WATER JET CONFERENCE - Waterjet Technology Association

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surface spall occurred, resulting in a shallow crater of comparatively large volume. These data were included in the statistical treatment; the resulting mean values, with and without the atypical data, are shown near the bottom of Table l. These data show only a moderate change in breakage performance for decreased standoff. It is also apparent that the check valve plunger yielded poorer breakage, possibly because of leakage past the check valve during extrusion. The overall mean crater volume, excluding the three atypical data, was 0.01 in (0.16 cc). The specific energy for face breakage was thus determined to be 79,000 ft-lb/in 3 (6700 joules/cc) at a nominal pulse energy of 792 ft-lb (1070 joules). At the same pulse energy, the semiempirical full face breakage model advanced by Grantmyre and Hawkes, 1975, for mechanical impact breakers indicates a specific energy of about 1300 ft-lb/in 3 (10 6 joules/cc) against rock. Yie, 1978, quotes specific energy for pneumatic hammers as 3000 to 19,000 ft-lb/in 3 (260 to 1600 joules/cc). This agrees with the Granymyre-Hawkes model at pulse energies typical of hand-held "jackhammer" type breakers, that is, on the order of 10 to 100 ft-lbs (13-130 joules). We thus conclude that the pulsed extrusion jet is at least 4 times less efficient in rock breaking than even the very smallest weight and pulse and pulse energy. It must be noted that the additional variable of target material is nested in these data. It is unlikely that this effect would be large enough to change the performance ratio significantly. Shortly after the data of Table 1 had been obtained, the device ceased to operate properly. In particular, the check valve plunger no longer moved freely in the packing gland and was quite badly scored and galled. The remainder of the hardware, particularly the nozzle, barrel, 15-5 PH stainless steel transducer-plunger, and the seal, showed no evidence of damage. CONCLUSIONS The extrusion pulsed jet device used in the current investigation produced a peak jet velocity of about 2900 ft/sec (880 m/sec). The measured pulse energy was 792 ft-lb (1070 joules) and peak chamber pressure was about 61,000 psi (4.2 k-bar). The full face breakage performance of this device does not compare favorably with that of mechanical breakers of similar size, weight and pulse energy. REFERENCES 1. Cooley, W. C., 1974, Fabrication and Testing of a Water Cannon for Rock Tunneling Experiments: Department of Transportation, Report No. FRAORD&D 7438. 2. Edney, B. E., 1976, Experimental Studies of Pulsed Water Jets: Third International Symposium on Jet Cutting Technology. 3. Gnirk, P. F. and Grams, W. H., 1972, Rock Drilling with Pulsed High-Velocity Water Jets: Rock Mechanics, p. 589-612. 4. Grantmyre, I. and Hawkes, I., 1975, HighEnergy Impact Rockbreaking: Can. Min. and Metall. Btllletin, v. 68, p. 63-70. 5. Leach, S. J. and Walker, G. L., 1965, The Application of High Speed Liquid Jets to Cutting: Philosophical Transactions, v. 260, p. 295-308. 6. Mohaupt, U. H., Burns, D. J., Yie, G. G. and Mellors, W., 1978, Design and Dynamic Response of a PulseJet Pavement Breaker: Fourth International Symposium on Jet Cutting Technology. 110
7. Voytsekhovskiy, B. V., Nikolayev, V. P., Dudin, V. M., Mayer O.F., and Cherminskiy G.P. 1964, Some Results of the Destruction of Rocks by Means of a Pulsed Water jet, New of the Siberian Department of the Academy of Sciences, USSR. 8. Watson, A. J., Williams, F. T. and Brade, R. G., 1982, Impact Pressure Characteristics of a Water Jet: Sixth International Symposium on Jet Cutting Technology. 9. Yie, G. G., Burns, D. J. and Mohaupt, U. H., 1978, Performance of a High-Pressure Pulsed Water-Jet Device for Fracturing Concrete Pavement: Fourch International Symposium on Jet Cutting Technology. 10. Young, Chapman, 1977, Rock Breakage with Pulsed Water Jets: The American Society of Mechanical Engineers, 77-Pet-78. Figure 1. Extrusion Schematic. Figure 2. Driving Force for an ideal gas spring. 111
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Proceedings of the Second U.S. WATE
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Visualization of the Central Core o
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A Status Report on the Conceptual D
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SESSION 7 - CIVIL & INDUSTRIAL Chai
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Cutting Hard Rock With Abrasive-Ent
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frictional and piping component rel
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R = a1 ⋅ A1 A2 a2 I = 2H o Q o
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attenuation of the output. The tran
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Figure 1. Branch System Modulator F
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Figure 5. Modulation Response for B
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Figure 9. Modulation response for s
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can be used for any form of input.
