System and method for calibrating hydraulic starters for turbomachinery.

Abstract

A system and method for calibrating hydraulic starters for turbomachinery are provided. [Solution] A system and method for calibrating a hydraulic starter for turbomachinery are provided. A hydraulic fluid source supplies fluid at high or low pressure to rotationally drive the hydraulic starter, and a valve is movable to regulate the flow rate of fluid supplied from the hydraulic fluid source to the hydraulic starter. The operation of the hydraulic fluid source and the valve is automatically controlled by a computing system to sequentially execute a plurality of basic modes with the valve in either the fully closed or fully open position. The plurality of basic modes include at least one standby mode test and at least one crank speed mode test. The rotational speed of the turbomachinery detected by a speed sensor during each of the plurality of basic modes is monitored by the computing system to calibrate the hydraulic starter.

Description

Technical Field

[0001] The present disclosure generally relates to a hydraulic starter for a turbomachine. Specifically, the present disclosure relates to calibrating a hydraulic starter for a turbomachine.

Background Art

[0002] Turbomachines are used in various industries and applications for energy transfer purposes. For example, a gas turbine engine generally includes a compressor section, a combustion section, a turbine section, and an exhaust section. The compressor section gradually increases the pressure of the working fluid entering the gas turbine engine and supplies the compressed working fluid to the combustion section. The compressed working fluid and fuel (e.g., natural gas) are mixed within the combustion section and burned within the combustion chamber to generate high-pressure and high-temperature combustion gases. The combustion gases flow from the combustion section into the turbine section, where they expand to generate work. For example, the expansion of the combustion gases within the turbine section can rotate a rotor shaft connected to a generator to generate electricity. The combustion gases are then discharged from the gas turbine through the exhaust section.

[0003] Gas turbine engines can utilize a hydraulic starter to provide power to accelerate the engine to its initial speed before fuel ignition occurs, and ignition generates and imparts additional thermal energy to bring the gas turbine engine to the desired speed without further assistance from the starter. However, if the hydraulic starter is not properly calibrated, air for ignition of the gas turbine engine may not be purged adequately during cranking, if the hydraulic starter torque exceeds the expected torque during cranking, gas turbine engine components may be damaged, and / or if the starter speed is too high or too low while idle, the gas turbine engine may not be cooled properly. However, it is difficult for operators to identify insufficient calibration across different modes when operating a gas turbine engine. Furthermore, inexperienced operators may not know what variations are acceptable for each mode.

[0004] Therefore, a system and method for calibrating a hydraulic starter for turbomachinery would be welcome in the art. [Overview of the project]

[0005] Some aspects and benefits of this disclosure are described in part in the following description, may become apparent from the description, or may be learned through the practice of this technology.

[0006] In one embodiment, the subject matter relates to a system for calibrating a hydraulic starter for turbomachinery. The system may include a hydraulic fluid source capable of supplying fluid at high or low pressure. The system may further include a hydraulic starter that is rotationally driven by the fluid from the hydraulic fluid source. Furthermore, the system may include a flow valve fluid-coupled between the hydraulic fluid source and the hydraulic starter, the flow valve may be movable between a plurality of positions, including a fully closed position and a fully open position, to adjust the flow rate of the fluid supplied from the hydraulic fluid source to the hydraulic starter, the flow rate being lowest when the flow valve is in the fully closed position, and the flow rate being highest when the flow valve is in the fully open position. Furthermore, the system may include a speed sensor configured to detect the rotational speed of the turbomachinery. In addition, the system may include a computing system. The computing system may be configured to receive requests to perform an automated diagnostic run of the hydraulic starter. The computing system may further be configured to control the operation of the hydraulic fluid source and the flow valve to perform an automated diagnostic run based on at least a portion of the requests. The automated diagnostic operation may include automatically executing a plurality of basic modes sequentially, the flow valve may be in either the fully closed or fully open position in the plurality of basic modes, and the plurality of basic modes may include at least one standby mode test and at least one crank speed mode test. The flow valve may be in the fully closed position for each of the at least one standby mode tests, and the flow valve may be in the fully open position for each of the at least one crank speed mode tests. The computing system may be further configured to monitor the rotational speed of the turbomachinery during each of the plurality of basic modes.

[0007] In a further embodiment, the subject matter relates to a method for calibrating a hydraulic starter for turbomachinery. A hydraulic fluid source may be operable to supply fluid at high or low pressure to rotationally drive the hydraulic starter, and a flow valve may be fluidly coupled between the hydraulic fluid source and the hydraulic starter. The flow valve may be movable between a plurality of positions, including a fully closed position and a fully open position, to adjust the flow rate of the fluid supplied from the hydraulic fluid source to the hydraulic starter, the lowest flow rate may be when the flow valve is in the fully closed position, and the highest flow rate may be when the flow valve is in the fully open position. The method may include receiving a request by a computing system to perform an automated diagnostic run of the hydraulic starter. The method may further include the computing system automatically controlling the operation of the hydraulic fluid source and the flow valve to perform an automated diagnostic run based on at least a portion of the request, the automated diagnostic run may include sequentially performing a plurality of basic modes. The flow valve may be in either the fully closed position or the fully open position in the plurality of basic modes. The multiple basic modes may include at least one standby mode test and at least one crank speed mode test, the flow valve may be in the fully closed position for each of the at least one standby mode tests and the flow valve may be in the fully open position for each of the at least one crank speed mode tests. In addition, the method may include monitoring the rotational speed of the turbomachinery detected by a speed sensor during each of the multiple basic modes by a computing system.

[0008] In additional embodiments, the subject matter relates to a method for calibrating a hydraulic starter for turbomachinery. A hydraulic fluid source may be operable to supply fluid at high or low pressure to rotatably drive the hydraulic starter, while a flow valve may be fluid-coupled between the hydraulic fluid source and the hydraulic starter, and the flow valve may be movable to adjust the flow rate of fluid supplied from the hydraulic fluid source to the hydraulic starter. The flow rate may be lowest when the flow valve is in the fully closed position, and the flow rate may be highest when the flow valve is in the fully open position. The method may include, by means of a computing system, automatically controlling the operation of the hydraulic fluid source and the flow valve to sequentially perform standby mode tests and crank speed mode tests, wherein the flow valve may be in the fully closed position for the standby mode test and the flow valve may be in the fully open position for the crank speed mode test. The method may further include, by means of a computing system, monitoring the standby rotational speed of the turbomachinery during the standby mode test and the crank rotational speed of the turbomachinery during the crank speed mode test. In addition, the method may include, by means of a computing system, automatically controlling the operation of the hydraulic fluid source and the flow valve to perform a medium-speed crank calibration when the standby rotational speed is within the standby speed range and the crank rotational speed is within the crank speed range, thereby determining the medium-speed crank position of the flow valve. The rotational speed of the turbomachinery may be within the medium-speed range when the hydraulic fluid source supplies fluid at high pressure and the flow valve is in the medium-speed crank position.

[0009] These and other features, aspects, and advantages of the present invention will be better understood by referring to the following description and the appended claims. The appended drawings incorporated herein and constituting part thereof, together with the description, illustrate embodiments of the art and help to illustrate the principles of the art.

[0010] A complete and effective disclosure of the present invention, including best modes of fabrication and use of the system and method intended for those skilled in the art, is described herein with reference to the accompanying figures. [Brief explanation of the drawing]

[0011] [Figure 1] This is a schematic diagram of a turbomachinery according to an aspect of the present disclosure. [Figure 2] This is a schematic diagram of a system for calibrating a hydraulic starter for turbomachinery according to an aspect of the present disclosure. [Figure 3A] A flowchart of a control algorithm for calibrating a hydraulic starter for turbomachinery, according to an aspect of this disclosure, is shown. [Figure 3B] A flowchart of a control algorithm for calibrating a hydraulic starter for turbomachinery, according to an aspect of this disclosure, is shown. [Figure 3C] A flowchart of a control algorithm for calibrating a hydraulic starter for turbomachinery, according to an aspect of this disclosure, is shown. [Figure 3D] A flowchart of a control algorithm for calibrating a hydraulic starter for turbomachinery, according to an aspect of this disclosure, is shown. [Figure 3E] A flowchart of a control algorithm for calibrating a hydraulic starter for turbomachinery, according to an aspect of this disclosure, is shown. [Figure 3F] A flowchart of a control algorithm for calibrating a hydraulic starter for turbomachinery, according to an aspect of this disclosure, is shown. [Figure 3G] A flowchart of a control algorithm for calibrating a hydraulic starter for turbomachinery, according to an aspect of this disclosure, is shown. [Figure 3H] A flowchart of a control algorithm for calibrating a hydraulic starter for turbomachinery, according to an aspect of this disclosure, is shown. [Figure 4A] Examples of data for calibrated hydraulic starter components in different operating modes of the hydraulic starter, according to aspects of this disclosure, are shown. [Figure 4B] Examples of data for calibrated hydraulic starter components in different operating modes of the hydraulic starter, according to aspects of this disclosure, are shown. [Figure 5] A flowchart of one method for calibrating a hydraulic starter for turbomachinery according to an aspect of this disclosure is shown. [Figure 6]A flowchart of a further method for calibrating a hydraulic starter for turbomachinery according to an aspect of this disclosure is shown.

[0012] The repeated use of reference numerals in this specification and in the drawings is intended to represent the same or similar features or elements of the Art. [Modes for carrying out the invention]

[0013] Embodiments of the present invention are described in detail below, with one or more examples of these being shown in the drawings. Each example is provided for illustrative purposes of the present art and is not intended to limit the present art. Indeed, it will be apparent to those skilled in the art that modifications and changes can be made in the present art without departing from the scope or spirit of the claimed art. For example, features illustrated or described as part of one embodiment can be used together with another embodiment to give rise to further embodiments. Thus, this disclosure is intended to encompass such modifications and changes within the scope of the appended claims and their equivalents.

[0014] The term “exemplary” is used herein to mean “serving as an example, case, or illustration.” Any implementation described herein as “exemplary” is not necessarily construed as being preferable or advantageous to other implementations. In addition, unless otherwise specified, all embodiments described herein should be considered exemplary.

[0015] Detailed descriptions use numerals and letters to refer to features in the drawings. Similar or identical reference numerals in the drawings and descriptions are used to refer to similar or identical parts of the invention. Where used herein, the terms “first,” “second,” and “third” may be used interchangeably to distinguish one component from another and are not intended to indicate the location or importance of any individual component.

[0016] The term "fluid" can be a gas or a liquid. The term "fluid communication" means that a fluid can make a connection between specified regions.

