HK1078231B - Porting - Google Patents

Description

Air inlet and outlet

Technical Field

The present invention relates to air intake and exhaust ports and heat removal in acoustic devices, and more particularly to heat removal from an open acoustic enclosure.

Background

Referring to fig. 1, a cross-section of a prior art loudspeaker is shown. The speaker 110 includes a housing 112 and an acoustic driver 114. Within the housing 110 are two air ports 116 and 118, positioned one 118 above the other. The gas ports 116 and 118 are flared. The upper gas port 118 is flared inwardly, i.e., the cross-sectional area of the inner end 118i is greater than the cross-sectional area of the outer end 118 e. The lower port is flared outwardly, i.e., the outer end 116e has a larger cross-sectional area than the inner end 116 i.

Disclosure of Invention

It is an important object of the present invention to provide an improved arrangement for the intake and exhaust ports. Another object is to remove unwanted heat from the acoustic device.

According to one aspect of the invention, an electro-acoustic device comprises: a speaker housing including a first acoustic port, an acoustic driver mounted to the speaker housing, and a heat generating device. The acoustic driver and the acoustic port are constructed and arranged to cooperate to provide a cooled, substantially co-directional flow of air through the heat-generating device, thereby transferring heat from the heat-generating device.

In another aspect of the invention, an electro-acoustic device comprises: an acoustic enclosure, a first acoustic port in the acoustic enclosure, and an acoustic driver mounted in the acoustic enclosure for inducing a first airflow in the port. The first gas stream flows alternately inwardly and outwardly within the gas port. The device also includes a heat generating device. The acoustic port is constructed and arranged to cause the first air flow to produce a second air flow in substantially the same direction. The device also includes structure for causing the same direction airflow to flow through the heat generating device.

In another aspect of the invention, a speaker enclosure having an interior and an exterior includes a first end with a cross-sectional area and a second end with a cross-sectional area, wherein the first end cross-sectional area is greater than the second end cross-sectional area. The first end is adjacent to the inner portion and the second end is adjacent to the outer portion. The housing also includes a second air port. The first air port is typically located below the second air port.

In another aspect of the invention, a speaker includes an electroacoustic transducer and a speaker housing. The speaker enclosure has a first port having an interior end and an exterior end, each end having a cross-sectional area. The outer end cross-sectional area is greater than the inner end cross-sectional area. The device also includes a second port having an inner end and an outer end. The first port is typically located above the second port.

In another aspect of the invention, a speaker enclosure includes a first air port having an interior end and an exterior end, each end having a cross-sectional area. The cross-sectional area of the inner end of the first air port is smaller than the cross-sectional area of the outer end of the first air port. The enclosure also includes a second port having an interior end and an exterior end, each end having a cross-sectional area. The second port inner end cross-sectional area is greater than the second port outer end cross-sectional area.

In another aspect of the invention, an electro-acoustic device for operating in an ambient environment includes an acoustic enclosure including a port having an outlet for radiating pressure waves; an electroacoustic transducer located within the acoustic enclosure for oscillating to generate pressure waves; a second housing having a first opening and a second opening; wherein the gas port outlet is located proximate the first opening such that pressure waves are injected through the first opening into the second enclosure; a mounting location for a heat generating device within the first opening is positioned such that airflow from the ambient environment into the opening flows through the mounting location.

In another aspect of the invention, an electro-acoustic device includes a first housing having a port with an end point for outward flow of air out of the housing to the ambient environment and inward flow of air into the housing. The apparatus also includes an electroacoustic transducer including a vibratable surface for generating pressure waves resulting in inward and outward airflow. The device also includes a second housing having a first opening and a second opening. The gas port end point is located adjacent the first opening and oriented such that the gas port end flows outwardly toward the second opening. The air port and the electroacoustic transducer cooperate to generate a substantially co-directional air flow into the first opening.

