CN210069096U

CN210069096U - Fluid regulator and device for regulating flow rate into loading chamber of fluid regulator

Info

Publication number: CN210069096U
Application number: CN201920451431.8U
Authority: CN
Inventors: M·R·科特拉古达巴萨帕; M·A·米赫涅维茨; J·布福德
Original assignee: Emerson Process Management Regulator Technologies Inc
Current assignee: Emerson Process Management Regulator Technologies Inc
Priority date: 2018-04-04
Filing date: 2019-04-04
Publication date: 2020-02-14
Anticipated expiration: 2029-04-04
Also published as: CN110345302A; WO2019195233A1

Abstract

The utility model discloses a fluid regulator and be used for adjusting the device that gets into the velocity of flow of fluid regulator's loading chamber. A fluid regulator has a valve body defining an inlet, an outlet, a loading port, an entry port, and a loading chamber disposed within the valve body and coupled to the loading port. A valve assembly is disposed at least partially between the inlet and the outlet and in communication with the loading chamber and is adapted to cooperate with the loading chamber to regulate fluid flow at the outlet by regulating a fluid flow rate between the inlet and the outlet. A flow restrictor is at least partially disposed within the inlet port, and the loading chamber and the valve assembly are adapted to respond to changes in the loading pressure such that a modified rate is achieved, and the flow restrictor is adapted to adjust the response speed to achieve the modified rate.

Description

Fluid regulator and device for regulating flow rate into loading chamber of fluid regulator

Technical Field

The present disclosure relates generally to fluid control devices and, more particularly, to fluid control devices having flow restrictors for adjusting the speed of the fluid control device in response to changes in operating pressure.

Background

Many process control systems use fluid control devices, such as fluid regulators, to control the pressure of a fluid. Pressure reducing fluid regulators are typically used to receive a relatively high pressure fluid and output a relatively lower regulated output fluid pressure. In this manner, the pressure reducing regulator can provide a relatively constant fluid pressure output for a wide range of output loads (i.e., flow requirements, capacity, etc.) regardless of the pressure drop across the regulator. For example, a fluid regulator associated with a piece of equipment (e.g., a boiler or a combustor) may receive a fluid (e.g., fuel or gas) having a relatively high and slightly variable pressure from a fluid distribution source, and may regulate the fluid to a lower, substantially constant pressure suitable for safe and effective use by equipment (e.g., a combustor) downstream of the fluid regulator.

Due to the instability of certain types of fluid control devices at a particular flow rate, the speed at which the device responds to changes in flow rate and/or desired pressure may be inappropriately fast or slow for proper operation of the device. In this way, the device may perform with reduced accuracy during subsequent flow conditions and may eventually lead to damage of the device. Dampers and restrictors have been used to limit the speed of the device in response to changes in flow rate, but these components typically require a skilled technician to manually open and adjust the restrictor to increase the inlet flow. These restrictors and dampers typically include complex, expensive components and may be prone to maintenance problems.

SUMMERY OF THE UTILITY MODEL

In view of the above-mentioned dampers and restrictors that typically require a skilled technician to manually open and adjust the restrictor to increase inlet flow, and that typically include complex, expensive components and may be prone to maintenance issues, the present invention provides a fluid regulator and apparatus for regulating the flow rate into the loading chamber of the fluid regulator.

According to an exemplary aspect of the present disclosure, a fluid regulator includes a valve body defining an inlet, an outlet, a loading port, and an entry port. A loading chamber is disposed within the valve body and coupled to the loading port, and a valve assembly is disposed at least partially between the inlet and the outlet and in communication with the loading chamber. The valve assembly is adapted to cooperate with the loading chamber to regulate fluid flow at the outlet by regulating a fluid flow rate between the inlet and the outlet. A flow restrictor is at least partially disposed within the inlet port, and the loading chamber and the valve assembly are adapted to respond to changes in the loading pressure such that a modified flow rate is achieved, and the flow restrictor is adapted to adjust the response speed to achieve the modified flow rate.

Further in accordance with any one or more of the preceding exemplary aspects of the present invention, the fluid regulator may also include any one or more of the following preferred forms, in any combination.

