair of legs 306
mounted thereto and having a recessed portion defining a chamber 308 and a
cylindrical protrusion 310 extending from the floor 312 of the chamber 308. A
stator support 314 is inserted within the chamber 308 and includes a hole 316
for
receiving the protrusion 310 therethrough. The stator support 314 includes a
tubular protrusion 318 about the hole 316. A stator 320 is mounted to the
stator
support 314 and includes a hole 322 for receiving the tubular protrusion 318
therein.
The plate 303 includes an ovaloidal aperture 324 defining an inner contour
326.
When the housing assemblies 302 are mounted to the plate 303, their respective
protrusions 310 are mated thereby defining a central protrusion. In this way,
an
ovaloidal chamber 328 is defined by the contour 326 and the laterally
positioned
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housing assemblies 302. A rhomboidal rotor assembly 330 is positioned within
this chamber 328 which rotates about the adjoined protrusions 310.
The rhomboidal rotor assembly 330 comprises a rotor blade assembly 332
sandwiched between two rotor support assemblies 334. The rotor blade
assembly 332 includes four blades 336 as well as four cylinders 338. Each
rotor
support assembly 334 includes four blade supports 340.
With particular reference to Figures 27, 29 to 33, each blade 336 includes a
slightly arched body 342 with concave longitudinal ends 344 for circumscribing
the cylinder 338 which includes a main cylinder body 346 and a shaft 348.
Each blade support 340 includes a bottom arched portion 350 for being directly
mounted to the blade body 342 via fasteners (not shown) which are inserted
through holes 352 aligned with corresponding holes 354 formed in the blade
body 342. A blade 336 sandwiched between a pair of supports 340 provides a
blade assembly 331 (see Figure 30).
The bottom portion 350 includes one end 356 having a ring 358 and an opposite
end 360 having an aperture 362. As shown in Figures 32 and 33, when two
adjacent supports 340 are joined they form a support joint 363 mating an end
360
of one support 340 with an end 356 of the other support 340. The rings 358
receive a bearing 364 for the cylinder shaft 348 that is kept in place via
snap ring
365. Ring elements 366 can also be mounted to the blade assemblies 331.
The outer faces 368 of the supports 340 (i.e. the faces not directly engaging
the
blade 338) include recesses 370 for receiving magnets therein which are
adhered thereto by a variety of suitable adhesive substances.
The supports 340 include top portion 372 that provide for forming a valley 374
when the blade 338 is interposed therebetween.
In operation, the stator 320 provides a rotating electromagnetic field, the
flux
provided within chamber 328 causes the magnets of the supports 340 to actuate
the rotor blade assembly 332 to rotate. The supports provide for maintaining
the
blades 336 and their cylinders 338 in place during rotation avoiding any
contact
with the contour 326 or between the blades 336 and their cylinders 338.
In the examples herein, four blades and four cylinders or rotatable members
were
shown, of course, a different number of each can be contemplated by the
skilled
artisan.
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The term movement imparting assembly includes the various stators, magnets,
conductors and combinations thereof for actuating the rhomboidal rotor
assembly.
Blade Profile
The following algorithm allows the calculation of a table of the (x, y)
coordinates
of half of the contour of the blade.
% INPUT
% R: Matrix of the (x, y) coordinates, in cm, of each point of the profile of
the ovaloid
% A: the measure, in cm, of the half small axis of the ovaloid
%e: the eccentricity of the ovaloid (e> 1)
% r: the radius, in cm, of the lubricated cylinders
% OUTPUT
% R2: Matrix of the (x, y) coordinates, in cm, of the blade profile
function [R2] = Blade(R, A, e, r)
tetamin = atan((A*e-r)/(A-r));
a = (A-r)/cos(tetamin);
% Blade profile
i = 1;
while (a/2+r*sgrt(2)/2) <= R(i,2)
i = 1+1;
end
i = i-1;
R2 = R(i:length(R),:);
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% Graphic
X = R2(:,1);
Y = R2(:,2);
plot(X,Y);
grid on;
axis equal;
end
The result obtained is a matrix of (x, y) coordinates of half the profile of
the blade.
