FAN WITH INTEGRAL ACOUSTIC TREATMENT

Abstract

A fan comprises a fan housing which includes a shroud having an upstream end that defines an inlet of the fan housing, a motor which is connected to the fan housing, and an impeller which is connected to the motor. The impeller includes an impeller hub and a number of impeller blades which extend radially outwardly from the impeller hub. The shroud includes a cylindrical micro-perforated panel (“MPP”) liner which extends axially from proximate the inlet to proximate the impeller.

Claims

1. A fan which comprises: a fan housing which includes a shroud having an upstream end that defines an inlet of the fan housing; a motor which is connected to the fan housing; and an impeller which is connected to the motor, the impeller including an impeller hub and a number of impeller blades which extend radially outwardly from the impeller hub; wherein the shroud includes a cylindrical micro-perforated panel (“MPP”) liner which extends axially from proximate the inlet to proximate the impeller.

2. The fan of claim 1, wherein the shroud comprises an inner shroud which includes the MPP liner and a tubular outer shroud which is positioned radially outwardly of the inner shroud to thereby define an annular backspace within the fan housing.

3. The fan of claim 2, wherein the MPP liner comprises a first diameter, the outer shroud comprises a second diameter, and the ratio of the second diameter to the first diameter is greater than or equal to about 1.6.

4. The fan of claim 2, further comprising a number of axially extending struts which are positioned between the inner and outer shrouds to thereby divide the annular backspace into a plurality of axially extending compartments.

5. The fan of claim 4, wherein the struts are spaced equally around the inner shroud.

6. The fan of claim 4, further comprising a number of walls which are positioned between the inner and outer shrouds and extend radially between the struts.

7. The fan of claim 6, wherein the struts are spaced equally around the inner shroud and the walls are spaced equally from each other.

8. The fan of claim 2, further comprising a number of radially extending walls which are positioned between the inner and outer shrouds to thereby divide the backspace into a plurality of cylindrical compartments.

9. The fan of claim 6, wherein the walls are spaced equally from each other.

10. The fan of claim 8, further comprising a number of struts which are positioned between the inner and outer shrouds and extend axially between the walls.

11. The fan of claim 10, wherein the walls are spaced equally from each other and the struts are spaced equally around the inner shroud.

12. The fan of claim 2, wherein the outer shroud converges between an upstream end of the outer shroud and a downstream end of the outer shroud.

13. The fan of claim 2, wherein the outer shroud diverges between an upstream end of the outer shroud and a downstream end of the outer shroud.

14. A vane-axial fan which comprises: a fan housing which includes a shroud having an upstream end that defines an inlet of the fan housing, the shroud comprising a cylindrical inner shroud and a tubular outer shroud which is positioned radially outwardly of the inner shroud to thereby define an annular backspace between the inner and outer shrouds; a motor which is connected to the fan housing; and an impeller which is connected to the motor, the impeller including an impeller hub and a number of impeller blades which extend radially outwardly from the impeller hub; wherein at least a portion of the inner shroud is comprised of a cylindrical micro-perforated panel (“MPP”) liner which together with the outer shroud defines at least a portion of the backspace.

15. The fan of claim 14, wherein the MPP liner comprises a first diameter, the outer shroud comprises a second diameter, and the ratio of the second diameter to the first diameter is greater than or equal to about 1.6.

16. The fan of claim 14, further comprising a number of axially extending struts which are positioned between the inner and outer shrouds to thereby divide the annular backspace into a plurality of axially extending compartments.

17. The fan of claim 16, wherein the struts are spaced equally around the inner shroud.

18. The fan of claim 16, further comprising a number of walls which are positioned between the inner and outer shrouds and extend radially between the struts.

19. The fan of claim 18, wherein the struts are spaced equally around the inner shroud and the walls are spaced equally from each other.

20. The fan of claim 14, further comprising a number of radially extending walls which are positioned between the inner and outer shrouds to thereby divide the backspace into a plurality of cylindrical compartments.