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with a cylindrical shape to the jet
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m/s. The range of power found from
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Figure 3. Power vs nozzle diameter
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Figure 5. Frequency vs length of th
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NAME: Gerald Zink COMPANY: StoneAge
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modulatornozzle assembly. The ordin
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DISCUSSION OF FLUID MECHANICS The i
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This process serves to protect the
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For test purposes, these concrete b
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REFERENCES CITED 1. Barker, C. R.,
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FIGURE 4. INNER CORE OF PERCUSSIVE
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FIGURE 9. EXAMPLE OF HIGH-PRESSURE
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NAME: John E. Wolgamott COMPANY: St
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THE FOCUSED SHOCK TECHNlQUE FORPROD
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The reflected wave is thus also cyl
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neglected. The introduction of a co
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DISCUSSION NAME: George Savanick CO
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H’ mean shape factor Hj theoretic
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Required streamline curvature at th
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2 x 2 ≅ ( e − 2 p + w)/k2 (2-8)
Page 66 and 67: eliminating 2 n r 2 from equations
Page 68 and 69: approximation to the actual flow si
Page 70 and 71: skin friction coefficient but are c
Page 72 and 73: where: (H) = A1H 3 + A2H 2 + A3H +
Page 74 and 75: effect (< 0.5%) on coefficients of
Page 76 and 77: TABLE 5 Rei x 10 5 β 3 4 5 6 Po Po
Page 78 and 79: TABLE 6 D(mm) d o(mm) L t(mm) L f(m
Page 80 and 81: expanding rather than contracting a
Page 82 and 83: 25. Weber, H.E., 1978, Boundary lay
Page 84 and 85: Figure 5. Wall velocity distributio
Page 86 and 87: Figure 9. Effect of nozzle design o
Page 88 and 89: Figure 12. CA+T Design Philosophy.
Page 90 and 91: Figure 16. Effect of inlet b 1 cond
Page 92 and 93: Figure 20. Relaminarization at nozz
Page 94 and 95: Figure 24. Pressure decay data. 88
Page 96 and 97: VISUALIZATION OF THE CENTRAL CORE O
Page 98 and 99: DISCUSSION Although employing the i
Page 100 and 101: 5. Lambert, J. H., 1760, Photometri
Page 102 and 103: Figure 6. Spectral sensitivity curv
Page 104 and 105: NAME: W.C. Cooley COMPANY: Terraspa
Page 106 and 107: INTRODUCTION Pulsed liquid jets sho
Page 108 and 109: y=X ∨ P A dy = p p A p 2 (L c y=0
Page 110 and 111: Using equation (15), the value of X
Page 112 and 113: Thus about the first 10% of the dri
Page 114 and 115: Many design cases, including those
Page 118 and 119: Figure 3. Chamber pressure at pisto
Page 120 and 121: Figure 7. Effect of nozzle area rat
Page 122 and 123: Figure 11. Extrusion device schemat
Page 124 and 125: Figure 15. Typical chamber pressure
Page 126 and 127: DISCUSSION NAME: W. C. Cooley COMPA
Page 128 and 129: material which are, in turn, affect
Page 130 and 131: the water jet. This method was not
Page 132 and 133: where h is the depth of penetration
Page 134 and 135: obtained during this phase of the i
Page 136 and 137: observed that the smallest depth of
Page 138 and 139: Figure 2. Idealized Relationships b
Page 140 and 141: Figure 6. Penetration as a Function
Page 142 and 143: DEVELOPMENT OF VARIABLE DELIVERY TR
Page 144 and 145: THE STRUCTURE AND FUNCTION OF THE P
Page 146 and 147: The injection pressure can be contr
Page 148 and 149: ACKNOWLEDGEMENTS The authors gratef
Page 150 and 151: Figure 4. Theoretical required powe
Page 152 and 153: Figure 9. Variation of efficiency w
Page 154 and 155: THE "SKIPJACK" SEWER CLEANING NOZZL
Page 156 and 157: HYDRO-BLASTING SAFETY C.W. Adaway,
Page 158 and 159: Remember, your Hydro-Blasting work
Page 160 and 161: horizontal, sometimes vertical, and
Page 162 and 163: Figure 2. Safety Gear Figure 3. Tub
Page 164 and 165: DEVELOPMENTS IN CLEANING COKE OVEN
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causing chain breakages and the scr
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was encountered, then the rotation
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(C) Capital Expenditure: Material i
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Figure 9. Swivel coupling Figure 10
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OPTIMIZING JET CUTTING POWER FOR TU
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PRESSURE DROP (psi) ELEMENT Cv @10
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power output. Undersized nozzles re
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Subscripts n - Nozzle p - Pump t -
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Figure 1. Cutting effect as a funct
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CONSIDERATIONS IN THE COMPARISON OF
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pressure can be lowered to perhaps
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Figure 2: Fan jet issuing from a no
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DISCUSSION NAME: John Griffiths COM
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where Q = Flow rate - gpm D = Jet O
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Again, not limited to Newtonian flu
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REFERENCES 1. Brown, R.W. and Loper
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Table 2. Jet Cleaning Speeds and ot
