Patent Application
20050186070
Fans are used to generate air movement in a wide variety of applications, such as in heating, ventilating, and cooling systems. For example, a variety of axial-type fans (i.e., fans in which fluid is moved in a direction along the axis of rotation of the fan) are used in many industrial applications such as for ventilation purposes in office buildings, greenhouses, barns, factories, and other structures. Axial ventilation fans also have residential uses, such as in kitchens and bathrooms. As previously mentioned, axial fans are also commonly used in heating and cooling systems for heat transfer purposes. For example, axial fans are used for heat transfer purposes in a variety of applications, such as in air conditioning units, refrigeration units, computers, and in cars and other vehicles. In most of these applications, the fan is used to move air across a heat exchanger, wherein heat is transferred to the air as it passes by and/or through the heat exchanger.
Fan efficiency has become increasingly important, regardless of the type or application of the fan. Fan efficiency is typically important because fans are commonly driven by electric motors or other driving devices that consume valuable power. Inefficient fans consume more power, and are therefore less desirable than more efficient fans. Also, inefficient fans tend to require a different rotor geometry than efficient fans in order to meet the ventilation and heat transfer requirements of the systems in which the fans are used. For example, if a certain air flow is necessary for a system, an inefficient fan may have a greater number of blades, a greater diameter, and/or a larger motor than a more efficient fan. Therefore, inefficient fans can cost more than efficient fans in terms of materials and manufacturing expenses, and can occupy valuable system space. As such, fan manufacturers continue to search for ways to increase the efficiency of axial fans.
The marketplace, however, often places contradictory constraints upon fan manufacturers. For example, users of axial fans typically desire a relatively high fan efficiency, but also want fans that are compact and that generate the least noise possible. These constraints are often contradictory because many believe that fans generally need to be larger in order to reduce fan noise and/or airflow. Thus, in some cases, one demand can be met at the expense of another.
Axial fan efficiency is affected by a number of factors. For example, the efficiency of the motor or other device driving an axial fan can be an important factor in the overall efficiency of a axial fan and motor assembly. As another example, the speed of the fan motor and blades can impact fan efficiency. Increased fan motor and blade speed generally increases the amount of air turbulence moving through the fan—a result that is normally detrimental to fan efficiency. Turbulence is also a primary factor influencing the noise level of a fan.
The design and orientation of axial fan blades (e.g., axial fan blade shape, orientation with respect to the rest of the fan, and the like) are also factors in axial fan efficiency. It is generally recognized that certain shapes of fan blades are more efficient than others. For example, a machete or teardrop-shaped blade can often be more efficient that a cloverleaf-shaped blade.
The clearance between the blades of a fan and the fan housing can also impact axial fan efficiency. In many cases, this clearance is the distance between the tips of rotating blades and an adjacent fan housing wall. Blade-to-housing clearance is typically important because it often has a direct bearing upon the static pressure capabilities of the fan. For example, larger clearances between fan blade tips and adjacent housing walls can result in lower static pressure capabilities and lower fan efficiencies.
The design of an axial fan housing also impacts the efficiency of the axial fan. For example, the design of an fan housing air inlet can significantly influence efficiency of the axial fan by impacting the amount of turbulence within the fan. Turbulence within an axial fan can create a phenomenon known as vena contracta, which results in the reduction of the effective cross sectional area of the air inlet. Such a reduction permits less air to move through the air inlet, thereby reducing the efficiency of the axial fan.
Many of the efficiency factors discussed above are taken into account when designing conventional axial fans. However, still other efficiency factors can be important to axial fan performance, some of which are often not considered in conventional axial fan designs. Higher efficiency axial fans would be a welcome addition to the art.
