CN1135306C - Axial-flow fan - Google Patents
Axial-flow fan Download PDFInfo
- Publication number
- CN1135306C CN1135306C CNB001213490A CN00121349A CN1135306C CN 1135306 C CN1135306 C CN 1135306C CN B001213490 A CNB001213490 A CN B001213490A CN 00121349 A CN00121349 A CN 00121349A CN 1135306 C CN1135306 C CN 1135306C
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- Prior art keywords
- blade
- flow fan
- axial flow
- hub
- tip
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- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/12—Sound
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
- F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
- F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
- F25D2317/068—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the fans
- F25D2317/0681—Details thereof
Abstract
The present invention discloses an axial flow fan for cooling a compressor and a condenser in a machine chamber of a refrigerator, which can provide necessary air for the machine chamber, and can reduce operation noise of the refrigerator. The axial flow fan comprises a hub installed on a rotating shaft of a driving motor, wherein a plurality of blades are regularly fixed at the circumference of the hub, the number of the baldes is three, and the ratio of the diameter of hub or the internal diameter of the axial flow fan to the external diameter of the axial flow fan is from 0.21 to 0.25. In addition, the axial flow fan of the present invention is provided with a large scanning angle, a large spiral angle and a high camber ratio.
Description
Technical field
The present invention relates generally to the axial flow fan that refrigerator is used, this axial flow fan is used for cooling off the machine that is installed in the refrigerator machine chamber, more specifically, the present invention relates to the axial flow fan that a kind of like this refrigerator is used, this axial flow fan is designed to have three blades, 0.21～0.25 boss ratio, big scanning angle, big helix angle and high camber ratio, thereby forms smooth air circulation and cool off machine in the machine chamber more effectively in machine chamber.
Background technique
Fig. 1 is one and shows the existing stereogram of type refrigerator structure side by side.Fig. 2 is a stereogram that shows the cold airflow in existing type refrigerator inside structure side by side and this refrigerator.Fig. 3 is the left view of Fig. 2.Fig. 4 is the right elevation of Fig. 2.Fig. 5 is a planimetric map that shows cold airflow in current refrigerator machine chamber internal structure and the machine chamber.Fig. 6 is the plan view of Fig. 2.
As shown in Figures 1 to 4, the casing of existing type refrigerator side by side portion within it vertically is divided into two vertical components, thereby limits a refrigerating chamber 10 and limit a cold storage room 20 in of two vertical components in another vertical component.
In above-mentioned refrigerator, a vaporizer 11 is installed in refrigerating chamber 10 rear portions and produces cold air by a heat exchanging process.A cool-air feed fan 13 is installed in vaporizer 11 tops and produces suction, so that infeed refrigerating chamber 10 and the cold storage room 20 from vaporizer 11 suction cold air and with cold air.
Above-mentioned axial flow fan 25 is installed in the rotating shaft of a drive motor 26 and along with motor 26 rotates together securely.A guard shield 27 is installed in the blade of axial flow fan 25 on every side with the protection blade.
In the running of this existing type refrigerator side by side, refrigerant becomes high temperature and high pressure gas refrigerant and flows into condenser 23 by compressor 22 compression.In condenser 23, gas refrigerant is dispersed into heat in condenser 23 ambient airs, thereby becomes room temperature highly pressurised liquid refrigerant.
After this, a capillary tube crossed by liquid refrigerant output stream from condenser 23 and pressure reduces, thereby partly becomes the two-phase refrigerant that comprises liquid and gas.Refrigerant from capillary tube flow into the refrigerating chamber 10 vaporizer 11 and in vaporizer 11 complete evaporation from vaporizer 11 ambient airs, absorb heat simultaneously to become low-pressure refrigerant, thereby cooling air.
The cool-air feed that heat exchanging process by vaporizer 11 forms is in refrigerating chamber 10 and cold storage room 20.Above-mentioned refrigeration cycle is carried out repeatedly so that refrigerating chamber 10 and cold storage room 20 are remained on required low temperature.