In one preferred form, the restrictor includes a tapered end that is adjustable to achieve a plurality of response speeds.

In another preferred form, the flow restrictor further comprises a threaded portion adapted to be threadedly inserted into the access port.

In another preferred form, the loading chamber is adapted to undergo a pressure change as the loading pressure changes, the pressure change causing the valve assembly to urge to a modified rate.

In another preferred form, the fluid regulator includes a transition portion positioned between the first portion and the second portion of the charging fluid passageway, and the flow restrictor is adapted to be at least partially disposed within the transition portion to adjustably restrict a flow rate of the fluid propagating through the charging fluid passageway.

In another preferred form, the flow restrictor includes a threaded portion.

In another preferred form, the fluid regulator includes a diaphragm disposed at least partially within the loading chamber, and the diaphragm is adapted to move in response to a change in the loading pressure to equalize the loading pressure in the loading chamber with the force applied by the biasing element.

In another preferred form, the flow restrictor includes a seal for sealing the flow restrictor within the inlet port.

According to another exemplary aspect of the present invention, an apparatus for regulating a flow rate into a loading chamber of a fluid regulator includes a flow restrictor adapted to be at least partially disposed in an entry port and a loading fluid passageway. The flow restrictor includes a screw extending along a longitudinal axis and a tapered end. The tapered end has a cross-section, wherein the cross-sectional area decreases along the length of the tapered end such that when the restrictor is inserted into the access port, the flow rate propagating through the loading fluid passage is limited based on the insertion depth.

Further in accordance with any one or more of the preceding exemplary aspects of the invention, an apparatus may also include any one or more of the following preferred forms, in any combination.

In one preferred form, the flow restrictor includes a threaded portion such that the flow restrictor is threadably coupled to the access port.

By the present disclosure, the rate or speed at which the fluid regulator moves from the closed position to the open position can be controlled, such that the example actuators disclosed herein can be used to reduce the possibility of pilot blow-off and/or flashback that may otherwise occur when the fluid regulator is opened too quickly, for example, during an ignition sequence of a burner.

Drawings

FIG. 1 is a schematic illustration of an example system implemented with an example fluid regulator constructed in accordance with the teachings of the present disclosure.

FIG. 2 is a cross-sectional schematic view of the example fluid regulator of FIG. 1;

FIG. 3A is a perspective, partial cross-sectional view of another example fluid regulator constructed in accordance with the teachings of the present disclosure.

FIG. 3B is an enlarged view of a portion of the example fluid regulator of FIG. 3A;

FIG. 4 is a side partial cross-sectional view of the example fluid regulator of FIGS. 3A and 3B;

FIG. 5A is a cross-sectional view of the example fluid regulator of FIGS. 3A, 3B, and 4;

FIG. 5B is a cross-sectional view of the example fluid regulator of FIG. 5A;

FIG. 6 illustrates another example fluid regulator constructed in accordance with the teachings of the present disclosure;

FIG. 7 is a side partial cross-sectional view of another example fluid regulator constructed in accordance with the teachings of the present disclosure; and

FIG. 8 is a cross-sectional view of a portion of the example fluid regulator of FIG. 7.

Skilled artisans will appreciate that elements in the figures are illustrated for simplicity and clarity and have not necessarily been drawn to scale. For example, the dimensions and/or relative positioning of some of the elements in the figures may be exaggerated relative to other elements to help to improve understanding of various embodiments of the present invention. Additionally, common but well-understood elements that are useful or necessary in a commercially feasible embodiment are often not depicted in order to facilitate a less obstructed view of these various embodiments. It will also be understood that certain actions and/or steps may be described or depicted in a particular order of occurrence while those skilled in the art will understand that such specificity with respect to sequence is not actually required. It will also be understood that the terms and expressions used herein have the ordinary technical meaning as is accorded to such terms and expressions by persons skilled in the technical field as set forth above except where different specific meanings have otherwise been set forth herein. Wherever possible, the same reference numbers will be used throughout the drawings and the accompanying written description to refer to the same or like parts.

