EP2185823A2

EP2185823A2 - Quiet fan

Info

Publication number: EP2185823A2
Application number: EP08783288A
Authority: EP
Inventors: Ghislain Lauzon
Original assignee: Individual
Current assignee: Individual
Priority date: 2007-07-31
Filing date: 2008-07-28
Publication date: 2010-05-19
Also published as: WO2009015469A2; EP2185823A4; WO2009015469A3; CA2598867A1

Abstract

The invention illustrates the assembly of a fan structure comprising a transmission shaft to each end of the shaft of which a ball bearing is fitted. A spring is incorporated between the ball bearings and arranged coaxially to the rotor and the stator in order to stabilize the centrifugal force, enabling a better rotational dynamic balance about the axis of the fan. This type of assembly substantially reduces the problem of the bowing of the shaft.

Description

Silent fan

FIELD OF APPLICATION OF THE INVENTION -Although the concept illustrated in page 5, 6, assembly description and assembly description in a bird's eye annexed that of an axial fan exhaust structure it should be known that this concept is also applicable in other fields. Here are the main applications: residential, commercial, industrial and institutional: Video Audio; Appliances;

Ventilation, air conditioning, heating and refrigeration; Kitchen and bathroom; HVAC;

Evacuation of smoke, heat, toxic and chemical products; Computer science; Aerospace; aerospace;

Automobile, heavy machinery and recreational vehicle; rail; Wind turbine; Military; Pharmaceutical; Agriculture;

Hydroponics, aeroponics; Forestry and mining; Naval;

Bestial breeding: (poultry, cattle and pigs); geothermal; tidal; Hydraulic; Film. PROBLEMS RESOLVED BY THE INVENTION

"Significant reduction of noise level (acoustic comfort);

"Significant reduction of energy consumption;

"Elimination of premature clogging and corrosion phenomena thanks to the special design of the rotor which completely protects the stator (see figure 1, 2, 3, 4 and 5)

"Marked improvement in evacuation capacity.The new system improves twice the performance of removal of suspended particles and gaseous fluids that are difficult to extract from a closed environment in a short time;

"Elimination of the vibrations that are usually due to bad assemblies of metal to metal parts;

• The invention according to the assembly of an axial exhaust fan structure optimizes the efficiency, (in Figures 1, 2, 3,4 and 5), in terms of air flow;

"The fan axial exhaust structure provides four times the performance found in prior art systems, and the system allows for the removal of unwanted particles such as mold, bacteria, solvents, toxic gases, pesticides, foul odors, carbon monoxide, cooking residues, dusts, etc. It has been designed to operate in very varied humidity temperature environments (according to FIGS. , 8, 9, 10, 11, 12, 19, 20, 21, 22 and 23);

• The innovative aspect of the assembly provides both increased performance in terms of air flow and remarkable acoustic qualities beyond those of the prior art. In addition, contrary to the system found in the prior art, the noise level does not increase proportionally with the increase of the air flow rate (according to FIGS. 6, 7, 8, 9, 10, 11, 12, 19, 20 , 21, 22, 23, 24 and 25); The fan axial exhaust structure requires no maintenance or cleaning throughout its useful life unlike the prior art product. In addition, it is not vulnerable to corrosion under operating conditions in the presence of moist air, heat, cold or chemical emanation where various gases, smoke or any toxic product (according to FIGS. 7, 13, 14, 15, 24, 25, 26, 27 and 28) in view of the assembly which makes it possible to optimize the absorption efficiency. The transmission shaft was manufactured in two pieces to give a shock absorber phenomenon versus the prior art;

"The new assembly system improves the particle removal performance thanks to the angle that can be given to its fins, from 0 to 180 degrees, which does not destabilize its rotation movement or consume no more energy given its very high stability versus the prior art.

"Elimination of the vibrations which are usually due to bad assembly of pieces of metal on metal and that one can have as inclination an angle of 0 to 90 degree of the angle perpendicular to the insertion of the dawn.

TYPES OF FEEDING;

The types of power supply that the fan can adapt to "Any type of existing fuel: gas, oil, diesel, ethanol, kerosene, hydrogen, fuel oil, propane gas and natural gas;" Any type of electrical energy; AC / DC, electricity in all its forms of existing currents; "Any type of static energy;

* Any type of wind propulsion; wind;

"Any type of existing battery (alkaline, acid and others);

" Solar energy;

"Any type of energy by water flow;

"Geothermal;

"Tidal;

"Hydraulic;

• Nuclear; "Coal.

ROTATION OF THE ENGINE

The rotation of the motor can be carried out between 5 and 500 000 rpm according to the needs of the mode of applications and according to the number of amperage necessary to make it work, while respecting the triggering is carried out automatically because a certain degree of heat where well has a certain number of amperage the engagement is done automatically not to damage the engine. The operation of the motor blades can be used in reverse rotation depending on the mode of application; BALL BEARINGS

The ball bearings used inside the blower are steel ball bearings, but other types of ball bearings can be used either in plastics, teflon, ceramic or porcelain where any existing materials.

SEALED JOINTS

Sealing joints can be affixed where needed to absorb vibration or other necessary uses.

DRIVE SHAFT

The power transmission shaft of the motor can differ from one model to another depending on the use to which the application will be made because the engagement phenomenon is not the same for a model to the 'other.