In another aspect of the invention, an electro-acoustic device for operating in an ambient environment includes an acoustic enclosure. The enclosure includes a gas port having an outlet for radiating pressure waves. The electro-acoustic device further includes an electro-acoustic transducer positioned within the acoustic enclosure to provide pressure waves. The device also includes an elongated second housing having a first extreme and a second extreme in an elongated direction. There is a first gas port at the first extreme and a second gas port at the second extreme. The vent outlet is located in the first opening such that pressure waves are injected into the second enclosure through the first vent opening toward the second opening. The device also includes a mounting location for a heat generating device within the elongated second housing positioned such that airflow from the ambient into the opening flows through the mounting location.

In yet another aspect of the invention, an electro-acoustic device includes a first housing having a port with an end point for outward flow of air out of the housing and inward flow of air into the housing. The apparatus also includes an electroacoustic transducer including a vibratable surface mounted within the first housing for generating pressure waves causing the inward and outward airflows. The device also includes a second housing having a first opening and a second opening. The port end point is located within the second housing and oriented such that the port end flows outwardly toward the second opening. The air port and the electroacoustic transducer cooperate to generate a substantially co-directional air flow into the first opening.

According to one aspect of the invention, a speaker enclosure having a speaker driver and a vent tube formed with an aperture intermediate its ends is constructed and arranged to introduce a leakage impedance into the vent tube to reduce the Q of at least one standing wave excited in the vent tube as acoustic energy passes therethrough. Hole venting may occur to the acoustic enclosure, to the enclosure exterior space, to a different portion of the port tube, to a small volume, to a closed end resonator tube, or other suitable volume.

Drawings

Other features, objects, and advantages will be apparent from the following detailed description taken in conjunction with the accompanying drawings.

Fig. 1 is a diagrammatic view of a prior art device.

Fig. 2 is a diagrammatic view of a device according to the invention.

Fig. 3A and 3B are views of the device of fig. 2, illustrating the operation of the device.

FIGS. 4A-4I are diagrammatic views of an embodiment of the present invention.

Fig. 5 is a partial enlargement of a loudspeaker employing the present invention.

Fig. 6A and 6B are a diagram and a cross-section taken along line B-B, respectively, of another embodiment of the present invention.

Fig. 7 is a diagrammatic view of an implementation of the embodiment of fig. 6A and 6B.

Figure 8 is a diagrammatic representation of a loudspeaker enclosure having an apertured air port tube in accordance with the present invention.

Figure 9 shows a form of the invention having a port tube opening in the exterior of the housing.

Figure 10 shows a form of the invention having a port tube with an opening at another location of the port tube.

Figure 11 shows a form of the invention with a stomal tube that opens into a small volume.

Figures 12 and 13 show a version of the invention having a gas port tube with an opening in the closed end resonator tube.

FIG. 14 shows the standing wave pattern within the gas port tube.

Figure 15 shows a version of the invention of a bore asymmetrically positioned and filled with closed end tubes of different lengths.

Detailed Description

Referring to the drawings and in particular to fig. 1, there is shown a cross-section of a prior art loudspeaker. The speaker 110 includes a housing 112 and an acoustic driver 114. Within the housing 110 are two air ports 116 and 118, positioned one 118 above the other. The gas ports 116 and 118 are flared. The upper gas port 118 is flared inwardly, i.e., the cross-sectional area of the inner end 118i is greater than the cross-sectional area of the outer end 118 e. The lower port is flared outwardly, i.e., the outer end 116e has a larger cross-sectional area than the inner end 116 i.

Referring to fig. 2, there is shown a cross-sectional view of a loudspeaker according to the invention. The loudspeaker 10 comprises a housing 12 and an acoustic driver 14 having a motor structure 15. Within the housing are two air ports 16 and 18 positioned such that one air port 16 is at a lower level within the housing 12 than the other air port 18. The lower port 16 is flared inwardly, i.e., the inner end 16i has a larger cross-sectional area than the outer end 16 e. The upper port 18 is flared outwardly, i.e., the outer end 18e has a larger cross-sectional area than the inner end 18 i. The flares of ports 16 and 18 are exaggerated for purposes of illustration and explanation. Exemplary port physical dimensions are shown below. Within the housing is a heating element. The heat generating element may comprise the motor structure 15 of the acoustic driver, or alternatively a heat generating means 20, such as a power supply or amplifier for the loudspeaker 10, another loudspeaker not shown, or both. For better results, the optional heat generating device 20 may be positioned lower than the upper air port 18. For better effectiveness, the motor structure 15 is arranged lower than the upper air port 18, which is advantageous for removing heat from the motor structure 15.

