Reduced-length sleeve valve

#The present invention is directed to a multiple-opening sleeve valve of a type which can be used for flow control and pressure dissipation and in particular to a multiple opening sleeve valve having a reduced length, compared to at least some previous configurations.

#Multiple-orifice sleeve valves are used in a number of applications including flow control and pressure dissipation applications, such as applications requiring reducing a high inlet pressure to a lower maximum output pressure through a relatively wide range of flows. For example, multiple-orifice sleeve valves can be used for receiving flow in the range of 0 to 250 cubic feet per second (cfs) at a pressure of about 85 pounds per square inch (psi) or more, and outputting at a pressure maximum of 12 psi and the like. A description of one type of multiple opening sleeve valve can be found, e.g., in U.S. Pat. No. 4,508,138 issued Apr. 2, 1985, incorporated herein by reference. Some types of sleeve valves have been configured to provide desired performance while reducing cavitation, noise, wear and/or vibration leading to long service life, including, e.g. providing tapered sleeve openings and/or cavitation control. Examples include at least some devices sold under the trade name POLYJET®, available from CMB Industries, Fresno, Calif.

#Although multiple opening sleeve valves have proved useful and successful in numerous applications, it is believed there are still opportunities for providing new configurations, e.g. to assist in meeting certain needs or providing certain conveniences. At least some previous configurations of multiple-opening sleeve valves have included movable gates (or rings) and/or actuators therefor, which have led to devices which occupy a certain amount of length. The length constraints in such previous devices may lead not only to limitations on the location in which the valve can be placed, but also direct and indirect cost effects, including the size and configuration of buildings or other enclosures for the valve, the types of existing systems into which it is feasible to retrofit the valves, the weight (and thus manufacturing, storage and transportation costs) for the valve and the like. Accordingly, it would be useful to provide a multiple-orifice sleeve valve which can be provided in a reduced-length configuration (compared to at least certain previous valves) and/or which can be fabricated, shipped, installed or enclosed at reduced costs (compared to previous valves).

#FIG. 1 is a cross sectional view of a multiple-opening sleeve valve according to previous approaches;

#FIG. 2 is a cross sectional view of a multiple-opening sleeve valve according to an embodiment of the present invention; and

#FIG. 3 is a perspective view of the valve of FIG. 2.

#Before describing features of the present invention, certain aspects of a multiple opening sleeve valve according to previous approaches will be described. In the configuration of FIG. 1, an inlet housing 112 substantially surrounds a generally cylindrical sleeve member 114 having a plurality of openings or nozzles 116 extending through the wall of the sleeve in an upstream portion thereof. The downstream portion of the sleeve provides fluid communication to the valve outlet 118. An annular valve gate or ring 122 can be sealingly positioned to cover some of the nozzles 116, as shown, and can also be moved in an upstream direction 124 to cover substantially all of the nozzles 116, or a downstream direction 126 to uncover substantially all of the nozzles 116. When at least some of the nozzles 116 are uncovered, the (typically high pressure) inlet flow 128 is received through the inlet opening 132 and diverges around a nose member 134. The high pressure fluid passes through the uncovered nozzles 116 and travels 138 through the interior of the sleeve 114 to pass out the (low pressure) outlet opening 118. By moving the gate 122 so as to progressively cover 124 or uncover 126 more of the nozzles 116, the outlet flow and/or pressure can be changed. In the configuration depicted in FIG. 1, drive motors or other sources of force 142a, b can be used to rotate drive screws 144a, b which are threadingly received in and engaged with interiorly-threaded drive tubes 146a, b. The upstream ends 172a, b of the drive tubes 146a, b are closed or sealed and the fluid which flows through the valve does not enter the interior of the drive tubes 146a, b. The interior of the drive tubes 146a, b are sealed with respect to the (high pressure) fluid flow 128, 138 (e.g. via packing or other seals 148a, b) and the interior of the tubes 146a, b, as well as the drive screws 144a, b are thus external to the valve and do not contact the fluid which passes through the valve. Since the drive tubes 146a, b and drive screws 144a, b do not contact the fluid, the drive mechanism can be provided with external lubricants (oils, greases and the like), without risking contaminating the fluid with the lubricants. Many uses of control valves such as depicted in FIG. 1, require accommodating extremely high inlet pressures 128. Accordingly, the seals 148a, b must be extremely tight seals, for withstanding such high inlet pressures which, in general, provide relatively large friction resistance to movement of the tubes 146a, b past the seals 148a, b and, accordingly, relatively high torque must be provided to the drive screws 144a, b.

#In some embodiments, a fluid path 152 directly from the inlet region to the interior of the sleeve, controlled, e.g., by a valve 154 can be provided to achieve backwash-type cleaning of the nozzles. In such configurations, a groove or similar structure may be provided in or coupled to the gate 122 to receive the back flow and directed to a waste outlet, e.g., as described in U.S. Pat. No. 4,508,138, incorporated herein by reference.

#As can be seen from FIG. 1, the longitudinal distance occupied by the seal 174 contributes to the overall length of the valve. In the configuration of FIG. 1, if the gate 122 is moved upstream 124 to its extreme position (covering substantially all of the nozzles 116) the drive tube 146a must have its downstream edge 156a, b engaged with (and thus substantially aligned with) the seals 148a, b. If the gate 122 is moved in a downstream direction 126 to its extreme position (uncovering substantially all of the nozzles 116) the downstream edge 156a, b of the drive tube 146a, b must move a distance equal to the longitudinal extent of the gate movement, i.e., to the longitudinal extent of the nozzle area of the sleeve 166 which, in general, will be approximately equal to the sleeve diameter 168. Therefore, the valve according to FIG. 1 is configured such there is sufficient space between the seals 148a, b and the upstream edges 168a, b of the motor or drive assemblies 142a, b to accommodate a longitudinal movement of the drive tubes 146a, b substantially equal to the nozzle region 166 (and thus approximately equal to the sleeve diameter 168).