Reduced noise abrasive blasting systems

Abstract

Reduced noise abrasive blasting assemblies and systems are described. The new assemblies and systems are comprised of standard blast hose, accelerator hose, couplings and nozzle. The improved abrasive blasting system maintains abrasive particle velocity while decreasing the exit gas velocity and consequently decreasing sound production. This is accomplished through an acceleration section with reduced inner diameter and sufficient length to provide the necessary abrasive particle velocity. The new system maintains the productivity and efficiency of conventional abrasive blasting systems but with greatly reduced acoustic noise production and reduces operator fatigue due to the lower weight of the carried portion of the system.

Claims

1. A reduced noise abrasive blasting system for abrasive blasting, the system comprising: (a) a flexible first diameter blast hose section; (b) a flexible reduced inside diameter accelerator hose section having an inside diameter smaller than that of the first diameter blast hose section; and (c) a tube-shaped coupler transitioning from a larger diameter on one side to a smaller diameter on an opposite side, connecting the flexible first diameter blast hose section to the flexible reduced inside diameter accelerator hose section, the reduced insider diameter accelerator hose ending in an output coupling.

2. The reduced noise abrasive blasting system of claim 1, further comprising a blasting nozzle connected to the output coupling of the reduced inside diameter accelerator hose section.

3. The reduced noise abrasive blasting system of claim 2, wherein a blasting nozzle exit diameter is selected to produce a desired diameter of an effective blasting region of abrasive action.

4. The reduced noise abrasive blasting system of claim 1, wherein said coupler further comprises a transition section connecting said first diameter and said reduced inside diameter accelerator hose sections to gradually and smoothly transition from one diameter to a next reduced diameter to reduce pressure losses at the coupler between hose sections.

5. The reduced noise blasting system of claim 1, further comprising abrasive particles carried by a compressed carry gas wherein the length and inside diameter of the reduced inside diameter accelerator hose section are calculated by determining a velocity of the compressed carry gas moving through the reduced inside diameter accelerator hose section for a particular hose length, and then calculating an estimated particle velocity at a nozzle exit, and repeating this calculation for a range of hose lengths and inside diameters and selecting the hose length and inside diameter which provides the best combination of high particle velocity and low gas velocity.

6. The reduced noise abrasive blasting system of claim 1, wherein the reduced diameter accelerator hose section possesses a diameter of about 75% of the diameter of the first diameter blast hose section.

7. The reduced noise abrasive blasting system of claim 1, wherein the rigid tube-shaped coupler comprises a housing enclosing a bore.

8. The reduced noise abrasive blasting system of claim 1, wherein the rigid tube-shaped coupler housing is cylindrical.

9. The reduced noise abrasive blasting system of claim 8, wherein the rigid tube-shaped coupler has an outer diameter greater than that of the first diameter blast hose section and the reduced inside diameter accelerator hose section.

10. The reduced noise abrasive blasting system of claim 1, further comprising one or more further reduced inside diameter accelerator hose sections and one or more further couplers, each of the further reduced inside diameter accelerator hose sections having a diameter less than that of the reduced diameter accelerator hose section.

11. A reduced noise abrasive blasting system, comprising a media tank, an abrasive media, a compressed carry gas to carry the abrasive media, a plurality of flexible hose sections having different inside diameters, at least one transition coupling connecting each of said flexible hose sections together providing a gradual and smooth transition from one diameter to a next diameter, and an output coupling connected to a nozzle and to one of the flexible hose sections, wherein the system is configured for abrasive media to exits the nozzle at supersonic speed and the compressed gas to exit the nozzle at subsonic speed.

12. The reduced noise abrasive blasting system of claim 11, wherein the length and inside diameter of a reduced inside diameter hose section are calculated by determining a velocity of a compressed carry gas moving through the reduced inside diameter hose section for a particular hose length, and then calculating an estimated media particle velocity being carried by said compressed carry gas leaving a nozzle exit, and repeating this calculation for a range of hose lengths and reduced inside diameters and selecting the hose length and reduced inside diameter which provides a best combination of high particle velocity and low gas velocity.

