US20120269618A1

US20120269618A1 - Blade support in a quasiturbine pump

Info

Publication number: US20120269618A1
Application number: US13/386,358
Authority: US
Inventors: Marc-Alexandre Curodeau
Original assignee: Gullivert Technology
Current assignee: GULLIVERT TECHNOLOGIES Inc; Gullivert Technology
Priority date: 2009-07-22
Filing date: 2010-07-22
Publication date: 2012-10-25
Also published as: EP2534378A1; CA2768255A1; CA2768255C; WO2011009216A1

Abstract

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.

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

The present application claims priority on U.S. Provisional Application No. 61/213,860 file on Jul. 22, 2009 which is incorporated herein by reference in its entirety.

TECHNICAL FIELD

The present invention relates to a rotary pump. More specifically, but not exclusively, the present invention relates to pistonless rotary pump, compresessor 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.

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 comprises 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.
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 tow 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.
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.
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

In the appended drawings, where like reference numerals denote like elements throughout and in where:

FIG. 1 is a schematic perspective view of the pump in accordance with a non-restrictive illustrative embodiment of the present disclosure;

FIG. 2 is a lateral side view of the pump of FIG. 1 showing the contents thereof in stippled lines;

FIGS. 3, 4, 7 and 14 are lateral side sectional views of the pump of FIG. 1;

FIG. 5 is a sectional view of the pump of FIG. 3;

FIG. 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;

FIG. 8 is a top view of a portion of the rotor assembly accordance with a non-restrictive illustrative embodiment of the present disclosure;

FIG. 9 is a sectional view of the portion of the rotor assembly of FIG. 8 along line 9-9;

FIG. 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;

FIG. 11 is a schematic perspective view of the pump in accordance with another non-restrictive illustrative embodiment of the present disclosure;

FIG. 12 is a lateral side view of the pump of FIG. 11 showing the contents thereof in stippled lines;

FIG. 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;

FIG. 15 is a schematic top view of a the cylinder during rotation of the rotor assembly in accordance with a non-restrictive illustrative embodiment of the present disclosure;

FIG. 16 is front elevation view of a pump in accordance a non-restrictive illustrative embodiment of the present disclosure;

FIG. 17 is a section view of the pump of FIG. 16 taken along line A-A′;

FIG. 18 is a perspective exploded view of the pump of FIG. 16;

FIG. 19 is perspective exploded view of the pump of FIG. 16 opposite the view of FIG. 18;

FIG. 20 is an exploded perspective view of a rotor blade in accordance a non-restrictive illustrative embodiment of the present disclosure;

FIG. 21 is an exploded perspective view of a rotor blade in accordance a non-restrictive illustrative embodiment of the present disclosure;

FIG. 22 is a perspective view of a rotor blade in accordance a non-restrictive illustrative embodiment of the present disclosure;

FIG. 23 is a perspective view of a squirrel cage for a blade in accordance a non-restrictive illustrative embodiment of the present disclosure;

FIG. 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;

FIG. 25 is a perspective view of a pump in accordance a non-restrictive illustrative embodiment of the present disclosure;

FIG. 26 is front elevational view of the pump of FIG. 25;

FIG. 27 is a section view of the pump of FIG. 25 taken along line A-A of FIG. 26;

FIG. 28 is an exploded perspective view of the pump of FIG. 25;

FIG. 29 is perspective view of the cylinder of the rhomboidal rotor assembly of the pump of FIG. 25;

FIG. 30 is a perspective view of the blade assembly of the rhomboidal rotor assembly of the pump of FIG. 25;

FIG. 31 is an exploded view the blade assembly of FIG. 30;

FIG. 32 is a partial perspective view the rhomboidal rotor assembly of the pump of FIG. 25;

FIG. 33 is an exploded perspective view of the rhomboidal rotor assembly of FIG. 32; and