[0017] As used herein, the terms "upstream" (or "forward") and "downstream" (or "rearward") refer to relative directions with respect to the flow of fluid in a fluid path. For example, "upstream" refers to the direction from which the fluid flows, and "downstream" refers to the direction in which the fluid flows. However, the terms "upstream" and "downstream" used herein may also refer to the flow of electricity. The term "radially" refers to a relative direction that is substantially perpendicular to the axial centerline of a particular component, the term "axially" refers to a relative direction that is substantially parallel to and / or coaxially aligned with the axial centerline of a particular component, and the term "circumferentially" refers to a relative direction that extends around the axial centerline of a particular component.

[0018] Approximating terms such as "about", "approximately", "generally", and "substantially" are not limited to the exact values specified. In at least some cases, the language indicating approximation may correspond to the accuracy of the equipment for measuring the value, or the accuracy of the method or machine for constructing or manufacturing components and / or systems. In at least some cases, the language indicating approximation may correspond to the accuracy of the equipment for measuring the value, or the accuracy of the method or machine for constructing or manufacturing components and / or systems. For example, the language indicating approximation may refer to being within a margin of 1, 2, 4, 5, 10, 15, or 20 percent at any of the individual values, ranges of values (if any), and / or endpoints defining ranges of values (if any). When used in the context of an angle or direction, such terms include ranges that are 10 degrees greater or less than the described angle or direction. For example, "generally perpendicular" includes directions within a range of 10 degrees in either direction, clockwise or counterclockwise, from perpendicular.

[0019] Terms such as "coupled", "fixed", and "attached" refer to both direct coupling, fixing, or attachment and indirect coupling, fixing, or attachment through one or more intermediate components or features, unless otherwise specified herein. As used herein, the terms "comprises", "comprising", "includes", "including", "has", "having" or any other variation thereof are intended to cover non-exclusive inclusion. For example, a process, method, article, or apparatus that includes a list of features is not necessarily limited to only those features, and may include other features not explicitly listed or inherent to such process, method, article, or apparatus. Further, unless explicitly stated to the contrary, "or" refers to an inclusive logical disjunction and not an exclusive logical disjunction. For example, the condition A or B is satisfied by any one of the following: A is true (or present) and B is false (or absent), A is false (or absent) and B is true (or present), and both A and B are true (or present).

[0020] Here, and throughout the specification and claims, ranges are combined and replaced, and unless the context and language specifically dictate otherwise, such ranges are identified and include all sub-ranges subsumed therein. For example, all ranges disclosed herein include endpoints, and the endpoints are combinable independently of each other.

[0021] As used herein, the term "fluidly coupled" may refer to any suitable combination of pipes, hoses, tubes, or other fluid conveyance conduits for transferring fluid between components.

[0022] In general, this subject concerns systems and methods for calibrating hydraulic starters for turbomachinery. More specifically, a hydraulic starter may be capable of operating in multiple basic modes depending on the required torque output. For example, the fluid source of the hydraulic starter may be capable of supplying fluid at high or low pressure, and the flow valve of the hydraulic starter may be capable of regulating the flow rate of fluid supplied from the fluid source to the starter motor of the hydraulic starter, such that different combinations of output torque and output speed of the starter motor can be established in different basic modes. For example, the basic modes may include standby modes such as a low-speed standby mode and a high-speed standby mode, and crank modes such as a low-speed crank mode and a high-speed crank mode. The fluid source supplies fluid at low pressure in the low-speed mode and at high pressure in the high-speed mode, and the flow valve is in the fully closed position in the standby mode and in the fully open position in the basic crank mode. If one or more components of a hydraulic starter are improperly calibrated and / or partially or completely faulty, air for ignition may not be adequately purged during turbomachinery cranking, and if the hydraulic starter torque exceeds the expected torque during cranking, turbomachinery components may be damaged and / or the turbomachinery may not be properly cooled. However, it is difficult for the operator to identify insufficient calibration across different operating modes of the hydraulic starter when operating the turbomachinery.

[0023] Therefore, according to embodiments of this subject, a method is proposed for calibrating a hydraulic starter while a turbomachinery is not in operation. The method includes automatically controlling the hydraulic starter to sequentially execute a plurality of basic operating modes, while monitoring the rotational speed of the turbomachinery (or starter motor) detected by a speed sensor in each of the basic operating modes. Based on the monitored rotational speed for each basic operating mode, the operator can make a more informed decision about the calibration status of the hydraulic starter before further calibrating the hydraulic starter. In some cases, the method may further include automatically controlling the hydraulic starter to perform a medium-speed crank calibration when it is determined that a basic operating mode is to be calibrated.

[0024] Referring next to the drawings, Figure 1 shows a schematic diagram of one embodiment of a turbomachinery, which in the illustrated embodiment is a gas turbine 10. The gas turbine 10 may be an industrial or onshore gas turbine, but this disclosure is not limited to onshore and / or industrial gas turbines. Furthermore, the present invention as described herein may use any suitable type of turbomachinery, including but not limited to steam turbines, aircraft gas turbines, or marine gas turbines.

[0025] As shown in the figure, the gas turbine 10 generally includes an inlet section 12, a compressor section 14 located downstream of the inlet section 12, a number of combustors (not shown) in a combustor section 16 located downstream of the compressor section 14, a turbine section 18 located downstream of the combustor section 16, and an exhaust section 20 located downstream of the turbine section 18. In addition, the gas turbine 10 may include one or more shafts 22 coupled between the compressor section 14 and the turbine section 18.

[0026] The compressor section 14 may generally include a plurality of rotor disks 24 (one of which is illustrated) and a plurality of rotor blades 26 connected to each rotor disk 24, extending radially outward from each rotor disk 24. Each rotor disk 24 may then be coupled to or form part of a shaft 22 extending through the compressor section 14. The compressor section 14 may further include one or more stator vanes (not shown) arranged circumferentially around the shaft 22. The stator vanes may be fixed to a compressor casing or static casing extending circumferentially around the rotor blades 26.

[0027] The turbine section 18 may generally include a plurality of rotor disks 28 (one of which is illustrated) and a plurality of rotor blades 30 interconnected with each rotor disk 28, extending radially outward from each rotor disk 28. Each rotor disk 28 may then be coupled to or form part of a shaft 22 extending through the turbine section 18. The turbine section 18 further includes a turbine casing 31 that circumferentially surrounds the portion of the shaft 22 and the rotor blades 30, thereby at least partially defining a hot gas path 32 through the turbine section 18. The turbine casing 31 may be configured to support a plurality of stationary nozzles (not shown) extending radially inward from the inner circumference of the turbine casing 31.

[0028] During operation, a working fluid such as air flows into the compressor section 14 through the inlet section 12, where the air is gradually compressed, and thus pressurized air is delivered to the combustors of the combustor section 16. The pressurized air is mixed with fuel and burned in each combustor to produce combustion gases 34. The combustion gases 34 flow from the combustor section 16 into the turbine section 18 through the hot gas path 32, where energy (kinetic and / or thermal energy) is transferred from the combustion gases 34 to the rotor blades 30, causing the shaft 22 to rotate. The mechanical rotational energy can then be used to provide torque as a mechanical drive (for example, to power the compressor section 14, to drive the propulsion of a ship, etc.) and / or to generate electricity. The combustion gases 34 exiting the turbine section 18 can then be exhausted from the gas turbine 10 through the exhaust section 20.

[0029] In addition, a hydraulic starter 50 is provided for use with the gas turbine 10, as will be described in more detail below. More specifically, the hydraulic starter 50 may be used to power the gas turbine 10 to an initial speed before fuel ignition occurs within the gas turbine 10. Although the hydraulic starter 50 is described as being selectively driven by a hydraulic fluid flow, it should be understood that the hydraulic starter 50 may be selectively powered by any suitable compressible or pressurized liquid such as air or a hydraulic fluid (e.g., lubricant, oil, etc.).

[0030] Referring next to Figure 2, a schematic diagram of a system 100 for calibrating a hydraulic starter for turbomachinery, such as a hydraulic starter 50 for a gas turbine 10, according to an aspect of the present disclosure. As shown in the figure, the system 100 includes a turbomachinery 10, a hydraulic starter 50, and a computing system 102. The hydraulic starter 50 is, in particular, part of a hydraulic starter system 52 which includes the hydraulic starter 50 and a hydraulic fluid source 54, the hydraulic fluid source 54 being controllable to drive the hydraulic starter 50. More specifically, the hydraulic starter 50 may have one or more components (e.g., rotors) that are rotationally driven by a fluid supplied from the hydraulic fluid source 54 and configured to rotate the output shaft 50A of the hydraulic starter 50 (directly or indirectly via a gearbox). The output shaft 50A may be selectively and rotatably coupled to or connectable to the shaft of the turbomachinery 10 (e.g., the input shaft 22) such that the output shaft 50A of the hydraulic starter 50 and the shaft 22 of the turbomachinery 10 rotate in cooperation to raise the shaft 22 of the turbomachinery 10 to a speed for ignition.

[0031] The hydraulic fluid source 54 may be operable to supply fluid at multiple pressures, such as high and low pressure. For example, in some embodiments, the hydraulic fluid source 54 includes a pump 56 driven by a pump motor 58 to guide fluid from a reservoir 60 to a hydraulic starter 50. In one embodiment, the pump 56 may be variably driven by the pump motor 58 to supply fluid at different pressures. However, in some cases, the pump 56 may be driven by the pump motor 58 at a substantially constant operating speed to supply fluid. In such cases, the pump 56 includes a high-pressure port 56H and a low-pressure port 56L, where the fluid exiting the pump 56 through the high-pressure port 56H is supplied at high pressure, and the fluid exiting the pump 56 through the low-pressure port 56L is supplied at low pressure, with the high pressure being higher than the low pressure. The hydraulic fluid source 54 may further include a supply actuator 62 for controlling the supply of fluid through the high-pressure port 56H or the low-pressure port 56L. For example, the supply actuator 62 may be a solenoid-operated valve that can be actuated to guide fluid through the high-pressure port 56H and the low-pressure port 56L, or to close the pump 56 (for example, if the fluid is not guided through either the high-pressure or low-pressure port 56H, 56L). However, in some cases, the supply actuator 62 may be any other suitable actuator for selecting the high-pressure port 56H or the low-pressure port 56L.

[0032] The flow rate of the fluid supplied from the hydraulic fluid source 54 can be regulated by a flow valve 64 fluid-coupled between the hydraulic fluid source 54 and the hydraulic starter 50. For example, the flow valve 64 may be movable between multiple positions, including a fully closed position and a fully open position, to regulate the flow rate of the fluid supplied from the hydraulic fluid source 54 to the hydraulic starter 50. The flow rate is lowest when the flow valve is in the fully closed position and highest when the flow valve is in the fully open position. The flow valve 64 may be a solenoid-operated proportional control valve movable to a fully closed position, a fully open position, or any position between the fully closed and fully open positions (as shown in the figure), and the flow rate supplied through the flow valve 64 is proportional to the distance between the fully closed and fully open positions (for example, proportional between the lowest and highest flow rates). However, the flow valve 64 may be any other suitable type of valve having any suitable number of positions.