In this running of refrigerator, the axial flow fan 25 that is installed in the machine chamber 21 utilizes air-flow cooling compressor 22 and condenser 23.
Air-flow from axial flow fan 25 flows in machine chamber 21 as follows: outside air or atmosphere since the suction that produced of axial flow fan 25 at first by air inlet 21 ' be inhaled in the machine chamber 21.
In machine chamber 21, the suction of inhaled air by fan 25 flow through drive motor 26 and flow through fan 25 and guard shield 27 to arrive condenser 23.
Air is walked around condenser 23, absorbs the heat that is distributed by flowing refrigerant in condenser 23 simultaneously.Air thereby cooler condenser 23.
After walking around condenser 23, air is walked around compressor 22, simultaneously the surface of cooled compressed engine housing before entering atmosphere by air outlet slit 21 ＂ from machine chamber 21.
In brief, the suction by axial flow fan 25 sucks and enters the main cooler condenser 23 of air in the machine chamber 21, thereby improves the heat exchange efficiency and the final refrigerating efficiency that improves refrigerator of condenser 23.Enter the outer surface that air is followed cooling compressor 22 in the machine chamber 21, thereby compressor 22 is remained on required low temperature and prevent that compressor 22 is damaged in running state.
Therefore, the running state of axial flow fan is one of key factor of determining refrigerator refrigerating efficiency and operation noise.
The external diameter that the existing axial flow fan 25 that this refrigerator is used has three blades, a fan 25 from 145mm to 165mm, the blade scanning angle is little, the blade screw angle is little and the blade camber ratio is low, bothers people around the refrigerator thereby regret very much to make refrigerator have low refrigerating efficiency and produce sizable noise.
Little blade scanning angle increases the operation noise of fan 25 unfriendly.Little blade screw angle causes width of blade to reduce, the result, and axial flow fan 25 is not suitable for absorbing the air of aequum.When blade camber ratio (%) is low as described above, may increase the static pressure of the fluid that flows through axial flow fan and guard shield hardly effectively, in order to overcome this problem, fan 25 must be with too high rpm rotation.
Therefore, must design each Blade Design parameter best, such as number, boss ratio, scanning angle, helix angle and the camber ratio of blade, so that design parameter is consistent with the required operating conditions of the refrigerator of manufacturing.When these design parameters of axial flow fan during as described above by optimal design, can move axial flow fan best by a converter Control process, air with aequum supplies to compressor and condenser and realizes required fan rpm simultaneously, and the operation noise that reduces fan effectively.
Summary of the invention
Therefore, the invention reside in and overcome the problems referred to above of the prior art, an object of the present invention is to provide the axial flow fan that a kind of refrigerator is used, this axial flow fan is designed to make air circulation actively in the refrigerator machine chamber, thereby realize that air flows into glibly and flows out and eliminates in machine chamber the caused operation noise of the air circulation of disturbance and increase the air quantity that flows into and flow out, and realize that air with aequum supplies to compressor and condenser and reduces refrigerator effectively and move noise.
To achieve these goals, the axial flow fan that the preferred embodiments of the present invention provide a kind of refrigerator to use, this axial flow fan comprise a leaf hub that is installed on the motor shaft, and a plurality of blades are fixed on around the leaf hub regularly.In axial flow fan of the present invention, each Blade Design parameter such as number, boss ratio, scanning angle, helix angle and the camber ratio of blade, is designed best so that these design parameters are consistent with the required operating conditions of the refrigerator of manufacturing.This axial flow fan thereby the air of aequum can be supplied to compressor and condenser in the machine chamber reduces the operation noise of refrigerator simultaneously effectively.
