LEAK-PROOF, HIGH PRESSURE, HIGH VELOCITY, FLUID JET CUTTING NOZZLE ASSEMBLY

Abstract: A leak-proof insert for sealing in a fluid passageway and which may be a plug for the passageway but in a preferred embodiment forms part of a nozzle assembly comprising a tubular sleeve (20), a nozzle (18) and a nozzle body (16). The nozzle and nozzle body are held in an assembled relation with their bores (40, 34) aligned by the tubular sleeve which encircles them. The sleeve provides a seal between the nozzle assembly and housing (10) into which the nozzle assembly is mounted, and also provides a seal between the nozzle and nozzle body. During use, when under working pressure, the tubular sleeve tends to flow and move both downstream and radially, forming seals between the nozzle assembly and housing; and between the nozzle and nozzle body, which seals tend to increase in effective­ ness as the working pressure increases. The nozzle body described is a set screw enabling insertion in the housing and may have a chamfer (50) which engages a corresponding circular corner (52) of the housing, preventing downstream flow of the sleeve therebetween.

Description: LEAK PROOF, HIGH PRESSURE, HIGH VELOCITY, FLUID JET CUTTING NOZZLE ASSEMBLY The present invention relates to an insert for forming a seal within a fluid passageway, more particularly though not exclusively, to a nozzle assembly such as a fluid cutting jet nozzle assembly, for insertion in a housing means defining a nozzle supply passageway for high pressure fluid. Mining tools have been developed which utilise high pressure, high velocity, liquid jets to cut and reduce rock to slurry. Typically such mining tools include at least one cutting head having a plurality of fluidjet forming nozzle assemblies. When operated at pressures of over 20,000 psi, the nozzle in each nozzle assembly is made, typically, from a jewel, such as synthetic sapphire, to reduce erosion of the orifice in the nozzle which forms the fluid jet. Preventing leakage in such a nozzle assembly when operated at such high pressure is critical since a leak will result in the rapid erosion of the nozzle assembly and the cutting head around the point of leakage. This erosion will reduce the nozzle assembly and cutting head to the point of uselessness in a period of time as short as several minutes, depending on the pressures involved and the materials used in the nozzle assembly and cutting head. Even in nozzles made from jewels, the orifices event ually erode or clog, thereby necessitating replacement of removal of the nozzle for cleaning. Thus, it is important that the nozzle assemblies can be easily removable from the cutting head. However, this needed removability increases the possibility of an undesirable leak each time a nozzle assembly is removed from and replaced in the cutting head. Thus reliable, repeat sealing of the nozzle assembly in the cutting head is essential. In cutting heads with multiple nozzle assemblies, it is highly desirable that the nozzle assemblies be removable from the exterior of the cutting head, rather than from its interior. This is because such a configuration wound likely reduce the cost of the cutting head, and/or the nozzle assemblies, due to increase each of machining the parts involved; and would likely simplify and reduce the cost of removing and replacing the nozzle assemblies for repain or replacement of the nozzles. In addition, with certain geometries of cutting heads, it might well be physically difficult or impossible to make the nozzle assemblies replaceable from the interior of the cutting head. This will be readily appreciated from a consideration of Fig. la. However, if the cutting head is made so the nozzle assemblies are removable and replaceable from the exterior of the cutting head then the very high pressure working fluid within the cutting head tends to force such a nozzle assembly outward, thereby tending to unseat the nozzle assembly seals, and causing catastrophic leaks. In addition, it is highly desirable that the nozzle assembly, including the nozzle itself, by easily replaceable in the field as a unit, in order to reduce expensive down time of the mining equipment, because the nozzle is, by way of non-limiting example, only .078 inches in diameter, is hard to handle, and typically has an asymmetric geometry which mandates that it must be placed right side up in the nozzle assembly. Field repair would be simplified if the nozzle assembly couldbe removed and replaced in the field without needing any special tools or equipment other than a common screw driver or allen wrench. Objects of the present invention are to provide a leakproof insert which has all of these desirable features and which solves all of these problems; which is