Title of Invention

METHOD FOR THE OPERATION OF AN ELEVATOR SYSTEM

Abstract Method for the operation of a lift installation, wherein the operating parameters (1.2) for achieving a desired performance (1.1) are determined by simulation of the operation of the lift installation, the operating parameter and the desired performance are comprised in a protocol (2.1), the lift installation is operated with the operating parameter, the actual performance (4.1) produced by the lift installation is measured and the actual performance is compared with the desired performance (Fig- 1)
Full Text

The present invention relates to an axial-flow fan, and more particularly, to an axial-flow fan that can reduce the camber ratios of blades up to a range between 33% and 85%, thereby achieving a very low noise level.
Background of the Related Art
An axial-flow fan includes a circular central hub and a plurality of blades radially arranged along the circumference of the hub, and as well known those skilled in the art, the axial-flow fan is a kind of fluid machinery and serves to blow air in the axial direction by the rotation of the plurality of the blades. A representative example of the axial-flow fan is a cooling fan that promotes heat radiation of an air-cooled heat exchanger, such as an electric fan, a ventilation fan, and a radiator or condenser of an automobile, by blowing air to or drawing air from the heat exchanger.
Le3] The axial-flow fan that is used as the cooling fan of the heat exchanger in the air conditioning system of the

automobile is mounted in the rear or front of the heat exchanger in conjunction with a shroud that is provided with a plurality of airflow guide vanes that serve to guide the air blown by the blades of the fan to an axial direction from the front or the rear of the heat exchanger. The axial-flow fan may be classified into a pusher-type axial-flow fan assembly and a puller-type axial-flow fan assembly in accordance with the arranged positions with respect to the heat exchanger.
As shown in FIGS. 1 and 2, the general axial-flow fan
I of an automobile is mounted in conjunction with a shroud 2
surrounding the blades of the fan and guiding air toward the
axial direction, in the front of the heat exchanger. The axial-
flow fan 1 includes a central hub 12 connected with the driving
shaft of a motor 3, a plurality of blades 11 extending radially
outwardly from the hub 12, and a circular fan band 13 to which
the peripheral ends of the plurality of blades 11 are fixed for
surrounding the plurality of blades 11. The axial-flow fan is
generally made of synthetic resin and integrated with the blades
II into a single body- The plurality of blades 11 that are
curved in the plane of the fan 1 are rotated as the motor 3 is
rotated, thereby producing a difference pressure of the airflow
velocity between the front and rear of the fan. Thus, the axial-
flow fan blows air to the axial direction,

Therefore, the plurality of blades 11 can give lots of influences to the airflow efficiency and the generation of noise in the axial-flow fan 1. As shown in FIG. 5 showing the terms used to describe the blades 11 of the axial-flow fan 1 are defined, the axial-flow fan 1 should be designed optimally with a variety of blade designing factors, such as setting angle of the blades 11, camber ratio, cross-directional curvature, chord length and axial-directional inclination angle.
The camber ratio is obtained by dividing a maximum camber value into a chord length.
The setting angle is obtained by subtracting a stagger angle at which each blade 11 is erected from 90 degree.
Among the afore-described designing factors, herein, the setting angle and the camber ration should be determined with great care.
As shown in FIGS. 5 and 6, the setting angle in the prior art is formed in such a way that it is constant from an intermediate region of each blade to a blade tip and decreases at a blade root, and the camber ratio decreases toward the blade tip from the hub 12. In this case, the percentage of decrease of the camber ratio is not over 30%.
According to the blade designing factors in the prior art, by the way, they exhibit the limits in suppressing the airflow noise generation during the rotation of the blades 11.