Specifically, the invention provides a kind of axial flow fan, comprise a leaf hub that is installed in the rotating shaft, a plurality of blades are fixed on around the described leaf hub, wherein regularly, the number of described blade is three, axial flow fan internal diameter and leaf hub equal diameters, the described external diameter of axial flow fan is 150 ± 1mm, the internal diameter of this fan is 35 ± 1mm, and to make the anterior leading edge distance setting of described blade be 43.5 ± 1mm, and the rear portion trailing edge distance setting of blade is 14.2 ± 1mm.
Description of drawings
Can more be expressly understood above and other objects of the present invention, feature or other advantage by detailed description below in conjunction with accompanying drawing.In the accompanying drawing:
Fig. 1 is one and shows the existing stereogram of type refrigerator structure side by side;
Fig. 2 is a stereogram that shows the cold airflow in existing type refrigerator inside structure side by side and this refrigerator;
Fig. 3 is the left view of Fig. 2;
Fig. 4 is the right elevation of Fig. 2;
Fig. 5 is a planimetric map that shows cold airflow in current refrigerator machine chamber internal structure and the machine chamber; Fig. 6 is the plan view of Fig. 2;
Fig. 7 is the plan view of axial flow fan according to the preferred embodiment of the invention;
Fig. 8 is the side view of Fig. 7;
Fig. 9 a and Fig. 9 b are the sectional views that shows the shape be included in a blade in the axial flow fan according to the preferred embodiment of the invention;
Figure 10 chart that to be a demonstration change along with the boss ratio of axial flow fan according to the operation noise of axial flow fan of the present invention;
Figure 11 chart that to be a demonstration change along with the maximum camber ratio of axial flow fan according to the operation noise of axial flow fan of the present invention;
Figure 12 chart that to be a demonstration change along with the helix angle of axial flow fan according to the operation noise of axial flow fan of the present invention;
Figure 13 chart that to be a demonstration change along with the scanning angle of axial flow fan according to the operation noise of axial flow fan of the present invention.
Embodiment
Fig. 7 is the plan view of axial flow fan according to the preferred embodiment of the invention.Fig. 8 is the side view of Fig. 7.Fig. 9 a and Fig. 9 b are the sectional views that shows the shape be included in a blade in the axial flow fan according to the preferred embodiment of the invention.
In the present invention, axial flow fan is designed to effectively atmosphere to be sucked in the machine chamber of refrigerator and cooler condenser at first, thereby improve the heat exchange efficiency of condenser, follow the outer surface of cooling compressor, thereby prevent that compressor is damaged in running state.To shown in Figure 9, axial flow fan of the present invention comprises a leaf hub 51 that is installed to securely in the drive motor rotating shaft 50 as Fig. 7, and a plurality of blades 55 are fixed on around the leaf hub 51 regularly.In axial flow fan of the present invention, the number of blade 55 is set at three, the ratio of the inner diameter, ID of axial flow fan and external diameter OD, and promptly boss ratio is set at 0.21～0.25.In this case, inner diameter, ID equals the diameter of leaf hub 51.
In detailed description, the external diameter OD of axial flow fan is 150 ± 1mm, and the fan inner diameter, ID is 35 ± 1mm.Therefore, the boss ratio of axial flow fan is 0.233.On the other hand, the anterior leading edge of blade 55 is 43.5 ± 1mm apart from FD, and the rear portion trailing edge distance R D of blade 55 is 14.2 ± 1mm.In this case, the rear portion trailing edge distance R D of blade 55 is shorter than leaf hub thickness HD.
The anterior leading edge of blade 55 is a distance on the Z axle apart from FD, or one in the central position (0 from the blade data, 0,0) extends to distance on the spin axis of maximum blade front edge RE, and the rear portion trailing edge distance R D of blade 55 is the distances on the Z axle, or the distance on spin axis that extends to maximum blade rear edge TE in central position (0,0,0) from the blade data.That is to say that two jointly are limited on the spin axis (Z axle) of fan apart from FD and RD.