1. The rotor and stator can assemble differently;

2. The driveshaft can be assembled differently or designed from several pieces;

3. The spring (tension / compression) can be fixed according to the compression and stability required or could be inserted upstream, downstream or add a plurality;

4. According to the fan model electric magnetism can be inserted between the ball bearings;

5. The multi-sheave, multi-belt, multi-belt or multi-gear or multi-gear driveshaft, the transmission shaft may be lengthened while becoming aerodynamic for the operation of the engines. using the belt drive shaft (multiple) or gear (multiple) depending on the desired application modes. 6. The transmission shaft can be made of several pieces that can be inserted into one another, the transmission shaft comes to play the role of damper, given its very high stability versus the prior art. The energy consumption is much less important because there is no instability phenomenon when the absorption of the fluids is absorbed inside its structure and propels by its fins according to the desired angle the electric dialysis of the engine that is not tested because there is no mechanical or physical obstruction versus the prior art;

7. Given the arrangement of the drive shaft which has been manufactured from two pieces that can be inserted into one another, the spring which is inserted between the two parts acts as damping versus the prior art;

8. Regardless of the volume of air drawn at the desired angle and the desired distance, there is no overconsumption and no more elasticity that can be found in any type of appliance combined. because the transmission shaft absorbs all vibration and keeps its stability when the blade is in operation on its axis of rotation, because the arrangement which is made of two pieces which one inserts one in the other while inserting a spring between the parts to give a tension / compression element and which comes to play the role of absorption of the shock absorber phenomenon versus the prior art.

DAWN

Dawn has a cylindrical, conical or aerodynamic shape. The dawn of the engine structure can be lengthened while becoming aerodynamic for the operation of the engines. The axial exhaust fan blade has a side surface and has a circular arc shape of 360 degrees. The blade may receive a plurality of blades, each of the blades having an edge portion and an attachment portion, the blade has a structure that has an upper boundary and a lower boundary for receiving the hub. The blades or attachment part of each blade is attached to the side surface of the blade or could be inserted into one another or the blades could be inserted above the blade and could be riveted, welded, molded, bolted, molded in one piece, glued or pressed. An air inlet space is formed from the edge portions of the upper boundary of the structure and upper surface of the blade and a surface is defined. A lateral region roughly describes the air inlet above the blade. The plurality of blades that are inserted at dawn may have an angle variation perpendicular to the blade insertion of 0 to 90 degrees depending on the desired design for the desired mode of application and the angle can be designed linear palms from 0 to 180 degrees. The blade can be lengthened while becoming aerodynamic for the operation of the engines and can be used in reverse rotation according to the mode of application. The operation of the motor blades can be used in reverse rotation depending on the mode of application.

RANGE OF FANS

"The range of centrifugal fans can be adapted by molding the squirrel cage on the stator where the rotor with the transmission modes of the aforementioned shaft;

"The helical propeller can be as well adapted to the concept while using springs, ball bearings or electric magnetism to stabilize the shaft on its rotation;

"The turbine can also be mounted on the rotor or on the stator while using the same concept mentioned above.

DETAILED DESCRIPTION OF ACHIEVEMENTS

As illustrated in FIGS. 24 and 25, an axial exhaust fan structure according to one embodiment of the invention has a fan structure, a cylindrical hub, a plurality of blades attached to a side surface of the dawn and aligned around the blade and a structure with a transmission shaft to which is fixed at each end of the ball bearings. The fan structure has an upper boundary and a lower boundary to receive the cylindrical blade and its blades which thus allow the assembly with the stator, which allows the remarkable dynamic balance thus decreasing axial radial forces which allows to obtain a great stability by having added a spring in the hub and between the two ball bearings, this spring coming to create a constant axial tension allowing to obtain a balance and a stability of the movement according to FIGS. 24 and 25, coming to play a role absorption. Ball bearings provide constant stability because the axial movement that is created in the opposite direction is balanced by the ball-bearing which creates a tight clearance allowing radial balancing which creates a dynamic equilibrium because its mechanism is not counteracted. no physical obstruction, mechanical or radial.

Referring to the pages of Figs. 24, 25, 26, 27, 28 and 29, the fan axial exhaust structure # 13 comprises a # 12 motor structure, a # 1 cylindrical conical hub where is attached to the end of the frame. motor a # 4 sealing plug. In engine # 12 where # 1 cylindrical conical hub is installed there is a # 3 ball bearing at each end. In the # 12 motor structure where is positioned the # 1 cylindrical conical hub is inserted a # 2 spring (tension / compression). The # 14 motor and the # 7 stator, are inside the # 12 motor frame, around the circumference of the # 1 cylindrical conical hub. The rotor # 8 has inside a # 9 drive shaft with a # 10 blade with a plurality of blades.

A # 7 stator is assembled with a # 8 rotor, in the # 8 rotor there is # 9 a drive shaft. When seating the # 7 stator and the # 8 rotor, the # 9 drive shaft enters inside the # 1 cylindrical conical hub. Thus, by reading assembly description # 1 and assembly as the crow flies, a structure with axial fan discharge, the phenomenon of instability of the rotational movement is solved by inserting a spring inside the shaft. transmission of axial fan motor framing structure for stabilized centrifugal and axial force.

The drive shaft which is made of two pieces that can be inserted into one another and inserting a spring inside the shaft between the two parts of the structure of axial fan motor framing for stabilized the centrifugal and axial force while coming to act as a shock absorber by absorbing any vibration while keeping its stability when the dawn and its fins propels the absorbed air inside its structure.