SUMMARY OF THE INVENTION
Accordingly, the present invention has been made in view of the above-mentioned problems occurring in the prior art.
An object of the present invention is to provide an axial-flow fan that can reduce the camber ratios of a plurality of blades up to a range between 33% and 85%, thereby achieving a very low noise level.
According to an aspect of the present invention, there is provided an axial-flow fan comprising a central hub connected with a driving shaft of a motor and a plurality of blades having setting angle which is an inclination angle of the blades with respect to the rotation direction extending radially along the circumference of the hub for blowing air toward an axial direction, the plurality of blades integrated with the hub into a single body, wherein assuming that a camber ratio at a blade root (crl) of each blade is the value obtained by dividing a maximum camber value at the blade root into a chord length, a camber ratio at a blade tip (cr2) of each blade is the value obtained by dividing a maximum camber value at the blade tip into the chord length, and a percentage of decrease of the camber ratio is the value obtained by dividing a difference value between the camber ratio at the blade root (crl) and the camber ratio at the blade tip (cr2) into the camber ratio at the blade root (crl), the percentage of decrease of the camber ratio is in a rang between 33% and 85%.

According to another aspect of the present invention, there is provided an axial-flow fan having a central hub connected with a driving shaft of a motor and a plurality of blades extending radially along the circumference of the hub 12 for blowing air toward an axial direction, the plurality of blades integrated with the hub into a single body, wherein each blade has a backward sweep angle at the blade root thereof and a forward sweep angle at the blade tip thereof, while having an airflow distributing region that is defined by a plurality of small regions where sweep angles are changed in turn formed on a region between the backward sweep angle region and the forward sweep angle region, and wherein assuming that a camber ratio at the blade root (crl) of each blade is the value obtained by dividing a maximum camber value at the blade root into a chord length, a camber ratio at the blade tip(cr2) of each blade is the value obtained by dividing a maximum camber value at the blade tip into the chord length, and a percentage of decrease of the camber ratio is the value obtained by dividing a difference value between the camber ratio at the blade root (crl) and the camber ratio at the blade tip(cr2) into the camber ratio at the blade root(crl), the percentage of decrease of the camber ratio is in a range between 33% and 85%.

BRIEF DESCRIPTION OF THE DRAWINGS
The above and other objects, features and advantages of the present invention will be apparent from the following detailed description of the preferred embodiments of the invention in conjunction with the accompanying drawings, in which:
FIG. 1 is an exploded perspective view of a general axial-flow fan assembly;
FIG, 2 is a front view of the axial-flow fan of FIG. 1;
FIG. 3 is a perspective view of the outer appearance of the axial-flow fan according to the present invention;
FIG, 4 is a front view of the axial-flow fan of the present invention;
FIG. 5 is a sectional view taken along the line V—V shown in FIG. 4, wherein the terms used to describe the blades of the axial-flow fan are defined;
■t^l] FIG. 6 is a graph showing the changes of the setting angle in the axial-flow fan of the present invention;
FIG. 7 is a graph comparing the degrees of noise of the prior art and the present invention with respect to the setting angle of the present invention;
FIG. 8 is a graph showing the changes of camber ratio in the axial-flow fan of the present invention; and

FIG. 9 is a graph showing the degree of noises with respect to the camber ratios in the axial-flow fan of the present invention when air volume is the same.
DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT -f2Sl Reference will now be made in detail to the preferred embodiments of the present invention, examples of which are illustrated in the accompanying drawings.
FIG. 3 is a perspective view of the outer appearance of the axial-flow fan according to the present invention, FIG. 4 is a front view of the axial-flow fan of the present invention, FIG. 5 is a sectional view taken along the line V--V shown in FIG, 4, wherein the terms used to describe the blades of the axial-flow fan are defined, FIG. 6 is a graph showing the changes of the setting angle in the axial-flow fan of the present invention, FIG. 7 is a graph comparing the degrees of noise of the prior art and the present invention with respect to the setting angle of the present invention, FIG. 8 is a graph showing the changes of camber ratio in the axial-flow fan of the present invention, and FIG. 9 is a graph showing the degree of noises with respect to the camber ratios in the axial-flow fan of the present invention when air volume is the same.
The axial-flow fan 10 0 of the present invention includes a central hub 120 connected with a driving shaft of a