In operation, a surface, such as the cone 13 of the acoustic driver 14, is driven by the motor structure 15 such that the cone 13 vibrates in the direction indicated by arrow 17, radiating sound waves to the exterior 24 of the housing and the interior 22 of the housing. Upon driving the acoustic driver cone, the motor structure 15 generates heat that is introduced into the housing interior 22. The sound waves radiated into the housing interior 22 cause the sound waves to radiate out through the ports 16 and 18. In addition to the sound waves radiated out through the ports, there is a DC flow indicated by arrow 26. This DC gas flow will be described in detail below. The DC airflow transfers heat from the motor structure 15 and optional heat generating components 20 out of the housing through the upper air port 18, thereby cooling the motor structure 15 and optional heat generating components 20.

Referring to fig. 3A and 3B, the speaker of fig. 2 is shown to explain the DC airflow of fig. 2. When the loudspeaker 10 is in operation, the air pressure Pi inside the housing alternately increases and decreases with respect to the air pressure Po outside the housing. When pressure Pi is greater than pressure Po, the pressure differential causes air to flow from the interior 22 to the exterior 24 of the enclosure, as shown in fig. 3A. When the pressure Pi is less than the pressure Po, the pressure difference causes air to flow from the exterior 24 to the interior 22, as shown in fig. 3B. For a given pressure value across the port, more air flows if the high pressure end is the small end than if the high pressure end is the large end. When the gas flow is from the inside to the outside, as shown in FIG. 3A, more gas flow passes from the outwardly flaring ports 18 than from the inwardly flaring ports 16, and the net DC gas flow 31 and the convective gas flow 32 flowing toward the outwardly flaring ports 18 are in the same direction. When the gas flow is from the outside to the inside, as shown in FIG. 3B, more gas flow passes from the inwardly flaring ports 16 than from the outwardly flaring ports 18, and the net DC gas flow 31 flows away from the inwardly flaring ports 16 toward the outwardly flaring ports 18. Regardless of whether Pi pressure is less than or greater than pressure Po, there is a net DC flow in the same direction. Thus, when the internal pressure Pi is above or below Po, in normal operation of the loudspeaker 10, a DC airflow flows in the same direction as the convective DC airflow 32, and this DC airflow serves to transfer heat from the interior of the enclosure 24 to the ambient environment.

The speaker according to the present invention has an advantage in that it has port-induced airflow in the same flow direction as the convection airflow, improving cooling efficiency.

The experimental results indicate that the experimental heat rise established using the configuration of fig. 1 is reduced by approximately 20% compared to the heat rise without signal transmission to the acoustic driver 114. Using the configuration of fig. 2, the heat rise is reduced by approximately 75% compared to the heat rise of no signal delivered to the acoustic driver 114.

