HOUSING FOR PADDLE FAN
Air turnover in a space achieved by a paddle fan having a plurality of blades is significantly increased by mounting an assembly radially outward from the blades. The assembly has a generally vertical shroud that is substantially impervious to air flow and a directing grid attached to the shroud at a lower end thereof. The directing grid has a plurality of intersecting members to reduce cross-sectional flow area and induce laminar air flow therethrough.
This application is a non-provisional of U.S. provisional application 60/766,432, filed 19 Jan. 2006, from which a claim of benefit of priority under 35 USC §120 is made and which is incorporated by reference as if fully recited herein.
TECHNICAL FIELDThe present invention, to the extent disclosed in the exemplary embodiments, relates to a housing for paddle fans and paddle fan assemblies incorporating such a housing.
BACKGROUND OF THE INVENTIONCeiling fans are well-known and commonly used in commercial and residential settings to “stir up” the air in a room, especially a room with a high “head space”, that is a large volume of empty space above the first six or seven feet above the floor. This is common in warehouses and other commercial settings and is increasingly common in residential units with vaulted or so-called “cathedral” ceilings.
Ceiling fans as presently known are characterized by several features. They typically have from 4 to 6 blades or paddles, although some may go as low as two blades and others may go as high as 8 blades. The blades or paddles are typically not designed to operate aerodynamically, that is, they would not be classified as propellers. The blades generally are planar or nearly so, although the plane of each blade is usually canted or skewed relative to a plane perpendicular to the axis of rotation. A typical diameter swept out by the blades is in the range of 30 to 60 inches.
Ceiling fans also tend to be powered by relatively small horsepower electric motors, with a rotational velocity of the motor usually being controlled by a rheostat. The motor usually has two to three velocity settings, but none of these speeds is as high as even the lowest speed that one sees in a floor or box fan, as described in more detail below. The rotational velocity and blade structure are designed to minimize noise and thrust force, especially the latter, since the generation of a thrust force would either pull or push upon a ceiling mount. Many of the ceiling fans are bi-directional, that is, the motor may be set to operate in either direction. The angle of the blades or paddles will therefore be able to direct air in either direction along the axis of rotation.
In contrast, floor or box fans are intended to circulate the air in a generally horizontal direction. For safety reasons, and due to the relatively high rotational velocity and proximity to people, floor or box fans are housed in a protective structure, which may or may not possess any capability for directing the exit gas flow.
In the past, ceiling fans have not been very efficient in moving air vertically in an effective manner. By this, we mean that the ceiling fans make little impact on air flow at or near the floor when the paddles are located high enough off the floor to minimize the danger of having them strike occupants in the room.
In U.S. Pat. No. 4,064,427 to Hansen, an annular ring is provided horizontally proximate to the blades of a ceiling fan. The ring is intended to act as a safety guard and an attachment area for light fixtures. Since no affect upon air circulation is described, and because the fan is positioned low enough that there is concern about the blades striking an occupant of the room, it is reasonable to assume that Hansen understood the annular ring as providing no significant result.
In U.S. Pat. No. 4,750,863 to Scoggins, another annular ring structure is placed around a ceiling fan, but the annular structure is described primarily as a base for a filter element to remove particulates from the air. The figures in that patent show the annular ring to be positioned slightly above the top surfaces of the blades. In other words, the ring does not even provide the safety features of Hansen '427. No enhancement of vertical air flow is described or claimed.
U.S. Pat. No. 5,094,676 to Karbacher is similar to the Scoggins '863 patent, but is shows an annular ring for supporting the filter element, but the ring is horizontally proximate to the blades. It claims no enhancement of vertical air flow and there are no features presented that would justify such a claim.
U.S. Pat. No. 6,193,384 to Stein teaches a frustoconical background positioned laterally inwardly from the tips of the modified blades of a ceiling fan. LED elements on the generally vertically extending tips are used to display messages as the blades rotate. The background is not described as providing any air flow enhancement and seems to be useful only in enhancing the visual display.
In U.S. Pat. No. 4,657,485 to Hartwig, an open grill member provides a guard function to the sides of, and below, a set of ceiling fan blades. The open structure would belie any claim of vertical air flow enhancement, although none is made.