DETAILED TECHNICAL DESCRIPTION, WITH DRAWINGS

The particular configuration of the assembly is illustrated in Figures 24, 25, 26, 27 and 28. As you can see in these figures, the motor drive shaft (power transmission) is mounted on two ball bearings at each end. This type of assembly makes it possible to achieve a better dynamic balance in rotation. Thus, with this type of assembly we greatly reduce the problems due to sagging that we find in the standard prior art assemblies of an engine with a propeller attached to one end of the drive shaft, thus accentuating the problems due to forces that may exceed the elastic limit of the materials used creating irreparable plastic deformations, these responsible for the premature wear of components such as ball bearings, flanges and even the drive shaft (power transmission) according to the teaching of the prior art.

As shown in Figures 16, 17 and 18 of the drawings and assembly description you will notice, that the rotor and the plurality of blades were inserted at dawn and are one piece, thus allowing for the assembly with the stator to achieve a remarkable dynamic balance compared to the prior art products.

In addition, we achieve great stability by adding a spring between the two parts that form the drive shaft, this spring creates a constant axial tension to achieve great stability. The ball bearings create a tight set allowing radial balancing and thus achieve a dynamic balance for a variable rotation.

It is thanks to the properties of high stiffness, stability, durability, high capacity and sound level that we can use this new technology in the different areas mentioned above.

he BRIEF SUMMARY OF THE INVENTION

1. The invention provides an axial fan exhaust structure for better air volume displacement of the fan (FIGS. 6, 7, 19, 20, 21, 22 and 23);

2. Figures 24, 25, 26, 27, 28 and 29 show a perspective view of the fan axial exhaust structure;

3. Figures 19, 20, 21, 22 and 23 show in perspective a ventilator axial discharge structure showing a partial section of axial evacuations fluids and its furrow;

4. Figures 6, 7, 8, 9, 10, 11, 12, 19, 20, 21, 22 and 23 show the evacuation capacity of the volume of area which is larger thanks to the suction of air which is sucked inside its structure and then redirected by its stator and the plurality of its blades;

5. Figures 19, 20, 21, 22, 23, 24 and 25 show a better air intake which is made by its plurality of blades which gives a better propulsion to its furrow on the distance during the evacuation;

6. Fig. 29 shows a surface view of the alignment of the drive shaft, which has been inserted inside the motor structure where the drive shaft is inserted to give it stability;

7. Figures 16, 17 and 18 shows the sectional view of the stator, the blade, the plurality of blades and the transmission shaft which by its assembly gives a better stability;

8. The innovative aspect of the assembly provides increased performance in terms of air flow, energy efficiency, outstanding acoustic qualities versus the prior art. Given the arrangement that can be conceived of the linear angle of the fins that can have an angle of 0 to 180 degrees to be able to propel a larger volume of air versus prior art and we can have as inclination an angle of 0 to 90 degree of an angle perpendicular to the insertion of the blade, because the arrangement of the shaft of the transmission which makes it possible to stabilize its rotational movement by the absorption of any vibration and any movement of elasticity eliminated versus the prior art because the drive shaft is made of two pieces that can be inserted into one another by inserting a spring between the two attachments. The spring plays the role of tension / compression of the absorption phenomenon when the mechanism st in continuous function, the transmission shaft comes to play the role of damper regardless of the volume of air that is absorbed inside the structure and propelled by the blades. The transmission shaft can not be destabilized or be any deformation versus the prior art. In addition, there is no overconsumption of energy that is seen by the proportion of desired fluids according to the inclination given to its blades.

DETAILED DESCRIPTION OF THE ASSEMBLY

A # 13 framing of a fan axial exhaust structure includes a # 12 motor frame to which is attached a # 1 cylindrical conical hub. Inside the # 1 cylindrical conical hub is inserted # 3 ball bearings and a # 2 spring so that the # 2 spring is between the # 3 two ball bearings and that these are between two # 5 washers that will end up at each end. In the # 12 motor frame is inserted the # 7 stator which includes a # 14 motor. The blade # 10 with its plurality of blades to which is fixed the # 8 rotor and the transmission shaft # 9 is one piece. During its assembly the transmission shaft # 9 is inserted inside the # 1 cylindrical conical hub, the # 8 rotor is affixed inside the # 7 stator.

Once the axial structure fan is in operation, the air sucked in enters the structure (Figures 6, 7, 8, 9, 10, 11 and 12) of the fan which means that the volume of air that is propelled by the plurality of blades is much larger at the exit of the structure. Because of its plurality of blades (see FIGS. 16, 17, 18, 19, 20, 21, 22 and 23) which is arranged at its blade and at the inclination of the blades as required, the volume of air is much more important which explains a better propulsion of its sillonnage over the distance exerted according to the prior art and according to the experimental experiments made, considering the arrangement of this type of assembly a fan axial exhaust structure is far superior to the prior art

PROJECT: LAUZONE FAN

END-TIME REPORT JUNE 6, 2005

MADE BY: BRUNO DETUNCQ Professor in the Department of Mechanical Engineering

ASSISTED BY: ANNE DIONNE technician in the mechanical engineering department

POLYTECHNIC SCHOOL OF MONTREAL

TABLE OF CONTENTS

A) List of symbols and abbreviation

B) Objectives of the project

C) Methodology

1 - AMCA Standards

2 - Description of the assembly

3 - Installation diagrams

4 - Calibration of equipment

5 - Experimental method

D) Presentation and analysis of the results

1 - Preliminary tests

2 - Lauzone Fan Testing # 6po-Al-7P

3 - Lauzone fan test # 6po-Al-5P

£) Recommendations

A) LIST OF SYMBOLS AND ABBREVIATION

AMCA Air Movement ans Control Association

AMP Electric current supplied to the fan under test (Amp)