Some embodiments of the present invention provide a fan assembly comprising a motor; a fan rotatably coupled to the motor for rotation about an axis and having a plurality of fan blades each having a leading edge with respect to a rotational direction of the fan blade and a trailing edge with respect to the rotational direction of the fan blade; and a shroud including a plurality of vanes extending transversely with respect to fluid flow through the fan assembly and through which fluid flows through the fan assembly, wherein the vanes are located downstream of the fan and oriented to extend away from a central area of the shroud, wherein each vane has a length defined between a radially inner end of the vane and a radially outer end of the vane, a leading edge, a trailing edge downstream of the leading edge of the vane with respect to fluid flow through the fan assembly, and a rearward swept angle defined between a first straight line extending through the radially inner and outer ends of the vane and a second straight line extending from the axis of the fan to the radially inner end of the vane, wherein the rearward swept angle is no less than about 5 degrees and is no greater than about 45 degrees, wherein each of the vanes is spaced from an adjacent vane by a gap measured from a first point on a first vane to a corresponding point on an adjacent vane, wherein each vane also has a chord length at the first point measured from the vane leading edge to the vane trailing edge, and wherein the fan assembly has a ratio of chord length to vane gap of no less than about 0.2 and no greater than about 3.5.
Also, some embodiments of the present invention provide a fan assembly comprising a motor; a fan rotatably coupled to the motor for rotation about an axis, wherein the fan has a plurality of fan blades each having a leading edge with respect to a rotational direction of the fan blade and a trailing edge with respect to the rotational direction of the fan blade; and a shroud including a plurality of vanes extending transversely with respect to fluid flow through the fan assembly and through which fluid flows through the fan assembly, wherein the vanes are located downstream of the fan and oriented to extend away from a central area of the shroud, wherein each vane has a length defined between a radially inner end of the vane and a radially outer end of the vane, a leading edge, a trailing edge downstream of the leading edge of the vane with respect to fluid flow through the fan assembly, and an inlet angle defined between a straight line tangent to the vane at the leading edge of the vane and a plane orthogonal to the axis of the fan, wherein the straight line lies in a plane tangent to an imaginary cylinder centered at the axis of the fan, wherein the inlet angle is no less than about 20 degrees and is no greater than about 70 degrees, wherein each of the vanes is spaced from an adjacent vane by a gap measured from a first point on a first vane to a corresponding point on an adjacent vane, wherein each vane also has a chord length at the first point measured from the vane leading edge to the vane trailing edge, and wherein the fan assembly has a ratio of chord length to vane gap of no less than about 0.2 and no greater than about 3.5.
In some embodiments, a fan assembly is provided, and comprises a motor; a fan rotatably coupled to the motor for rotation about an axis, wherein the fan has a plurality of fan blades each having a leading edge with respect to a rotational direction of the fan blade and a trailing edge with respect to the rotational direction of the fan blade; and a shroud including a plurality of vanes extending transversely with respect to fluid flow through the fan assembly and through which fluid flows through the fan assembly, wherein the vanes are located downstream of the fan and oriented to extend away from a central area of the shroud, wherein each vane has a length defined between a radially inner end of the vane and a radially outer end of the vane, a leading edge, a trailing edge downstream of the leading edge of the vane with respect to fluid flow through the fan assembly, and an outlet angle defined between a straight line tangent to the vane at the trailing edge of the vane and a line parallel to the axis of the fan, wherein the straight line lies in a plane tangent to an imaginary cylinder centered at the axis of the fan, wherein the outlet angle is no less than about 30 degrees in a direction counter to rotation of the fan and is no greater than about 30 degrees in a rotational direction of the fan; wherein each of the vanes is spaced from an adjacent vane by a gap measured from a first point on a first vane to a corresponding point on an adjacent vane, wherein each vane also has a chord length at the first point measured from the vane leading edge to the vane trailing edge, and wherein the fan assembly has a ratio of chord length to vane gap of no less than about 0.2 and no greater than about 3.5.
Some embodiments of the present invention provide a fan assembly, comprising a motor; a fan rotatably coupled to the motor for rotation about an axis, wherein the fan has a plurality of fan blades each having a leading edge with respect to a rotational direction of the fan blade and a trailing edge with respect to the rotational direction of the fan blade; and a shroud including a plurality of vanes extending transversely with respect to fluid flow through the fan assembly and through which fluid flows through the fan assembly, wherein the vanes are located downstream of the fan and oriented to extend away from a central area of the shroud, wherein each vane has a length defined between a radially inner end of the vane and a radially outer end of the vane, a leading edge, and a trailing edge downstream of the leading edge of the vane with respect to fluid flow through the fan assembly, wherein the shroud is separated from the fan by an axial gap between the leading edges of the vanes and the trailing edges of the fan blades, wherein the gap is no less than about 0.15 inches and no greater than about 1.5 inches, wherein each of the vanes is spaced from an adjacent vane by a gap measured from a first point on a first vane to a corresponding point on an adjacent vane, wherein each vane also having a chord length at the first point measured from the vane leading edge to the vane trailing edge, and wherein the fan assembly also has a ratio of chord length to vane gap of no less than about 0.2 and no greater than about 3.5.