13. The reduced noise abrasive blasting system of claim 11, wherein said hose sections further comprise: (a) a first flexible hose section having a 1 inch inside diameter that connects said media tank to a second flexible hose section; (b) said second flexible hose section having a inch inside diameter that connects to said first flexible hose section; and (c) a one of the transition couplings connects the first and second flexible hose sections.

14. The reduced noise abrasive blasting system of claim 13, further comprising the nozzle connected to the output coupling at an end of said second hose section opposite from the one of the transition couplings and wherein a diameter of an exit from the nozzle is selected to produce a desired diameter of an effective blasting region of abrasive action.

15. The reduced noise abrasive blasting system of claim 11, further comprising the transition coupling that connects a first hose section to a second hose section to gradually and smoothly transition from a larger diameter to a next smaller diameter to reduce pressure losses at the transition coupling between the first and second hose sections.

16. The reduced noise blasting system of claim 11, wherein a reduced inside diameter hose section having reduced weight is attached to a nozzle and held by an operator, and wherein the reduced noise blasting system imparts lower ergonomic stress to the operator from a reduced weight of a carried portion of the system.

17. An abrasive blasting system employing abrasive media particles carried by a compressed carry gas that produces less noise, the abrasive blasting system comprising: (a) a flexible first diameter blast hose section; (b) a flexible reduced inside diameter hose section; and (c) a transition coupling connecting the flexible first diameter blast hose section to the flexible reduced inside diameter hose section whereby the compressed gas is capable of moving at supersonic speed upon entering the transition coupling; (d) wherein a length of the reduced inside diameter hose section provides an accelerator hose section to facilitate acceleration of abrasive media particles to a velocity equal to supersonic speed; and (e) wherein the reduced inside diameter hose section is capable of reducing velocity of the compressed carry gas for the abrasive media to less than supersonic speed upon exiting an attached nozzle; and (f) wherein the abrasive media is capable of exiting the attached nozzle at supersonic speed using a narrowed and lengthened accelerator section formed by the reduced inside diameter hose section to maintain media particles exit velocity at supersonic speed while decreasing the compressed carry gas exit velocity to subsonic speed.

18. The abrasive blasting system of claim 17, wherein the length and inside diameter of said reduced inside diameter hose section are calculated by determining a velocity of a compressed carry gas moving through the reduced inside diameter hose section for a particular hose length, and then calculating an estimated particle velocity at a hose exit, and repeating this calculation for a range of hose lengths and inside diameters and selecting a hose length and inside diameter which provides the best combination of high particle velocity and low gas velocity.

19. The abrasive blasting system of claim 17, further comprising a nozzle attached to one end of the reduced inside diameter hose section and wherein a nozzle exit diameter is selected to produce a desired diameter of an effective blasting region of abrasive action.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 illustrates a conventional state of the art supersonic abrasive blasting system.

(2) FIG. 2 depicts, in cross section, a conventional supersonic convergent-divergent nozzle used in the abrasive blasting system illustrated in FIG. 1.

(3) FIG. 3 reproduce graphs from Settles' paper (Settles G., A scientific view of the productivity of abrasive blasting nozzles, 1996), showing predicted and measured velocities through a conventional Laval nozzle and the large difference between abrasive velocity and exit gas velocity.

(4) FIG. 4 is a graph showing the drag coefficient as a function of Mach number for two Reynolds numbers for spheres.

(5) FIG. 5 is a graph showing the required reduction in jet exit velocity to achieve desired reduction in Sound Pressure Level (SPL) based on the relationship of jet exit velocity to jet noise production.

(6) FIG. 6 is a graph demonstrating modeled particle velocity versus distance in 345 m/s accelerator section for Type V acrylic media 20/30 mesh.

(7) FIG. 7 is a Moody Diagram used for estimation of Friction Factor from Reynolds Number and pipe roughness.