relatively low in cost, both to manufacture and replace; which effectively seals for an extended period of time against pressures of up to at least 60,000 psi; which utilises hydrostatic pressure to form seals which are stronger as the pressure increases, and which when the insert is a nozzle assembly will also provide an accurate, high quality cutting jet. In accordance with one aspect of the present invention, we propose a leak-proof insert for forming a seal within a fluid passageway, comprising an insert body adapted to fit in the passageway and having a snout upstream of a shoulder on the body, sealing means at least substantially encircling the snout upstream of the shoulder and means for mounting the insert in the passageway, the sealing means being sized to make a snug seal between the passageway and the insert body means and such that when subject to working pressure, compression thereof against the shoulder increases the firmness of the seal as the working pressure increases. The insert may be in the form of a plug for the passageway or in the form of a nozzle assembly including jet forming means, the insert body defining a bore through which the fluid jet is adapted to pass, the snout having a surface thereof adapted to seat the jet forming means. According to another aspect of this invention, a nozzle assembly particularly high velocity fluid jet cutting nozzle assembly comprises a nozzle and a nozzle body preferably in the form of a set screw, having complementary flat surface which mate very accurately. The nozzle and set screw are about the same diameter at their mating surfaces and have axially aligned bores through which the fluid jet passes. Sealing means hold the nozzle and set screw together in an assembled relationship to form the nozzle assembly, the sealing means preferably, a tight fitting tubular plastic sleeve which encircles and extends between them, also acting as a seal between the nozzle assembly and the cutting head. Creep of the plastic sleeve under hydrostatic pressure can be eliminated by forming a corner in the cutting head, against which the set screw, which has a corresponding chamfer, makes contact downstream from the plastic sleeve. The sealing effectuated by the plastic sleeve tends to increase as the hydrostatic pressure applied to it increases. Other features of the present invention are set forth in the appendant claims. Embodiments of the invention will now be described by way of example with reference to and as illustrated in the accompanying drawings in which: Figure 1 is a perspective view of a cutting head having a plurality of nozzle assemblies; Figure la is a schematic cross-sectional view taken along line la-la of Figure 1; Figure 2 is a cross-sectional view, taken along line 2-2 of Figure la; and Figure 3 is a cross-sectional view of another nozzle assembly shown installed in a cutting head. Figure 1 schematically illustrates a cutting head 10 having a plurality of nozzle assemblies 12 and a plurality of cutter tips 14. Cutting head 10, in operation, is connected to a suitable source of high pressure liquid. Cutting head 10 and cutter tips 14 are shown simply in an example of a housing in which nozzle assemblies are fitted. One or more nozzle assemblies 12 can be used with any particular cutting head 10, the number shown in Figure 1 being by way of example. A nozzle assembly 12 is shown in Figure 2 installed in housing means, namely cutting head 10, comprises three parts: nozzle body means, namely set screw 16; jet forming means for forming a liquid cutting jet, namely nozzle 18, and sealing mens, namely sleeve 20. Cutting head 10 defines a nozzle supply passage 22 and a threaded bore 24. Set screw 16 has a threaded shank 26 sized to threadedly engage bore 24; a first snout 28 of a diameter smaller than the diameter of the nozzle supply passage 22 to permit its entry therein; a second snout 30, smaller in diameter than first snout 28 and terminating in a flat upstream surface 32; a longitudinal bore 34 passing therethrough; a drive recess 36 for being engaged by a drive means, a shoulder 31 formed by the upstream face of first snout 28, and a peripheral corner 33 of shoulder 31. Nozzle 18 defines a longitudinal bore 40 and a flat surface 42. Sleeve 20 is tubular, and has a peripheral chamfer 46 on its upstream end 44. Nozzle assembly 12 is assembled by first placing sleeve 20 over the end of second snout 30, so its downstream end 47 is seated on shoulder 31. The nozzle 18 is then inserted into sleeve 20 until its flat surface 42 is firmly against flat surface 32 of set screw 16. Flat surfaces 42,32 form a seal therebetween, while the sleeve 20 seals the peripheries of nozzle 18 and second snout 30. To better effectuate these seals, it is