In additional embodiments of the present invention, a fan assembly is provided, and comprises a motor; a fan rotatably coupled to the motor for rotation about an axis, wherein the fan has a plurality of fan blades each having a leading edge with respect to a rotational direction of the fan blade and a trailing edge with respect to the rotational direction of the fan blade; and a shroud including a plurality of vanes extending transversely with respect to fluid flow through the fan assembly and through which fluid flows through the fan assembly, wherein the vanes are located downstream of the fan and oriented to extend away from a central area of the shroud, wherein each vane has a leading edge and a trailing edge downstream of the leading edge with respect to fluid flow through the fan assembly, wherein each of the vanes is spaced from an adjacent vane by a gap measured from a first point on a first vane to a corresponding point on an adjacent vane, wherein each vane also has a chord length at the first point measured from the vane leading edge to the vane trailing edge, and wherein the fan assembly has a ratio of chord length to vane gap of no less than about 0.2 and no greater than about 2.5.
Further objects and advantages of the present invention, together with the organization and operation thereof, will become apparent from the following detailed description of the invention when taken in conjunction with the accompanying drawings, wherein like elements have like numerals throughout the drawings.
The present invention is further described with reference to the accompanying drawings, which show an exemplary embodiment of the present invention. However, it should be noted that the invention as disclosed in the accompanying drawings is illustrated by way of example only. The various elements and combinations of elements described below and illustrated in the drawings can be arranged and organized differently to result in embodiments which are still within the spirit and scope of the present invention.
In the drawings, wherein like reference numeral indicate like parts:
An exemplary embodiment of an axial flow fan assembly 10 according to the present invention is illustrated in
As illustrated in
The fan shroud 14 in the illustrated exemplary embodiment has a set of mounting bosses 15 that can be employed to mount the fan assembly 10 to a frame, housing, or other structure. Any number of mounting bosses having any shape can be employed, such as tab-shaped protrusions extending from the wall 17 of the shroud 14 as shown in the figures, lugs, posts, or fingers extending from the wall 17, a rib or flange extending partially or fully around the wall 17, and the like. Such mounting elements or features can be secured to a frame, housing, or other structure by bolts, screws, nails, rivets, pins, or other conventional fasteners, by clamps, clips, inter-engaging or snap-fit fingers or other features, and the like.
In some embodiments, the same fan assembly 10 can be mounted in different orientations as needed in different applications. For example, it may be desirable to mount the fan assembly 10 in one orientation in order to pull air through a condenser or other device, while in another application is may be desirable to mount the fan in a reversed direction to blow air into a condenser or other device. This mounting versatility is provided in some embodiments by the use of two different shrouds 14, each of which has mounting elements or features (described above) located at different axial positions on the shroud 14. In the illustrated embodiment for example, one shroud 14 has mounting bosses 15 located at a downstream end of the fan assembly 10 (see
In other embodiments, the mounting elements or features of the shroud 14 can be located in any axial position along the shroud 14. By way of example only, mounting bosses 15 can be located at an axial mid-point between the ends of the shroud 14, thereby permitting the fan assembly 10 to be mounted in both orientations described above without the need for two different shrouds and while still keeping a substantial portion of the fan assembly 10 recessed within the structure to which it is mounted in both orientations. Regardless of the axial location of the mounting elements or features employed on the shroud 14, the fan assembly 10 can still be mounted in two opposite orientations (although the ability to recess a majority or the entirety of the fan assembly 10 in both orientations may be limited).