Two US patents, utility U.S. Pat. No. 4,515,538 to Shih and design Pat. D484,587 to Bucher, show an annular ring crowned with a grill structure, but both are shown as being intended for use in association with a high-speed aerodynamic fan blade set. Shih '538 shows a front guard structure intended at influencing or directing downward vertical air flow beneath the blades. This front guard is taught as being rotating in the same direction as the fan, but at a much slower speed. Bucher '587 shows a series of concentric bell-shaped structures located below the blade set.
While not strictly confined to a ceiling fan, U.S. Pat. No. 4,730,551 to Peludat shows a high speed fan, similar to a bathroom exhaust fan, which has a circular exhaust port that is surrounded by a square or rectangular inlet area. The Peludat '551 is mounted above a suspended ceiling and teaches that ceiling fans are not capable of directing a vertical column of warm air all the way to the floor of a room, especially a high-ceilinged room.
Accordingly, it is an unmet need of the prior art to provide a ceiling fan system with sufficient vertical air movement to affect an air temperature gradient between the top and bottom of a room in which the fan is located.
SUMMARY OF THE INVENTIONThis and other advantages are achieved, at least in the preferred embodiments, by an assembly for improving the turnover of air in a space by a paddle fan having a plurality of blades extending a first radial distance from a centerline thereof. The assembly comprises a generally vertical shroud, having an internal diameter at least at a top end thereof that is slightly larger than a diameter of the paddle fan. It also comprises a directing grid attached to the shroud at a lower end thereof, the directing grid comprising a plurality of intersecting members to reduce cross-sectional flow area. The assembly is also provided with means for mounting the shroud radially outwardly from the fan blades.
In some embodiments, the shroud is cylindrical, while in other embodiments, the shroud is frustoconical.
In some embodiments the mounting means attaches the shroud to the paddle fan, while in other embodiments, the mounting means attaches the shroud to a ceiling from which the paddle fan is suspended.
In the preferred embodiments, the average airflow velocity at a point between 80 and 100% of the radial distance from the centerline to the blade tip is greater when the paddle fan is operated with the assembly in place relative to identical operation of the paddle fan without the assembly in place.
In the preferred embodiments, a ratio of the average airflow velocity measured at a point between 80 to 100% of the radial distance form the centerline to the blade tip to the average airflow velocity measured at the centerline under the same operating conditions increases by at least a factor of 4.
A better understanding of the invention will be had when reference is made to the appended drawings, wherein identical parts are identified by identical part numbers and wherein:
Referring first to
A housing 30 is positioned around, and laterally adjacent to, the paddles 22 in the exemplary embodiment. This housing 30 is characterized by a shroud 32. As illustrated, the shroud 32 is provided in two semi-circular pieces that may be fastened together in the field to encompass an existing paddle fan 20. In most embodiments of the invention, the shroud 32 is cylindrical, with an upper end 34 having the same diameter than a lower end 36. In some instances, though, the upper end 34 can have a diameter X1 and the lower end has a diameter X2. If the upper and lower ends are vertically separated by a height Y, then the shroud 32 can be described as having a cone angle A, where A=sin(2Y/(X1−X2)). The shroud 32 will be designed for use with a paddle fan 20 having a blade diameter X3 such that X1 is greater than X3. In some situations, X3 will be between X1 and X2, but in other situations, X3 may be smaller than X2. If X3 is greater than X2, then the shroud needs to be mounted so that a diameter XF of the shroud, measured at the horizontal level of the paddles 22 is at least as large as X3. In other words, the paddles 22 fit inside the shroud 32 so that they may freely rotate without striking the shroud.
Shroud 32 is constructed from a continuous sheet of material that has no substantial penetrations that would permit air flow through the sheet, either from within or from without. A sheet of a metal, especially galvanized steel or aluminum, would be useful in this application, although a polymeric material may also suffice, provided that it gives the necessary mechanical strength to support the weight of other parts of the assembly.
A further parameter that may be important in designing or selecting a housing for a particular paddle fan 20 is the vertical spacing of the paddles 22 from the ceiling surface, or, perhaps more importantly, the vertical spacing of the upper end 34 of shroud 32 from the ceiling. This is because the product of the circumference of the upper end 34 and the vertical spacing of the upper end from the ceiling defines an effective collection area through which air expelled out of the lower end 36 of the shroud must pass.
