WATER JET CONFERENCE - Waterjet Technology Association

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DISCUSSION NAME: John Griffiths COMPANY: Sheldon Birmingham England QUESTION: "Do you agree that in part the relative inefficiency of a fan jet, when compared with a round jet is due to the form and method of production of conventional fanjets? With fan jets of a more exact form, where care is taken, on the shape and surface finish, destructive power is exhibited at distances up to 4 times shown in your paper." ANSWER: While it is true that considerable improvement in jet performance can be achieved where care is taken in the construction of the nozzle, it must be recognized that the basic form of the fan issuing from a spray nozzle is such that as the sheet leaving the nozzle moves further away, it will, at the same time get thinner. Thus a point is reached, as a function of the flow rate through the nozzle, at which the sheet is no longer thick enough to resist the surface tension forces and it will therefore disintegrate into droplets. This phenomenon is unlikely to be much affected by changes in the nozzle geometry, beyond a certain point, although it will of course be markedly affected by the angle at which the jet is directed away from the nozzle. NAME: Larry Pater COMPANY: Dravo QUESTION: "Does the shape of the tip of center body probe strongly affect the generation of cavitation bubbles?" ANSWER: The shape of the centerbody has a substantial affect on the induction of cavitation bubbles into the jet stream. From our experience a flat ended shape has been the best, although our study has been by no means exhaustive. I would suggest that there may be better shapes, information on these might well be obtained from studies of cavitation flows induced in conventional fluid streams. 184
<strong>WATER</strong> <strong>JET</strong> CLEANING SPEEDS - THEORETICAL DETERMINATIONS Casper William Zublin, Consulting Bakersfield, California 93308 ABSTRACT In an effort to improve state-of-theart water jet cleaning techniques as used in oilwells, a study was undertaken in 1980, to evaluate certain known parameter and their relationships. Using theoretical, observed, and empirical field data, a statement based on rotary applications was developed. Cleaning speeds and effectiveness were increased, and job results, in economic terms, were significantly improved in most cases. This paper deals not so much with the results of that development, as it does with the suggested use of those relationships to a linear application. BACKGROUND Oilwell water jet cleaning is a patented process (Hutchison, 1973 & Zublin, 1982) whereby directionally controlled hydronic energy is applied through very small jet nozzles to clean liner slots or perforations, and well screens that are partially or completely plugged. During normal operations the jets are rotated, as well as pulled up or lowered, through the interval to be cleaned. The resulting overlapping spiral track created by the jet streams removes most of the plugging material contacted. DEVELOPMENT In early 1971 tank tests were performed (Hutchison, 1973) that clearly demonstrated the effective cleaning width of a water jet with respect to nozzle size ("D") and standoff distance ("X"). It was shown that for a range of short dwell times or single pass operations, effective cleaning was not accomplished for "X/D" ratios in excess of 10. Limited jet sizes and narrow ranges of pressure drops across the jets were explored. Track cleaning speeds (the reciprocal of dwell time) covered a goodly range and were not considered critical. In utilizing this information and other related data, this author explored the results and concluded that dwell time needed to be evaluated further. Additionally it was expected that dwell time for effective cleaning, with respect to differing deposited plugging materials, would be different. The following analysis furnished an understanding of travel rate requirements for effective cleaning under varying field conditions. Fluid Rate and Velocity Early workers (Pittman, Harriman and St. John, 1961) developed a relationship between the flow rate, jet diameter pressure drop and fluid density as follows: Q = 69 D^2(P/e)^1/2 (1) 185
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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)
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eliminating 2 n r 2 from equations
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approximation to the actual flow si
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skin friction coefficient but are c
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where: (H) = A1H 3 + A2H 2 + A3H +
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effect (< 0.5%) on coefficients of
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TABLE 5 Rei x 10 5 β 3 4 5 6 Po Po
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TABLE 6 D(mm) d o(mm) L t(mm) L f(m
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expanding rather than contracting a
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25. Weber, H.E., 1978, Boundary lay
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Figure 5. Wall velocity distributio
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Figure 9. Effect of nozzle design o
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Figure 12. CA+T Design Philosophy.
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Figure 16. Effect of inlet b 1 cond
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Figure 20. Relaminarization at nozz
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Figure 24. Pressure decay data. 88
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VISUALIZATION OF THE CENTRAL CORE O
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DISCUSSION Although employing the i
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5. Lambert, J. H., 1760, Photometri
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Figure 6. Spectral sensitivity curv
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NAME: W.C. Cooley COMPANY: Terraspa
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INTRODUCTION Pulsed liquid jets sho
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y=X ∨ P A dy = p p A p 2 (L c y=0
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Using equation (15), the value of X
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Thus about the first 10% of the dri
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Many design cases, including those
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surface spall occurred, resulting i
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Figure 3. Chamber pressure at pisto
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Figure 7. Effect of nozzle area rat
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Figure 11. Extrusion device schemat
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Figure 15. Typical chamber pressure
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DISCUSSION NAME: W. C. Cooley COMPA
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material which are, in turn, affect
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the water jet. This method was not
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where h is the depth of penetration
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obtained during this phase of the i
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observed that the smallest depth of
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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
Page 166 and 167: causing chain breakages and the scr
Page 168 and 169: was encountered, then the rotation
Page 170 and 171: (C) Capital Expenditure: Material i
Page 172 and 173: Figure 9. Swivel coupling Figure 10
Page 174 and 175: OPTIMIZING JET CUTTING POWER FOR TU
Page 176 and 177: PRESSURE DROP (psi) ELEMENT Cv @10
Page 178 and 179: power output. Undersized nozzles re
Page 180 and 181: Subscripts n - Nozzle p - Pump t -
Page 182 and 183: Figure 1. Cutting effect as a funct
Page 184 and 185: CONSIDERATIONS IN THE COMPARISON OF
Page 186 and 187: pressure can be lowered to perhaps
Page 188 and 189: Figure 2: Fan jet issuing from a no
Page 192 and 193: where Q = Flow rate - gpm D = Jet O
Page 194 and 195: Again, not limited to Newtonian flu
Page 196 and 197: REFERENCES 1. Brown, R.W. and Loper
Page 198 and 199: Table 2. Jet Cleaning Speeds and ot
Page 200 and 201: ANSWER: The utilization of the stat
Page 202 and 203: complexity and short component life
Page 204 and 205: Figure 4, for ap values ranging fro
Page 206 and 207: Decontamination Methods for rapidly
Page 208 and 209: a. “PULSER” b.”ORGAN-PIPE”
Page 210 and 211: Figure 5 - Removal rate for various
Page 212 and 213: DISCUSSION NAME: David A. Summers C
Page 214 and 215: DRILLING BORE HOLES IN COAL MINES U
Page 216 and 217: pile could not be judged as represe
Page 218 and 219: DISCUSSION NAME: David Summers COMP
Page 220 and 221: HYDRAULIC MINING EXPERIMENTS IN AN
Page 222 and 223: The monitor was fed pressurized wat
Page 224 and 225: The IH rig was considered to be sup
Page 226 and 227: REFERENCES 1. Okhrimenki, V. A., A.
Page 228 and 229: Figure 2. Jet cutting sandstone at
Page 230 and 231: Figure 5. Schematic plan view of In
Page 232 and 233: Figure 7. Suction Box. 226
Page 234 and 235: USE OF HIGH PRESSURE WATER JETS FOR
Page 236 and 237: flame torch to cut this block, redu
Page 238 and 239: 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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