The mounting elements or features 15 of the shroud 14 described above can be integral with the shroud 14. However, in other embodiments these mounting elements or features 15 are attached to the shroud 14 in any suitable manner, such as by a ring (not shown) encircling the shroud 14 and that can be secured with respect to the shroud 14 in a number of different axial positions. As another example, the mounting elements or features 15 can be attached to the shroud 14 at different axial locations by screws, bolts, nails, rivets, pins, or other conventional fasteners, inter-engaging elements, adhesive or cohesive bonding material, and the like.
The size of the fan ring 17 with respect to the fan 50 can have an impact on the efficiency of the fan assembly 10. As will be described in greater detail below, the efficiency of the fan assembly 10 can increase as the spacing between the fan 50 and the fan ring 17 decreases. Thus, in some embodiments of the present invention, the fan ring 17 generally has an inside diameter nearly matching the outside diameter of the fan 50. More specifically, in some embodiments good performance results are achieved by using a fan ring 17 having an inside diameter providing a non-contacting clearance fit with the fan blades 58 or a clearance not exceeding 0.125 inches. A clearance between the fan blades 58 and the fan ring 17 of no greater than 0.08 can provide better performance results. Also, a clearance between the fan blades 58 and the fan ring 17 not exceeding 0.05 inches can provide still better performance results.
As seen in
The shroud 14 in the illustrated exemplary embodiment has a plurality of vanes 18 directly or indirectly attached to the fan cylinder 17 at one end of the fan cylinder 17. Although the vanes 18 can be integral with the fan cylinder 17 as shown in
The vanes 18 of the shroud 14 can be arranged on the shroud 14 in any desired manner. By way of example only, the vanes 18 can be equally spaced from one another, can be arranged in any pattern desired (i.e., repeating or non-repeating pattern), or can be randomly spaced. In the illustrated exemplary embodiment, the vanes 18 extend in a generally radial direction and are also angled with respect to the direction of fan rotation. More specifically, the radially innermost end of each vane 18 illustrated in the figures is located circumferentially ahead of the radially outermost end of the vane 18 (with reference to the direction of rotation of the fan 50). As explained above, the vanes 18 can instead be oriented in an opposite direction, in which case the radially innermost end of each vane 18 is located circumferentially behind the radially outermost end of the vane 18.
If employed, vanes 18 can be located on all or any portion of the shroud 14, including the fan cylinder 17. As shown in the illustrated embodiment, vanes 18 cover the majority of the shroud 14 surface perpendicular to the axis of rotation of the fan 50. However, as illustrated, the vanes 18 extend only partially between the fan cylinder 17 and the center of the fan cylinder 17. In the illustrated embodiment of the present invention, vanes 18 extend across the same general area in front of the fan 50 (downstream of the fan 50) as the fan blades 58. The remainder of the center portion of the shroud 14, as seen in
Regardless of the number and orientation of the vanes 18, the vanes 18 can take any cross-sectional shape desired. For example, each vane 18 can be flat, triangular, U-shaped, can have a generally airfoil shape, can present a concave or convex shape toward or away from the direction of rotation of the blades 58 and/or in either direction along the axis of rotation of the fan 50, and the like. Furthermore, the vanes 18 can be cambered between the vane leading edges 30 and vane trailing edges 34 and/or can be twisted along the length of the vanes (in a clockwise or counterclockwise direction viewed along the length of the blade from tip to root), or the like. As best illustrated in
In some embodiments of the present invention, the orientation of the leading and trailing edges of the vanes can significantly influence the performance of the fan assembly 10. With reference to
Iri some embodiments, this leading edge or “inlet” angle D of the vanes 18 is at least 20° and/or is no greater than 70°. Better performance results can be achieved by employing an angle D that is at least 30° and/or is no greater than 60°. Still better performance can be achieved by employing an angle D that is at least 45° and/or is no greater than 55°. These ranges are generally applicable to fans having a nominal size from about six inches to about eighteen inches, although such vane inlet angles D can be employed in fan assemblies having any diameter. Depending upon other parameters on the fan assembly 10, such as the type and characteristics of the fluid being moved, the normal operational speed (or anticipated ranges of speeds) of the fan assembly 10, and the like, the vane inlet angle D can vary.