As shown in
A further feature of the disclosed embodiment is disclosed in
As best seen in the side sectional views of
While it is recognized that many paddle fans 20 will possess bi-directional capability, as described above, this feature may not be necessary. The primary object of the housing embodiment disclosed herein is to enhance vertical downflow of air directly under the paddles, rather than enhancing vertical upflow of air onto the ceiling above the paddles, so the paddle fan 20 preferably can provide such downflow.
Since an objective of the disclosed embodiment is to provide increased turnover of room air, particularly in enclosed spaces with high overhead volume, a commercial testing laboratory was engaged to confirm the efficiency of the paddle fan assembly 10 described above. Two different tests were performed.
In a first test, a series of paddle fans were tested to determine the effect of the paddle fan assembly 10 on a series of fans, operating with and without the assembly 10.
Test 1AA paddle fan, manufactured by Dayton Electric Manufacturing Company of Niles, IL, was mounted from a ceiling. The paddle fan, Model 4C852B, has a 36 inch blade diameter, comprising 3 blades, and is rated by the manufacturer as operating at an airflow rating of 12,500 cubic feet per minute (“CFM”) and a blade speed, as stated by the manufacturer, in the range of 370-395 revolutions per minute (“rpm”). The motor was rotated in a direction to cause downward airflow. Measurements of the average air velocity were taken below the fan, starting at the axial centerline and moving radially outwardly, while the fan was in stable operation. The shroud was effectively cylindrical with an internal diameter about two inches larger than the blade diameter. The discharge diameter to the adaptor was 35.75 inches. The directing grid at the lower end of the assembly, with the fan blades positioned close to the top of the directing grid, had 0.5 inch square grid openings. Data were collected with and without the assembly in place, as follows:
These data are shown graphically at
The same test as in Test 1A was performed, with a Dayton Model 4C853B paddle fan used instead of the prior fan. The fan has a 48 inch blade diameter, comprising 3 blades, and is rated by the manufacturer as operating at an airflow rating of 21,000 cubic feet per minute (“CFM”) and a blade speed, as stated by the manufacturer, in the range of 285-315 revolutions per minute (“rpm”). Measurements were taken as in the prior test. A larger shroud was substituted, to provide an internal diameter about two inches larger than the blade diameter. The discharge diameter to the adaptor was 46.75 inches. The directing grid at the lower end of the assembly, with the fan blades positioned close to the top of the directing grid, had 0.5625 inch square grid openings. Data were collected with and without the assembly in place, as follows:
These data are shown graphically at
The same test as above was performed, with a Dayton Model 4C854B paddle fan used instead of the prior fan. The fan has a 56 inch blade diameter, comprising 3 blades, and is rated by the manufacturer as operating at an airflow rating of 27,500 cubic feet per minute (“CFM”) and a blade speed, as stated by the manufacturer, in the range of 245-265 revolutions per minute (“rpm”). Measurements were taken as in the prior test. A larger shroud was substituted, to provide an internal diameter about two inches larger than the blade diameter. The discharge diameter to the adaptor was 53 inches. The directing grid at the lower end of the assembly, with the fan blades positioned close to the top of the directing grid, had 0.625 inch square grid openings. Data were collected with and without the assembly in place, as follows:
These data are shown graphically at
The same test as above was performed, with a Dayton Model 4C721B paddle fan used instead of the prior fan. The fan has a 60 inch blade diameter, comprising 3 blades, and is rated by the manufacturer as operating at an airflow rating of 46,000 cubic feet per minute (“CFM”). The manufacturer's stated blade speed is not known. Measurements were taken as in the prior test. A larger shroud was substituted, to provide an internal diameter about two inches larger than the blade diameter. The discharge diameter to the adaptor was 58.5 inches. The directing grid at the lower end of the assembly, with the fan blades positioned close to the top of the directing grid, had 0.625 inch square grid openings. Data were collected with and without the assembly in place, as follows:
These data are shown graphically at
These data show that the placement of the assembly around the paddle fan moves the maximum average airflow velocity radially outwardly from where the maximum velocity occurs without the assembly. It is believed that a further effect is a more laminar flow of air in the column of air pushed downwardly.