In order to obtain the final result, symmetry with regard to the X axis must
be
effectuated.
Figure 34 (Table 1) shows the result obtained for the following values:
A= 15
e = 1.31
r=1.76
Optimization of the Compressor.
The following algorithm allows the calculation of the displacement volume per
turn.
% INPUT
% A: the measure, in cm, of the half small axis of the ovaloid
% e: the eccentricity of the ovaloid (e> 1)
% r: the radius, in cm, of the lubricated cylinders
% t: the interior thickness in cm
% OUTPUT
% V: displacement volume in cc
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function [V] = Displacement(A, e, r, t)
[R,a,B,tetamin,tetamax] = Ovaloid(A,e,r,10000,0);
A) Blade profile
i= 1;
5 while (a/2+r*sgrt(2)/2) <= R(i,2)
i=i+1;
end
i=i-1;
R2 = R(i:length(R),:);
% Processing of the ovaloid profile
R = R(1:i,:);
% Numerical integration using the trapezoid rule
% Numerical integration of the ovaloid profile
j = length(R);
Al = 0;
for i = 1:1:j-1
Al = Al +
abs((R(i+1,1)-R(i,1))*(R(i,2)-
R(i+1,2)))/2+abs(R(i+1,2)*(R(i+1,1)- R(i,1)));
end
% Numerical integration of the blade profile
j = length(R2);
A2 = 0;
for i = 1:1:j-1
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A2 = A2 +
abs((R2(i+1,1)-R2(i,1))*(R2(i,2)-
R2(i+1,2)))/2+abs(R2(i,1)*(R2(i,2)-R2(i+1,2)));
end
% Displacement volume
V = 161*(A1 - A2);
end
The following algorithm allows the calculation of the air compression rate.
% INPUT
% v: displacement volume per turn in cc
% RPM: Revolutions Per Minute
% P_gros: input power in kW
% P_fric: friction power in kW
% n: electrical efficiency in %
% OUTPUT
% rp: compression rate
function [rp] = compression(v,RPM, P_gros,P_fric,n)
T1 = 300;
R = 0.287;
k = 1.4;
rho = 1.2;
P_charge = (n/100)*P_gros - P_fric;
dv = v*RPM/60000000;
dm = dv*rho;
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w = P_charge/dm;
rp = (w*(k-1)/(k*R*T1)+1)^(k/(k-1));
end
The following algorithm allows the calculation of the mechanical power loss.
"Yo INPUT
% A: the measure, in cm, of the half small axis of the ovaloidal
%e: the eccentricity of the ovaloidal (a> 1)
% r: the radius, in cm, of the lubricated cylinders
% RSext: exterior radius of the stator, without the coil thickness, in m
% n: engine speed in RPM
% OUTPUT
% Pv: total mechanical power loss in W
function [Pv] = Mechanical_loss(A, e, r, RSext, n)
N = 1000;
u=0.1;
g = 0.5;
gc = 0.5;
dr = 30;
% Solving of the R matrix
B = e*A;
tetamax = atan((A*e-r)/(A-r));
a = (A-r)/cos(tetannax);
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i = 1;
for TETAR = 0:(pi/2)/(N-1):pi/2
TETA =
(TETARA3)/6-(pi/8)*(TETARA2) (1+(piA2)/48-
(4*tetamax/pi))*TETAR+tetamax;
R(i,1) = a*cos(TETA)*cos(TETAR);
R(i,2) = a*cos(TETA)*sin(TETAR);
i=i+1;
end
for i = 1:1:(N-1)
c(i,1) = R(i,1) + r*sin(atan((R(i,2)-R(i+1,2))/(R(i+1,1)-R(i,1))));
c(i,2) = R(i,2) + r*cos(atan((R(i,2)-R(i+1,2))/(R(i+1,1)-R(i,1))));
end
R=c;
% Calculation of the perimeter
p=0;
c = length(R) - 1;
for i = 1:1:c
p = ((abs(R(i+1,1) - R(i,1)))^2 + (abs(R(i+1,2) - R(1,2)))^2) ^0.5+p;
end
p = p*4;
% Calculation of the viscous friction loss at the blades
zi = RSext;
z0 = (A*e+A)/200;
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PAv = (piA3*n^2*u/(0.9*g))*(ziA4-z0^4);
% Calculation of the loss due to the ring
PRv = (piA3*n^2*u/(0.9*0.1))*(RSext^4-(RSext-0.003) ^4);
% Calculation of the loss due to the ring near the cylinders
PRCv = (piA3*n^2*u/(0.9*0.1))*((A*e/100)^4-(A*e/100-0.003)A4);
% Power loss due to the viscous friction of the cylinders
nc = p*n/(2*pi*r);
TCv = (r/100)Ardr/1000)*u*(nc*2*pi/60)*4.6188/(gc/1000);
PCv = 4*TCv*(nc*2*pi/60);
% Total power loss
Pv = PCv + PAv + PRv + PRCv;
end
The following algorithm allows calculation of the displacement volume and the
force density in order to optimize the compressor. Ideally, a force density of
Fd = 10kN/m^2 is to be obtained.