In some embodiments of the present invention, the vane inlet angles (or ranges of vane inlet angles) described above are employed alone or in combination with other characteristics of the fan assembly 10 described herein to generate superior fan performance. With continued reference to
In some embodiments, this trailing edge or “outlet” angle E of the vanes 18 is at least −30° and/or is no greater than 30° (wherein a negative angle refers to an angle in a direction opposite the direction of rotation of the fan 50 as viewed in
In some embodiments of the present invention, the vane outlet angles (or ranges of vane outlet angles) described above are employed alone or in combination with other characteristics of the fan assembly 10 described herein to generate superior fan performance.
In some embodiments of the present invention, selected rearwardly-swept angles or ranges of angles of the vanes 18 (when viewed along the axis of rotation of the fan assembly 10) are employed alone or in combination with other characteristics of the fan assembly 10 described herein to generate superior fan performance. A vane 18 is said to be rearwardly-swept when a radially outermost end of the vane 18 is located circumferentially behind a radially innermost end with reference to the direction of rotation of the fan 50. A rearwardly-swept vane 18 can be defined by an angle between a line extending along the leading or trailing edge 34, 30 of the vane 18 and a straight line extending from the axis of rotation of the fan assembly 10 through a radially innermost point on the vane 18. In other embodiments (such as those embodiments in which the vane 18 is not straight along the length of the vane 18), the amount which a vane 18 is rearwardly-swept can be defined by an angle between the chord of the vane 18 (or, if no chord can be readily identified, a straight line extending through the radially innermost and outermost points of the vane 18) and a straight line extending from the axis of rotation of the fan assembly 10 through the radially innermost point of the vane 18. All measurements of the angle defining the rearward sweep of the vane 18 (referenced herein and in the appended claims) are made with reference to a plan view of the fan assembly 10 such as that shown in
In some embodiments of the present invention, this rearward sweep angle of the vanes 18 is no less than 5° and/or is no greater than 45°. However, better performance results can be achieved by employing a rearward sweep angle that is less than 10° and/or is no greater than 35°. Also, a rearward sweep angle that is less than 10° and/or is no greater than 25° can produce still better fan performance. These ranges are generally applicable to fans having a nominal size from about six inches to about eighteen inches. However, these ranges are not limited to fans of such size. Depending upon other parameters on the fan assembly 10, such as the type and characteristics of the fluid being moved, the normal operational speed (or anticipated ranges of speeds) of the fan 50, and the like, this angle can vary.
As illustrated in
The vanes located in various tiers need not necessarily have the same characteristics as vanes located in other tiers. For example, the inner vanes 26 in the illustrated embodiment can have the same or different cross-sectional shapes as the outer vanes 22, and can have any shape described above. By way of example only, the inner vanes 26 in the illustrated embodiment can have a first shape, while the outer vanes 22 can have a second shape different from the first. Additionally, the different tiers of vanes can be oriented in any manner described above. Thus, the inner vanes 26 can have first orientation, while the outer vanes 22 can have a second orientation different than the first.
In some embodiments, the number of vanes in each tier can be the same. However, in other embodiments, the number of vanes in each tier can be different. In some embodiments, the blade-to-vane count is about 10:50 (e.g., in some 11-inch diameter fans according to the present invention). However, regardless of the number of vaned areas or tiers employed (i.e., the number of areas of the shroud 14 having different sets of vanes 18), it is desirable in some embodiments to employ a number of vanes that is not a multiple of the blade count. When the vane count is a multiple of the blade count, harmonics can be more likely to develop, causing pressure problems within the fan 50 and resulting performance reductions of the fan assembly 10. For example, if the fan 50 were to have a blade count of ten blades 58, then in some embodiments none of the vanes areas (if there is more than one) would have a vane count equal to a multiple of ten, such as twenty, thirty, forty, fifty, sixty, etc. In some embodiments, the blade-to-vane count is about 10:65 (e.g., in some 12-inch diameter fans according to the present invention).