[0033] Generally, the hydraulic starter system 52 may be controlled to perform various different startup modes of the turbomachinery 10 in order to provide the turbomachinery 10 with different combinations of speed and torque. For example, different startup modes may include several basic modes, such as at least one standby mode (e.g., a low-speed standby mode, a high-speed standby mode, etc.) and at least one start mode (e.g., a low-speed start mode, a high-speed start mode, etc.). In each standby mode, the supply actuator 62 is controlled to supply fluid from the pump 56 (e.g., via the high-pressure port 56H in the case of the high-speed standby mode, or via the low-pressure port 56L in the case of the low-speed standby mode), but the flow valve 64 is configured to move to the fully closed position so that little or no hydraulic fluid is supplied to the hydraulic starter 50 (e.g., so that fluid is supplied to the hydraulic starter 50 at the lowest flow rate). Thus, the hydraulic starter 50 is configured to be ready to rotate in standby mode, but either not rotate or rotate at a very slow speed. Conversely, in each basic start-up mode, the supply actuator 62 is similarly controlled to supply fluid from the pump 56 (for example, via the high-pressure port 56H in the high-speed standby mode, or via the low-pressure port 56L in the low-speed standby mode), but the flow valve 64 is configured to be moved to the fully open position so that substantially all of the hydraulic fluid from the pump 56 is supplied to the hydraulic starter 50 (for example, so that the fluid is supplied to the hydraulic starter 50 at the highest flow rate). Thus, the hydraulic starter 50 rotates in each start-up mode, but is configured to rotate at a higher speed in the high-speed crank mode than in the low-speed crank mode. The rotational speed of the turbomachinery can be monitored by a sensor 66. The sensor 66 may be any suitable rotational speed sensor or combination of sensors, such as a rotary encoder(s), positioned at any suitable location to determine the rotational speed of at least one component of the turbomachinery 10, such as the shaft 22, rotor disc 24, and / or rotor disc 28, and / or the rotational speed of at least one component of the hydraulic starter 50, such as the output shaft 50A.

[0034] However, it is often difficult for the operator to determine where a fault has occurred in the hydraulic starter system 52 across different modes. Therefore, as will be described in more detail below, the hydraulic starter system 52 may be controlled by the computing system 102 to perform calibration, with one or more corresponding test modes for basic test modes (e.g., low-speed standby mode test, high-speed standby mode test, low-speed start mode test, and high-speed start mode test) being automatically executed sequentially. Based on the rotational speed of the turbomachinery 10 (e.g., shaft 22, rotor disc 24, and / or rotor disc 28) detected in each of the basic test modes, the computing system 102 may identify whether any of the modes is not properly calibrated. If all modes are properly calibrated, the computing system 102 may control the hydraulic starter system 52 to perform an automatic calibration procedure for an additional mode (e.g., medium-speed crank mode).

[0035] It should be understood that the computing system 102 may be any suitable controller or combination of controllers, and may generally include a control circuit having one or more processors 104 coupled to memory 106. The processors 104(or more) may include any suitable processing devices(or more) (e.g., control circuits, processor cores, microprocessors, application-specific integrated circuits, field-programmable gate arrays, controllers, microcontrollers, etc.) and may be one or more operably connected processors. The memory 106 may include one or more non-temporary computer-readable storage media, such as RAM, ROM, EEPROM, EPROM, one or more memory devices, flash memory devices, etc., and combinations thereof. The memory 106 may store information and data 108 that can be accessed by the processors 104(or more). For example, the memory 106 (e.g., one or more non-temporary computer-readable storage media, memory devices) may include computer-readable instructions 110 that can be executed by the processors 104(or more). Instruction 110 may be software, firmware, or both written in any preferred programming language, or it may be implemented in firmware or hardware. In addition, or alternatively, instruction 110 may be executed in a separate logical and / or virtual thread on the processor 104(or more). For example, memory 106 may store instruction 110 that, when executed by the processor 104(or more), causes the processor 104(or more) to perform an operation such as any of the operations and functions described herein.

[0036] The computing system 102 can communicate with various components of system 100. For example, sensors 66(or more), as well as any controllable components of the pump motor 58, supply actuator 62, flow valve 64, hydraulic starter 50 (e.g., gearbox elements), and / or any controllable components of the turbomachinery 10, can be communicatively coupled to the computing system 102. Furthermore, the computing system 102 can communicate with one or more user interfaces 68. The user interfaces 68(or more) may include one or more feedback devices (not shown), such as a display screen, speaker, and / or warning light. In addition, some embodiments of the user interfaces 68(or more) may include one or more input devices (not shown), such as a touchscreen, keypad, touchpad, knob, button, slider, switch, mouse, and / or microphone, to enable an operator to provide input to the computing system 102.

[0037] The computing system 102 receives data 108 from sensors 66(or more) (e.g., the detected rotational speed of the turbomachinery 10) and from user interfaces 68(or more) (e.g., system configuration and / or requests), and controls (e.g., modulates) the hydraulic starter system 52 and / or user interfaces 68(or more) based on at least a portion of such data 108. The computing system 102 may communicate with various components of the system via wired and / or wireless interfaces such as ultra-wideband (UWB) communication networks, wireless universal serial bus (USB) communication networks, communication networks implementing ZigBee® of ZigBee Alliance Corporation, or wireless communication modes such as general-purpose packet radio service (GPRS) networks (e.g., as shown by dashed lines).

[0038] The computing system 102 generates command instructions that generally control the operation of the hydraulic starter system 52 in order to calibrate the hydraulic starter system based on one or more algorithms stored in the data 108 and instruction 110. These algorithms may allow the computing system 102 to sequentially execute different test modes, for example, to determine whether the hydraulic starter system 52 is properly calibrated to operate within certain predetermined limits (e.g., predetermined respective speed ranges for each test mode) and / or to automatically calibrate the settings of the hydraulic starter system 52 for the medium-speed crank mode, thereby improving the reliability of the hydraulic starter system 52 and reducing the possibility of damage to the hydraulic starter system 52 and / or the turbomachinery 10.

[0039] Figures 3A to 3H show flowcharts of a control algorithm 200 for calibrating a hydraulic starter for a turbomachinery, such as the hydraulic starter 50 of a hydraulic starter system 52 for a turbomachinery 10, according to aspects of this disclosure. Generally, the control algorithm 200 is described herein as being implemented by the computing system 102 of the system 100 described above with reference to Figure 2. However, it should be understood that the various processes described below may alternatively be implemented by other computing devices or any combination of computing devices. In addition, although Figures 3A to 3H show steps or functions performed in a particular order for illustrative purposes, the calibration routines described herein are not necessarily limited to a particular order or arrangement unless expressly stated otherwise. Those skilled in the art will understand that, using the disclosures provided herein, various steps or functions of the algorithms disclosed herein can be omitted, rearranged, combined, and / or adapted in various ways without departing from the scope of this disclosure.

[0040] As shown in Figure 3A, during the calibration process initiated in (202), it may be determined in (204) whether permission is granted to continue the calibration process. In particular, in (204), it may be confirmed that the hydraulic starter 50 is stopped (e.g., the rotational speed of the turbomachinery 10 is substantially equal to 0), that the trip or stop is not active, that the flow valve 64 is in the fully closed position, and that the hydraulic starter motor (e.g., the pump motor 58) is in automatic mode and is turned off. The process waits until all the conditions in (204) have been confirmed. Once all the conditions in (204) have been confirmed, it is determined in (206) whether the operating mode is automatic. In one embodiment, the computing system 102 receives input in (206) via a user interface 68(or more) indicating a selection of manual or automatic mode. If manual mode is selected in (206), the process proceeds to (208), where manual selection of basic mode tests is enabled, and the user can then select one or more mode tests to be performed, starting from (210). However, if automatic mode is selected in (206), automatic calibration is started in (212) and the process proceeds to (214).

[0041] As shown in Figure 3B, the user can generally select between different basic modes to be tested. For example, if the user selects in (210) that the slow standby mode should be tested, the computing system 102 starts the timer in (216), enables the low-pressure port 56L in (218) (e.g., by controlling the operation of the supply actuator 62 to select the low-pressure port 56L), and starts the motor in (220) (e.g., by controlling the pump motor 58 to begin drawing fluid into the pump 56). In (222), it is determined whether the user has requested to stop the test. If no input to stop the test is received in (222) and the timer in (224) has not reached a predetermined time limit T for stopping the test, the computing system 102 continues to wait for a request to stop the test in (222) until the timer in (224) reaches the predetermined time limit T. In one example, the predetermined time limit T in (224) may be 15 minutes. However, the predetermined time limit T in (224) may be any other suitable time.

[0042] If no input to stop the test is received in (222) and a predetermined time limit T has elapsed in (224), the computing system 102 determines in (226) whether the flow valve 64 is open. If the flow valve 64 is open in (226), the computing system 102 controls the flow valve 64 to close it in (228) (for example, by controlling the solenoid of the flow valve 64 to move the flow valve 64 to the fully closed position). If the flow valve 64 is closed in (226) or closed in (228), the computing system 102 stops the motor in (230) (for example, by controlling the pump motor 58 to stop drawing fluid into the pump 56). In (232), the selected pressure port (for example, the low-pressure port for the low-pressure standby mode) is deactivated by the computing system 102 (for example, by controlling the operation of the supply actuator 62 so as not to select a port for supplying fluid from the pump 56). Subsequently, in (234), it is determined whether it has been requested that the manual mode be terminated. For example, if the operator has selected multiple basic modes for the test in (208), the manual mode returns to (210). If the operator has selected only one basic mode in step (208), or otherwise requests in (234) to terminate the manual selection for the test via the user interface 68, the process terminates in step (248).

[0043] If the slow standby mode is not selected for testing in (210) or not selected as part of the group in (208), the process proceeds to (236), where the computing system 102 determines whether the slow crank mode is selected. If the slow crank mode is selected in (236), the computing system 102 performs steps (216), (218), and (220) as described above. The computing system 102 then controls and opens the flow valve 64 in (238) (for example, by controlling the solenoid of the flow valve 64 to move the flow valve 64 to the fully open position). After opening the flow valve 64, the computing system 102 performs steps (222) to (234) as described above.