Referring to fig. 4A-4I, several embodiments of the present invention are shown. In FIG. 4A, the lower port 16 is a straight-walled port and the upper port 18 is flared inwardly. In FIG. 4B, the upper port 18 is a straight-walled port and the lower port 16 is flared inwardly. The airflow for the embodiment of fig. 4A and 4B is similar to that for the embodiment of fig. 2 and 3, but airflow is not shown. In FIG. 4C, it is shown that vents 16 and 18 can be on different sides of housing 12; if the housing has curved sides, ports 16 and 18 may be at any point of the curve. Fig. 4D is a front view showing that the acoustic driver 14 and the two ports 16 and 18 may not be collinear. The location and alternate location of acoustic driver 14 shown in phantom, and the location and alternate location of ports 16 and 18 shown in phantom, indicate that acoustic driver 14 need not be equidistant from ports 16 and 18, and that the acoustic driver need not be vertically centered between ports 16 and 18. In the embodiment of FIG. 4E, the outwardly flaring upper air ports 18 are in the upper surface, facing upward, and the inwardly flaring lower air ports 16 are in the lower surface. If the air vent 16 is in the lower surface, as shown in FIG. 4E, the enclosure typically has legs or some other spacing structure to space the air vent 16 from the surface 28 on which the speaker 10 is placed. FIG. 4F shows that the port walls need not deviate linearly, and the cross-section of the walls need not be straight. The embodiment of FIG. 4G shows that the deviation need not be monotonic, but may flare both inward and outward, as long as the cross-sectional area of the outer end 18e of the upper port 18 is greater than the cross-sectional area of the inner end 18i, or as long as the cross-sectional area of the outer end 16e of the lower port 16 is less than the cross-sectional area of the inner end 16i, or both. A two-way flared port may have acoustic advantages over a straight-walled port or a port that is monotonically flared. In fig. 4H and 4I, the invention is used in loudspeakers with more complex port and chamber structures, and acoustic drivers that do not radiate directly to the outside. The third port 117 of fig. 5 is for acoustic purposes. Operation of the embodiment of fig. 4H and 4I causes the internal pressure Pi to circulate above or below the external pressure Po, resulting in a net DC airflow as in other embodiments, even if the acoustic driver 14 does not radiate acoustic waves directly outside the enclosure. Aspects of the embodiments of fig. 4A-4I may be combined. Fig. 4A-4I depict some of the various ways in which the invention may be practiced and do not show all possible embodiments of the invention. In all of the embodiments of FIGS. 4A-4I, there is an upper port and a lower port, either the upper port has a net outward flare, or the lower port has a net inward flare, or both.

Referring to fig. 5, there is shown a partial perspective view of a loudspeaker employing the present invention. The cover 30 of the element is removed to show the internal details of the speaker. The embodiment of fig. 5 is of the form of fig. 4I. Reference numerals designate elements of fig. 5 that correspond to like-numbered elements of fig. 4I. The acoustic driver 14 (not shown in this figure) is mounted within the cavity 32. The ports 19 help reduce standing waves in the port tube as follows. Variation in the cross-sectional area of ports 16 and 18 is achieved by varying the dimensions in the x, y and z directions. Appendix 1 shows exemplary dimensions of the two air ports 16 and 18 of the loudspeaker of fig. 5.

Referring to fig. 6A and 6B, two schematic views of another embodiment of the present invention are shown. In fig. 6A ported speaker 10 has a port 40 with a port exit 35 in the airflow channel 38. In one configuration, both the air port 40 and the air flow passage 38 are tubular structures, one dimension being relatively long compared to the other, and open at both longitudinal ends; the cross-sectional area As of port outlet 35 is less than the cross-sectional area A of flow passage 38; the port outlets 35 are located in the gas flow path such that the longitudinal axes are parallel or coincident. The following considers the size and placement of the ports 40, port outlets 35, and airflow channels 38. The heat generating device 20 or 20' is shown in two positions within the airflow passage 38. In actual practice, the heat generating device or devices may be placed in many other locations within the airflow passageway 38.

When the acoustic driver 14 is operating, it causes airflow into and out of the air port 40. When the airflow introduced by operation of the acoustic driver exits the air outlet 40 in direction 36, as shown in FIG. 6A, the air outlet and air flow channel act as a jet pump which causes the airflow in the air flow channel 38 to exit the air flow channel air outlet 44 through the air flow channel in direction 45, which is the same direction as the airflow exiting the air outlet, in this case air flow channel air outlet 42. Jet pumps are generally described in documents such as the following website:

http：//www.mas.ncl.ac.uk/～sbrooks/book/nish.mit.edu/2006/Textbook/Node s/chap05/node16.html

a print thereof is attached to appendix 2 hereinafter.

Referring to fig. 6B, when the acoustic driver introduces air into air port 40 in direction 37, there is no jet pump effect. The flow of air into port 40 enters port 40 in all directions, including inwardly through flow channel port 42. Because the airflow is from all directions, there is little net airflow in the airflow path.