In some embodiments of the present invention, superior performance results can be obtained by employing a particular shroud solidity or by employing any shroud solidity within a range of shroud solidities. In such embodiments, selected shroud solidities (or ranges of shroud solidities) are employed alone or in combination with other characteristics of the fan assembly 10 described herein to generate superior fan performance. Shroud solidity is a characteristic of the overall fan assembly 10 that can be selected to change the efficiency of the fan assembly 10. Referring to
With continued reference to the measurement of shroud solidity described above, in some embodiments, the chord length of the vanes 18 is variable along the length of the vane from root to tip. Thus, the chord length of the vanes 18 used to measure shroud solidity is measured at the same location used to measure the gap between adjacent vanes 18 as described above (both measurements being made at the same location anywhere along the length of the vanes 18). In the illustrated embodiment, for example, the gap and chord length measurements of the vanes 18 are taken at the same point: at the midpoint of the outer vanes 22. In other words, the either or both measurements can be taken at a radial mid-point in the outer two-thirds of the fan assembly 10. As discussed above, either or both measurements can be taken elsewhere in other embodiments, such as anywhere along the outer vanes 22 in the illustrated exemplary embodiment, at a location half way between the axis of rotation and the radially outermost ends of the vanes 18, at a location half way between the radially innermost and radially outermost ends of the vanes 18, and the like.
The solidity of the shroud 14 in some embodiments of the present invention is at least 0.2 and/or is no greater than 3.5 (e.g., measured at the vane trailing edges and at a midpoint along the vanes of the shroud, such as at the midpoint of the outer vanes 22 in the illustrated embodiment).
However, a shroud solidity of at least 0.5 and/or no greater than 2.5 can produce better performance results. Also, still better performance results can be achieved by employing a shroud solidity of at least 1.0 and/or no greater than 2.0. These ranges are generally applicable to fans having a nominal size from about six inches to about eighteen inches. However, these ranges are not limited to fans of such size. In still other embodiments of the present invention, the above-described solidity ranges are different, often depending at least in part upon other parameters on the fan assembly 10, such as the number of blades 58 of the fan 50, the distance of the fan 50 from the shroud 14, the normal operational speed (or anticipated ranges of speeds) of the fan 50, and the like.
As shown in the illustrated exemplary embodiment, a motor 42 is used to power the fan assembly 10. The motor 42 of the fan assembly 10 can be any conventional motor 42, such as an AC or DC electric motor (by way of example only, a permanent split capacitor AC induction motor or a brushless DC motor). Some embodiments of the present invention utilize a high efficiency motor 42 to help reduce overall system inefficiencies. In some embodiments such as that shown in the figures, the motor 42 has a motor housing 38 secured to the shroud 14. The motor 42 can instead be attached to the shroud 14 by one or more brackets connected to the motor 42 and shroud 14, by mounting lugs on the motor 42 and/or shroud 14, and the like. In the illustrated exemplary embodiment, the motor housing 38 is attached to the shroud 14 through the use of conventional fasteners, such as screws, nuts and bolts, rivets, pins or other conventional fasteners, by snap fit connections, adhesive or cohesive bonding material, press fits, and the like.
With continued reference to the illustrated embodiment, the motor 42 mounted on the shroud 14 has a drive shaft 46 that extends through the motor housing 38 to drive the fan 50. As shown in
In the illustrated embodiment of the present invention, the hub 54 has a first face 55 that extends in a generally radial direction and which is generally perpendicular to the drive shaft 46. This first face 55 can be circular in shape with the drive shaft coupling to this face substantially at the center of the circle. In other embodiments, the portion to which the drive shaft 46 couples can have any shape desired, including without limitation a first face 55 that is concave or convex in the direction away from the fan assembly 10 (e.g., whether having a rounded profile in either direction, a profile defined by planar surfaces joined at angles with respect to one another, and the like). In other embodiments, the forward end of the hub 54 is pointed or otherwise protrudes along the axis of rotation of the fan assembly 10. Other hub shapes 54 can be employed in still other embodiments of the present invention. With reference back to the illustrated exemplary embodiment, a second face 56 of the illustrated hub 54 extends from the periphery of the first face 55 towards the shroud 17, and can be joined directly to the first face 55 or can be joined thereto by a curved or angled intermediate surface as shown in the figures. In the illustrated embodiment, this second face 56 wraps around and partially encloses a portion of the motor housing 38. As illustrated, the hub 54 in cooperation with the shroud 14 can substantially enclose the motor housing 38. In some embodiments, the motor 42 can be entirely enclosed or encased by the hub 54 and shroud 17 with the exception of a gap sufficient (or only sufficient) to provide rotational clearance between the hub 54 and shroud 14.