21. The fan of claim 20, wherein the walls are spaced equally from each other.

22. The fan of claim 20, further comprising a number of struts which are positioned between the inner and outer shrouds and extend axially between the walls.

23. The fan of claim 22, wherein the walls are spaced equally from each other and the struts are spaced equally around the inner shroud.

24. The fan of claim 14, wherein the outer shroud converges between an upstream end of the outer shroud and a downstream end of the outer shroud.

25. The fan of claim 14, wherein the outer shroud diverges between an upstream end of the outer shroud and a downstream end of the outer shroud.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0019] FIG. 1 is a cross-sectional view of an example of a prior art vane axial cooling fan;

[0020] FIG. 2 is a cross sectional representation of one embodiment of the cooling fan of the present invention;

[0021] FIG. 3 is a front elevation representation of the cooling fan depicted in FIG. 2;

[0022] FIG. 4 is a front elevation representation of a second embodiment of the cooling fan of the present invention;

[0023] FIG. 5 is a cross sectional representation of a third embodiment of the cooling fan of the present invention;

[0024] FIG. 6 is a cross sectional representation of a fourth embodiment of the cooling fan of the present invention;

[0025] FIG. 7 is a cross sectional view of a fifth embodiment of the cooling fan of the present invention;

[0026] FIG. 8 is a front perspective view of the cooling fan shown in FIG. 7;

[0027] FIG. 9 is an exploded perspective view of an embodiment of a shroud component of a fan housing comprising a conical backspace in accordance with the present invention;

[0028] FIGS. 10A-10D are side elevation views illustrating the steps of assembling the fan shroud shown in FIG. 9; and

[0029] FIG. 11 is a graph showing the results of the noise reduction achieved by the fan of FIG. 7.

DETAILED DESCRIPTION OF THE INVENTION

[0030] The present invention is applicable to a variety of air movers. For purposes of brevity, however, it will be described in the context of an exemplary vane-axial cooling fan. Nevertheless, a person of ordinary skill in the art will readily appreciate how the teachings of the present invention can be applied to other types of air movers. Therefore, the following description should not be construed to limit the scope of the present invention in any respect.

[0031] To provide context for the present invention, an exemplary prior art vane-axial cooling fan will first be described with reference to FIG. 1. The prior art cooling fan, which is indicated generally by reference number 10, is shown to comprise a tubular fan housing 12, a motor 14 which is supported in the fan housing 12, an impeller 16 which is driven by the motor 14, and an outlet guide vane assembly 18 which extends radially between the motor 14 and the fan housing 12. The fan housing 12 includes a shroud 20 which surrounds the impeller 16, an inlet opening 22 which is formed at the upstream edge of the shroud, and a diffuser section 24 which is connected to the downstream edge of the shroud proximate the outlet guide vane assembly 18.

[0032] The motor 14 includes a motor housing 26, a stator 28 which is mounted in the motor housing, a rotor 30 which is positioned within the stator and a rotor shaft 32 which is connected to the rotor. The rotor shaft 32 is rotatably supported in a front bearing 34 which is mounted in an upstream end of the motor housing 26 and a rear bearing 36 which is mounted in a tail cone 38 that in turn is mounted to the downstream end of the motor housing. The impeller 16 includes an impeller hub 40 and a number of impeller blades 42 which extend radially outwardly from the impeller hub. The impeller hub 40 may also include a removable nose cone 44 to facilitate mounting the impeller 16 to the rotor shaft 32. The outlet guide vane assembly 18 includes an inner ring 46 which is attached to or formed integrally with the motor housing 28, an outer ring 48 which is connected to or formed integrally with the fan housing 12 and a plurality of guide vanes 50 which extend radially between the inner and outer rings. Thus, in addition to its normal function of straightening the air stream generated by the impeller 16, the outlet guide vane assembly 18 serves to connect the motor 14 to the fan housing 12.