motor (not shown), a plurality of blades 110 extending radially along the circumference of the hub 12 0 for blowing air toward an axial direction, the plurality of blades 110 integrated with the hub into a single body, and a circular fan band 130 to which the peripheral ends of the plurality of blades 110 are fixed for surrounding the plurality of blades 110.
Each of the plurality of blades 110 has a front peripheral side 110a and a rear peripheral side 110b that are formed in a shape of waveform.
The axial-flow fan 100 of the present invention may be applied to a pusher-type axial-flow fan assembly and a puller-type axial-flow fan assembly in accordance with the arranged positions with respect to the heat exchanger.
In the first embodiment of the present invention, assuming that a camber ratio at a blade root (crl) of each blade 110 is the value obtained by dividing a maximum camber value at the blade root into a chord length, a camber ratio at a blade tip (cr2) of each blade 110 is the value obtained by dividing a maximum camber value at the blade tip into the chord length, and
a percentage of decrease Acr of the camber ratio is the value obtained by dividing a difference value between the camber ratio at the blade root(crl) and the camber ratio at the blade tip(cr2) into the camber ratio at the blade root (crl), the percentage of

decrease Acr of the camber ratio is in a range between 33% and 85% .
According to the present invention, the percentage of
decrease Acr of the camber ratio is preferably in a range between 50% and 70%.
The setting angle sa of each blade 110 increases from an intermediate region of each blade 110 to the blade tip.
The setting angle sa increases in a range between 2 degree and 8 degree at a smallest angle point.
The camber ratio at the blade root(crl) of each blade 110 has a greatest value of 0.1 and the camber ratio at the blade tip(cr2) of each blade 110 has a smallest value of 0.01.
More preferably, the camber ratio at the blade root(crl) of each blade 110 has a greatest value of 0.065 and the camber ratio at the blade tip (cr2) of each blade 110 has a smallest value of 0.025.
According to another embodiment of the present invention, each blade 110 has a backward sweep angle at the blade root thereof and a forward sweep angle at the blade tip thereof, and it also has an airflow distributing region that is defined by a plurality of small regions where sweep angles are changed in turn formed on a region between the backward sweep angle region and the forward sweep angle region.

In more detail, each blade is slanted in a direction opposite to the rotation at the blade root abutting the hub 12 0 and is slanted in a rotating direction at the blade tip. Thus,
the sweep angle σr is an angle between a tangent line extending from an arbitrary point on the leading edges line or trailing
edges line of the blades 110, and a radius line extending from
the center of the hub 120 through the arbitrary point. The sweep
angle is backward (-) at the blade root and starts to be changed
at a predetermined point toward the blade tip in such a way as to
be forward (+) at the blade tip. That is to say, each blade has
the backward sweep angle σr1 at the blade root portion and the
forward sweep angle σr2 st the blade tip portion.
The leading edges line or trailing edges line have an airflow distributing region D where the sweep angle is changed from backward to the forward at a first turning point rn, changed to the rear direction again at a second turning point ri2, and changed to the front direction again at a third turning point r13, at the intermediate portion thereof.
σ The airflow distributing region D forms two airflow concentrating portions C1 and C2 at the rear peripheral side of each blade, and therefore, the axial-flow fan of the present invention can greatly suppress the collection of the airflow when compared with the conventional practice where a single airflow concentrating portion C is formed, as shown in FIG. 2.

On the other hand, assuming that a camber ratio at a blade root(crl) of each blade is the value obtained by dividing a maximum camber value at the blade root into a chord length, a camber ratio at a blade tip (cr2) of each blade is the value obtained by dividing a maximum camber value at the blade tip into
the chord length, and a percentage of decrease Acr of the camber ratio is the value obtained by dividing a difference value between the camber ratio at the blade root(crl) and the camber ratio at the blade tip (σr2) into the camber ratio at the blade
root(σrl), the percentage of decrease Acr of the camber ratio is in a range between 33% and 85%.
According to the present invention, the percentage of
decrease Acr of the camber ratio is preferably in a range between 50% and 70%.
The setting angle sa of each blade 110 increases from an intermediate region of each blade 110 to the blade tip.
The setting angle sa increases in a range between 2 degree and 8 degree at a smallest angle point.
The camber ratio at the blade root (crl) of each blade 110 has a greatest value of 0.1 and the camber ratio at the blade tip(cr2) of each blade 110 has a smallest value of 0.01.
H[45t^ More preferably, the camber ratio at the blade root(crl) of each blade 110 has a greatest value of 0.065 and the