The blades 58 of the fan 50 can be attached to or integral with the hub 54 along the second surface 56 as shown in the figures. In other embodiments, the blades extend from other portions of the hub determined at least in part upon the shape of the hub 54 employed. Each blade 58 has a root 62 and a tip 66. The blades 58 are coupled to or are integral with the hub 54 at the root 62, with the remainder of the blade 58 extending at least radially therefrom to the tip 66. The blades 58 can have any shape desired, such as a cloverleaf, machete, or teardrop shape by way of example only. In addition, the shape of the blades 58 can change along their length (from root 62 to tip 66). By way of example only, the shape of each blade 58 illustrated in the figures tapers from root 62 to tip 66. This tapered blade 58 can provide significant performance enhancements to the fan assembly 10 of the present invention. In other embodiments, non-tapered blades 58 can instead be employed.
The blades 58 can have any cross-sectional shape desired, including without limitation rectangular, flat, triangular, irregular, and other cross-sectional shapes. In the illustrated embodiment for example, the fan blades 58 each have a generally airfoil-shaped cross-section as best shown in
Referring to
In some embodiments of the present invention, it is the angle of blade pitch that helps determine the amount of airflow and the pressure differential across the airfoil. In some embodiments, the pitch angle of each blade 58 varies radially. Stated another way, each blade's angle of attack is different at the root 62 than it is at the tip 66. This characteristic can be referred to as blade twist. In some embodiments of the present invention, selected blade twist angles (or ranges of blade twist angles) are employed alone or in combination with other characteristics of the fan assembly 10 described herein to generate superior fan performance.
In some embodiments of the present invention, the fan blades 58 extend radially toward positions immediately adjacent the fan cylinder 17 of the shroud 14, wherein clearance exists (and in some cases, only sufficient clearance exists) for rotation of the fan blades 58 with respect to the shroud 14. The position of the fan blades 58 with regard to the shroud 14 can have an effect on the efficiency and performance of the fan assembly 10. For example, the clearance between the tips 66 of the blades 58 and the inside wall of the fan cylinder 17 as just described can be an important parameter relating to the efficiency and performance of the fan assembly 10. If close tip clearance is not maintained, leakage can occur between the fan blade tips 66 and the shroud 14 because air will take the path of least resistance through the fan assembly 10, thereby generating reduced performance in regard to pressure capabilities and airflow.
In some embodiments of the present invention, another parameter that can influence performance of the fan assembly 10 is the spacing between the vanes 18 on the shroud 14 and the blades 58 of the fan 50. In those embodiments in which the portions of the fan blades 58 and vanes 18 closest to one another are the trailing edges 74 of the fan blades 58 and the leading edges 30 of the vanes 18 (as discussed above), this spacing is measured between the trailing edges 74 of the fan blades 58 and the leading edges 30 of the vanes 18. However, in other embodiments in which the pitch of the fan blades 58 is different and/or in which the orientation of the vanes 18 is different, this spacing is measured between the closest portions of the fan blades 58 and vanes 18. In some embodiments of the present invention, selected vane-to-blade spacings (or ranges of vane-to-shroud spacings) are employed alone or in combination with other characteristics of the fan assembly 10 described herein to generate superior fan performance. With reference to the illustrated exemplary embodiment,
In some embodiments of the present invention, significant performance improvements are achieved over conventional fan assemblies when one or more of the fan assembly characteristics is employed as discussed above. By way of example only, the performance of the illustrated fan assembly 10 having a nominal diameter of twelve inches is illustrated in
The characteristic curve plots in
The embodiments described above and illustrated in the figures are presented by way of example only and are not intended as a limitation upon the concepts and principles of the present invention. As such, it will be appreciated by one having ordinary skill in the art that various changes in the elements and their configuration and arrangement are possible without departing from the spirit and scope of the present invention. For example, one or more of the above mentioned embodiments can be applied to an axial fan individually or in combination to increase the efficiency of the fan as desired.