CPW Performance Criterion (CFM / Watt)

01 ₅ Mass flow rate of air (kg / s)

P ₂ Absolute static pressure at the fan outlet (kPa)

P ₂ , _v Static pressure measured at the fan outlet (Volt)

P ₂ , _in. Static pressure measured at fan outlet (in. H ₂ O)

P ₄ , _m Static pressure measured upstream of orifice plate (mm Hg)

ΔP ₅ .V Differential pressure measured at orifice plate (Volt)

RPM Rotation speed of the blower (rpm)

SCFM Standard Airflow Rate (ft ³ / min)

T ₃ Air temperature upstream of orifice plate ( ⁰ C)

TPM Rotation speed of the fan under test (rpm)

U ₄ Air velocity in pipe 6 "(m / s)

6 "pipe outlet flap opening opening flap

(values from: 0 completely closed to 1 fully open)

VOLT Voltage supplied to the fan under test (Volt)

WATT Electrical power consumed by the fan under test (Watt)

W _s Mechanical power transmitted to air (Watt) η _s Energy efficiency of the ventilator measured in relation to the electrical energy supplied to the motor (%) p ₄ Density of the air in the measurement pipe upstream of the heating plate orifice (kg / m ³ )

B) OBJECTIVES OF THE PROJECT

The main objective of this project is to characterize 2 Lauzone brand fans with nominal diameter of 6 inches, one fan has 7 blades and the other fan has 5 blades.

A secondary objective of the project is to develop a consistent methodology to measure the characteristics of these small capacity fans, which involves rigorous calibration and measurement work. The measurement range being in very small ranges, it is necessary that each step is controlled and validated precisely.

If this objective is met, this project will serve as a basis for developing a broader and longer-term collaboration. This first step took place in May and June 2005. C) METHODOLOGY 1 - AMCA Standards

The laboratory tests were carried out according to AMCA standards (Air Movement ans Control Association). These standards define the test conditions and ensure reproduction of these tests in other laboratories.

System of units used: because the responses of the measuring devices can be in electrical voltage, in the English system or in the metric system, it was decided to convert all the raw results into a metric system for processing, then to present the results. results in English system according to AMCA standards.

2 - Description of the assembly

A short description of the equipment will be made in the following lines. Figure 1 on the following page shows a diagram of the entire measurement system and the following pictures show some particularities of this arrangement.

Overall the assembly consists of a 6 inch long steel pipe of nominal internal diameter, used to rectify the profile of the air flow to allow measurement using the depression caused by the plate with orifice. At the exit of the pipe is a shutter with adjustable opening that allows to vary the pressure in the pipe. Between the tested fan and the air flow measurement line is a blower connected to a variable frequency drive that provides the ability to vary the speed of the blower from 50 to 3600 rpm.

This blower has the function of combating the pressure losses induced by the flow measurement system and thus allow to lower the static pressure at the outlet of the fan at zero pressure, which corresponds to the maximum flow point.

A profile rectifier is located at the outlet of the blower in order to tend towards the air profile as flat as possible.

List of equipment used:

- Fan upstream pressure (1): atmospheric pressure

Laboratory Mercury Barometer (mm Hg)

- Atmospheric air temperature:

Mercury thermometer ( ⁰ C)

- Relative humidity of the laboratory air:

Laboratory Hygrometer (%)

- Static pressure downstream to the fan (2):

Schaevitz LVDT pressure probe (10 "H2O) S / N: 10949

- Measurement of the upstream temperature at the orifice plate (3):

Thermocouple type 'T' and temperature gauge Omega model: HH-25 TC

- Static pressure sensor upstream of the orifice plate:

Omega 50mm Hg & Omega Indicator DP-25-S

- Flow meter for air:

Orifice plate; hole diameter = 98.63 mm (3.883 inches) - Differential pressure sensor for orifice plate (5):

Schaevitz LVDT pressure sensor (10 in. H2O) S / N: 5404

- Electric power supplied to the fan motor:

Fluke Power Meter # 39 (S / N: DM7450003)

Small clamp (current probe): Fluke # 80 i - 110s; Scale: 10 mVolt / Amp

Read values (AMP and WATT) of the device divided by 10 before entering the file

- Rotation speed of the fan under test:

Tachymeter Dynapar # HT-100; S / N: CT-610075

- Rheostat for adjusting the speed of rotation of the fan:

Brand ¹ LEVITON '; Trimatron ¹ model; No: 612-6616 continuously adjustable speeds

3 - Mounting diagrams Figure - 1: Mounting diagrams

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Voladcαaaβiedc Praes of m »Pnsβ * pitsami

Pl-l-c Im-Ce ab-fcs

V-- * ^

Air outlet

Your 110 Vi *

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Air inlet H

LAUZONE PROJECT

VenU-ue-r β po Λ Λ l cm cm cm Mom Mom Mom Mom Mom Fichier Fichier Fichier Fichier Fichier Fichier Fichier Fichier Fichier Fichier Fichier Fichier Fichier Fichier Fichier Fichier Figure -2: Photo of assembly, blower, measuring line and fan under test

Figure - 3: Side photo of mounting with tachometer and wattmeter

Figure - 4: Front view of the fan (5 blades) and tachometer

4 - Calibration of equipment

Figure - 5: Photo of the Schaevitz pressure probe calibration bench

The tachometer has been calibrated in comparison with the rotational speed of a fan having a 60 tooth gear and a magnetic sensor. The response of the devices is the same at 1 rpm for a range between 500 and 2000 rpm. Both LVDT pressure probes were calibrated as opposed to a Dwyer liquid gauge for a range of 0 to 1 inch of water. The response is linear and polynomial I ^e obtained order is included in the SEA module compilation results.