FIG. 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.
FIGS. 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 FIG. 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 FIGS. 2 and 7, each blade 28, comprises a slightly arched body 32 having concave longitudinal ends 34. Turning to FIG. 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 FIG. 6, each cylinder 30 comprises 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 FIGS. 8, 9 and 10 the concave ends 34 of the cylinder 30 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 FIG. 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.
FIGS. 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 FIGS. 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. FIGS. 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 FIG. 2 to a rhomb configuration shown in FIG. 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 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 axis 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 FIGS. 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 axis 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 FIGS. 8, 9 and 10).
In another embodiment, shown in FIGS. 11, 12 and 13 the rotation of the rotor assembly 26′ is provided electromagnetically as is known in the art.
FIGS. 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.
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 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 cylinders 144. The blades are interconnected by a parallelogramic bracket assembly 146.
Turning to FIG. 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 therebewteen providing a bracket joint that is adjacent a respective joint 154 (see FIG. 18) of the rotor assembly 140 defined by a cylinder 144 interposed between the longitudinal ends of two adjacent blades 142.
In operation, 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 FIG. 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.
Turing to FIG. 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 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 FIG. 21) mounted through holes 186 (see FIG. 21) formed in the body 162 of the blade 142 and positioned through the holes 152 of the bracket members 148.
FIG. 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.
FIG. 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 FIGS. 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 303 a, 303 b thereof. As better shown in FIG. 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 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 FIGS. 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 FIG. 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 FIGS. 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.
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*sqrt(2)/2) <= R(i,2)
i = i+1;
end
i = i−1;
R2 = R(i:length(R),:);
% 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.
FIG. 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
function [V] = Displacement(A, e, r, t)
[R,a,B,tetamin,tetamax] = Ovaloid(A,e,r,10000,0);
% Blade profile
i = 1;
while (a/2+r*sqrt(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);
A1 = 0;
for i = 1:1:j−1
A1 = A1 + 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
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 = 16t(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;
	w = P_charge/dm;
	rp = (w(k−1)/(kR*T1)+1){circumflex over ( )}(k/(k−1));
	end

The following algorithm allows the calculation of the mechanical power loss.


% INPUT
% A: the measure, in cm, of the half small axis of the ovaloidal
% e: the eccentricity of the ovaloidal (e > 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(tetamax);
i = 1;
for TETAR = 0:(pi/2)/(N−1):pi/2
TETA = (TETAR{circumflex over ( )}3)/6−(pi/8)*(TETAR{circumflex over ( )}2)+
(1+(pi{circumflex over ( )}2)/48−(4tetamax/pi))TETAR+tetamax;
R(i,1) = acos(TETA)cos(TETAR);
R(i,2) = acos(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))){circumflex over ( )}2 + (abs(R(i+1,2) −
R(i,2))){circumflex over ( )}2){circumflex over ( )}0.5+p;
end
p = p*4;
% Calculation of the viscous friction loss at the blades
zi = RSext;
z0 = (A*e+A)/200;
PAv = (pi{circumflex over ( )}3n{circumflex over ( )}2u/(0.9g))(zi{circumflex over ( )}4−z0{circumflex over ( )}4);
% Calculation of the loss due to the ring
PRv = (pi{circumflex over ( )}3n{circumflex over ( )}2u/(0.90.1))(RSext{circumflex over ( )}4−(RSext−0.003){circumflex over ( )}4);
% Calculation of the loss due to the ring near the cylinders
PRCv = (pi{circumflex over ( )}3n{circumflex over ( )}2u/(0.90.1))((A*e/100){circumflex over ( )}4−
(A*e/100−0.003){circumflex over ( )}4);
% Power loss due to the viscous friction of the cylinders
nc = pn/(2pi*r);
TCv = (r/100){circumflex over ( )}3(dr/1000)u(nc2pi/60)4.6188/(gc/1000);
PCv = 4TCv(nc2pi/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=10 kN/m̂2 is to be obtained.