Detailed Description

A fluid or pressure regulator typically receives a supply fluid from an upstream fluid distribution source having a relatively high pressure and regulates the pressure of the supply for use with a downstream demand source, a pressure regulator, or any other stagnation point(s) that require process fluid at a desired (e.g., lower) pressure. The example actuators disclosed herein may be used with a fluid regulator to prevent and/or reduce excessive gas (e.g., combustible gas) accumulation or build-up, flashback, and/or pilot flame blow-out during operation (e.g., during the ignition phase of a primary combustor). To prevent gas buildup, flashback, and/or pilot flame blow-out, the actuators disclosed herein employ a velocity flow device to control the rate or speed at which a fluid regulator moves from a closed position (e.g., a fully closed position that prevents a supply fluid (e.g., combustible gas) from flowing to an outlet) to an open position (e.g., a fully open position that allows fluid to flow to the outlet). In some examples, the velocity flow device may be adjustable to effect an increase or decrease in the rate or velocity at which the fluid regulator moves from the closed position toward the open position. By controlling the speed at which the fluid regulator moves from the closed position to the open position, the example actuators disclosed herein may be used to reduce pilot blow-off and/or flashback that may otherwise occur when the fluid regulator is opened too quickly, for example, during an ignition sequence of a combustor.

Further, to achieve relatively rapid closing of an example fluid regulator, the actuators disclosed herein may employ a bleed arrangement that is unaffected by the velocity flow arrangement. Thus, while the speed control device controls the rate at which the fluid regulator moves from the closed position to the open position, the speed control device does not affect the speed at which the fluid regulator moves from the open position to the closed position.

The example actuators disclosed herein may be used to retrofit existing fluid regulators and/or actuators in the field. In other words, the actuators disclosed herein may be provided separately or as individual units. In some examples, only the housing of the example actuators disclosed herein may be provided (e.g., to retrofit existing actuators in the field). Accordingly, the example actuator apparatus disclosed herein may implement a fluid regulator assembly in a plant or may be provided (e.g., sold) as a stand-alone unit to retrofit existing fluid regulators and/or actuators in the field.

FIG. 1 is a schematic diagram of an exemplary burner system 100 (e.g., a firetube vessel or direct-fire heater) that may be implemented with an exemplary fluid regulator 102 constructed in accordance with the teachings of the present disclosure. For example, the combustor system 100 of FIG. 1 may be employed to provide heat to a process fluid of an oil and/or natural gas application or process (e.g., a fuel refining application). The system 100 of the illustrated example employs a combustor management system 104 to enable startup or ignition, operation, and/or shutdown of a combustor portion 106 of the combustor system 100. The combustor portion 106 of the exemplary combustor system 100 includes a main burner 108 for providing heat to the process fluid and a pilot 110 for igniting the main burner 108. The main burner 108 and pilot 110 of the illustrated example receive a supply fluid (e.g., a combustible gas or fuel such as natural gas) from a fuel supply 112. Main combustor 108 is fluidly coupled to supply 112 via a main line 114, and pilot burner 110 is fluidly coupled to supply 112 via a pilot line 116. The fluid regulator 102 is fluidly coupled to the main line 114 and controls the supply fluid to the main combustor 108 based on a loading pressure provided to the fluid regulator 102 by a loading regulator 118 via a loading line 120. The loading fluid has a pressure that is less than the pressure of the supply fluid upstream of the fluid regulator 102 and greater than the pressure of the supply fluid downstream of the fluid regulator 102. The main line 114, the pilot line 116, and/or the loading line 120 may include one or more fluid control components 122 (e.g., fluid regulators and/or solenoid valves) to prevent or limit the supply fluid flow to the main burners 108 and/or the pilot 110.

In operation, combustor management system 104 monitors and/or manages the ignition, shutdown, and/or operation of main combustor 108 to control the temperature of the process fluid to a desired temperature. For example, the combustor management system 104 regulates the heat output of the main combustor 108 via the fluid regulator 102 to precisely control the temperature of the process fluid while increasing the efficiency of the combustor system 100 during operation. To improve combustor efficiency, the combustor management system 104 may be configured to manage user-defined temperature set points that ensure that the main combustor 108 (e.g., burning fuel) is turned on only when needed. For example, the combustor management system 104 detects that a flame of the main combustor 108 is absent (e.g., via a flame sensor, such as a flame ionization rod, ultraviolet or infrared scanner, etc.), and ignites the main combustor 108 via the pilot 110 when additional heat is needed.