The central position of blade data (0,0,0) is arranged in leaf hub 51, and is the central position of leaf hub 51.
In addition, the maximum radian set positions of each blade 55 is 0.7～0.75, and the radian position is evenly distributed on each blade 55 from blade and blade hub BH to blade tip BT.The maximum camber ratio of each blade 55 is 4.8～5.2% at blade and blade hub BH place, is 6.1～6.5% at blade tip BT place, and is implemented in the linear distribution on the blade 55.
In this case, the maximum radian position of each blade 55 is meant at this position blade 55 apart from the straight line CL that extends to blade rear edge TE from blade front edge RE farthest, and is expressed as from blade front edge RE to straight line CL upward apart from the length C P of blade 55 position farthest and the ratio of chord length CX.
Distance between the described position on described straight line and each blade 55 is maximum camber C, and maximum camber ratio is maximum camber C and the ratio of chord length CL.
The helix angle Ψ of each blade 55 is 43.8 °～44.2 ° at blade and blade hub BH place, is 29.8 °～30.2 ° at blade tip BT place, and from blade and blade hub BH to blade tip BT linear distribution on blade 55.
In this case, the helix angle Ψ of each blade 55 is formed in an X-axis and an angle between a straight line that extends between blade front edge RE and the blade rear edge TE.That is to say that the helix angle Ψ of each blade 55 is expressed as blade 55 with respect to a gradient perpendicular to the plane of fan rotation axis line (Z axle).
The scan angle theta of each blade 55 is 0.0 °～37.0 ° a part from BH to the neutral position between blade and blade hub BH and blade tip BT of blade and blade hub, at the another part from middle position to blade tip BT is 37.0 °～49.5 °, and is distributed on the blade 55 from blade and blade hub BH to blade tip BT secondary parabola type.
The above-mentioned scan angle theta of each blade 55 is formed in a Y-axis and an angle between a straight line that extends between blade and blade hub BH center and the blade tip BT center, and blade and blade hub BH is centered close on the Y-axis.That is to say that the scan angle theta of each blade 55 is expressed as the inclination angle of blade 55 along the sense of rotation of blade 55.
When axial flow fan of the present invention had this high scan angle theta, high helix angle Ψ and high camber ratio, this fan reduced its operation noise ideally and has the wide width of blade BD that can increase air quantity.In addition, can be desirable and increase the static pressure of the air that flows through fan and guard shield effectively, thereby fan per minute rotating speed that can be lower is realized required fan air amount.
On the other hand, 8.0mm is located to be set in the impeller clearance between the blade 55 1. in the position, 2. locates to be set at 27.0mm in the position, 3. locates to be set at 16.0mm in the position, 4. locates to be set at 27.0mm in the position, as shown in Figure 7.When the set positions of the blade and blade hub BH on each blade 55 is the set positions of zero (0.00) and blade tip BT when being 1.00, the impeller clearance is set at 8.0 ± 1mm basically on the position around the blade and blade hub BH.On the other hand, the secondary parabola type ground, impeller clearance in 0～0.75 primary importance zone is increased to 27.0 ± 1mm from 8.0 ± 1mm.In addition, the secondary parabola type ground, impeller clearance in 0.75～0.97 second place zone is reduced to 16.0 ± 1mm from 27.0 ± 1mm.In comprising 0.97～1.00 the 3rd band of position of blade tip BT, cubic parabola type ground, impeller clearance is increased to 27.0 ± 1mm from 16.0 ± 1mm.
In brief, the impeller clearance of 27.0mm and 16.0mm is positioned at 0.75 and 0.97 position of extended length from blade and blade hub BH to blade tip BT.In this case, the boundary position 0.75 between three zones and the differential derived function at 0.97 place are zero, and the distribution of the impeller clearance in three zones forms secondary or cubic parabola shape distributes.