preferred that the diameters and peripheral configurations of snout 30 and nozzle 18 be the same, although they could be different. Since the internal diameter of sleeve 20 is about the same as, or slightly smaller than the diameter of snout 30 and nozzle 18, it will be appreciated that the sleeve 20 grips both snout 30 and nozzle 18 in a relatively firm friction and/or elastic grip, thereby holding the nozzle assembly 12 together in an assembled relation so it can be handled conveniently as a unit. Although in Figure 2 sleeve 20 is shown extending upstream from shoulder 31 past the upstream face of nozzle 18, it need not necessarily do so. For example, nozzle 18 could be held in place on set screw 16 by other means such as, for example, with an adhesive and/or by providing a recess in the upstream face 32 of second snout 30 sized to receive nozzle 18. In such event, sleeve 20 could be a much shorter length and extend upstream from shoulder 31 only a short distance, for example, below or up to the level of the upstream face 32 of the second snout 30. The outer diameter of sleeve 20, when assembled as part of nozzle assembly 12, and prior to insertion into nozzle supply passage 22 in cutting head 20, is preferably slightly larger than the diameter of passage 22, and the upstream end 44 of sleeve 20 preferably extends a short distance past nozzle 18, but it need not do so, for the reasons set out below. Nozzle supply passage 22, sleeve 20, nozzle 18 and set screw 16 are preferably symmetrical about their longitudinal axes and are of circular cross-sectional configurations, but they need not be. Bore 40 in nozzle 18, bore 34 in set screw 16, and drive recess 36 are preferably axially aligned, though they need not be as long as the fluid jet passing, during operation, through bore 34 is not interfered with as it travels through and exits nozzle assembly 12. Drive recess 36 preferably is sized to be driveable by any conventional drive means such as an allen wrench or screwdriver, but it could assume other configurations so as to be driven by some other tool. Drive recess 36 need not be located on the longitudinal axis of set screw 16, in which case bore 34 of set screw 16 would extend to the downstream surface 48 of set screw 16. One working embodiment was tested at up to 60,000 psi and did not leak. The working fluid was water. There is no reason to believe it would leak at pressures above 60,000 psi. As to materials, the cutting head 10 and set screw 16 are formed from materials, such as stainless steel, which are stron enough to withstand design operating pressures plus normal safety margins, and which are resistant to corrosion from the working fluid and operating environment. Nozzle 18 is formed from synthetic sapphire, but other materials could be used depending on the particular operating pressures and working fluids used. Sleeve 20 is formed from UHMW-PE (ultra-high molecular weight polyethylene). At working pressures higher than 60,000 psi, soft metals could be used, such as bronze or brass. As for the size of the components of this working embodiment, nozzle supply passage 22 and first snout 28 have respective diametes of .125 and .124 inches, leaving a radial clearance of .0005 inches therebetween. A smaller clearance would be of advantage. First snout 28 extends into passage 22 .020 inches past the upstream end of threaded bore 24. Threaded bore 24 and the threaded shank 26 were about .160 inches in length and had at least three full threads, and preferably more, to prevent blowout of set screw 16 at operating pressure. Second snout 30 and nozzle 18 have a diameter of .078 inches, but this is not critical. Bore 40 in nozzle 18 has a diameter which is dictated by the particular job in hand, and typically runs from .005 to .025 inches. The diameter of bore 34 in set screw 16 is, as a rule of thumb, at least twice the diameter of bore 40. Second snout 30 extends .030 inches past shoulder 31 of first snout 28, but this dimension is not critical. The external diameter of sleeve 20, prior to assembly is .125 inches -- the same as the diameter of supply passage 22. Sleeve 20's internal diameter, prior to assembly, is 0.76 inches -- .002 inches smaller in diameter than snout 30 and nozzle 18, which it is designed to receive. Thus, when, sleeve 20, nozzle 18 and snout 30 are assembled, as has been described, sleeve 20 snugly holds nozzle assembly 12 firmly assembled. When assembled, the external diameter of the sleeve 20 increases by about .002 inches, as the snout 30 and nozzle 18 are inserted into sleeve 20 which has an undersized internal diameter - making the external diameter of the sleeve 20, when assembled, about .002 inches greater in diameter than supply passage 22. When assembled, the