To summarize, when the acoustic driver introduces a flow in direction 36, a jet pump effect is created that causes a flow to enter the flow channel port 42 and exit the channel port 44. When the acoustic driver introduces airflow in direction 37, there is little jet pumping effect in airflow channel 38. The net effect of the operation of the acoustic driver is a net DC airflow in direction 45. This net DC airflow can be used to transfer heat from heat-generating components, such as devices 20 and 20' placed in the airflow path.

Several considerations are needed to determine the size, shape and positioning of the air ports 40 and air flow passages 38. The combined acoustic effects of port 40 and flow channel 38 are preferably consistent with the desired acoustic properties. It is desirable to arrange the port 40 to have desired acoustic properties and to arrange the passage 38 to have very little acoustic effect, while maintaining the airflow momentum in the desired direction 45 and preventing the momentum in a direction transverse to the desired direction. In this regard, the ports 40 may be relatively elongated and the linear axis of elongation parallel to the direction of the desired impulse. It is desirable that the configuration of the airflow passages 38 increase the proportion of laminar flow in the airflow portion and reduce the proportion of turbulent airflow to provide the desired amount of airflow.

Referring to fig. 7, there is shown a mechanical schematic of a practical experimental implementation of the embodiment of fig. 6A, 6B, the numbered elements being similar to the corresponding elements of fig. 6A and 6B. In the test implementation, the airflow channel 38 and the heat generating device were two elements of a unitary structure. A damper is arranged in thermal contact with a heat sink (heat sink) of tubular form of appropriate size so that it can act as an air flow channel 38. In the case of airflow through the damper and the acoustic driver 14 is not operating, the temperature near the heat absorber rises by 47 ℃. With the acoustic driver operating at 1/8, the temperature near the heat sink rises by 39 ℃. With the acoustic driver operating at 1/3 power and radiating pink noise (pink noise), the temperature near the heat absorber rises by 25 ℃. In addition, the thermal effect of the device at other points within the loudspeaker enclosure was measured. For example, in region 55, convection heating causes a temperature rise of 30.5 ℃, when airflow passes through the damper and the acoustic driver 14 is not operating. When the acoustic driver is operated at 1/3, the temperature near the heat sink rises by 30.5 ℃. With the acoustic driver operating at 1/8 power and radiating pink noise, the temperature near the heat absorber rose by 30.5 ℃. With the acoustic driver operating at 1/3 power and radiating pink noise, the temperature near the heat absorber rises by 21 ℃. This means that if the acoustic driver is operating at a sufficiently high power and thus moves more air than when it is operating at a lower power, the air flow generated from the loudspeaker according to the invention transfers heat from the vicinity of the air flow, rather than directly within the air flow.

Referring to fig. 8, a diagrammatic illustration of a speaker enclosure 61 is shown, the speaker enclosure 61 having a driver 62 and a vent tube 63, with an aperture 64 formed generally at a point along the length of the vent tube 63 corresponding to the pressure maximum of the dominant standing wave established within the vent tube 63 when the driver 62 is excited to reduce audible vent noise. A sound dampening material 90, such as polyester or cloth, may be located in or near the aperture 64.

This aspect of the invention reduces the deleterious effects of port noise caused by self-resonance. Consider, for example, the case of increased noise at a frequency of one-half wavelength equal to the port length. In the self-resonant example, the standing wave in the gas port produces the highest pressure halfway between the ends of gas port 63. By using a small amount of damping leakage (resistive leak) established near this point in the tube bore 64, the Q of the resonance is greatly reduced to greatly reduce the harmfulness of port noise at this frequency. The sound damping material 90 may further reduce the Q value of the high frequency resonance.

As shown in fig. 8, the leakage may pass through the holes 64 into the acoustic enclosure. Alternatively, as shown in FIG. 9, the leakage may be through the airThe hole 64 'of the mouth tube 63' leaks into the space outside the housing 61. As shown in FIG. 10, the air port tube 63 "may leak through the holes 64" into different portions of the air port tube 63 ". As shown in FIG. 11, the port tube 63Can pass through the hole 64Leaking into the small volume 65. As shown in fig. 12, the air port tube 63 "" may leak through the hole 64 "" into the closed end resonator tube 65'. In the embodiment of fig. 9-12, sound damping material 90 is placed adjacent to apertures 64 '-64'.