The burner management system 104 may employ a processor or logic responsive to a process signal (e.g., from a temperature sensor) indicative of the temperature of the process fluid to be heated by the main burner 108. Based on the received signals, the combustor management system 104 provides control function signals (e.g., via a wireless or wired connection) to the various fluid control components 122 and/or the fluid regulators 102 of the combustor system 100. For example, if the received signal indicates a temperature of the process fluid that is below a threshold temperature, the burner management system 104 ignites the main burner 108 when the burner management system 104 detects the absence of a flame at the main burner 108. To ignite main burner 108, burner management system 104 commands fluid regulator 102 to move to an open position to allow supply fluid to flow to main burner 108. The supply fluid to the main burners 108 is ignited by the pilot burners 110.

To prevent and/or reduce excessive gas buildup, flashback, and/or pilot flame blow-out during ignition of main burner 108, the example fluid regulator 102 of the illustrated example controls the rate at which the fluid regulator 102 moves to the open position to allow supply fluid to flow to main burner 108. In this manner, the example fluid regulator 102 of the illustrated example regulates a rate at which the fluid regulator 102 moves from a closed position to an open position (e.g., via a controller) to control a flow rate of the supply fluid to the main burner 108.

FIG. 2 is a cross-sectional schematic view of the example fluid regulator 102 of FIG. 1. The fluid regulator 102 of the illustrated example includes a regulator body 202 coupled to an actuator 204. The regulator body 202 defines a fluid flow passage 206 between an inlet 208 and an outlet 210. For example, the inlet 208 is fluidly coupled to the supply 112 (fig. 1) via the main line 114, and the outlet 210 is fluidly coupled to the main combustor 108. The fluid flow channel 206 defines an orifice 212 between the inlet 208 and the outlet 210. The orifice 212 is defined by a valve seat 214 located in the fluid flow passage 206 and is removably coupled to the regulator body 202.

The illustrated example actuator 204 moves a flow control member 216 (e.g., a valve plug) adjacent a valve seat 214 in the fluid flow passage 206 to control (e.g., close, throttle, etc.) fluid flow between the inlet 208 and the outlet 210. For example, the actuator 204 moves the flow control member 216 relative to the valve seat 214 between a first position (e.g., a fully closed position) in which the flow control member 216 is sealingly engaged with the valve seat 214 to prevent flow of the supply fluid between the inlet 208 and the outlet 210, and a second position (e.g., an open position) in which the flow control member 216 is spaced apart or disengaged from the valve seat 214 to allow flow of the supply fluid between the inlet 208 and the outlet 210. To move the flow control member 216 relative to the valve seat 214, the actuator 204 of the illustrated example includes a diaphragm 218, the diaphragm 218 being operatively coupled to the flow control member 216 via a stem 220 and a diaphragm plate 222. The diaphragm 218 is captured between a first housing 224 of the actuator 204 and a second housing 226 of the actuator 204 that is removably coupled to the first housing 224 via fasteners 223. Specifically, a first side 232 of the diaphragm 218 and the first housing 224 define a first chamber 228 (e.g., a spring chamber) of the actuator 204, and a second side 234 of the diaphragm 218 and the second housing 226 define a second chamber 230 (e.g., a loading chamber) opposite the first chamber 228. A biasing element or spring 236 is disposed within the first chamber 228 and between the diaphragm plate 222 and an adjustable spring seat 238. A spring adjuster 240 (e.g., a screw) enables adjustment (e.g., increase or decrease) of the amount of a preset force or load that the spring 236 exerts on the first side 232 of the diaphragm 218 to provide a desired pressure set point or outlet pressure. In this example, the first chamber 228 is fluidly coupled to, for example, the atmosphere via a vent or orifice 242. Additionally, to detect a leak through a seal assembly 244 (e.g., packing) located within a bore 246 of the actuator 204 and/or the regulator body 202 through which the valve stem 220 slides, the actuator 204 of the illustrated example includes a leak detection passage or port 248.