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ANSWER: The utilization of the stat
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complexity and short component life
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Figure 4, for ap values ranging fro
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Decontamination Methods for rapidly
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a. “PULSER” b.”ORGAN-PIPE”
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Figure 5 - Removal rate for various
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DISCUSSION NAME: David A. Summers C
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DRILLING BORE HOLES IN COAL MINES U
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pile could not be judged as represe
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DISCUSSION NAME: David Summers COMP
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HYDRAULIC MINING EXPERIMENTS IN AN
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The monitor was fed pressurized wat
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The IH rig was considered to be sup
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REFERENCES 1. Okhrimenki, V. A., A.
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Figure 2. Jet cutting sandstone at
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Figure 5. Schematic plan view of In
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Figure 7. Suction Box. 226
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USE OF HIGH PRESSURE WATER JETS FOR
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flame torch to cut this block, redu
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the order of 360 rpm. Under these c
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Figure 3. Slot cut by jet at 11 o s
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JET-MINER SURFACE AND IN-SEAM TRIAL
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The hydraulic drive of the haulage
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The surface trials had have the obj
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Figure 2. Experimental version. Fig
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Figure. 7 Jet-Miner prototype Figur
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SOME PATTERNS OF TECHNOLOGY TRANSFE
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Development of High Pressure_Techno
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configurations, the design of an op
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and public sectors. After a haitus
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Souder, W.E. and Evans, R.J., "The
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Figure 5. Technological achievement
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Table 3. Perceived disadvantages of
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already been, or is being applied w
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Using the requirements profile and
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ant hose combination, a guiding sys
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HYDRAULIC MINING TESTS Site selecti
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SAFETY All operations were carried
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TABLE V. Categories of Jet Mining D
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Figure 2. Generalized geologic prof
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SECONDARY FRAGMENTATION WITH WATER
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do possess a maximum point (Fig. 8)
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Figure 4. Rossin-Rammler plot. Figu
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Figure 8. Non-dimensional plot for
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HYDRAULIC COAL MINING SYSTEM Typica
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Figure 4. (From ref. 1) DISCUSSION
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INTRODUCTION Developing an unique t
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The coefficients "b " in Eq. (1) ca
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By the end of 1982, a total of more
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Figure 4. Cutting ability of swing-
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Figure 10. An operating performance
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for an abrasive, the abrasive parti
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the particles, while at slower spee
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to break away the remaining segment
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Table 1. Concrete saw technology. T
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NAME: Tom Brunsing COMPANY: Foster-
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FEASIBILITY STUDY OF CUTTING SOME M
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hydraulic power required to cut thr
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pressure was varied from 103 to 310
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2.1 Heading and gutting fresh cod f
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Figure 5. The cuts surface of a blo
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Figure 17. Cuts made across the cla
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JET NOTCHING USED IN THE CONSTRUCTI
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Bottom notch diameter was determine
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σ H = in-situ stress in the horizo
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Figure 3. Final block displacement.