camber ratio at the blade tip (cr2) of each blade 110 has a smallest value of 0.025.
In this case, an axis X in FIG. 6 represents each blade ranging from the blade root to the blade tip that is divided by 17 in a direction of a line V—V in FIG. 4, and an axis
Y therein represents the setting angles, as shown in FIG. 5.
In more detail, the setting angle 1 (n) represents the setting angle that increases from an intermediate region of the hub 12 0 to the blade tip of each blade 110, as appreciated from
the embodiment of the present invention, the setting angle 2(0) represents the setting angle that is approximately constant from an intermediate region of the hub 120 to the blade tip of each blade 110, and the setting angle 3(0), the setting angle 4(0) and the setting angle 5(0) represent the setting angles that increase from an intermediate region of the hub 120 to the blade tip of each blade 110, as appreciated from the prior art.
In this case, an axis X in FIG. 8 represents each blade ranging from the blade root to the blade tip that is divided by 17 in a direction of a line V—V in FIG. 4, and an axis
Y therein represents the camber ratios, as shown in FIG. 5.
In more detail, • represents the camber ratio embodied in the prior art that is approximately constant from the hub 120 to the blade tip of each blade 110, wherein the camber ratio is 0,06 to 0,07 in a full range.

 represents the camber ratio, which somewhat decreases from the hub 120 to the blade tip of each blade 110, wherein the camber ratio is in a range of 0.05 to 0.06.
 represents the camber ratio embodied in the present invention, which decreases greatly from the hub 120 to the blade tip of each blade 110, wherein the camber ratio is in a range of 0.065 to 0.025.
The setting angle of each blade is determined as described in the first and second embodiments of the present invention, and as shown in FIG. 7, the present invention can achieve a gradually lower noise level when compared with the
prior art when the air volume is the same in the setting angle n.
And the present invention generates relatively higher noise
levels in accordance with the order of the setting angle 2 D, the setting angle 3(D) , the setting angle 4(□) and the setting angle 5(0).
Also, the percentage of decrease of the camber ratio of each blade is determined as described in the first and second embodiments of the present invention, and as shown in FIGS. 8 and 9, the present invention generates a gradually lower noise level in accordance with the order of the camber ratio 1 •, the camber ratio 2 D and the camber ratio 3 D when the air volume is the same.

The optimal camber ratio  in the present invention generates a remarkably lower noise level, as shown in FIG. 9, when the air volume is the same.
 As clearly described above, there is provided an axial-flow fan that can reduce the camber ratios of a plurality of blades up to a range between 33% and 85%, thereby achieving a very low noise level.
While the present invention has been described with reference to the particular illustrative embodiments, it is not to be restricted by the embodiments but only by the appended claims. It is to be appreciated that those skilled in the art can change or modify the embodiments without departing from the scope and spirit of the present invention.



Patent Claims
1. Method for the operation of a lift installation, characterised in that at least one operating parameter (1.2) for achieving a desired performance (1.1) is determined by simulation of the operation of the lift installation and/or by calculation, that the lift installation is operated with the operating parameter, that at least one actual performance (4.1) produced by the lift installation is measured and that the actual performance is compared with the desired performance.
2. Method according to claim 1, characterised in that as operating parameter there is or are used a number of stops served by lifts and/or the distance between stops and/or a number of persons to be served at a stop and/or a number of lifts in the lift installation under consideration and/or the stops served by a lift and/or the kind of drive of a lift (maximum speed, data with respect to graphical travel plot by means of acceleration and jolt or travel times between stops or specific distances) and/or the type of cage of a lift (number of decks, size, maximum load weight, maximum number of persons) and/or the type of cage doors of a lift (width, opening time, time for keeping open and closing time) and/or the type of lift control and passenger interfaces and/or a passenger traffic.
3. Method according to claim 1, characterised in that as desired performance and actual performance, respectively, there is or are ascertained a destination time of the user and/or a waiting time of the user and/or an acceleration and/or a speed and/or a number of served passengers and/or a number of stops per passenger.
4. Method according to claim 1, characterised in that the calculation and/or simulation of the operation is carried out on a computer installation, with a computer program loaded in a memory of the computer installation, by a processor of the computer installation which executes the computer program, wherein the desired performance is linked with the operating parameter by way of a simulation rule.
5. Method according to claim 4, characterised in that calculations and/or simulations of the operation of the lift installation are optimised by at least one changed operating parameter and that this optimisation is repeated until the operating parameter fulfils the requirement of the desired performance.