The example fluid regulator 102 includes a loading or inlet port 250 to fluidly couple loading fluid (fig. 1) provided by the loading regulator 118 (fig. 1) to the second chamber 230. To control (e.g., reduce or limit) the flow rate of the loading fluid to the second chamber 230, the example fluid regulator 102 of the illustrated example includes a controller or velocity control device 252 (e.g., a restrictor, a valve, etc.). Further, to achieve a relatively rapid (e.g., substantially instantaneous, less than one second, etc.) evacuation of the loading fluid from the second chamber 230, the fluid regulator 102 includes a fluid control device 254 (e.g., a check valve). In some examples, the fluid control device 254 may be formed or implemented with the velocity control device 252. In some such examples, the speed control device 252 may be implemented as a fluid flow restrictor that includes a one-way check valve implemented within the restrictor. In some examples, the fluid control device 254 may be formed as a separate component and/or spaced apart from the velocity control device 252. In some such examples, the speed control device 252 may be a flow restrictor located within the second housing 226 between the inlet port 250 and the second chamber 230, and the fluid control device 254 may be a one-way check valve located between the second chamber 230 and the exhaust passage 256.

A solenoid valve 258 (e.g., a three-way solenoid valve) moves between a first position (e.g., a closed position) and a second position (e.g., an open position) to control or allow the flow of loading fluid to the second chamber 230 via the inlet port 250 and the speed control device 252. For example, during ignition of main combustor 108 (fig. 1), combustor management system 104 of fig. 1 commands solenoid valve 258 to move to the second position to allow loading fluid to flow to inlet port 250. During the shut down of the main combustor 108, the combustor management system 104 of fig. 1 commands the solenoid valve 258 to move between a second position (e.g., an open position) and a third position (e.g., a vent position) to enable the pressurized fluid in the second chamber 230 to be vented or exhausted from the second chamber 230. The loading fluid is discharged to the main line 114 downstream of the outlet 210 via the fluid control device 254 and the discharge passage 256. In some examples, the solenoid valve 258 may be separate from the regulator body 202, the actuator 204, and/or, more generally, the fluid regulator 102. In some examples, the solenoid valve 258 may be located within the regulator body 202, the actuator 204, and/or, more generally, the fluid regulator 102 (e.g., within the size range of the regulator body 102, the actuator 204, and/or the fluid regulator 102).

In operation, to ignite the main combustor 108, the combustor management system 104 of fig. 1 provides a signal to the solenoid valve 258 to move to a position (e.g., an open position) that allows loading fluid to flow into the second chamber 230. The velocity control device 252, in turn, limits the velocity of the loading fluid flowing into the second chamber 230. In this manner, the second chamber 230 fills at a relatively slow rate compared to a fluid regulator that is not implemented with the speed control device 252. Thus, as the loading fluid fills the second chamber 230, the loading fluid gradually increases the pressure applied to the second side 234 of the diaphragm 218, causing the flow control member 216 to gradually or slowly move away from or away from the valve seat 214 as the flow control member 216 moves from a closed position (e.g., a fully closed position) sealingly engaging the valve seat 214 to an open position spaced apart from or disengaged from the valve seat 214. For example, the velocity control device 252 may be configured or adjusted such that the flow control member 216 moves between the fully closed position and the fully open position in approximately 2 seconds to 10 seconds. This gradual opening or separation between the flow control member 216 and the valve seat 214 allows the supply fluid to flow through the orifice 212 at a relatively slow rate. By controlling the speed at which the flow control member 216 moves from the closed position to the open position, the fluid regulator 102 reduces or substantially prevents pilot blow-off and/or flashback that may otherwise occur when the fluid regulator opens too quickly and surges and/or excessive accumulations of supply fluid flow to the main burner 108 during (e.g., prior to) ignition. For example, when the fluid regulator 102 moves too quickly to the open position, a surge of supply fluid to the main burner 108 may blow out or extinguish the pilot burner 110 (e.g., pilot light blow-off). In some examples, accumulation and/or excessive supply of fluid at main combustor 108 during an ignition phase or start-up may cause flashback or a small explosion. Accordingly, the example fluid regulator 102 provides a controlled flow rate of supply fluid to reduce or prevent surging and/or oversupply of fluid when the main combustor 108 is ignited. For example, the fluid regulator 102 may be configured with an opening rate that is compliant with canadian standard law section 149.3 (CSA 149.3).