[0044] If the slow standby mode is not selected for testing in (210) or not selected as part of the group in (208), and if the slow crank mode is not selected for testing in (236) or not selected in (208), the process proceeds to (240), where the computing system 102 determines whether the fast standby mode is selected for testing. If the fast standby mode is selected in (240), the computing system 102 performs step (216) as described above, enables the high-pressure port 56H in (242) (for example, controls the operation of the supply actuator 62 to select the high-pressure port 56H for supplying fluid from the pump 56), and performs step (220) as described above before performing steps (222) to (234) as described above.

[0045] If the slow standby mode is not selected for testing in (210) or not selected as part of the group in (208), if the slow crank mode is not selected for testing in (236) or not selected in (208), and if the fast standby mode is not selected for testing in (240) or not selected in (208), the process proceeds to (244), where the computing system 102 determines whether the fast crank mode is selected for testing. If the fast crank mode is selected in (244), the computing system 102 performs steps (216), (242), and (220) as described above. The computing system 102 then controls the flow valve 64 to open it in (246) (for example, by controlling the solenoid of the flow valve 64 to move the flow valve 64 to the fully open position). After opening the flow valve 64, the computing system 102 performs steps (222) to (234) as described above.

[0046] If the low-speed standby mode is not selected for testing in (210) or not selected as part of the group in (208), if the low-speed crank mode is not selected for testing in (236) or not selected in (208), if the high-speed standby mode is not selected for testing in (240) or not selected in (208), and if the high-speed crank mode is not selected for testing in (244) or not selected in (208), it is determined that the manually selected test mode in (234) can be terminated, and the process terminates in (248).

[0047] In particular, as shown in Figures 3C to 3H, the computing system 102 may be configured to automatically control the hydraulic starter system 52 to sequentially perform different mode tests when the automatic test is started in (212) (Figure 3A). For example, starting from Figure 3C, the computing system 102 may start with the low-speed standby mode test in (214). In particular, the computing system 102 may start the first automatic timer in (250), enable the low-pressure port in (252) (for example, by controlling the operation of the supply actuator 62 to select the low-pressure port 56L for supplying fluid from the pump 56), and start the motor in (254) (for example, by controlling the pump motor 58 to begin drawing fluid into the pump 56). In (256), the computing system 102 determines whether the rotational speed of the turbomachinery 10 is within the respective speed ranges of the low-speed standby mode test. In general, since the flow valve 64 is in the fully closed position at (204) (Figure 3A), the rotational speed of the turbomachinery 10 (e.g., of the shaft 22, rotor disk 24, and / or rotor disk 28) should be close to zero or equal to zero in standby mode. Thus, each speed range in the low-speed standby mode test may be less than 30 rpm (revolutions per minute), but any other suitable limit may be used instead.

[0048] If the rotational speed of the turbomachinery 10 is outside the respective speed ranges for the low-speed standby mode test in (256), a warning is issued in (258) indicating that the low-speed standby mode test has failed. However, if the rotational speed of the turbomachinery 10 is within the respective speed ranges for the low-speed standby mode test in (256), and the first timer reaches a predetermined first threshold time T1 in (260), a flag is set in (262) indicating that the low-speed standby mode test was successful and that the low-speed standby mode has been properly calibrated. In some cases, the predetermined first threshold time T1 is 2 to 10 minutes, such as about 5 minutes. However, it should be understood that any other suitable time may be used instead.

[0049] If the computing system 102 determines in (258) that the low-speed standby mode test has failed or in (262) that it has succeeded, the computing system 102 stops the motor in (264) (for example, by controlling the pump motor 58 to stop drawing fluid into the pump 56) and starts the watchdog timer in (266). If in (268) the watchdog timer has not reached the minimum watchdog time, the computing system 102 determines in (270) whether the hydraulic starter 50 has stopped (i.e., whether the rotational speed of the turbomachinery 10 is below the stop threshold). The minimum watchdog time can be 2 to 10 minutes, such as about 5 minutes. However, the minimum watchdog time may be any other suitable time. Furthermore, in some cases, the stop threshold may be less than 30 rpm, such as 0 rpm, or may be any other suitable speed. If, before the minimum watchdog time elapses in (268), the rotational speed of the turbomachinery 10 is greater than or equal to the stop threshold (e.g., zero) in (270), the automatic calibration process ends in (272). If, when the watchdog timer reaches the minimum watchdog time in (268), the rotational speed of the turbomachinery 10 is below the stop threshold (e.g., zero) in (270), the process proceeds to (274).

[0050] As shown in Figure 3D, in (274), a high-speed standby mode test is initiated after a low-speed standby mode test has been performed. For example, the computing system 102 may start a second automatic timer in (276), enable the high-pressure port in (278) (for example, by controlling the operation of the supply actuator 62 to select the high-pressure port 56H for supplying fluid from the pump 56), and start the motor in (280) (for example, by controlling the pump motor 58 to begin drawing fluid into the pump 56). In (282), the computing system 102 determines whether the rotational speed of the turbomachinery 10 is within the respective speed ranges for the high-speed standby mode tests. Each speed range for the high-speed standby mode tests may be less than 30 rpm, but any other suitable limit may be used instead. If the rotational speed of the turbomachinery 10 is outside the respective speed ranges for the high-speed standby mode tests in (282), a warning is issued in (284) indicating that the high-speed standby mode test has failed. However, if the rotational speed of the turbomachinery 10 is within the respective speed ranges for the high-speed standby mode test in (282) and the second timer reaches a predetermined second threshold time T2 in (286), a flag is set in (288) indicating that the high-speed standby mode test was successful and the high-speed standby mode was properly calibrated. In some cases, the predetermined second threshold time T2 is 2 to 10 minutes, such as about 5 minutes. However, it should be understood that any other suitable time may be used instead. If the computing system 102 determines in (284) that the high-speed standby mode test has failed or in (288) that it has succeeded, the computing system 102 performs steps (264) to (272) as described above, but if the rotational speed of the turbomachinery 10 is below the stop threshold (e.g., zero) in (270) when the watchdog timer reaches the minimum watchdog time in (268), the process proceeds to (290).

[0051] As shown in Figure 3E, in (290), a low-speed crank mode test is started after a high-speed standby mode test has been performed. For example, the computing system 102 may start a third automatic timer in (292), enable a low-pressure port in (294) (for example, by controlling the operation of the supply actuator 62 to select a low-pressure port 56L for supplying fluid from the pump 56), and start a motor in (296) (for example, by controlling the pump motor 58 to start drawing fluid into the pump 56). In (298), the computing system 102 controls and opens the flow valve 64 (for example, by controlling the solenoid of the flow valve 64 to move the flow valve 64 to the fully open position). In (300), when the third timer reaches a third predetermined threshold time T3, in (302), the computing system 102 determines whether the rotational speed of the turbomachinery 10 is within the respective speed ranges for the low-speed crank mode test. In some cases, the predetermined third threshold time T3 is 2 to 10 minutes, such as about 5 minutes. However, it should be understood that any other suitable time may be used instead. Furthermore, it should be understood that, in general, the rotational speed range for the low-speed crank mode test may be higher than the rotational speed range for the standby mode and lower than the rotational speed range for the high-speed crank test mode. For example, each speed range for the low-speed crank mode test may be 50 rpm to 150 rpm, such as 80 rpm to 120 rpm, but any other suitable range limit may be used instead.

[0052] If the rotational speed of the turbomachinery 10 in (302) is outside the respective speed ranges for the low-speed crank mode test, a warning is issued in (304) indicating that the low-speed crank mode test has failed. However, if the rotational speed of the turbomachinery 10 in (302) is within the respective speed ranges for the low-speed crank mode test, a flag is set in (306) indicating that the low-speed crank mode test was successful and that the low-speed crank mode has been properly calibrated. If the computing system 102 determines in (304) that the low-speed crank mode test has failed or in (306) that it has succeeded, the computing system 102 controls the flow valve 64 to close in (308) (for example, by controlling the solenoid of the flow valve 64 to move the flow valve 64 to the fully closed position) and performs steps (264) to (272) as described above, but if the rotational speed of the turbomachinery 10 is below the stop threshold (e.g., zero) in (270) when the watchdog timer reaches the minimum watchdog time in (268), the process proceeds to (310).

[0053] As shown in Figure 3F, in (310), a high-speed crank mode test is started after a low-speed crank mode test has been performed. For example, the computing system 102 may start a fourth automatic timer in (312), enable a high-pressure port in (314) (for example, by controlling the operation of the supply actuator 62 to select a high-pressure port 56H for supplying fluid from the pump 56), and start a motor in (316) (for example, by controlling the pump motor 58 to start drawing fluid into the pump 56). In (318), the computing system 102 controls and opens the flow valve 64 (for example, by controlling the solenoid of the flow valve 64 to move the flow valve 64 to the fully open position). In (320), when the fourth timer reaches a fourth predetermined threshold time T4, in (322), the computing system 102 determines whether the rotational speed of the turbomachinery 10 is within the respective speed ranges for the high-speed crank mode test. In some cases, the predetermined fourth threshold time T4 is 2 to 10 minutes, such as about 5 minutes. However, it should be understood that any other suitable time may be used instead. Each speed range in the high-speed crank mode test may exceed 2000 rpm, such as exceeding 2400 rpm, but any other suitable range limit may be used instead.

[0054] If the rotational speed of the turbomachinery 10 is outside the respective speed range of the high-speed crank mode test in (322), a warning is issued in (324) indicating that the high-speed crank mode test has failed. However, if the rotational speed of the turbomachinery 10 is within the respective speed range of the high-speed crank mode test in (322), a flag is set in (326) indicating that the high-speed crank mode test was successful and that the high-speed crank mode has been properly calibrated. Once the computing system 102 determines in (324) that the high-speed crank mode test has failed or in (326) that it has succeeded, the computing system 102 performs steps (308) and (264) as described above and determines in (332) whether all the flags set for the different basic modes indicate success. If one or more of the flags set for the different basic modes that have been performed indicate failure in (332), the automatic calibration process terminates in (334). In some cases, in (334), the computing system 102 may further control the operation of the user interface 68(or more) to indicate each of the multiple basic modes with a flag indicating failure.

[0055] However, if in (332) all flags set for the different basic modes executed indicate success, the computing system 102 proceeds to steps (266) to (270) as described above, and if, in (268) the watchdog timer reaches the minimum watchdog time and the rotational speed of the turbomachinery 10 is greater than or equal to the stop threshold (e.g., zero) in (270), proceeds to step (336); if, in (268) the watchdog timer reaches the minimum watchdog time and the rotational speed of the turbomachinery 10 is less than the stop threshold (e.g., zero) in (270), proceeds to step (338).