(8) FIG. 8 illustrates the major component parts of a preferred embodiment of the improved reduced noise abrasive blasting system of the subject invention.

(9) FIG. 9 shows, in cross-section, details of the transition coupling used to step down the inside diameter of the abrasive media path employed in the reduced noise abrasive blasting system illustrated in FIG. 8 and the relative geometry of the nozzle and accelerator hose.

(10) FIG. 10 is a photograph of a prototype reduced noise abrasive blasting accelerator hose and nozzle.

(11) FIG. 11 is a photograph illustrating, in comparative format, productivity of the invention prototype (left side) and conventional blasting (right side) using #8 nozzle blasting Type V media on half of an exposed coated baking pan for 30 seconds, both with 4 turns of abrasive metering valve knob.

(12) FIG. 12 is a photograph comparing the results of using a reduced noise blasting system of the subject invention operating with additional abrasive to a conventional system operating with a Marco #8 nozzle.

(13) FIG. 13 is an autospectrum of a conventional state of the art supersonic abrasive blasting apparatus with a Marco #8 nozzle and the subject invention prototype with Type V media and 40 psi operating pressure, along with background noise levels from blasting compressor unit.

DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS

(14) A solution to the problem of excessive noise from state of the art supersonic abrasive blasting systems is found as set forth in the following.

(15) The acceleration of particles in a stream can be modeled using empirically determined drag coefficient presented previously (Settles & Geppert, 1997) based on data from Bailey and Hialt. The acceleration of a particle of mass, m, is found from the drag, D, as

(16) $a=\frac{D}{m}=\frac{1}{m}\frac{1}{2}{U}_{\mathrm{rel}}^2{\mathrm{AC}}_d$
where A is the cross-sectional area of the sphere and U.sub.rel is the relative velocity between the gas and the particle. Illustrated in FIG. 4 is the drag coefficient as a function of Mach number for two Reynolds numbers for spheres.

(17) Previous studies have demonstrated that the noise power, P, of a jet scales with the eighth power of velocity and the square of jet diameter (Powell, 1959) as
PU.sup.8D.sup.2
Furthermore, sound pressure level, SPL, is proportional to sound power level, SWL where

(18) $\mathrm{SWL}=10\log \left(\frac{\mathrm{Power}}{1{10}^{-12}W}\right)$
As a result, it can be inferred that SPL, velocity and diameter scale as:

(19) ${\mathrm{SPL}}_2-{\mathrm{SPL}}_1=80\log \left(\frac{U_2}{U_1}\right)$

(20) This relationship is shown in graph form in FIG. 5. Thus, if the exit velocity of the nozzle is reduced by 30%, for example, then a drop in SPL of 12.5 dB is expected.

(21) In order to have the same production as a current state of the art nozzle blasting system, the velocity of the particles must be maintained. Conventional nozzles, as illustrated in FIG. 2, have much higher gas velocities than particle velocities, and these high gas velocities are responsible for high sound production levels. The subject invention maintains the particle velocity while decreasing the nozzle exit gas velocity and such, decreasing the sound production. This requires a longer acceleration length relative to conventional art nozzle blasting systems.

(22) The mass of the sphere is the density of the particle, .sub.particle multiplied by the volume

(23) $\frac{4}{3}{r}^3.$
So acceleration becomes

(24) $a=\frac{3}{8}{C}_d\frac{{}_{\mathrm{gas}}}{{}_{\mathrm{particle}}}\frac{U_{\mathrm{rel}}^2}{r}$

(25) The solution can be found in a stepwise manner and is shown in FIG. 6 for Type V acrylic media of 20/30 mesh in an air stream with a velocity of 345 m/s. This demonstrates that to achieve 275 m/s particle velocity a 4 meter accelerator section is required.

(26) Based on an estimated exit velocity of 483 m/s from a previous model of the Marco #8 nozzle operating at 40 psi pressure, an exit velocity reduction of 30% to 345 m/s (roughly sonic) produced a 12.5 dB reduction in SPL. The length of hose then needs to be sufficiently long to match the particle velocity of the #8 nozzle at 40 psi.