In the axial flow fan that refrigerator is used according to the preferred embodiment of the invention, the anterior leading edge that the inner diameter, ID that most preferably number of blade 55 is set at 3, the external diameter OD of blade 55 is set at 150mm, blade 55 is set at 35mm, blade 55 is set at 14.2mm apart from the rear portion trailing edge distance R D that FD is set at 43.5mm and blade 55, and makes the rear portion trailing edge distance R D of blade 55 shorter than leaf hub thickness HD.
On the other hand, most preferably the maximum radian position CP with each blade 55 is set at 0.73, and the radian position is evenly distributed on each blade 55 from blade and blade hub BH to blade tip BT.In addition, the maximum camber ratio of each blade 55 most preferably is set at 5.00% at blade and blade hub BH place, is set at 6.30% at blade tip BT place, is implemented in the linear distribution on the blade 55 simultaneously.
The helix angle Ψ of each blade 55 most preferably is set at 44.00 ° at blade and blade hub BH place, is set at 30.00 ° at blade tip BT place, realizes simultaneously from blade and blade hub BH to the linear distribution of blade tip BT on blade 55.
The scan angle theta of each blade 55 is set at 0.0 °～37.0 ° a part from BH to the neutral position (Rt+Rh)/2 between blade and blade hub BH and blade tip BT of blade and blade hub, be set at 37.0 °～49.5 ° at another part, and be distributed on the blade 55 from blade and blade hub BH to blade tip BT secondary parabola type from middle position (Rt+Rh)/2 to blade tip BT.
In addition, 8.0mm is located to be set in the impeller clearance between the blade 55 1. in the position, 2. locates to be set at 27.0mm in the position, 3. locates to be set at 16.0mm in the position, 4. locates to be set at 27.0mm in the position, as shown in Figure 7.
Figure 10 to Figure 13 is the chart that the operation noise of demonstration axial flow fan of the present invention changes along with the different designs parameter of fan.
That is, Figure 10 is the chart that the operation noise of a demonstration axial flow fan changes along with the boss ratio of axial flow fan.This chart shows when the inner diameter, ID (leaf hub diameter) of blade 55 when being set at 0.2～0.25, can realize 22.6 decibels the desirable minimum noise that moves than the boss ratio (ID/OD) of the external diameter OD of blade 55.
Figure 11 is the chart that the operation noise of a demonstration axial flow fan changes along with the maximum radian position CP of fan.This chart shows that working as maximum camber ratio CP is set at 4.8%～5.2% at blade and blade hub BH place, be set at 6.1%～6.5% at blade tip BT place, when realizing from blade and blade hub BH to blade tip BT linear distribution simultaneously on blade 55, can realize 22.4 ± 0.1 decibels desirable minimum operation noise.
Figure 12 is the chart that the operation noise of a demonstration axial flow fan changes along with the helix angle Ψ of each blade 55.This chart shows that the helix angle Ψ when each blade 55 is set at 43.8 °～44.2 ° at blade and blade hub BH place, be set at 29.8 °～30.2 ° at blade tip BT place, when realizing from blade and blade hub BH to blade tip BT on blade 55 linear distribution simultaneously, can realize 22.5 ± 0.1 decibels desirable minimum operation noise.
Figure 13 is the chart that the operation noise of a demonstration axial flow fan changes along with the scan angle theta of each blade 55.This chart shows that the scan angle theta when each blade 55 is set at 0.0 °～37.0 ° a part from BH to the neutral position between blade and blade hub BH and blade tip BT of blade and blade hub, be set at 37.0 °～49.5 ° at another part from middle position to blade tip BT, when realizing simultaneously being distributed on the blade 55, can realize 22.5 ± 0.1 decibels desirable minimum operation noise from blade and blade hub BH to blade tip BT secondary parabola type.
When axial flow fan of the present invention is used for one side by side during the type refrigerator, to compare with refrigerator with existing axial flow fan, the operation noise of refrigerator can be reduced significantly.