[0056] As shown in Figure 3G, at (338), after performing a high-speed crank mode test, a medium-speed crank mode calibration is initiated. For example, the computing system 102 may start a fifth, sixth, and seventh automatic timer at (340), enable the high-pressure port at (342) (for example, by controlling the operation of the supply actuator 62 to select the high-pressure port 56H for supplying fluid from the pump 56), and start the motor at (344) (for example, by controlling the pump motor 58 to begin drawing fluid into the pump 56). At (346), the computing system 102 controls the flow valve 64 to partially open it. For example, the computing system 102 controls the solenoid of the flow valve 64 to move the flow valve 64 to a first intermediate position between a fully open position and a fully closed position, which is associated with a flow rate between the highest and lowest flow rates. For example, the first intermediate position may be associated with a flow rate equal to about 20% of the fully open flow rate. After partially opening the flow valve 64 in (346), the computing system 102 may determine in (350) whether the turbomachinery 10 has reached a stable rotational speed in (348) before the fifth timer reaches a predetermined fifth threshold time T5. It should be understood that "stable" means that the rotational speed over time has only small predetermined changes. In some cases, the predetermined fifth threshold time T5 is 2 to 10 minutes. However, it should be understood that any other suitable time may be used instead.

[0057] If the rotational speed of the turbomachinery 10 is not stable at (348) when the fifth timer reaches a predetermined fifth threshold time T5, the process proceeds to (352). However, if the rotational speed of the turbomachinery 10 is stable at (348), the process proceeds to determine whether the rotational speed of the hydraulic starter 50 is within the rotational speed range of the medium-speed crank mode. Generally, the rotational speed range for the medium-speed crank mode test is greater than the rotational speed range for the standby mode, higher than the rotational speed range for the low-speed crank test mode, and lower than the rotational speed range for the high-speed crank test mode. For example, the rotational speed range for the medium-speed crank mode may be between a minimum speed of approximately 900 rpm and a maximum speed of approximately 1100 rpm.

[0058] In (354), the computing system 102 determines whether the rotational speed of the turbomachinery 10 (e.g., the rotational speed of the shaft 22, rotor disk 24, and / or rotor disk 28) is below the minimum speed in the medium speed range. If the rotational speed of the turbomachinery 10 is below the minimum speed in the medium speed range in (354), the computing system 102 is configured to control the flow valve 64 to open further at a given rate or interval in (356), and to recheck the rotational speed of the turbomachinery 10 in (354) until the rotational speed of the turbomachinery 10 in (354) exceeds the minimum speed in the medium speed range. For example, the computing system 102 controls the solenoid of the flow valve 64 to move the flow valve 64 from a first intermediate position toward the fully open position at a given ramp-up rate. The ramp-up rate may be 0.3% to 2% per second (distance between the fully closed position and the fully open position), such as about 1% per second.

[0059] If, in (354), the rotational speed of the turbomachinery 10 exceeds the minimum speed in the medium speed range, the computing system 102 determines in (358) whether the rotational speed of the turbomachinery 10 (e.g., the rotational speed of the shaft 22, rotor disk 24, and / or rotor disk 28) exceeds the maximum speed in the medium speed range. If, in (358), the rotational speed of the turbomachinery 10 exceeds the maximum speed in the medium speed range, the computing system 102 is configured to control the flow valve 64 to further close in (360) at a given rate or interval and return to (354) until the rotational speed of the turbomachinery 10 exceeds the minimum speed in the medium speed range in (354) and falls below the maximum speed in the medium speed range in (358). For example, the computing system 102 controls the solenoid of the flow valve 64 to move the flow valve 64 toward the fully closed position (e.g., from a first intermediate position) at a given ramp-down rate. The ramp-down rate can be 0.3% to 2% per second (distance between the fully closed and fully open valve positions), such as approximately 1% per second.

[0060] If, in (358), the rotational speed of the turbomachinery 10 falls below the maximum speed in the medium speed range, the computing system 102 determines in (362) whether the rotational speed of the turbomachinery 10 (e.g., the rotational speed of the shaft 22, rotor disk 24, and / or rotor disk 28) is stable. It should be understood that “stable” is intended to mean that the rotational speed over time has only small predetermined changes. If, in (362), the rotational speed of the turbomachinery 10 is not stable, and in (364) the seventh timer has reached a predetermined seventh threshold time T7, the process proceeds to (352). In some cases, the predetermined seventh threshold time T7 is 2 to 10 minutes. However, it should be understood that any other suitable time may be used instead.

[0061] If the rotational speed of the turbomachinery 10 is stable in (362), the computing system 102 determines in (366) whether the rotational speed of the turbomachinery 10 is still within the rotational speed range for the medium-speed crank mode. If the rotational speed of the turbomachinery 10 is still within the rotational speed range for the medium-speed crank mode in (366), then in (368), the current open position of the flow valve 64 for performing the medium-speed crank mode on the turbomachinery 10 is set as the medium-speed crank mode position of the flow valve 64, and the process proceeds to (370). However, if the rotational speed of the turbomachinery 10 is not yet within the rotational speed range for the medium-speed crank mode in (366), and the sixth timer reaches a predetermined sixth threshold time T6 in (372), the process proceeds to (352). If, in (366), the rotational speed of the turbomachinery 10 is not yet within the rotational speed range of the medium-speed crank mode, and in (372), the sixth timer has not reached a predetermined sixth threshold time T6, the process returns to (354). In some cases, the predetermined sixth threshold time T6 is 10 to 20 minutes, such as about 15 minutes. However, it should be understood that any other suitable time may be used instead.

[0062] In Figure 3H, once all eligibility conditions have been tested, the automatic calibration process ends. For example, in (336), if all flags set for the different basic modes performed show success in (332) of Figure 3F, and the rotational speed of the turbomachinery 10 does not fall below the stop threshold (e.g., zero) in (270) of Figure 3F, then in (336), a warning is issued indicating that there is a problem causing the turbomachinery 10 to stop during the performed mode. In (374), all flags within the calibration process are reset for the next calibration process, and then in (376), the calibration process ends.

[0063] Similarly, if the rotational speed of the turbomachinery 10 is unstable in (350) or (364) in Figure 3G, or is not within the limits set by (372) in Figure 3G, a warning is issued in (352) in Figure 3G indicating that a problem with the medium-speed crank calibration has occurred. Furthermore, the computing system 102 controls the flow valve 64 to close in (308) (for example, by controlling the solenoid of the flow valve 64 to move the flow valve 64 to the fully closed position), and performs steps (264) to (270) as described above, and proceeds to step (374) if the rotational speed of the turbomachinery 10 is below the stop threshold (e.g., zero) in (270) when the watchdog timer reaches the minimum watchdog time in (268), or proceeds to step (336) if the rotational speed of the turbomachinery 10 is not below the stop threshold (e.g., zero) in (270) when the watchdog timer reaches the minimum watchdog time in (268).

[0064] Finally, if the medium-speed crank mode position of the flow valve 64 is successfully set at (368) in Figure 3G, the computing system 102 sets a flag at (370) indicating that the medium-speed crank mode calibration was successful and that the medium-speed crank mode was properly calibrated. The computing system 102 then controls the flow valve 64 to close at (308) (for example, by controlling the solenoid of the flow valve 64 to move the flow valve 64 to the fully closed position) and executes steps (264) to (270) as described above, but proceeds to step (374) if the rotational speed of the turbomachinery 10 is below the stop threshold (e.g., zero) at (270) when the watchdog timer reaches the minimum watchdog time at (268), or proceeds to step (336) if the rotational speed of the turbomachinery 10 is not below the stop threshold (e.g., zero) at (270) when the watchdog timer reaches the minimum watchdog time at (268).

[0065] It should be understood that by notifying of each failed mode test (e.g., (258) in Figure 3C, (284) in Figure 3D, (304) in Figure 3E, (324) in Figure 3F, (336) in Figure 3H, and / or (352) in Figure 3H), the computing system 102 may provide further recommendations to facilitate troubleshooting for each specific failed mode test. Furthermore, the operator may terminate the automated calibration process at any time. For example, if a failure flag is issued (e.g., (258) in Figure 3C, (284) in Figure 3D, (304) in Figure 3E, (324) in Figure 3F, (336) in Figure 3H, and / or (352) in Figure 3H), the operator may input a request to stop the calibration process (e.g., via the user interface 68). After a fault flag(s) is notified, the user may select manual mode in (206) of Figure 3A to troubleshoot the flagged fault mode. In some cases, manual mode selection in (206) may only be provided if an automatic calibration run has been performed at least partially.

[0066] It should be further understood that the automated diagnostic operation shown by algorithm 200 causes the computing system 102 to perform a low-speed standby mode, a high-speed standby mode after performing the low-speed standby mode, a low-speed crank mode after performing the high-speed standby mode, and a high-speed crank mode after performing the low-speed crank mode and before performing the medium-speed crank calibration mode. The low-speed standby mode has the lowest potential rotational speed, and the potential rotational speed increases in each mode of such a sequence, so such a sequence has the lowest risk of causing damage, as the operator can stop the test if there is a problem in the lower-risk mode before proceeding to a higher-risk mode. However, other preferred patterns may be used instead before performing the medium-speed crank calibration mode. For example, in one embodiment, the low-speed basic mode may be performed before the high-speed basic mode. In another embodiment, the high-speed basic mode may be performed before the low-speed basic mode.

[0067] Figures 4A and 4B show examples of data for calibrated hydraulic starter components in different operating modes of the hydraulic starter according to aspects of the present disclosure. For example, in Figure 4A, graph 400 shows the operation of the pump motor 58 by plot 402, the position of the supply actuator 62 by plot 404, the position of the flow valve 64 by plot 406, the detected rotational speed of the turbomachine 10 by plot 408, and the requested rotational speed of the turbomachine 10 by plot 410, across multiple operating modes of the hydraulic starter 50. Figure 4B shows plot 412 of the detected rotational speed of the turbomachine 10 by plot 408 versus the requested rotational speed of the turbomachine 10 by plot 410, across multiple operating modes of the hydraulic starter 50.

[0068] In Figures 4A and 4B, the multiple operating modes include a low-speed crank mode that extends between the start time ti0 and the first time ti1, a low-speed standby mode that extends between the first time ti1 and the second time ti2, a medium-speed crank mode that extends between the second time ti2 and the third time ti3, a high-speed standby mode that extends between the third time ti3 and the fourth time ti4, and a high-speed crank mode that extends between the fourth time ti4 and the fifth time ti5. For the pump motor 58, the pump motor 58 is off when plot 402 is at a value of zero, and the pump motor 58 is on when plot 402 is at a value of 1. Similarly, for the supply actuator 62, the supply actuator 62 supplies fluid via the low-pressure port 56L when plot 404 is at a value of zero, and the supply actuator 62 supplies fluid via the high-pressure port 56H when plot 404 is at a value of 1. The flow valve 64 is in the fully open position when plot 406 is at the value OPF, in the fully closed position when plot 406 is at the value of zero, and in the middle crank position when plot 406 is at the value OPM.