5 - Experimental method

Test conditions for the 2 fans:

- The free air inlet to the fan is free, without filter and without obstacle

- The fan is recessed at the entrance to the 6 inch ID acrylic pipe and 44 inches in length. The air outlet of the fan is therefore confined

- The fan speed must be measured and readjusted by the rheostat at each new condition

- The presence of the rheostat limits the maximum speed, it is difficult to operate at a speed above 1460 rpm. Without rheostat the maximum speed is of the order of 1850 rpm.

- The use of the small current measuring clamp and the use of the measuring scale of 10 mVolt / Amp, requires dividing the values of current (Amp) and power (Watt) read on the wattmeter by a value of 10

- When the blower is started (at low flow rates), there is a discontinuity area for the static pressure, there is interaction between the blower and the blower, a larger balance chamber after the blower would be needed

D) PRESENTATION AND ANALYSIS OF RESULTS

List of tests:

FAN DATE NUMBER TEST DESCRIPTION DURATION (hr)

Test to Determine Blower and Conduit Capabilities

2005-05-10 None of 6 in CFM Vs P Static 2.0

Preliminary evaluation test of the system with a fan and all 2005-05-17 LAUZONE # 6 2 0 "- A1 - 7P measuring devices E # 6 Real 2-speed fan test 880 and 1600 t -05-24 UUZO pm 2005 N ion velocity fluctuation according to P and flow 2.5 "- A1 - 7P Finding

Calibration of the 10 "LVDT H2O Probe (S / N ^• 5404) over the range of 2005-05-27 No measurement from 0 to 1" H2O 1 5

Fan test without rheostat, target speed about 1600 rpm

2005-05-27 LAUZONE # 6 Significant fluctuation in velocity vs. static pressure and po - A1 - 7P 1 5 (A) flow rate

2005-05-27 LAUZONE # 6 Fan test with gradual adjustment rheostats, velocity

6

(B) po - A1 - 7P instructions - 800 - 1200 - 1300 rpm 30

LAUZONE # 6 Fan test with gradual adjustment rheostat, speed of

7 2005-05-30 in - A1 - 7P setpoint 1000 rpm 20

LAUZONE # 6 Fan test with gradual adjustment rheostat, velocity

8 2005-05-31 in - A1 - 5P setpoint 1400 rpm 20

Fan test with gradual adjustment rheostat, velocity

9 2005-06-01 LAUZONE # 6 in - A1 - 5P setpoint 1200 - 1000 - 800 rpm 2.5

LAUZONE # 6 Fan test with smoke 3 stars used blue, white, black 2

10 2005-06-02 po - A1 - 5p speeds 800, 1300 rpm Photos and Video 20 The raw data is keyed into the computer and an EES module (V-7.177) is used to convert and process this data to obtain usable results and generate tables and graphs.

1- Preliminary tests

LAUZONE FAN TEST: 6 oo - Al - 7P (7 oales) DATE: 2005-05-27

Comments:

Preliminary tests have shown that the operation of the fan without rheostat or with fixed position rheostat gives the same behavior to the fan. That is, a fluctuation of the actual speed of the fan. It is therefore necessary to measure and readjust the speed for each change of measurement condition.

Preliminary tests have also shown that the presence of the rheostat decreases the maximum fan speed. The rheostat consuming a certain amount of electrical energy that can no longer be used by the engine.

The characteristic curves obtained when the fan speed fluctuates are slightly different from the curves for the case where the speed is constant. - Lauzone # 6po-Al-7P fan tests (7 blades)

LAUZONE FAN TEST: 6 "- Al - 7P (7 blades)

DATE: 2005-05-27 & 2005-05-30 Adjustable

10 20 30 40 SO 60 70 80 90 100 110

SCFM [pi3 / min]

LAUZONE FAN TEST: 6 "- Al - 7P (7 blades)

DATE: 2005-05-27 & 2005-05-30

SCFM [ft ³ / min] Table - 1: 1300 rpm fan speed

TPM WATT SCFM CPW

(rpm) (Watt) (Po H ₂ O) (piVmin) (%) (CFM / Watt)

1304 35 0.0920 0.08 0.003 0.002

1302 36 0.0840 0.08 0.002 0.002

1302 35 0.0766 0.08 0.002 0.002

1303 33 0.0620 16.01 0.377 0.485

1300 33 0.0680 22.32 0.577 0.676

1300 31 0.0536 26.79 0.581 0.864

1302 28 0.0460 30.58 0.630 1.092

1304 27 0.0370 35.98 0.619 1.333

1304 29 0.0376 43.39 0.706 1.496

1303 31 0.0414 48.77 0.817 1.573

1303 33 0.0440 53.67 0.898 1.626

1301 34 0.0442 59.57 0.972 1.752

1301 35 0.0418 64.58 0.968 1.845

1302 36 0.0382 70.03 0.932 1.945

1303 35 0.0316 75.53 0.856 2.158

1303 35 0.0246 80.50 0.710 2.300

1302 33 0.0130 85.01 0.420 2.576

1304 30 0.0000 92.20 0.000 3.073

Table -2: Fan speed of 1200 rpm

TPM WATT ^P 2, in. SCFM% CPW

(rpm) (Watts) (P H ₂ O) (pi'Vmin) (%) (CFM / Watt)