A first alternate view of these data is presented in
A second alternate view of these data is shown in
The same independent commercial testing laboratory that conducted the tests reported above as Test 1 performed a second test to verify that the air turnover in a room is increased by the presence of the assembly as described above. The test was conducted using the 36 inch diameter fan of Test 1, both with and without the assembly. The fan was mounted 16 feet above the floor in a room having 80 feet of clear lateral space from the projection of the fan centerline on to the floor. Temperatures were measured at the floor level. Temperature levels were measured at 2 foot intervals from the fan centerline projection onto the floor in a room that was allowed to stratify to develop a natural convective air turnover. Once the fan was turned on, temperature measurements were made to determine the effective radial distance the air was moved. Some definitions are in order here. “Delta Temperature” refers to difference between the measured temperature and the ambient temperature. “Effective Range” is the distance across the floor from the fan centerline at which the Delta Temperature drops to zero. “Stable Air Flow” is established when the measured temperature first levels off from the initial temperature drop. The “Stabilized Temperature Range” is the distance between which Stable Air Flow is established and the Effective Range.
Working in this system, the fan operating without the assembly was observed to have an Effective Range of 22 feet from centerline, but when operating with the assembly, the Effective Range increased to 40 feet. The increase in floor area coverage by the fan with the assembly is therefore the ratio of the squares of the Effective Ranges, that is, 402/222, or 3.31. In economic terms, this means that a fan operating with the assembly of this embodiment greatly increases the air turnover in a room that would be provided by the same fan in the same room without the assembly installed. This increase in turnover is achieved without increasing the power consumption of the fan, so any energy savings in heating or cooling realized by the additional turnover are achieved at a constant cost. It is noted that the 36 inch fan, as demonstrated above, while marginally better with the assembly than without it, triples the floor coverage. The data show that the 36 inch diameter fan with the assembly operates similarly to a 60 inch diameter fan without the assembly, as shown in
While the foregoing examples describe the use of the assembly in conjunction with a paddle fan that is suspended from a ceiling, the beneficial effects of increased air turnover described in the foregoing are not expected to be limited to situations where a ceiling is present. Accordingly, it is expected that a paddle fan used on a patio or similar open space, or even under a portable covering such as a tent, will have its performance increased substantially by the use of an embodiment of the assembly. It is known that increasing air turnover in such a space deters insects such as mosquitoes from landing on and biting humans.
The inventor believes that the object of the invention is to maximize the vertical distance of the room through which the air is effectively turned over. Since any vertical downflow will be balanced out by a corresponding upflow, it is believed that the primary objects are best achieved by using the paddle fan 20 in a downflow mode with the disclosed embodiment.
Claims
1. An assembly for improving the turnover of air in a space by a paddle fan having a plurality of blades extending a first radial distance from a centerline thereof, comprising:
- a generally vertical shroud, having an internal diameter at least at a top end thereof that is slightly larger than a diameter of the paddle fan;
- a directing grid attached to the shroud at a lower end thereof, the directing grid comprising a plurality of intersecting members to reduce cross-sectional flow area; and
- means for mounting the shroud radially outwardly from the fan blades.
2. The assembly of claim 1, wherein:
- the shroud is cylindrical.
3. The assembly of claim 1, wherein:
- the shroud is frustoconical.
4. The assembly of claim 2, wherein:
- the mounting means attaches the shroud to the paddle fan.
5. The assembly of claim 2, wherein:
- the mounting means attaches the shroud to a ceiling from which the paddle fan is suspended.
6. The assembly of claim 1, wherein:
- the average airflow velocity at a point between 80 and 100% of the radial distance from the centerline to the blade tip is greater when the paddle fan is operated with the assembly in place relative to identical operation of the paddle fan without the assembly in place.
7. The assembly of claim 1, wherein:
- a ratio of the average airflow velocity measured at a point between 80 to 100% of the radial distance form the centerline to the blade tip to the average airflow velocity measured at the centerline under the same operating conditions increases by at least a factor of 4.
8. The assembly of claim 1, wherein:
- the internal diameter of the shroud is at least about 30 inches.
9. The assembly of claim 3, wherein:
- the mounting means attaches the shroud to the paddle fan.
10. The assembly of claim 3, wherein:
- the mounting means attaches the shroud to a ceiling from which the paddle fan is suspended.
Type: Application
Filed: Jan 19, 2007
Publication Date: Jun 10, 2010
Inventor: Tony R. Anchors (Columbus, OH)
Application Number: 12/161,074
International Classification: F01D 25/28 (20060101);