Patent Application
20100242718
Utilization of a hydraulic fluid to actuate a device or system is nearly as old as engineering itself The use of hydraulics allows for the relatively easy application of a first force in one location to be transferred to a remote location, to be translated into a higher or lower force using differential area, etc. In general hydraulic actuation is often fairly well controlled either by pressure control alone or through the use of a metering configuration such as a spool valve. In most conditions these types of control are reliable and hence hydraulic actuation is relied upon in many industries.
Although actuation of devices hydraulically can be fairly well controlled under most conditions, significant changes in ambient conditions such as temperature and/or high actuation pressures can render control less reliable and can have noticeable effects on the actuation process including the volume of hydraulic fluid required for completion of the intended movement. This can be especially true in devices or systems requiring actuation pressures in the hundreds or thousands of pounds per square inch (PSI) of pressure. These kinds of conditions and systems situations can be difficult to precisely control. Since precision control is sometimes very important to a particular type of actuation and because hydraulic actuation is a likely consideration is countless applications, the art is always interested in alternatives that improve precision control.
A hydraulic actuation system includes a metering valve; and a piston arrangement hydraulically in parallel with the metering valve, the system configured to preferentially move the piston to precharge an end device with hydraulic fluid prior to supplying an actuation fluid volume to the end device.
A method for actuating a hydraulic end device includes pressuring a control line with parallel hydraulic access to a metering valve and a floating piston arrangement; stroking a piston of the piston arrangement if the piston arrangement is in a position that allows stroking; and stroking the metering valve after the piston arrangement is in a position that prevents further stroking of the piston.
Referring now to the drawings wherein like elements are numbered alike in the several Figures:
Referring to
In some systems, a fluid metering valve such as a spool valve 12, for example, is used to meter a specific amount of hydraulic fluid for a particular desired actuation, which may be a complete actuation in itself or may be an incremental actuation of a system. While other metering components are contemplated herein, a spool valve is an illustrative component to enhance understanding of the system being disclosed. Generally, spool valves do not contain any seals and instead use a tight tolerance labyrinth to inhibit fluid flow past the spool of the spool valve. Inherent in all spool valves so configured is a by-pass flow rate that passes around the spool within the spool valve. The rate is dependent upon fluid properties and in most applications can be managed relative to the time and displacement of the spool travel such that the total by-pass fluid volume is negligible relative to the volume of the fluid displaced by the traveling spool. However, in applications subject to large temperature changes where the fluid viscosity changes significantly, the by-pass flow can become significant. Generally the spool valve's by-pass flow rate (Df) is inversely proportional to the viscosity (v) and proportional to the diametrical clearance (d) to the third power or Df˜(d̂3)/v. The equation makes clear that a viscosity change of any significant amount will herald a significant change in by-pass flow rate and thereby a reduction in effective precision of metered fluid. The system 10 addresses these issues to substantially improve precision of actuation in hydraulic systems and particularly those experiencing largely changing temperature and pressure environments.
Temperature accommodation of the system 10 is directed to addressing the proportionality of the change in by-pass flow to the change in temperature by automatically adjusting a diametrical clearance between a spool 14 and a sleeve 16 of a spool valve 12. Because the by-pass flow rate is proportional to the diametrical clearance to the third power, relatively small changes in that clearance are required to offset large changes in the viscosity.
To achieve changes in the diametrical clearance between the spool 14 and the sleeve 16, the spool is configured with a dissimilar coefficient of thermal expansion to that of the rest of the valve 12. Upon exposure to temperature that acts upon the spool valve 12, the spool 14 expands at a greater rate than the rest of the valve 12. Accordingly, the diametrical clearance between the spool 14 and the sleeve 16 necessarily is reduced so that a relatively constant by-pass flow rate across the temperature range is maintained in the valve 12. In one embodiment the spool is fabricated from Inconel metal with a coefficient of thermal expansion of 7.22×10̂6 in/in/F and the sleeve 16 that it travels within is fabricated from 440 C metal with a coefficient of thermal expansion of 5.56×10̂6 in/in/F. Hence as the temperature of the system increases the spool 14 expands more than the sleeve 16 and the diametrical clearance becomes smaller. As will be appreciated from the above, the tighter clearance will substantially negate the increase in fluid by-pass concomitant the reduction in viscosity of the fluid due to temperature. While Inconel and 440 C were given in the present example, one skilled in the art will recognize that other materials can be used. The materials used will be dependent upon but not limited to the initial clearance at ambient conditions, the desired by-pass flow rate, fluid material properties and range of operating pressures and temperatures. Materials include but are not limited to metals, ceramics, plastics and epoxy such as steel, stainless steel, monel, nickel alloys, tungsten, tungsten carbide, berrylium copper, copper alloys, zinc alloys, thermoplastics, thermoset plastics, alumnina and zirconia.
The second concept identified above relates to system compliance compensation. The compensation system operates hydraulically in parallel with the metering valve but does not require that the metering valve comprise a temperature accommodating construction. In operating hydraulic tools, for example a downhole flow control device 18 as schematically illustrated in
Still referring to
In another embodiment, the piston 22 may be at another position within the housing 24. In embodiments where the piston is other than at end 36, an amount of hydraulic fluid will be within the housing 24 adjacent end 28 of piston 22. This fluid is to be estimated to be a correct amount of fluid to take up compliance within the end device when subject to the conditions (temperature, pressure) where the device is expected to be actuated. In such an embodiment, the first actuation will substantially avoid compliance related reduced actuation but rather will be a substantially complete actuation increment. This is because the fluid volume within housing 24 will be preferentially squeezed back into the end device pursuant to fluid pressure in line 30. In operation, as the control line pressure 30 is increased, the pressure at the control line 30 side of the spool 14 and the pressure at the control line 30 side of the piston 22 increase simultaneously. Because the piston 22 floats, the piston imposes the pressure of the control line 30 to the actuation control line 34 such that pressures in control line 30 and control line 34 are close to the same pressure. The pressure in control line 30 is increased above the pressure in control line 34 causing movement of the piston 22, thereby re-equalizing pressures, until the piston 22 contacts end 36 of the housing 24, at which time, the end device 18, for example downhole flow control valve, is compliance compensated. The actuation pressure in control line 34 also acts on check valve 46 and prevents any fluid from moving into the spool valve 12 from the control line 34 side of the spool valve 12. In order for the spool 14 to move, the control line pressure 30 must exceed both the fluid pressure existing at the control line 34 side of the spool 14 and the a spring 40 preload. During the time that the spool is not moving, the control line pressure 30 will by-pass around the spool and maintain the pressure below the spool at the relatively same pressure as the control line pressure. This configuration ensures that the spool 14 will not begin to move until end device 18 compensation has been achieved as signaled by the piston 22 shouldering at end 36 of housing 24. Once the piston 22 shoulders and has supplied the fluid to compensate for the end device compliance, continued control line pressure increase will cause pressure at the control line 30 side of the check valve 46 to exceed the pressure at the control line 34 side of the check valve 46 creating a condition that allows the spool to deliver fluid to the end device 18. As the pressure continues to increase, the spool will begin to move and deliver the fluid to actuate the end device 18.
Having explained operation of the two concepts, the operation ofthe system 10 as illustrated in
After the increment is completed, pressure in line 30 is bled off, see
As noted above, greater precision is obtained if the thermal concept and the compliance concept are both used at the same time.
While one or more embodiments have been shown and described, modifications and substitutions may be made thereto without departing from the spirit and scope of the invention. Accordingly, it is to be understood that the present invention has been described by way of illustrations and not limitation.