[0033] As discussed above, aerodynamic interactions between the impeller blades and other components of the fan can generate unwanted noise. In accordance with the present invention, acoustic treatments are integrated into the fan in order to reduce the unwanted noise to acceptable levels. These acoustic treatments may be incorporated into such components as the fan housing or the impeller hub.

[0034] Referring to FIGS. 2 and 3, for example, a first embodiment of the present invention is shown schematically to include sound absorbing acoustic treatments which are incorporated into the fan housing. The fan of this embodiment, generally 100, includes an inner shroud 102 having a cylindrical liner 104 which is constructed from a sound absorbing micro-perforated panel (“MPP”). In order to increase the sound absorbing effect of the MPP liner 104, the shroud 102 may also include an annular backspace 106 which is formed by securing a cylindrical outer shroud 108 to the fan housing 12 over the MPP liner 104. In this embodiment, optimal sound absorption is achieved when two geometric characteristics are met; 1) the acoustic impedance of the MPP is matched to the impedance of the sound waves; and 2) the geometry of the backspace is tuned to reduce noise in the intended frequency range.

[0035] For a particular fan application, the desired acoustic impedance of the MPP can be estimated based on the fan acoustic modes which are to be attenuated and the mode propagation angle. The acoustic impedance of an MPP is dependent on the geometry, i.e., the hole or slit dimensions, percent open area, and sheet thickness of the MPP. This value can be estimated for an MPP with circular holes, but needs to be measured for more complicated geometry. In some cases, the impedance values can be obtained from the MPP supplier. The MPP can be made from any number of materials, such as aluminum alloy, and the perforations can be circular holes or slits. The MPP can either be purchased commercially or designed specifically for an intended application. The specific MPP selected for a particular application may be based on the acoustic impedance, manufacturability, cost and availability of the material. Depending on the size and acoustic characteristics of the fan in which the MPP will be employed, commercially available MPP products may be suitable.

[0036] The geometry of the backspace 106 is designed with three factors in mind: [0037] frequency range where noise attenuation is needed; [0038] fan geometry; and [0039] available space.

[0040] The frequency range of noise attenuation is dependent on the geometry of the backspace 106. This frequency range can be easily calculated for a simple constant air gap. However, when the geometry of the backspace is irregularly shaped, the frequency range of noise attenuation is more challenging to estimate. In these circumstances, the frequency range can be determined experimentally or by using boundary element method analysis.

[0041] When the MPP liner 104 is integrated into the inner shroud 102, the fan geometry and available space may lend themselves to design practices for the backspace 104 which are similar to a muffler found on an internal combustion engine. For a small fan, it may be practical to design the backspace 106 to achieve a sufficient expansion ratio for the desired noise reduction. For example, up to 1 dB of noise reduction is possible for an expansion ratio of 1.6 or greater, which is defined as the diameter S.sub.2 of the outer shroud 108 divided by the diameter S.sub.1 of the MPP liner 104.

[0042] In accordance with the present invention, further improvements in noise attenuation may be achieved by compartmentalizing the backspace 106. Without compartments, the MPP liner 104 is most effective for a sound wave front that is normal to the MPP liner. In the fan 100, however, the acoustic waves are multi-directional, with some acoustic modes travelling at an angle or nearly parallel to the MPP liner 104. Compartmentalizing the backspace enhances the acoustic absorption in a multidirectional sound field by forcing the local acoustic velocity to be normal to the MPP liner 104. The compartments are effective in this way when the dimensions are small compared to the wavelength of the frequencies of interest.

[0043] Referring to FIG. 4, for example, a second fan embodiment 200 is shown in which the backspace is divided into a plurality of axially extending compartments 106a by positioning a plurality of equally spaced, axially extending struts 202 between the MPP liner 104 and the outer shroud 108. When the annular backspace is divided in this manner, the compartments 106a will assume a generally trapezoidal shape.

[0044] Referring to FIG. 5, a third fan embodiment 300 is shown in which the backspace is divided into successive cylindrical compartments 106b by positioning a series of equally spaced radially extending walls 302 between the MPP liner 104 and the outer shroud 108. These multiple rows of compartments 106b may be used if space allows, since the increased treatment surface area will improve noise attenuation.