An advantage of the embodiment of fig. 11-12 is that the disclosed structure is closed to a significant effect on the low frequency output. The sound damping material 90 may further reduce the Q value of the high frequency resonance.

The structures shown in figures 9-12 reduce the Q-value of the self-resonance corresponding to the half-wave resonance of the gas port tube. The principles of the present invention may be used to reduce the Q value at frequencies corresponding to wavelength resonance, 3/2 wavelength resonance, and other resonances. To reduce the Q at these different resonances, it is desirable to open the holes at points other than halfway between the gas port tube ends. Consider, for example, the wavelength resonance when the pressure peaks at a tube length of one quarter each from each end. The holes at these locations reduce the Q value of the wavelength resonance more effectively than the holes at the midpoint of the tube. The holes at these and other points can be provided with leakage flow for the same small volume used for the medium point holes. Alternatively, each may have a dedicated closed end resonator tube. Still alternatively, they may allow leakage into or out of the housing. To reduce the audible output of multiple resonances, multiple holes are available, including slots, considered as a series of continuous holes.

Open cell structures, there are many combinations of structures (including resonant closed end tubes) that define a volume for the open cell.

Referring to fig. 13, there is shown a schematic representation of one embodiment of the present invention for reducing the Q value of the half wave resonance of a ported tube 73 of length a1 in a housing 71, the ported tube 73 having a driver 72, using a tube 75, the tube 75 being 0.3a1 in length, closed at one end and ported at a hole 74 at the other end. Fig. 14 shows a standing wave of half-wave resonance along the length of the tube 73, (tube 75 not shown), showing a pressure profile 76 and a volume velocity profile 77. The pressure reaches a maximum at point 74. Energy from the standing wave in the gas port tube 73 is removed from the gas port tube at the point of maximum pressure 74. Energy can be dissipated by the sound attenuating material 90 in the resonance tube, greatly reducing the Q of the half wave resonance.

In the resonance pipe 75, there may be a sound-deadening material. The sound damping material may fill only a small portion of the illustrated resonator tube 75 with the sound damping material 90 or the resonator tube may be substantially filled with the sound damping material 90'. The sound damping material 90 or 90' reduces the Q value of high frequencies that are multiples of the half-wave resonant frequency.

Referring to FIG. 15, a diagrammatic representation of the gas port tube 83 is shown, the gas port tube 83 having a bore 84 six tenths of the length s of the gas port tube from the left end and four tenths of the length of the gas port tube from the right end, a resonance tube 85 at the closed end having a length of 0.5 and a diameter of 3 "of the length of the gas port tube 83, and another closed end tube 85' having a length of 0.25 and a diameter of 1.5" of the length of the gas port tube 83. There may be a sound damping material 90 in one or both of the closed end resonator tube 85 and the closed end resonator tube 85'. For the embodiment of fig. 13, the sound attenuating material may fill a portion of one or both of the closed end resonance tubes 85 and 85 ', or substantially fill one or both of the closed end resonance tubes 85 and 85'.

It is no doubt that those skilled in the art may make various uses, modifications and departures from the specific apparatus and techniques disclosed above without departing from the inventive concepts. Consequently, the invention is to be construed as embracing each and every novel feature and novel combination of features described or possessed by the apparatus and techniques and not limited solely by the spirit and scope of the appended claims.

Claims (17)

1. An electro-acoustic device comprising:

a speaker housing including a first acoustic port;

an acoustic driver mounted within the speaker enclosure;

a heat generating device that heats ambient air and causes a convective air flow;

the acoustic driver and the acoustic port are constructed and arranged to cooperate to provide a cooling airflow across the heat generating device in substantially the same direction as the convective airflow, thereby transferring heat from the heat generating device.