% INPUT
% Fd: force density at the rotor in kN/m{circumflex over ( )}2
% 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
% nel: electrical efficiency in %
% rr: radius ratio
% OUTPUT
% A: the measure, in cm, of the half small axis of the ovaloidal
% V: displacement volume per turn in cm{circumflex over ( )}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
% 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;
Amin = 0;
bi = 1;
Fd2 = 0;
while abs(Fd − Fd2) > 0.1 && bi < 100
A = (Amax+Amin)/2;
% Displacement volume in cc
[V] = Displacement(A, e, r, t);
% Estimation of the electromechanical torque in N*m
T = Pgros(nel/100)60/(2pin);
% Estimation of the force density in N/m{circumflex over ( )}2
% 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 = 2pi(RSext{circumflex over ( )}2 − (RSext*rr){circumflex over ( )}2);
rm = (RSext+RSext*rr)/2;
Fd2 = T/(1000Asrm);
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 = (RSextrr − Db)2000;
RSe = (RSext − RSextrr)1000;
% Calculation of the mechanical loss
[Pv] = Mechanical_loss(A, e, r, RSext, n);
% Calculation of the compression rate
[rpAir] = compression(V,n,Pgros/1000,Pv/1000,nel);
% Calculation of the compression efficiency
ncomp = 100( Pgros(nel/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

Claims

1. 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, said rhomboidal rotor assembly comprising a plurality of blades adjoined together at a joint, said joint comprising a rotating member;

a movement imparting assembly for imparting a rotational 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.

2. (canceled)

3. A pump according to claim 2, wherein said rotating member is interposed between said two blades and space therefrom.

4. A pump according to claim 2, wherein two adjacent blades comprises respective ends circumscribing a rotating member and being spaced therefrom.

5. A pump according to claim 1, wherein said rhomboidal rotor assembly comprises adjacent blades with rotating cylinders interposed therebetween.

6. A pump according to claim 5, wherein said cylinders rotate about their longitudinal axis.

7. A pump according claim 5, wherein 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.

8. A pump according to claim 7, wherein said two ends comprise respective concave configuration.

9. A pump according to claim 7, wherein said longitudinal ends comprise a respective bearing.

10. A pump according to claim 9, wherein a said bearing is outwardly biased relative to a said longitudinal end.

11. A pump according to claim 9, wherein said bearing and said cylinder are so positioned as to be spaced apart.

12. A pump according to claim 5, wherein said chamber comprises a lubricant therein positioned between a pair of adjacent said blades and said cylinders.

13. A pump according to claim 1, wherein said the blades are moved away from said contour during rotation.

14. A pump according to claim 1, wherein said blades comprise respective arched configurations.

15. A pump according to claim 1, wherein said rhomboidal rotor assembly comprises four said blades.

16. A pump according to claim 1, wherein said chamber comprises a lubricating fluid, said rhomboidal rotor assembly rotating about said lubricating fluid.

17. A pump according to claim 1, further comprising a support assembly for supporting said rhomboidal rotor assembly.

18. A pump according to claim 1, further comprising a bracket assembly for supporting said blades.

19. A pump according to claim 18, wherein said bracket assembly is pivotally mounted to said blades.

20. A pump according to claim 19, wherein said bracket assembly comprises elongated members pivotally interconnected.

21. A pump according to claim 1, further comprising a blade support assembly comprising a pair of support members for each said blade, each pair of support members receiving a respective blade therebetween.

22. A pump according to claim 21, wherein said support members comprise a larger respective surface area than that of said blade.

23. A pump according to claim 21, wherein two adjacent said pairs of support members of two adjacent blades are hinged together at a joint therebetween.

24. A pump according to claim 23, wherein said rotatable member is pivotally mounted to said joint between said adjacent pair of support members.

24. (canceled)

25. A pump according to claim 21, wherein said support members comprise magnets.

26. A pump according to claim 25, wherein 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.

27. A pump according to claim 1, further comprising magnets operatively communicating with at least one said blade.

28-36. (canceled)