[0045] As an alternative to the fan embodiments shown in FIGS. 4 and 5, the backspace can be divided in to multiple compartments having differing geometries in order to target a number of frequency ranges for noise attenuation.

[0046] Referring to FIG. 6, a fourth fan embodiment 400 is shown in which the outer shroud 108 converges between its upstream and downstream ends to thereby create a backspace 106c having a conical shape. In this regard, it should be noted that conical mufflers are especially effective at reducing tone noise. When tuned to the correct frequency, tones at all harmonic multiples are attenuated with a conical muffler. The high frequencies of interest, thus small wavelengths, in a small high-speed fan make this possible in a smaller space than required for an internal combustion engine muffler. Of course, the shroud 108 could be designed to diverge instead of converge.

[0047] An illustrative embodiment of the invention incorporating the acoustic treatments described above is shown in FIGS. 7 and 8. The fan of this embodiment, generally 500, includes a fan housing 12 which is comprised of an inner shroud 502 and an outer shroud 504. The inner shroud 502 includes a cylindrical MPP liner 506 which extends axially from proximate the inlet opening 22 to proximate the upstream edge of the impeller blades 42. The outer shroud 504 is spaced radially from the inner shroud 502 to thereby define a cylindrical backspace 508 within the fan housing 12. The backspace 508 may extend axially from the upstream end of the housing 12 to proximate the outlet guide vane assembly 18. Also, the backspace 508 may be divided into multiple compartments 508a by a plurality of axially extending struts 510 and/or radially extending walls 512.

[0048] In the specific embodiment of the fan 500 shown in FIGS. 7 and 8, the diameter of the inner shroud 502 is 8.2 inches, the diameter of the outer shroud 504 is 10.0 inches, and the height of the radial backspace 508 is accordingly 0.9 inch. In addition, the backspace 508 is compartmentalized by spaces 508a measuring 2.65 inches by 2.65 inches at the face of the MPP liner 506. The downstream end of the MPP liner 506 is spaced 0.4 inches from the upstream edge of the impeller blades 42, and the axial length of the MPP liner is 5.8 inches. Also, the MPP liner 506 extends around the entire circumference of the inner shroud 502 and therefore comprises a total surface area of 150 inches squared. The backspace geometry was chosen to target noise reduction in a specific frequency range in order to meet maximum noise requirements for a particular fan application. As shown in FIG. 11, the results are significant. Noise reduction of up to 6 dB was achieved at certain frequencies. The largest impact was seen in broadband noise between 2 kHz and 4 kHz.

[0049] Referring now to FIGS. 9 and 10A-10D, an embodiment of a fan shroud is shown which includes some of the acoustic treatments described above. The fan shroud, generally 600, comprises a conical inner shroud 602 and a cylindrical outer shroud 604. The inner shroud comprises an MPP liner 606 which is positioned between an upstream ring 608 and a downstream ring 610 and is held in position by a number of stringers 612 connected between the upstream and downstream rings. In order to assemble the shroud 600, the inner shroud 602 is inserted into the outer shroud 604 until the upstream and downstream rings 608, 610 are sealed against the respective upstream and downstream ends of the outer shroud. The sequence of such assembly is shown in FIGS. 10A-10D. Since the inner shroud 602 is conical and the outer shroud 604 is cylindrical, the backspace defined between the inner and outer shrouds is conical. The shroud 600 may be used in conjunction with a conventional fan to provide the sound reducing advantages of the MPP liner 606 and the conical backspace.

[0050] It should be recognized that, while the present invention has been described in relation to the preferred embodiments thereof, those skilled in the art may develop a wide variation of structural and operational details without departing from the principles of the invention. For example various features of the different embodiments may be combined in a manner not described herein. Therefore, the appended claims are to be construed to cover all equivalents failing within the true scope and spirit of the invention.