As mentioned above, the invention provides the axial flow fan that a kind of refrigerator is used, this axial flow fan is designed to have three blades, 0.21～0.25 boss ratio, big scanning angle, big helix angle and high camber ratio, thereby forms smooth air circulation and make air circulation actively in machine chamber in the refrigerator machine chamber.Axial flow fan of the present invention thereby the smoothness that realizes air flow into and flow out and eliminate in machine chamber the caused operation noise of the air circulation of disturbance and increase the amount that flows into and flow out air.The final realization of this axial flow fan supplies to the air of aequum compressor and condenser and reduces refrigerator operation noise effectively.
Although disclose the preferred embodiments of the present invention for illustrative purposes, those skilled in the art will be appreciated that, under the situation that does not break away from disclosed scope and spirit of the present invention in claims, can carry out different modifications, interpolation and replacement to the present invention.
Claims (4)
1. an axial flow fan comprises a leaf hub that is installed in the rotating shaft, and a plurality of blades are fixed on around the described leaf hub regularly, it is characterized in that:
The number of described blade is three, axial flow fan internal diameter and leaf hub equal diameters, the described external diameter of axial flow fan is 150 ± 1mm, the internal diameter of this fan is 35 ± 1mm, and to make the anterior leading edge distance setting of described blade be 43.5 ± 1mm, and the rear portion trailing edge distance setting of blade is 14.2 ± 1mm.
2. axial flow fan as claimed in claim 1, it is characterized in that: the maximum radian set positions of each blade is 0.7～0.75, and make the radian position be evenly distributed on each blade from the blade and blade hub to blade tip, and the maximum camber ratio of each blade is set at 4.8～5.2% at blade and blade hub place, the place is set at 6.1～6.5% at blade tip, is distributed on the blade linearly to blade tip from the blade and blade hub simultaneously.
3. axial flow fan as claimed in claim 1, it is characterized in that: the helix angle of each blade is set at 43.8 °～44.2 ° at blade and blade hub place, be set at 29.8 °～30.2 ° at the blade tip place, be distributed on the blade linearly to blade tip from the blade and blade hub simultaneously.
4. axial flow fan as claimed in claim 1, it is characterized in that: the scanning angle of each blade is set at 0.0 °～37.0 ° in the part from the blade and blade hub to the neutral position described blade and blade hub and blade tip, be set at 37.0 °～49.5 ° at another part, be distributed on the blade simultaneously secondary parabola type from described neutral position to described blade tip.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB001213490A CN1135306C (en) | 2000-07-21 | 2000-07-21 | Axial-flow fan |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNB001213490A CN1135306C (en) | 2000-07-21 | 2000-07-21 | Axial-flow fan |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1335455A CN1335455A (en) | 2002-02-13 |
| CN1135306C true CN1135306C (en) | 2004-01-21 |
Family
ID=4588746
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB001213490A Expired - Fee Related CN1135306C (en) | 2000-07-21 | 2000-07-21 | Axial-flow fan |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1135306C (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN100360881C (en) * | 2003-04-11 | 2008-01-09 | 乐金电子(天津)电器有限公司 | Air supply device for cold air circulation of refrigerator |
| KR100547328B1 (en) * | 2003-09-05 | 2006-01-26 | 엘지전자 주식회사 | The fan of air-conditioner outdoor unit |
| JP4627409B2 (en) | 2004-04-20 | 2011-02-09 | 日本電産サーボ株式会社 | Axial fan |
| CN101835990B (en) * | 2007-10-25 | 2013-06-19 | Lg电子株式会社 | Fan |
| CN102008872A (en) * | 2010-10-27 | 2011-04-13 | 常熟理工学院 | Fan-shaped helical blade |
-
2000
- 2000-07-21 CN CNB001213490A patent/CN1135306C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| CN1335455A (en) | 2002-02-13 |
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Granted publication date: 20040121 |