[0069] During the low-speed crank mode between the start time ti0 and the first time ti1, the pump motor 58 is controlled to start operating (e.g., plot 402 moves from zero to 1), the supply actuator 62 supplies fluid through the low-pressure port 56L, and the flow valve 64 is moved to the fully open position (e.g., plot 406 moves from zero to OPF). As a result, the detected rotational speed of the turbomachinery 10 increases from zero at plot 408 to the first rotational speed R1, which substantially matches the requested rotational speed R1' (e.g., about 100 rpm) of the turbomachinery 10 at plot 410 in the low-speed crank mode.

[0070] During the low-speed standby mode between the first and second times ti1 and ti2, the pump motor 58 is controlled to continue operating, the supply actuator 62 continues to supply fluid through the low-pressure port 56L, and the flow valve 64 is moved to the fully closed position (e.g., plot 406 moves from OPF to zero). As a result, the detected rotational speed of the turbomachinery 10 decreases from the first rotational speed R1 of plot 408 to approximately zero, which substantially matches the requested rotational speed of the turbomachinery 10 of plot 410 during the low-speed standby mode (e.g., approximately 0 rpm).

[0071] During the medium-speed crank mode between the second and third times ti2 and ti3, the pump motor 58 is controlled to continue operating, the supply actuator 62 is controlled to supply fluid through the high-pressure port 56H, and the flow valve 64 is moved to the medium-speed crank position and partially opened (e.g., plot 406 moves from zero to OPM). As a result, the detected rotational speed of the turbomachinery 10 increases from zero to the second rotational speed R2 of plot 408, which substantially matches the requested second rotational speed R2' of the turbomachinery 10 at plot 410 during the medium-speed crank mode (e.g., 800 rpm to 1200 rpm, such as 1200 rpm).

[0072] During the high-speed standby mode between the third and fourth times ti3 and ti4, the pump motor 58 is controlled to stop operating, the supply actuator 62 continues to select the high-pressure port 56H, and the flow valve 64 is moved to the fully closed position (e.g., plot 406 moves from OPM to zero). As a result, the detected rotational speed of the turbomachinery 10 decreases from the second rotational speed R2 of plot 408 to approximately zero, which substantially matches the requested rotational speed of the turbomachinery 10 of plot 410 during the high-speed standby mode (e.g., approximately 0 rpm).

[0073] During the high-speed crank mode between the fourth and fifth times ti4, ti5, the pump motor 58 is controlled to operate again, the supply actuator 62 is controlled to supply fluid through the high-pressure port 56H, and the flow valve 64 is moved to the fully open position (e.g., plot 406 moves from zero to OPF). As a result, the detected rotational speed of the turbomachinery 10 increases from zero to the third rotational speed R3 of plot 408, which substantially matches the requested third rotational speed R3' (e.g., about 2450 rpm) of the turbomachinery 10 at plot 410 during the high-speed crank mode.

[0074] Figure 5 is a flowchart of one method 500 for calibrating a hydraulic starter for turbomachinery according to an aspect of this disclosure. Generally, method 500 is described herein as being carried out by a computing system 102 of the system 100 described above with reference to Figure 2, in accordance with a control algorithm 200 described with reference to Figures 3A to 3H. However, it should be understood that the various processes described below may be carried out by alternative computing devices or any combination of computing devices. In addition, although Figure 5 shows steps or functions performed in a particular order for illustrative purposes, the method steps described herein are not necessarily limited to any particular order or arrangement unless expressly stated otherwise. Those skilled in the art will understand that, using the disclosures provided herein, various steps or functions of the methods disclosed herein can be omitted, rearranged, combined, and / or adapted in various ways without departing from the scope of this disclosure.

[0075] As shown in Figure 5, method 500 may include receiving a request in (502) to perform an automated diagnostic run of a hydraulic starter for turbomachinery. For example, as described above, an operator may input a request via the user interface 68(or more) to cause the computing system 102 to start an automated diagnostic run of the hydraulic starter 50 for turbomachinery 10.

[0076] Furthermore, in (504), the method 500 may include performing an automated diagnostic operation which involves controlling the operation of a hydraulic fluid source and a valve coupled between the hydraulic fluid source and a hydraulic starter to sequentially perform a plurality of basic modes, including at least one standby mode test and at least one crank speed mode test. For example, as described above, the computing system 102 may control the operation of the hydraulic fluid source 54 (e.g., a pump motor 58 and a supply actuator 62) and the flow valve 64 to perform an automated diagnostic operation which involves sequentially performing a plurality of basic modes, the plurality of basic modes including at least one standby mode test (e.g., a low-speed standby mode or a high-speed standby mode) and at least one crank speed mode test (e.g., a low-speed crank mode or a high-speed crank mode).

[0077] Furthermore, in (506), method 500 may include monitoring the rotational speed of the turbomachinery as detected by a speed sensor during each of the multiple basic modes. For example, as described above, the computing system 102 may monitor the rotational speed of the turbomachinery 10 (e.g., the rotational speed of the shaft 22, the rotor disk 24, and / or the rotor disk) as detected by a speed sensor 66 during each of the multiple basic modes. The computing system 102 facilitates the diagnosis of failure modes and reduces the likelihood of damage to the hydraulic starter system 52 and / or the turbomachinery 10 by automatically executing the basic modes sequentially while monitoring the rotational speed of the turbomachinery 10, as disclosed herein.

[0078] Figure 6 is a flowchart of a further method 600 for calibrating a hydraulic starter for turbomachinery according to an aspect of this disclosure. Generally, method 600 is described herein as being carried out by the computing system 102 of the system 100 described above with reference to Figure 2, in accordance with the control algorithm 200 described with reference to Figures 3A to 3H. However, it should be understood that the various processes described below may be carried out by alternative computing devices or any combination of computing devices. In addition, although Figure 6 shows steps or functions performed in a particular order for illustrative purposes, the method steps described herein are not necessarily limited to any particular order or arrangement unless expressly stated otherwise. Those skilled in the art will understand that, using the disclosures provided herein, various steps or functions of the methods disclosed herein can be omitted, rearranged, combined, and / or adapted in various ways without departing from the scope of this disclosure.

[0079] As shown in Figure 6, method 600 may include, in (602), controlling the operation of a hydraulic fluid source and a valve coupled between the hydraulic fluid source and a hydraulic starter to sequentially perform standby mode tests and crank speed mode tests. For example, as described above, the computing system 102 may control the operation of the hydraulic fluid source 54 (e.g., a pump motor 58 and a supply actuator 62) and the flow valve 64 to sequentially perform standby mode tests (e.g., a low-speed standby mode and / or a high-speed standby mode) and crank speed mode tests (e.g., a low-speed crank mode and / or a high-speed crank mode).

[0080] Furthermore, in (604), method 600 may include monitoring the standby rotational speed of the turbomachinery detected by the speed sensor during standby mode testing and the crank rotational speed of the turbomachinery detected during crank speed mode testing. For example, as described above, the computing system 102 may monitor the standby rotational speed of the turbomachinery 10 detected by the speed sensor 66 during standby mode testing (e.g., the rotational speed of the shaft 22, rotor disk 24, and / or rotor disk 28), and the crank rotational speed of the turbomachinery 10 detected by the speed sensor 66 during crank speed mode testing (e.g., the rotational speed of the shaft 22, rotor disk 24, and / or rotor disk 28).

[0081] In addition, in (606), method 600 may include controlling the operation of the hydraulic fluid source and the valve to perform a medium-speed crank calibration when the standby rotational speed is within the standby speed range and the crank rotational speed is within the crank speed range, thereby determining the medium-speed crank position of the valve. For example, as described above, when the standby rotational speed is within the standby speed range (e.g., (262) in Figure 3C and / or (288) in Figure 3D) and the crank rotational speed is within the crank speed range (e.g., (306) in Figure 3E and / or (326) in Figure 3F), the computing system 102 may control the operation of the hydraulic fluid source 54 (e.g., the pump motor 58 and the supply actuator 62) and the flow valve 64 to perform a medium-speed crank calibration (e.g., (338) in Figure 3G), thereby determining the medium-speed crank position OPM of the flow valve 64 (e.g., (368) in Figure 3G). The computing system 102 automatically performs the medium-speed crank calibration, which significantly reduces or completely eliminates user errors from the calibration process, thereby reducing the possibility of damage to the hydraulic starter system 52 and / or turbomachinery 10.

[0082] This specification discloses the present invention, including its best mode, using examples, and enables any person skilled in the art to practice the invention, including the fabrication and use of any device or system, and the execution of any incorporated method. The patentable scope of the present invention is defined by the claims and may include other examples that a person skilled in the art may conceive. Such other examples are intended to be within the scope of the claims if they include structural elements that are not different from the language of the claims, or equivalent structural elements that do not substantially differ from the language of the claims.

[0083] Further aspects of the present invention are provided by the subject matter of the following clauses.

[0084] A system for calibrating a hydraulic starter for turbomachinery. The system includes a hydraulic fluid source capable of supplying fluid at high or low pressure. The system further includes a hydraulic starter that is rotationally driven by the fluid from the hydraulic fluid source. Furthermore, the system includes a flow valve fluid-coupled between the hydraulic fluid source and the hydraulic starter, the flow valve being movable between multiple positions, including a fully closed position and a fully open position, to regulate the flow rate of fluid supplied from the hydraulic fluid source to the hydraulic starter. The flow rate is lowest when the flow valve is in the fully closed position and highest when the flow valve is in the fully open position. Furthermore, the system includes a speed sensor configured to detect the rotational speed of the turbomachinery. In addition, the system includes a computing system. The computing system is configured to receive requests to perform an automated diagnostic run of the hydraulic starter. The computing system is further configured to control the operation of the hydraulic fluid source and the flow valve to perform an automated diagnostic run based on at least a portion of the requests. The automated diagnostic run involves automatically and sequentially executing a plurality of basic modes, in which the flow valve is either in the fully closed position or the fully open position. The multiple basic modes include at least one standby mode test and at least one crank speed mode test, with the flow valve in the fully closed position for each of the at least one standby mode tests and the flow valve in the fully open position for each of the at least one crank speed mode tests. In addition, the computing system is configured to monitor the rotational speed of the turbomachinery during each of the multiple basic modes.