% INPUT
% Fd: force density at the rotor in kN/rnA2
% e: the eccentricity of the ovaloidal (e> 1)
% r: the radius, in cm, of the lubricated cylinders
% t: the interior thickness in cm
% n: engine speed in RPM
%Pgros: Gross power entering the compressor in W
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% nel: electrical efficiency in %
% rr: radius ratio
% OUTPUT
% A: the measure, in cm, of the half small axis of the ovaloidal
5 % V: displacement volume per turn in cm^3
% Pv: viscous friction loss in W
% rpAir: compression rate
% ncomp: compression efficiency in %
% Dsext: exterior diameter of the stator, including the coil, in mm
10 % Dsint: interior diameter of the stator, including the coil, in mm
% RSe: width of stator iron in mm
function [A, V, Pv, rpAir, ncomp, DSext, DSint, RSe] = Optimization(Fd e,
r, t, n, Pgros, nel, rr)
Amax= 100;
15 Amin = 0;
bi = 1;
Fd2 = 0;
while abs(Fd - Fd2) > 0.1 && bi < 100
A = (Amax+Amin)/2;
20 % Displacement volume in cc
[V] = Displacement(A, e, r, t);
% Estimation of the electromechanical torque in N*m
T = Pgros*(ne1/100)*60/(2*pi*n);
% Estimation of the force density in N/m2
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% Db: thickness of the stator coil in m
Db = 0.01;
% RSext: exterior radius of the stator, without the coil thickness, in m
RSext = (A*e+1)/100;
As = 2*pi*(Rsext2 - (RSext*rr)2);
rm = (RSext+RSext*rr)/2;
Fd2 = T/(1000*As*rm);
if Fd2 < Fd
Amax = A;
else if Fd2 > Fd
Amin = A;
end
end
bi = bi + 1;
end
% Calculation of the exterior radius, interior of the stator space and of the
width of the stator teeth
DSext = (RSext+Db)*2000;
DSint = (RSext*rr - Db)*2000;
RSe = (RSext - RSext*rr)*1000;
% Calculation of the mechanical loss
[Pv] = Mechanical_loss(A, e, r, RSext, n);
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=
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% Calculation of the compression rate
[rpAir] = compression(V,n,Pgros/1000,Pv/1000,nel);
A Calculation of the compression efficiency
ncomp = 1001 Pgros*(ne1/100) - Pv)/Pgros;
end
It should be noted that the various components and features described above
can be combined in a variety of ways so as to provide other non- illustrated
embodiments within the scope of the invention. As such, it is to be understood
that the invention is not limited in its application to the details of
construction and
parts illustrated in the accompanying drawings and described hereinabove. The
invention is capable of other embodiments and of being practiced in various
ways. It is also to be understood that the phraseology or terminology used
herein
is for the purpose of description and not limitation. Hence, although the
present
invention has been described hereinabove by way of embodiments thereof, it can
be modified, without departing from the spirit, scope and nature of the
subject
invention as defined in the appended claims