upstream end of sleeve 20 extends .010 to .015 inches past the upstream end of nozzle 18. Thus, this sizing of sleeve 20 serves triple purposes and solves three problems at the same time. That is, it holds sleeve 20, nozzle 18, and second snout 30 in an assembled relation, it forms a good seal therebetween, and it provides for the necessary oversizing of sleeve 20 as compared to passage 30 to effectuate a good seal therebetween also. Of course, other ways of solving these problems are possible such as making the internal diameter of sleeve 20 about the same as or slightly greater than the external diameter of nozzle 18 and second snout 30, and using a friction fit and/or adhesive to hold them together and form a seal therebetween. Then sleeve 20 could be made with the necessary oversize external diameter for a good seal with passage 22. The internal diameter of the threaded bore 24 in cutting head 10 is larger than the assembled external diameter of the sleeve 20 to prevent interference therewith when nozzle assembly 12 is being assembled with cutting head 10. As will be seen from Figure 2, the set screw 16, supply passage 22 and threaded bore 24 are physically uncomplicated, thereby making them very easy and low cost to machine, resulting in a simple, low cost nozzle assembly 12. To assemble the nozzle assembly 12 to cutting head 10, nozzle assembly 12 is screwed into head 10 from the exterior of head 10 by applying a drive tool to drive recess 36 of set screw 16; the chamfer 46 on sleeve 20 aiding in insertion of the oversize sleeve 20 into supply passage 22. Thus, assembly, even in the field is fast, easy, fool proof and requires only a common tool such as an allen wrench or screwdriver. Removal is just as easy and only requires the set screw 16 to be backed out. Then the sleeve 20 and nozzle 18, which are inexpensive enough to be considered throw-away items; are blown out ofthe supply passage 22 by pressurising the fluid therein, although they could be caught and saved for examination, repair or possible re-use, if desired. In operation, supply passage 22 is connected to any suitable source of working fluid at the desired operating pressure. The working fluid forces the flat surfaces 42,32 of nozzle 18 and second snout 30 tightly together, forming a seal therebetween. The working fluid also bears against the upstream end 44 of sleeve 20, thereby tending to force sleeve 20 downstream until sleeve 20 seats and seals against shoulder 31. Once stopped by shoulder 31, the sleeve 20 then tends to swell radially, both inwardly and outwardly, thereby firmly sealing against nozzle supply passage 22, second snout 30, and nozzle 18. It is important to note that the seals between sleeve 20 and shoulder 31, nozzle 18, second snout 30 and passage 22 grow tighter and more effective as the working fluid pressure increases. Since the sleeve 20 tends to flow plastically under the working pressure, it will seal effectively even if the surfaces it contacts are scratched or irregular. In time, sleeve 20 will tend very gradually to flow through the very small clearance between first snout 28 and supply passage 22, but since such flow would be very slow, and since the upstream end 44 of sleeve 20 was chosen to extend past nozzle 18, sleeve 20 has a longitudinal length sufficient to compensate for any such downstream flow during the design life of nozzle assembly 12. Increased design life is easily achieved by either making sleeve 20 thicker, longer, or from a material which flows less under pressure than UHMW-PE or by reducing the clearance between first snout 28 and passage 22. The embodiment of Figure 3, is identical to that shown in Figure 2 except as described below, and so that same parts are referredto by the same reference numerals but with a prime appended thereto. In this embodiment , a chamfer 50 has been provided on an enlarged snout 28'. Thus, as the set screw 16' is screwed into cutting head 10', the chamfer 50 of first snout 28' engages corner 52 on passageway 22' so preventing any tendency of sleeve 20' to flow downstream under working pressure past corner 52 of passage 22'. Alternatively, a chamfer could be provided at the upstream end of threaded bore 24, and first snout 28 could be enlarged and have a square corner 33 adapted to engage such a chamfer when set screw 16 is tightened down to achieve the same end. Since fluid flow is from the top to the bottom in Figures 2 and 3 references in the foregoing to "upstream and "downstream" indicate flow towards the top and the bottom respectively. The above described embodiments could be easily modified to make a leak-proof plug for passageway 22. This is doen by simply eliminating bore 34,34' in set screw 16,16' and by eliminating nozzle 18,18'.