2. The electro-acoustic device of claim 1, wherein the speaker enclosure further comprises a second acoustic port,

the heat generating device is located within the housing,

the first acoustic port, the second acoustic port, and the acoustic driver are constructed and arranged to cooperate to provide cooling airflow in substantially the same direction across the heat-generating device, thereby transferring heat from the heat-generating device.

3. The electro-acoustic device of claim 1, further comprising an airflow channel outside the speaker enclosure,

the heat generating device is positioned in the airflow channel.

4. The electro-acoustic device of claim 1, wherein the acoustic port is formed with an aperture, and further comprising an acoustic element in communication with the aperture and cooperating therewith to introduce an acoustic impedance into the acoustic port that reduces an amplitude of a standing wave of at least one predetermined wavelength in the acoustic port.

5. An electro-acoustic device comprising:

an acoustic enclosure;

a first acoustic port within the acoustic enclosure;

an acoustic driver mounted within the acoustic enclosure for inducing a first airflow within the first acoustic air port,

the first gas flow alternately enters and exits the housing;

a heat generating device;

wherein the acoustic port and the acoustic driver are constructed and arranged to cooperate to provide a second air flow in substantially the same direction as the first air flow; and

structure for directing the second air flow in the same direction across the heat generating device.

6. The electro-acoustic apparatus of claim 5, further comprising:

a second acoustic port constructed and arranged to coact with the first acoustic port to provide the second gas flow.

7. The electro-acoustic apparatus of claim 6, further comprising:

an airflow channel outside the acoustic enclosure for directing the second airflow.

8. A speaker enclosure having an interior and an exterior, comprising:

a first port having a first end with a cross-sectional area and a second end with a cross-sectional area,

wherein said first end cross-sectional area is greater than said second end cross-sectional area, said first end being adjacent to said inner portion and said second end being adjacent to said outer portion; and

a second air port located above the first air port,

wherein the first air port is capable of cooperating with an acoustic driver to be mounted in the speaker enclosure to produce a substantially co-directional air flow.

9. The loudspeaker enclosure as defined in claim 8,

wherein said second port has a first end with a cross-sectional area and a second end with a cross-sectional area, said first end cross-sectional area being greater than said second end cross-sectional area, and wherein said second end is adjacent said inner portion and said first end is adjacent said outer portion.

10. The speaker enclosure of claim 8, further comprising mounting points for at least one heat generating device located below the second air port.

11. A loudspeaker enclosure as claimed in claim 10, wherein the mounting point is constructed and arranged to mount an acoustic driver.

12. A speaker system comprising:

an electroacoustic transducer;

a speaker enclosure having a first port with an interior end and an exterior end, said interior end and said exterior end each having a cross-sectional area,

wherein the outer end cross-sectional area is greater than the inner end cross-sectional area; and

a second gas port having an inner end and an outer end, wherein the first gas port is located above the second gas port,

wherein the first air port is capable of coacting with the electroacoustic transducer to generate a substantially co-directional air flow.

13. The speaker system of claim 12 wherein the second port inner end and the second port outer end each have a cross-sectional area,

wherein the second port interior end cross-sectional area is greater than the second port exterior end cross-sectional area.

14. The speaker system of claim 12 wherein the electro-acoustic transducer is located within the speaker enclosure above the first air port and below the second air port.

15. A speaker enclosure having a top and a bottom, comprising:

a first port having an inner end and an outer end, said first port inner end and said first port outer end each having a cross-sectional area,

wherein the first port inner end cross-sectional area is less than the first port outer end cross-sectional area;

a second gas port having an inner end and an outer end, said second gas port inner end and said second gas port outer end each having a cross-sectional area,

wherein the second port interior end cross-sectional area is greater than the second port exterior end cross-sectional area,

wherein the first and second air ports are capable of cooperating with an acoustic driver to be mounted in the speaker enclosure to produce substantially co-directional air flow.

16. The speaker enclosure of claim 15, wherein the first port exterior end cross-sectional area is located closer to the roof than the second port interior cross-sectional area.

17. The speaker enclosure of claim 15, further comprising an opening for an electro-acoustic transducer located over the first port interior end and the second port interior end.