1202 32 0.0776 0.08 0.002 0.003

1202 31 0.0620 18.46 0.463 0.596

1200 28 0.0456 25.22 0.515 0.901

1204 25 0.0318 33.40 0.533 1.336

1205 26 0.0316 39.31 0.599 1.512

1203 28 0.0364 45.39 0.740 1.621

1205 30 0.0380 51.25 0.814 1.708

1202 31 0.0356 57.48 0.828 1.854

1201 32 0.0314 63.91 0.787 1.997

1205 31 0.0238 70.22 0.676 2.265

1200 30 0.0148 74.91 0.464 2.497

1203 28 0.0000 83.89 0.000 2.996 Table - 3: Fan speed of 1000 rpm

TPM WATT ^P 2, in. SCFM CPW

(rpm) (Watt) (in H ₂ O) (pVmin) (%) (CFM / Watt)

1000 25 0.0538 0.08 0.002 0.003

1001 21 0.0294 1 1.92 0.209 0.568

1001 20 0.0248 20.66 0.321 1.033

1002 20 0.0218 25.28 0.346 1.264

1000 22 0.0242 32.25 0.445 1.466

1001 23 0.0260 37.31 0.529 1.622

1000 24 0.0260 40.53 0.551 1.689

1001 25 0.0250 46.29 0.581 1.852

1002 25 0.0220 50.69 0.560 2.027

1003 24 0.0158 56.39 0.466 2.350

1000 24 0.01 16 59.81 0.363 2.492

1002 22 0.0000 67.60 0.000 3.073

Table - 4: 800 rpm fan speed

TPM WATT SCFM η _s CPW

(rpm) (Watt) (P H ₂ O) (p _-3 / min) (%) (CFM / Watt)

800 18 0.0274 0.08 0.002 0.004

802 18 0.0296 0.08 0.002 0.004

800 18 0.0288 14.12 0.283 0.784

795 15 0.0090 16.87 0.127 1.125

805 17 0.0100 24.86 0.183 1.462

804 18 0.0104 35.24 0.255 1.958

800 18 0.0058 42.78 0.173 2.377

808 18 0.0018 49.23 0.062 2.735

800 17 0.0000 51.25 0.000 3.014

- Lauzone # 6po-Al-5P fan test (5 blades)

LAUZONE FAN TEST; 6 "- Al - 5P (5 blades)

DATE: 2005-05-31 & 2005-0641 Adjustable - 800 rpm

SCFM [pB / min]

LAUZONE FAN TEST: 6 "- Al - 5P (5 blades>

DATE: 209545-31 & 200541641

SCFM [piVmin] Table - 5: 1400 rpm fan speed

(rpm) (Watt) (in H ₂ O) (pVmin) (%) (CFM / Watt)

1400 20 0.0891 0.08 0.004 0.004

1410 17 0.0450 14.20 0.465 0.835

1399 16 0.0380 19.30 0.567 1.206

1402 16 0.0338 25.78 0.674 1.611

1404 16 0.0345 30.63 0.819 1.914

1412 17 0.0361 34.47 0.905 2.028

1404 18 0.0395 40.49 1.099 2.249

1397 18 0.0359 46.75 1.154 2.597

1401 18 0.0340 52.01 1.215 2.889

1406 19 0.0317 56.35 1.163 2.966

1409 19 0.0237 63.56 0.982 3.345

1408 18 0.0131 69.80 0.627 3.878

1403 17 0.0047 74.69 0.255 4.394

1402 16 0.0000 77.87 0.000 4.867

Table - 6: Rotation speed of 1200 rpm tt)

1204 18 0.0678 0.08 0.004 0.004

1195 14 0.0304 16.50 0.443 1.179

1198 15 0.0294 22.42 0.544 1.495

1198 16 0.0300 27.44 0.637 1.715

1206 16 0.0292 34.05 0.770 2.128

1200 17 0.0254 41.48 0.768 2.440

1200 17 0.0228 46.53 0.771 2.737

1204 16 0.0150 53.12 0.615 3.320

1206 16 0.0074 58.74 0.334 3.671

1201 15 0.0028 63.05 0.145 4.203

Table - 7: Rotational speed of 1000 rpm

997 14.0 0.0457 0.08 0.003 0.006

1004 12.0 0.0188 20.29 0.393 1.690

1000 13.5 0.0186 26.66 0.454 1.975

999 13.7 0.0150 33.27 0.450 2.429

995 13.5 0.01 10 39.04 0.393 2.892

1007 13.4 0.0070 43.69 0.282 3.260

1004 12.5 0.0000 50.19 0.000 4.015 Table - 8: Speed of rotation of 800 rpm

796 11.3 0.0290 0.08 0.003 0.007

800 10.7 0.0123 13.10 0.186 1.224

796 10.8 0.0110 22.28 0.280 2.063

800 11.0 0.0110 26.73 0.330 2.430

802 10.4 0.0026 29.76 0.092 2.861

814 10.3 0.0003 33.81 0.013 3.282

E) RECOMMENDATIONS

1) The results show that the tests went well. Comparison with axial fans of other brands highlights that the shape of the curves is typical for this type of fan.

2) The measurements made in May 2005 used equipment dedicated to teaching in the Department of Mechanical Engineering. Some are well adapted, but others are less so. In order to improve the measurement system, it would be necessary to obtain new devices that better meet the constraints of this type of test, and also to release the equipment for use in teaching.