Claims: CLAIMS: 1. A fluid cutting jet nozzle assembly for a housing means defining a nozzle supply passageway, comprising: a) jet forming means for forming a fluid cutting jet b) nozzle body means, defining a bore through which the cutting jet is adapted to pass, a first snout means adapted to be snugly received in and extend upstream in the fluid supply passageway, a second snout means extending upstream from the first snout means and atleast partly of smaller diameter than the first snout means, the second snout means having a surface adapted to seat the jet forming means, and a shoulder means defined by the upstream end of the first snout means; c) sealing means at least substantially encircling the second snout means upstream from the shoulder means; d) mounting means for mounting the nozzle body means in the nozzle supply passageway; ; wherein the sealing means are sized to make a snug seal between the passageway and the nozzle body means when the nozzle body means are mounted in the passageway means, and wherein the sealing means tends to flow downstream towards the shoulder means under working pressure and expand radially inwardly and outwardly under working pressure to increase the firmness of the seal as the working pressure increases. 2. An assembly according to claim 1, wherein the assembly is mounted to the housing means from the exterior of the housing means. 3. An assembly according to claim 1 or claim 2, wherein the sealing means snugly grips the jet forming means and second snout means to hold the jet forming means and second snout means in an assembled relation even when the assembly is not mounted in the housing means. 4. An assembly according to any one of claims 1 to 3, wherein the passageway defines a corner, and wherein the first snout defines a chamfer which is sized to firmly contact the corner when the nozzle assembly and housing means are assembled, to prevent downstream flow of the sealing means between the corner and the chamfer under pressure. 5. A leak-proof insert for forming a seal within a fluid passageway, comprising: a) insert body means, defining a first snout means adapted to be snugly received in and extend upstream in the passageway, a second snout means extending upstream from the first snout means and at least partly of smaller diameter than the first snout means, and a shoulder means defined by the upstream end of the first snout means; b) sealing means at least substantially encircling the second snout means upstream from the shoulder means; and c) mounting means for mounting the insert body means in the passageway; wherein the sealing means are sized to make a snug seal between the passageway and the insert body means when the insert body means are mounted in the passageway, and wherein the sealing means tends to flow downstream towards the shoulder means under working pressure and expand radially inwardly and outwardly under working pressure to increase the firmness of the seal as the working pressure increases. 6. An insert according to claim 5 and which is in the form of a plug for the passageway. 7. An insert according to claim 5 and in the form of a nozzle assembly including jet forming means for forming a fluid jet, the insert body defining a bore through which the fluid jet is adapted to pass and the second snout thereof having a surface adapted to seat the jet forming means.

Inventors: O'HANLON, THOMAS A.
Applicants: FLOW INDUSTRIES INC.
Application year: 1984
Main classification: F16J15
IPC codes: B05B17, E21B10, B26F3, F16J15