(27) The instant invention achieves sufficient abrasive particle velocity through greater acceleration distances in an airstream with a lower exit velocity, thereby reducing nozzle generated noise experience with supersonic blast nozzles. Adjustments to blasting productivity can be made by adjusting the abrasive mass flow rate.

(28) Pressure loss, or head loss, is unavoidable and must be considered. As the length of the hose increases, the pressure will decrease and eventually decrease the flow velocity. But this loss can be calculated. The head loss, or pressure loss, due to friction along a pipe is given by the Darcy-Weisbach equation as

(29) $p=f_D\frac{L}{D}\frac{V^2}{2}$
where L is the length of the pipe section, D is the pipe diameter, p is the density of the fluid, V is the average fluid velocity, and f.sub.D is the Darcy friction factor based on Reynolds Number, Re and relative pipe roughness, /d and is equal to approximately 0.02 for plastic/rubber. FIG. 7 shows a Moody Diagram used for estimation of Friction Factor from Reynolds Number and pipe roughness.

(30) A inner diameter blast hose operating close to choked condition has a velocity of 230 to 340 m/s and a Reynolds number of 300,000 to 436,000. Drag over the length of the hose induces pressure losses which decrease the average velocity in the pipe.

(31) Velocity in the hose will be sonic if the choked flow conditions exist where the pressure downstream falls below a critical value, p*, given by

(32) $\frac{p^{*}}{p_0}={\left(\frac{2}{k+1}\right)}^{\frac{k}{k-1}}$
where the heat capacity ratio, k, is 1.4 for air, giving
p*=0.528p.sub.0
For 40 psi gage pressure, or 54.7 psi absolute pressure, p* is 28.9 psia or 14.2 psig.

(33) Based on the results of analytical models discussed above, a preferred embodiment of the subject invention was designed that takes airborne particles from the example 1 hose and accelerate them through a smaller diameter hose a sufficient distance such that a productive particle speed is obtained. Transition couplings that step down the inside diameter of the hose provide smooth transitions between the different hose section diameters with minimal pressure losses.

(34) According to a preferred embodiment of the reduced noise abrasive blasting systems of the subject invention depicted in FIG. 8, compressor 112 pressurizes gas to near 120 psi. Compressed carry gas is pumped through initial hose section 114 into abrasive media tank 116 containing abrasive media 118 to mix with the media 118 and carry the media 118 through the system. An abrasive metering valve 120 controls the rate of release of abrasive media 118. A standard 1 inside diameter blast hose 124 attaches, at one end to metering valve 120 and, at the other end, to a transition coupling 122. A length of reduced inside diameter, for example, accelerator hose 130 connects transition coupling 122 to a nozzle 134 through a claw coupling 132. Transition coupling 122 serves to step down the inside diameter of the path that is taken by abrasive media 118 from the 1 diameter blast hose 124 to the smaller diameter acceleration hose 130.

(35) The details of transition coupling 122, and nozzle 134, are illustrated, in cross-section, in FIG. 9. Coupling 122 is comprised of housing 128 enclosing a bore (not shown). The blast hose side 125 of transition coupling 122 has a 1 inside diameter bore, while the accelerator side 130 of transition coupling 122 has a diameter bore. Each side of transition coupling 122 connects with the respective hose using conventional claw coupling 132 technology.

(36) The nozzle 134 exit diameter 136 is sized to control the desired abrasive hot spot diameter such that the effective blasting region of the reduced noise abrasive blasting system can match that of a conventional supersonic nozzle.

(37) Other preferred embodiments of the reduced noise abrasive blasting systems of the present invention are systems that comprise more than one section of acceleration hose and that employ more than one transition coupling, each section of acceleration hose having a decreasing inside diameter. Other types of couplings, nozzles, metering valves and abrasive media may be employed in the systems of the instant invention without departing from the scope of the invention.