3) To improve the measurement system it would be necessary to add a buffer box between the fan under test and the fan, in order to stabilize the pressure measurement zone downstream of the fan.

4) Before undertaking a new series of tests, it would be necessary to define the dimensions of fans to be characterized and work in a consistent range in terms of flow to avoid difficulties.

5) To meet the mission of the Polytechnic School which is a primary mission of teaching, it would be interesting to join a student in the end of studies project to help the completion of the fall 2005 tests.

6) If the results of this first phase are conclusive and to the satisfaction of the company

Lauzone, it is recommended to develop a research project over a period of 1 year. This project will then have to be supervised by the BRCDT of the Polytechnic School to give it a legal base. LEGEND

1. Cylindrical conical hub

2. Spring

3. Ball bearing

4. Sealing plug

5. Washers

6. Washers

7. Stator

8. Rotor

9. Transmission shaft

10. Dawn with a plurality of blades

11. Position where the seal is located

12. Engine frame

13. Frame of axial fan exhaust structure

14. Engine

Claims

We claim:

1. An axial fan evacuation structure comprising a motor structure where a transmission shaft is installed, which can be made of several parts which can be inserted one into the other, playing the role of shock absorber and stabilizer its axis of rotation, to receive its stator and its motor inside. Inside the conical hub a ball bearing has been inserted as well as a spring to give stability to its rotor once assembled one into the other. The rotor comprises a conical and cylindrical aerodynamic blade to which there are a plurality of blades which may be molded, attached to the side surface of the blade, the blades could be inserted one into the other or the plurality of blades could be inserted above the blade could be riveted, welded, cast, bolted, pressure-glued or made in one piece. The plurality of blades which are inserted into the blade can have an angle inclination perpendicular to the insertion of the blade from 0 to 90 degrees depending on the desired design, for the desired mode of application and it can be designed the linear angle of the fins from 0 to 180 degrees. The rotor comprises an aerodynamic cylindrical conical blade to which there are a plurality of blades thus allowing during assembly with the stator a very high balance of rotation thus reducing the radial and axial forces which increases the lifespan of the components. The hub of the motor frame of the axial fan structure allows to obtain great stability when the transmission shaft is inserted in the center of its stator which is aligned inside the frame where ball bearings are installed at each end of the transmission shaft where a spring is installed inside the shaft between the two ball bearings. This spring creates a constant axial tension, given the arrangement that can be conceived of the linear of the fins from 0 to 180 degrees and that we can have as inclination an angle of 0 to 90 degrees of the angle perpendicular to the insertion of the blade, allowing great stability to be achieved versus the prior art. In addition, the motor which is inserted inside the motor frame where the stator is inserted which allows the hermetic protection of the motor from corrosion and all bad weather: heat, humidity, cold, evacuation of emanations from various gas and residue, smoke evacuation or any toxic or chemical product. The plurality of blades which are attached to the blade can have an angle variation perpendicular to the blade from 0 to 90 degrees, which allows absorbing a greater volume of air thanks to the motor assembly which is mounted in the center of its structure which makes it possible to increase the air thrust given the assembly which is fixed in the center of the structure. The groove of the thrust which has a circular arc shape of 360 degrees, is much higher compared to the prior art which means stability and performance. The design of the axial exhaust fan motor structure can be made of all existing composite materials, plastics, metal alloys, litho, organic, ecological and all existing materials, in the desired shapes and dimensions. The blade has a conical, aerodynamic cylindrical shape. The blade can be elongated while becoming aerodynamic for the operation of the engines and can be used in reverse rotation depending on the mode of application.

2. The axial fan evacuation structure according to claim #1, there can be no deformation of the material of the fins, given the increase in fluids and the curvature of the angles that can be given to its fins to take a greater volume of air is from 0 to 180 degrees, given the arrangement of the transmission shaft which can be modified according to the arrangement mode which can be made of several parts which can be inserted one into the the other, while inserting a spring between the parts to give a tension/compression element and which plays the role of absorption of the damping phenomenon and which gives stability to its axis of rotation when the mechanism is in continuous operation versus the prior art;

3. The axial fan evacuation structure according to claim #1, according to the innovative aspect of the assembly which makes it possible to obtain increased performance in terms of energy efficiency in terms of air flow and has acoustic qualities remarkable surpassing those of the prior art given the arrangement that can be conceived. The linear angles of the fins from 0 to 180 degrees to absorb a greater volume of air which is subsequently propelled outside its framing the furrowing of fluids and much more important in terms of air flow and therefore even though we can have as inclination an angle of 0 to 90 degrees of perpendicular angle of insertion of the blade versus the prior art (refer to the bird's eye assembly);

4. The axial fan evacuation structure according to claim #1, when the motor #14 is put into operation and the fluid absorption phenomenon takes place this is where the new way of assembling the shaft transmission versus the angle of the fins from 0 to 90 degrees and 0 to 180 degrees comes into line, because the pressure which this does by the absorption of fluids inside its structure does not destabilize the transmission shaft and does not allow the deformation of the fins because there is a continuous damping phenomenon which is done by the transmission shaft versus the prior art, regardless of the volume of air which is absorbed and redirected by the blades it does not there is no overconsumption of energy which occurs because there is no obstruction of the driving or physical force of the mechanism versus the desired angle according to the desired volume of air because the transmission shaft plays the damping role versus prior art;