[0085] A system according to one or more of these provisions, wherein at least one standby mode test includes one or more of the low-speed standby mode or high-speed standby mode, for the low-speed standby mode the hydraulic fluid source is configured to supply fluid at low pressure and the flow valve is in the fully closed position, and for the high-speed standby mode the hydraulic fluid source is configured to supply fluid at high pressure and the flow valve is in the fully closed position. At least one crank speed mode test includes one or more of the low-speed crank mode or high-speed crank mode, for the low-speed crank mode the hydraulic fluid source is configured to supply fluid at low pressure and the flow valve is in the fully open position, and for the high-speed crank mode the hydraulic fluid source is configured to supply fluid at high pressure and the flow valve is in the fully open position.

[0086] A system as described in one or more of these clauses, wherein the computing system is configured to control the hydraulic fluid source and flow valve to perform an automated diagnostic operation by automatically controlling the hydraulic fluid source and flow valve to perform a low-speed standby mode, a high-speed standby mode after performing the low-speed standby mode, a low-speed crank mode after performing the high-speed standby mode, and a high-speed crank mode after performing the low-speed crank mode.

[0087] A system as described in one or more of these clauses, wherein the computing system is configured to automatically perform a medium-speed crank calibration when the rotational speed of the turbomachinery, as detected by a speed sensor in each of several basic modes, is within the respective speed range, by which the computing system is configured to control a hydraulic fluid source to supply fluid at high pressure. A computing system further configured to control the operation of a flow valve to move the flow valve to a first position among several positions, wherein the flow rate of the fluid supplied from the hydraulic fluid source to the hydraulic starter is a first flow rate when the flow valve is in the first position, and the first flow rate is between the lowest and highest flow rates. A computing system further configured to control the operation of a flow valve to adjust the flow rate by moving the flow valve from the first position at a given rate until the rotational speed of the turbomachinery is within the medium-speed range for medium-speed crank calibration.

[0088] The system described in one or more of these clauses, wherein the computing system is further configured to set the medium-speed crank position of the flow valve as one of a plurality of positions of the flow valve when the rotational speed of the turbomachinery is within the medium-speed range during medium-speed crank calibration.

[0089] A system as described in one or more of these clauses, wherein the computing system is further configured to control the operation of the user interface to indicate that the medium-speed crank calibration has failed when the rotational speed of the turbomachinery detected by the speed sensor during the medium-speed crank calibration is not within the medium-speed range before the flow valve is in the fully open position.

[0090] The system described in one or more of these clauses, wherein the computing system is further configured to control the operation of the user interface to indicate each of the one or more basic modes when the rotational speed of the turbomachinery, as detected by a speed sensor in one or more of the basic modes, is outside the respective speed range after a threshold time has elapsed.

[0091] A system according to one or more of these provisions, wherein the hydraulic fluid source has a high-pressure port for supplying fluid at high pressure and a low-pressure port for supplying fluid at low pressure, and the hydraulic fluid source further includes a supply actuator that is operable to guide fluid through the high-pressure port or the low-pressure port of the hydraulic fluid source. A method for calibrating a hydraulic starter for turbomachinery, wherein a hydraulic fluid source is operable to supply fluid at high or low pressure to rotationally drive the hydraulic starter, and a flow valve is fluid-coupled between the hydraulic fluid source and the hydraulic starter. The flow valve is movable between a plurality of positions, including a fully closed position and a fully open position, to adjust the flow rate of the fluid supplied from the hydraulic fluid source to the hydraulic starter, the lowest flow rate being when the flow valve is in the fully closed position, and the highest flow rate being when the flow valve is in the fully open position. The method includes receiving a request by a computing system to perform an automated diagnostic run of the hydraulic starter. The method includes the computing system automatically controlling the operation of the hydraulic fluid source and the flow valve to perform an automated diagnostic run based on at least a portion of the request. The automated diagnostic run includes sequentially performing a plurality of basic modes, the flow valve being in either the fully closed position or the fully open position in the plurality of basic modes. A plurality of basic modes, comprising at least one standby mode test and at least one crank speed mode test, wherein the flow valve is in the fully closed position for each of the at least one standby mode tests and the flow valve is in the fully open position for each of the at least one crank speed mode tests. In addition, the method includes monitoring the rotational speed of the turbomachinery, as detected by a speed sensor, during each of the plurality of basic modes by a computing system.

[0092] The method according to one or more of the provisions of the above method, wherein at least one standby mode test comprises one or more of a low-speed standby mode or a high-speed standby mode, for the low-speed standby mode the hydraulic fluid source is configured to supply fluid at low pressure and the flow valve is in the fully closed position, and for the high-speed standby mode the hydraulic fluid source is configured to supply fluid at high pressure and the flow valve is in the fully closed position. At least one crank speed mode test comprises one or more of a low-speed crank mode or a high-speed crank mode, for the low-speed crank mode the hydraulic fluid source is configured to supply fluid at low pressure and the flow valve is in the fully open position, and for the high-speed crank mode the hydraulic fluid source is configured to supply fluid at high pressure and the flow valve is in the fully open position.

[0093] The method of one or more of the provisions of the above method, wherein controlling a hydraulic fluid source and flow valve to perform an automatic diagnostic operation includes automatically controlling the hydraulic fluid source and flow valve to perform a low-speed standby mode, a high-speed standby mode after performing the low-speed standby mode, a low-speed crank mode after performing the high-speed standby mode, and a high-speed crank mode after performing the low-speed crank mode.

[0094] The method of one or more of the provisions of the above method, further comprising: when the rotational speed of the turbomachinery in each of a plurality of basic modes is within the respective speed range, the method automatically performs a medium-speed crank calibration by: controlling a hydraulic fluid source by a computing system to supply fluid at high pressure; controlling the operation of a flow valve by a computing system to move the flow valve to a first position among a plurality of positions, such that the flow rate of the fluid supplied from the hydraulic fluid source to the hydraulic starter is a first flow rate when the flow valve is in the first position, and the first flow rate is between the lowest flow rate and the highest flow rate; and controlling the operation of a flow valve by a computing system to adjust the flow rate by moving the flow valve from the first position at a given rate until the rotational speed of the turbomachinery is within the medium-speed range for medium-speed crank calibration.

[0095] The method of one or more of the provisions of the above method, further comprising determining the medium-speed crank position of the flow valve as one of a plurality of positions of the flow valve when the rotational speed of the turbomachinery is within the medium-speed range, by a computing system.

[0096] The method of one or more of the provisions of the above method, further comprising controlling the operation of the user interface to indicate that the medium-speed crank calibration has failed if the rotational speed of the turbomachinery detected in the medium-speed crank calibration is not within the medium-speed range before the flow valve is in the fully open position, by a computing system.

[0097] The method of one or more of the provisions of the above method, further comprising, after medium-speed crank calibration, the method controlling a computing system to control a hydraulic fluid source to stop supplying fluid and to control the operation of a flow valve to move the flow valve to the fully closed position. The method further comprises, by a computing system, controlling the operation of a user interface to indicate an error when the rotational speed of the turbomachinery exceeds a stop threshold after a threshold time has elapsed since the hydraulic fluid source was controlled to stop supplying fluid.

[0098] The method of one or more of the provisions of the above method, further comprising controlling the operation of a user interface by a computing system to indicate each of the one or more basic modes when the rotational speed of a turbomachinery detected in one or more of the basic modes is outside the respective speed range.

[0099] The method according to one or more of the provisions of the above method, wherein the hydraulic fluid source has a high-pressure port for supplying fluid at high pressure and a low-pressure port for supplying fluid at low pressure. Controlling the hydraulic fluid source and flow valve to perform an automated diagnostic operation includes controlling a supply actuator of the hydraulic fluid source, the supply actuator being controllable to guide fluid through the high-pressure port or the low-pressure port of the hydraulic fluid source.

[0100] A method of one or more of the provisions of the above method, further comprising controlling a hydraulic fluid source by a computing system to stop supplying fluid after each of a plurality of basic modes. A method further comprising controlling the operation of a user interface by a computing system to indicate an error when the rotational speed of a turbomachinery exceeds a stop threshold after a threshold time has elapsed since the hydraulic fluid source was controlled to stop supplying fluid.

[0101] The method of one or more of the provisions of the above method, further comprising controlling a hydraulic fluid source and a flow valve to automatically stop sequentially executing multiple basic modes when the rotational speed of the turbomachinery exceeds a stop threshold, after a threshold time has elapsed following a computing system has controlled the hydraulic fluid source to stop supplying fluid.

[0102] A method for calibrating a hydraulic starter for turbomachinery, wherein a hydraulic fluid source is operable to supply fluid at high or low pressure to rotationally drive the hydraulic starter, and a flow valve is fluid-coupled between the hydraulic fluid source and the hydraulic starter. The flow valve is movable to regulate the flow rate of fluid supplied from the hydraulic fluid source to the hydraulic starter, the lowest flow rate being when the flow valve is in the fully closed position, and the highest flow rate being when the flow valve is in the fully open position. The method includes automatically controlling the operation of the hydraulic fluid source and the flow valve by a computing system to sequentially perform standby mode tests and crank speed mode tests, wherein the flow valve is in the fully closed position for the standby mode test and the flow valve is in the fully open position for the crank speed mode test. The method further includes monitoring the standby rotational speed of the turbomachinery during the standby mode test and the crank rotational speed of the turbomachinery during the crank speed mode test by the computing system. In addition, the method includes a computing system automatically controlling the operation of the hydraulic fluid source and the flow valve to perform a medium-speed crank calibration when the standby rotational speed is within the standby speed range and the crank rotational speed is within the crank speed range, thereby determining the medium-speed crank position of the flow valve, wherein the rotational speed of the turbomachinery is within the medium speed range when the hydraulic fluid source supplies fluid at high pressure and the flow valve is in the medium-speed crank position. [Explanation of Symbols]

[0103] 10 Gas turbines, turbomachinery 12 Entrance Section 14 Compressor Section 16. Combustor Section 18 Turbine Section 20 Exhaust Section 22 shafts 24 Rotor Discs 26 rotor blades 28 Rotor Discs 30 rotor blades 31 Turbine Casing 32 High-temperature gas pathway 34 Combustion gases 50 Hydraulic Starter 50A output shaft 52 Hydraulic Starter System 54 Hydraulic fluid source 56 pumps 56H High-Voltage Port 56L Low-Pressure Port 58 Pump motor 60 Reservoir 62 Supply Actuator 64 Flow valve 66 Speed ​​Sensor 68 User Interface 100 Systems 102 Computing Systems 104 Processors 106 memory 108 data 110 instructions 200 Control Algorithms 400 graphs 402 Plot 404 Plot 406 plots 408 plots 410 plot OPF value OPM value R1 First rotational speed R1' Requested rotational speed R2 Second rotation speed R2' The second rotational speed requested R3 Third rotation speed R3' The requested third rotational speed T1 A predetermined first threshold time T2 A predetermined second threshold time T3 A predetermined third threshold time, a third predetermined threshold time T4 A predetermined fourth threshold time, a fourth predetermined threshold time T5 A predetermined fifth threshold time T6 A predetermined sixth threshold time T7 A predetermined seventh threshold time ti0 start time ti1 First time ti2 Second time ti3 The third time ti4 The 4th time ti5 The fifth time