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Figure 8. Comparison of Slurry Pump
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THE FURTHER DEVELOPMENT OF AN UNDER
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use taps or hydrants. To achieve th
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supply line. It was determined that
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The rotating head requires major mo
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Figure 4. System field test set-up
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Figure 10. Bentonite drilled clay s
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MECHANICAL TOOLS Cutting Tool Energ
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Ψ = cos −1 ⎧ ⎪ ⎪ ⎨ ⎪
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mode also contributes to chip flush
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NAME: Simon Johnson COMPANY: Newcas
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ROLLER TOOLS COMBINED WITH HIGH-PRE
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Various designs and applications ar
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Figure 1. Full-face tunneling machi
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Figure 11. roadway profile cutting
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Figure 19. High-pressure water jet
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DESIGN AND OPERATION OF TWO LARGE-S
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The hydraulic system for the thrust
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Results of Trial Tests As part of m
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cutting rates, degree of bit wear,
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Overall approximate Weight: Basic M
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Figure 5. 3 ft. diameter laboratory
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nozzle diameter and cutting speed w
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2. Cutting Speed The influence of c
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energy it effects an increase in me
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Tip angle (degrees) 87 Off-set angl
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Figure 5. Figure 6. Figure 7 Figure
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Figure 17. Figure 18. Figure 19. Fi
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SCHEMES OF COAL MASSIF BREAKAGE BY
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out thoroughly an efficient scheme
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Research analysis has proved that t
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DEPENDENCE OF POWER INDICES OF COMB
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The experiments have shown how the
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K Ay = coefficient correcting for f
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Figure 1. Schemes of combined break
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Figure 5. Dependence of specific en
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Figure 12. Percentage of grade R -6
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Figure 1. Particle size analysis. T
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NAME: Dr. Henkel COMPANY: Bergbau-F
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presented. This study, of course, i
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identifying a general trend for the
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Effect of Abrasive Hardness, Shape
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In some situations, especially in c
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Figure 1. Abrasive waterjet nozzles
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Figure 8. Effect of standoff distan
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Figure 13. Abrasive waterjet cuts i
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CUTTING WITH ABRASIVE WATERJETS M.
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3.3 Abrasive Feed Systems For abras
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Because of the large number of infl
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due to wear. Although actual operat
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from this new technology. Table 2 l
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Table 1. materials cut by abrasive
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Figure 1. Abrasive waterjet nozzles
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a) kerfs in mild steel b) S.S. 15.5
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a) circle cutting in glass b) lamin
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DISCUSSION NAME: Andrew F. Conn COM
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CUTTING HARD ROCK WITH ABRASIVE-ENT
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slurry nozzle. Testing at water pre
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DISCUSSION OF TEST RESULTS Jet Conf
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materials. The flexibility in nozzl
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pressure can be wiped out if diffic
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9. Maurer, W.C., and Heilheckler, J
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Figure 5. Effect of abrasive feed r
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Figure 9. Accumulated depth of mult
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Figure 13. Close-up view of quartzi
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ABRASIVE INJECTION USAGE IN THE UNI
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sudden changes in the feed rate eff
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or the abrasive must be manually to
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clog; there not being sufficient ar
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CODE OF PRACTICE FOR THE USE OF ABR
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Figure 5. Water abrasive cleaning h
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Figure 15. 360 0 abrasive pipe clea
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ECONOMIC CONSIDERATIONS IN WATER JE
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Other criteria to be considered in
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3 MANUAL METHODS OF JET CLEANING &
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contractor with old, unsafe, equipm
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Figure 1. Showing the increased cos
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Figure 8. Automatic tube bundle cle
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ackground to the subsequent coopera
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The molecules of SUPER-WATER posses
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shaken just before use. SUPERWATER
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26. Bednarz, L.P., "Effects of Poly
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