6. Method according to one of claims 1 to 5, characterised in that operating parameters and target performance are comprised in a protocol (2.1) and that the protocol is provided in the form of an electronic file and/or a written document.
7. Method according to claim 6, characterised in that a guaranteed value for the desired performance of a lift installation is determined and that the guaranteed value is diminished relative to the desired performance by a predetermined factor.
8. Method according to claim 6 or 7, characterised in that the desired performance and the actual performance are compared by means of a protocol analyser.
9. Protocol for the operation of a lift installation, characterised in that the protocol comprises at least one operating parameter (1.2) for achieving a target performance (1.1). which operating parameter is determined by simulation of the operation of the lift installation and/or by calculation, that the protocol also comprises the desired performance corresponding with the operating parameter and that the lift installation is operable with the operating parameter.
10. Protocol according to claim 9, characterised in that the protocol comprises a guaranteed value for the desired performance of a lift installation and that the guaranteed value is diminished relative to the desired performance by a predetermined factor.
11. Protocol according to claim 9 or 10, characterised in that the protocol comprises a falsification protection in order to prevent the operating parameter and/or the desired performance from being changed unnoticed and/or that the protocol contains an exhaustion data which ensures that claims derived from the protocol are valid only for a restricted time period and/or that a comparison of an actual performance of the lift installation, which is operated with the operating parameter, with the desired performance is designed so that the operating parameter or the protocol is not disclosed or is only partly disclosed and/or that the protocol can be unambiguously checked with respect to the genuineness thereof by means of a publicly available method.
12. Guaranteed value for the desired performance of the operation of a lift installation, characterised by: determination of at least one operating parameter (1.2) for achieving a desired performance (1.1) by simulation of the operation of the lift installation and/or by

calculation wherein a desired performance of the lift installation corresponds with the operating parameter, and the guaranteed value is diminished relative to the desired performance by a predetermined factor.
13. Guaranteed value according to claim 12, characterised in that a measured actual performance of the lift installation operated with the operating parameter can be compared with the guaranteed value.

14. A method for the operation of a lift installation, substantially as herein described
with reference to the accompanying drawings.
15. A protocol for the operation of a lift installation, substantially as herein described
with reference to the accompanying drawings.


Documents:

196-CHE-2004 CORRESPONDENCE OTHERS 01-11-2011.pdf

196-CHE-2004 AMENDED CLAIMS 25-07-2012.pdf

196-CHE-2004 AMENDED PAGES OF SPECIFICATION 25-07-2012.pdf

196-CHE-2004 EXAMINATION REPORT REPLY RECEIVED 25-07-2012.pdf

196-CHE-2004 FORM-1 25-07-2012.pdf

196-CHE-2004 FORM-3 25-07-2012.pdf

196-CHE-2004 OTHER PATENT DOCUMENT 25-07-2012.pdf

196-CHE-2004 POWER OF ATTORNEY 25-07-2012.pdf

196-che-2004-abstract.pdf

196-che-2004-claims.pdf

196-che-2004-correspondnece-others.pdf

196-che-2004-description(complete).pdf

196-che-2004-drawings.pdf

196-che-2004-form 1.pdf

196-che-2004-form 26.pdf

196-che-2004-form 3.pdf

196-che-2004-form 5.pdf

abs-196-che-2004.jpg


Patent Number 253577
Indian Patent Application Number 196/CHE/2004
PG Journal Number 31/2012
Publication Date 03-Aug-2012
Grant Date 01-Aug-2012
Date of Filing 05-Mar-2004
Name of Patentee INVENTIO AG
Applicant Address SEESTRASSE 55 CH-6052 HERGISWIL
Inventors:
# Inventor's Name Inventor's Address
1 FINSCHI, LUKAS WEYSTRASSE 26 CH-6006 LUCERNE
PCT International Classification Number B66B1/20
PCT International Application Number N/A
PCT International Filing date
PCT Conventions:
# PCT Application Number Date of Convention Priority Country
1 03405163.1 2003-03-10 EUROPEAN UNION