EXAMPLES

(38) Initial Prototype Fabrication and Testing

(39) A prototype comprising the component parts illustrated in FIGS. 8 and 9 was fabricated as shown in FIG. 10 with the following characteristics for testing: Four-meter accelerator section with inner diameter to achieve sonic conditions (345 m/s) Straight bore nozzle with 0.79 bore diameter to match output diameter of #8 nozzle to achieve same hot spot as current standard #8 setup Couplers, etc.

(40) Sound pressure levels were measured using both handheld integrating sound pressure meter and a stand-alone microphone data acquisition system. Nozzle pressures were measured near the end of the 1 hose before coupler to be 40 psi. Type V media was introduced by opening the media valve 4 full turns. Results of the sound pressure level testing, in dB, were as follows:

(41) TABLE-US-00001 Nozzle Integrated SPL (dB) Marco #8 108 QB-1 Prototype 94.5

(42) Productivity was qualitatively assessed by using both the #8 nozzle and the subject prototype for 30 seconds on an exposed half of a coated baking pan, as illustrated in FIG. 11. The effect of adjusting the abrasive metering valve knob was examined by adjusting the knob to six turns for the prototype and comparing the production of that setup to a Marco #8 nozzle that used the 4-turn setting.

(43) FIG. 12 illustrates that the prototype operating at the 6-turn setting was clearly more productive than the Marco #8 operating at the 4-turn setting. These results show that the subject invention can be operated with equal or better productivity compared to a standard #8 nozzle while producing 16 dB less noise as measured at the operator.

(44) Testing was also performed to examine total sound pressure levels as well as acoustic spectra for the prototype as compared to a standard #8 nozzle, both operating at 40 psi. The testing results demonstrate noise reduction is broad spectrum, as illustrated in FIG. 13.

SUMMARY AND SCOPE

(45) As will be appreciated from the description, drawings and examples set forth above and referenced herein, the reduced noise abrasive blasting systems of the present invention allow for abrasive blasting with significantly reduced resultant noise while providing the equivalent productivity and efficiency compared with conventional abrasive blasting systems. The improved reduced noise blasting system promotes worker health and safety and a quieter environment for those in the vicinity.

(46) The improved abrasive blasting system exploits a narrowed and lengthened accelerator section in order to maintain particle velocity while decreasing the gas exit velocity. A straight bore nozzle can be used to produce the desired active abrasive area. The maintained particle velocity provides the equivalent abrasive productivity while the decreased gas velocity provides for the reduced resultant noise.

(47) While specific preferred embodiments and examples of fabrication and testing of the invention have been illustrated and described, it will be clear that the invention is not so limited. Numerous modifications or alterations, changes, variations, substitutions and equivalents will occur to those skilled in the art without deviating from the spirit and scope of the invention, and are deemed part and parcel of the invention disclosed herein.

(48) By way of example and not limitation, the nozzle and hose dimensions, and the coupling types, and the specific configuration and sizes of hose, couplings, nozzle and accelerator section, can be varied in accordance with the general principals of the invention as described herein in order to accommodate different working conditions, target materials, project specification, budgetary considerations and user preferences. In addition, more than one transition coupling and accelerator hose section and inside diameter may be employed in the systems of the subject invention. The invention described herein is inclusive of all such modifications and variations.

(49) Further, the invention should be considered as comprising all possible combinations of every feature described in the instant specification, appended claims, and/or drawing figures which may be considered new, inventive and industrially applicable.

(50) Multiple variations and modifications are possible in the embodiments of the invention described here. Although certain illustrative embodiments of the invention have been shown and described here, a wide range of modifications, changes and substitutions is contemplated in the foregoing disclosure. While the above description contains many specifics, these should not be construed as limitations on the scope of the invention, but rather as exemplifications of one or another preferred embodiment thereof. In some instances, some features of the present invention may be employed without a corresponding use of the other features.

(51) Accordingly, it is appropriate that the foregoing description be construed broadly and understood as being given by way of illustration and example only, the spirit and scope of the invention being limited only by the claims which ultimately issue.