Claims

1. A system (100) for calibrating a hydraulic starter (50) for a turbomachinery (10), wherein the system (100) A hydraulic fluid source (54) capable of supplying fluid at high or low pressure, A hydraulic starter (50) is rotationally driven by the fluid from the hydraulic fluid source (54), A flow valve (64) fluid-coupled between the hydraulic fluid source (54) and the hydraulic starter (50), wherein the flow valve (64) is movable between a plurality of positions, including a fully closed position and a fully open position, to adjust the flow rate of the fluid supplied from the hydraulic fluid source (54) to the hydraulic starter (50), the flow rate being lowest when the flow valve (64) is in the fully closed position, and the flow rate being highest when the flow valve (64) is in the fully open position, A speed sensor (66) configured to detect the rotational speed of the turbomachinery (10), A computing system (102) is provided, and the computing system (102) is The system receives a request to perform an automatic diagnostic operation of the hydraulic starter (50), Controlling the operation of the hydraulic fluid source (54) and the flow valve (64) to perform the automatic diagnostic operation based on at least a portion of the above requirements, wherein the automatic diagnostic operation includes automatically sequentially executing a plurality of basic modes, wherein the flow valve (64) is in either the fully closed position or the fully open position in the plurality of basic modes, wherein the plurality of basic modes include at least one standby mode test and at least one crank speed mode test, wherein the flow valve (64) is in the fully closed position for each of the at least one standby mode tests, and the flow valve (64) is in the fully open position for each of the at least one crank speed mode tests. In each of the above-mentioned basic modes, the rotational speed of the turbomachinery (10) is monitored, It is configured to do the following: System (100).

2. The at least one standby mode test includes one or more of a low-speed standby mode or a high-speed standby mode, wherein, for the low-speed standby mode, the hydraulic fluid source (54) is configured to supply the fluid at the low pressure and the flow valve (64) is in the fully closed position, and for the high-speed standby mode, the hydraulic fluid source (54) is configured to supply the fluid at the high pressure and the flow valve (64) is in the fully closed position. The at least one crank speed mode test includes one or more of a low-speed crank mode or a high-speed crank mode, wherein for the low-speed crank mode, the hydraulic fluid source (54) is configured to supply the fluid at the low pressure and the flow valve (64) is in the fully open position, and for the high-speed crank mode, the hydraulic fluid source (54) is configured to supply the fluid at the high pressure and the flow valve (64) is in the fully open position. The system (100) according to claim 1.

3. The system (100) according to claim 2, wherein the computing system (102) is configured to automatically control the hydraulic fluid source (54) and the flow valve (64) to perform the automatic diagnostic operation by executing the low-speed standby mode, the high-speed standby mode after executing the low-speed standby mode, the low-speed crank mode after executing the high-speed standby mode, and the high-speed crank mode after executing the low-speed crank mode.

4. When the rotational speed of the turbomachinery (10) detected by the speed sensor (66) in each of the above-mentioned basic modes is within the respective speed range, the computing system (102) performs a medium-speed crank calibration. Controlling the hydraulic fluid source (54) to supply the fluid at the high pressure, Controlling the operation of the flow valve (64) to move the flow valve (64) to a first position among the plurality of positions, such that the flow rate of the fluid supplied from the hydraulic fluid source (54) to the hydraulic starter (50) is a first flow rate when the flow valve (64) is in the first position, and the first flow rate is between the lowest flow rate and the highest flow rate. The operation of the flow valve (64) is controlled to adjust the flow rate by moving the flow valve (64) from the first position at a given rate until the rotational speed of the turbomachinery (10) is within the medium speed range for the medium speed crank calibration. It is configured to perform this action, and is configured to execute automatically. The system (100) according to claim 1.

5. The computing system (102) is further configured to set the medium-speed crank position of the flow valve (64) as one of the plurality of positions of the flow valve (64) when the rotational speed of the turbomachinery (10) is within the medium-speed range during the medium-speed crank calibration, and / or The computing system (102) is further configured to control the operation of the user interface (68) to indicate that the medium-speed crank calibration has failed if the rotational speed of the turbomachinery (10), as detected by the speed sensor (66) during the medium-speed crank calibration, is not within the medium-speed range before the flow valve (64) is in the fully open position. The system (100) according to claim 4.

6. The system (100) according to claim 1, further configured such that when the rotational speed of the turbomachinery (10) detected by the speed sensor (66) in one or more of the plurality of basic modes is outside the respective speed range after a threshold time has elapsed, the computing system (102) controls the operation of the user interface (68) to indicate each of the one or more of the plurality of basic modes.

7. The system (100) according to any one of claims 1 to 6, wherein the hydraulic fluid source (54) has a high-pressure port (56H) for supplying the fluid at high pressure and a low-pressure port (56L) for supplying the fluid at low pressure, and the hydraulic fluid source (54) further comprises a supply actuator (62) that can be operated to guide fluid through the high-pressure port (56H) or the low-pressure port (56L) of the hydraulic fluid source (54).

8. A method for calibrating a hydraulic starter (50) for a turbomachinery (10), wherein a hydraulic fluid source (54) is operable to supply fluid at high or low pressure to rotationally drive the hydraulic starter (50), a flow valve (64) is fluidly coupled between the hydraulic fluid source (54) and the hydraulic starter (50), the flow valve (64) is movable between a plurality of positions including a fully closed position and a fully open position to adjust the flow rate of the fluid supplied from the hydraulic fluid source (54) to the hydraulic starter (50), the flow rate being lowest when the flow valve (64) is in the fully closed position, and the flow rate being highest when the flow valve (64) is in the fully open position, and the method is The computing system (102) receives a request to perform an automatic diagnostic operation of the hydraulic starter (50), The computing system (102) automatically controls the operation of the hydraulic fluid source (54) and the flow valve (64) to perform the automatic diagnostic operation based on at least a portion of the request, wherein the automatic diagnostic operation includes sequentially executing a plurality of basic modes, wherein the flow valve (64) is in either the fully closed position or the fully open position in the plurality of basic modes, wherein the plurality of basic modes include at least one standby mode test and at least one crank speed mode test, wherein the flow valve (64) is in the fully closed position for each of the at least one standby mode tests, and the flow valve (64) is in the fully open position for each of the at least one crank speed mode tests. The computing system (102) monitors the rotational speed of the turbomachinery (10) detected by the speed sensor (66) in each of the plurality of basic modes, Methods that include...

9. The at least one standby mode test includes one or more of a low-speed standby mode or a high-speed standby mode, wherein, for the low-speed standby mode, the hydraulic fluid source (54) is configured to supply the fluid at the low pressure and the flow valve (64) is in the fully closed position, and for the high-speed standby mode, the hydraulic fluid source (54) is configured to supply the fluid at the high pressure and the flow valve (64) is in the fully closed position. The at least one crank speed mode test includes one or more of a low-speed crank mode or a high-speed crank mode, wherein for the low-speed crank mode, the hydraulic fluid source (54) is configured to supply the fluid at the low pressure and the flow valve (64) is in the fully open position, and for the high-speed crank mode, the hydraulic fluid source (54) is configured to supply the fluid at the high pressure and the flow valve (64) is in the fully open position. The method according to claim 8.

10. The method according to claim 9, wherein controlling the hydraulic fluid source (54) and the flow valve (64) to perform the automatic diagnostic operation includes automatically controlling the hydraulic fluid source (54) and the flow valve (64) to perform the low-speed standby mode, the high-speed standby mode after performing the low-speed standby mode, the low-speed crank mode after performing the high-speed standby mode, and the high-speed crank mode after performing the low-speed crank mode.

11. When the rotational speed of the turbomachinery (10) in each of the above-mentioned basic modes is within the respective speed range, the method performs a medium-speed crank calibration. The computing system (102) controls the hydraulic fluid source (54) to supply the fluid at the high pressure, The computing system (102) controls the operation of the flow valve (64) to move the flow valve (64) to a first position among the plurality of positions, and controls the flow rate of the fluid supplied from the hydraulic fluid source (54) to the hydraulic starter (50) to be a first flow rate when the flow valve (64) is in the first position, and the first flow rate is between the lowest flow rate and the highest flow rate. The computing system (102) controls the operation of the flow valve (64) to adjust the flow rate by moving the flow valve (64) from the first position at a given rate until the rotational speed of the turbomachinery (10) is within the medium speed range for the medium speed crank calibration, The method according to claim 8, further comprising being performed automatically by...

12. The aforementioned medium-speed crank calibration is performed as follows: The computing system (102) determines the medium-speed crank position of the flow valve (64) as one of the plurality of positions of the flow valve (64) when the rotational speed of the turbomachinery (10) is within the medium-speed range, and / or The computing system (102) controls the operation of the user interface (68) to indicate that the medium-speed crank calibration has failed if the rotational speed of the turbomachinery (10) detected during the medium-speed crank calibration is not within the medium-speed range before the flow valve (64) is in the fully open position. The method according to claim 11, further comprising:

13. After the aforementioned medium-speed crank calibration, the method is performed as follows: The computing system (102) controls the hydraulic fluid source (54) to stop supplying the fluid and controls the operation of the flow valve (64) to move the flow valve (64) to the fully closed position, The computing system (102) controls the operation of the user interface (68) to indicate an error when the rotational speed of the turbomachinery (10) exceeds a stop threshold after a threshold time has elapsed since the hydraulic fluid source (54) was controlled to stop supplying the fluid, The method according to claim 11, further comprising:

14. The method according to claim 8, further comprising the computing system (102) controlling the operation of the user interface (68) to indicate each of the one or more of the multiple basic modes when the rotational speed of the turbomachinery (10) detected in one or more of the multiple basic modes is outside the respective speed range.

15. The computing system (102) controls the hydraulic fluid source (54) to stop supplying the fluid after each of the plurality of basic modes, The computing system (102) controls the operation of the user interface (68) to indicate an error when the rotational speed of the turbomachinery (10) exceeds a stop threshold after a threshold time has elapsed since the hydraulic fluid source (54) was controlled to stop supplying the fluid, It further includes, The above method is preferably, The computing system (102) further includes controlling the hydraulic fluid source (54) and the flow valve (64) to stop automatically sequentially executing the plurality of basic modes when the rotational speed of the turbomachinery (10) exceeds the stop threshold after the threshold time has elapsed since the hydraulic fluid source (54) was controlled to stop supplying the fluid, The method according to any one of claims 8 to 14.

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