5. An axial exhaust fan structure which comprises a #12 motor frame which can be referred to in Figure 1;

6. An axial fan evacuation structure includes #13 structure to which is attached a #7 stator and its #14 motor ref. in Figures 13, 14, and 15;

7. An axial exhaust fan structure has a #8 rotor with reference to Figures 16, 17, 18, 19, 20, 21, 22 and 23 having a top surface, a side surface and a plurality of blades connected to the surface side of blade #10, where each blade has an upper part higher than the upper surface of the blade to form an axial air inlet region and an edge part next to the upper surface of the blade to form a side air inlet region with the upper surface of the blade;

8. The axial exhaust fan structure according to claim 7 wherein the lateral air inlet region has a cylindrical conical shape;

9. The axial fan exhaust structure according to claim 7 wherein the side surface of the blade #10 has a circular arc shape;

10. The axial exhaust fan structure according to claim 7 and in Figures 16, 17, 18, 19, 20, 21, 22 and 23 where a space is formed between each of the edge portions of the blades and the side surface of the 'dawn;

11. The axial fan evacuation structure according to the drawings figures 24 and 25 thanks to the transmission shaft which was fixed to the frame of the structure where the #2 spring is installed between the two parts as well as #3 bearing marbles;

12. The axial fan evacuation structure according to claim 11 in Figure 7 we can see the alignment of the transmission shaft #9 which is inserted in the center of the framing in Figure 29 where there has been an addition of a #2 spring which receives the #8 rotor and the #7 stator in support of one another;

13. The axial fan evacuation structure according to the drawings figures 24, 25, 26 and 27 where we can see the points of stability and support where the #2 spring is installed inside the shaft #12 engine timing transmission;

14. The #13 axial fan evacuation structure according to claim 13 where we can see the #7 stator and the #8 rotor assembled End to the other by having added a #2 spring, a stability tension is created thanks to the arrangement of the #8 rotor and the #7 stator thereby giving better axial rotation propulsion;

15. The axial fan evacuation structure according to claim 7 wherein an upper end of the attachment part of each blade is flush with an upper edge of the side surface of the blade #10;

16. The axial fan evacuation structure according to claim 11, figures 24, 25, 26 and 27, the transmission shaft #9 can be integrated into the #8 rotor where a #2 spring is added inside of the transmission shaft to obtain axial stability;

17. The axial fan evacuation structure according to claim 16 by affixing #3 ball bearings to each end of the shaft #9 and adding a #2 spring, inside the shaft, a tension is created and stability is created thus giving a better rotary impulse to its axial rotation;

18. The axial fan evacuation structure according to claim 6 figures 13, 14 and 15 where a #7 stator and a #14 motor are integrated which protects it hermetically from all bad weather, corrosion, heat, humidity, cold, evacuation emanation of various gases, smoke evacuation or any chemical or toxic product;

19. The axial exhaust fan structure comprising a #8 rotor and a #7 stator where the operating mode can be reversed;

20. A structure with axial fan evacuation according to claim 7 figures 16, 17, 18, 19, 20, 21, 22 and 23 the blade #10 which has the particularity of a plurality of blades which can be designed from any composite materials , plastics, organic, ecological and all existing metals, are inserted at the end of the circumference of its #8 rotor which gives a desired inclination to be able to reduce the effect of turbulence and to cut even better the air to which these blades face to take a greater volume of air and thus have the desired inclination of 0 to 90 degrees perpendicular to the blade and an angle of 0 to 180 degrees to be able to absorb a greater volume of air according to needs;

21. An axial exhaust fan structure according to claim 16 the #3 ball bearings which are inserted at each end of the shaft #9 inside the shaft can be lubricated by the installation of a nozzle lubricator for better axial propulsion;

2. A structure with axial fan evacuation according to claim 11, the transmission shaft #9 as well as its assembly can be used for all existing transmission shafts, so-called the installation of a transmission shaft which can be assembled in different ways while using #3 ball bearings, #2 springs where electric magnetism, creating a constant axial tension, allowing very high stability to be achieved, the #3 ball bearings which allow radial swinging and thus giving a dynamic rotational balance;

23. The axial fan evacuation structure according to claim 7, blade #10 has a cylindrical and conical shape. The blade of the axial evacuation fan has a lateral surface which has a circular arc shape where the fins are inserted which can have an angle perpendicular from 0 to 90 to the insertion of the blade and which we can design the linear angle and according to the desired curvature from 0 to 180 degrees.

24. The axial exhaust fan structure according to claim 7 the plurality of blades which are inserted into blade #10 can have an angle variation of 0 to 90 degrees depending on the design as well as the desired air volume;

25. The axially vented fan structure according to the description of the assembly: of an axially vented fan structure figure 29 the assembly of the #7 stator and the #8 rotor which is inserted inside the structure axial exhaust of the fan. The quantity of air that the fan propels is much more efficient compared to the prior art;

26. The axial exhaust fan structure demonstrates experimental and scientific tests, rotation speed at different levels as well as different tables 15 pages of scientific results: energy consumption, static pressure, TPM, WATT, (POH20), (CP3/min ) % CFMAVATT NOT SHOWN;

27. The axial exhaust fan structure can be manufactured in all possible shapes and sizes according to requirements;

28. Although the concept illustrated in Figures 2, 3, 4, 5, 24, 25, 26, 27 and 28 and assembly description, shows an air exhaust system made of a metal assembly, this concept is not limited to this type of materials but can also be made of plastic, composite materials, various alloys, biological, ecological and litho components according to claim 1.