To shut down the main combustor 108, the combustor management system 104 provides a signal to the solenoid valve 258 to move to a position (e.g., a drain position) that allows the loading fluid in the second chamber 230 to drain to the main line 114 via the fluid control device 254 and the drain passage 256. When the second chamber 230 is evacuated or vented via the fluid control device 254, the force exerted on the second side 234 of the diaphragm 218 decreases below the preset force exerted on the first side 232 of the diaphragm 218 via the spring 236. When the pressure in the second chamber 230 is lower than the pressure in the first chamber 228, the spring 236 causes the diaphragm 218 to move toward the second chamber 230. In turn, the flow control member 216 moves toward the valve seat 214 to restrict or prevent the flow of the supply fluid between the inlet 208 and the outlet 210. For example, the flow control member 216 moves from an open position (e.g., a fully open position) to a closed position (e.g., a fully closed position) in which the flow control member 216 sealingly engages the valve seat 214 to prevent the flow of the supply fluid between the inlet 208 and the outlet 210. While the example fluid regulator 102 enables the flow control member 216 to gradually open from the closed position to the open position via the velocity control device 252, the fluid control device 254 enables the flow control member 216 to move from the open position to the closed position substantially instantaneously (e.g., less than 3 seconds, less than one second, etc.). In other words, the flow control member 216 moves from the closed position to the open position at a speed or rate that is significantly slower than the speed or rate at which the flow control member 216 moves from the open position (e.g., the fully open position) to the closed position (e.g., the fully closed position). Thus, the fluid control device 254 provides a substantially quick or expeditious shut-off capability during, for example, an emergency.

Fig. 3A is a perspective partial cross-sectional view of an actuator 300 constructed in accordance with the teachings of the present disclosure. For example, the actuator 300 may be used to implement the example fluid regulator 102 and/or the example actuator 204 of fig. 1 and 2.

Fig. 3B is an enlarged view of a portion of the example actuator 300 of fig. 3A. Those components of the example actuator 300 that are substantially similar or identical to and have substantially similar or identical functions to the components of the example actuator 204 and/or the fluid regulator 102 described above in connection with fig. 1 and 2 will not be described in detail below. Instead, the interested reader is referred to the corresponding description above. To facilitate this process, like reference numerals will be used for like structures.

Referring to fig. 3A and 3B, the example actuator 300 is removably coupled to the regulator body 202 via, for example, a fastener 302. The actuator 300 of the illustrated example includes a first housing portion 304 (e.g., body) coupled to a second housing portion 306 (e.g., cap) via a plurality of fasteners 308. An actuating member or diaphragm 310 is positioned between the first housing portion 304 and the second housing portion 306 to define a loading chamber 312. In some examples, the actuation member 310 may be a piston and/or any other suitable actuation member.

Referring to fig. 3B, the first housing portion 304 of the actuator 300 defines a loading fluid passage 314 to fluidly couple the inlet port 316 and the loading chamber 312. The loading fluid passageway 314 of the illustrated example includes a first inlet 318 defined by an inlet port 316, and a first outlet 320 in fluid communication with the loading chamber 312. In this example, the loading fluid passage 314 is integrally formed in the first housing portion 304 of the actuator 300, and the first outlet 320 is formed in a surface 322 of the first housing portion 304 that defines the loading chamber 312. The loading fluid passageway 314 includes a first portion 324 defining the inlet port 316 and a second portion 326 defining the first outlet 320. The first portion 324 of the loading fluid passageway 314 has an axis 328 that is substantially perpendicular relative to a longitudinal axis 330 of the actuator 300, and the second portion 326 has an axis 332 that is substantially parallel relative to the longitudinal axis 330 and/or substantially perpendicular relative to the axis 328. While the axis 332 is substantially parallel relative to the longitudinal axis 330, the second portion 326 of the loading fluid passage 314 is laterally offset or spaced apart from the central opening 334 of the first housing portion 304, which first housing portion 304 receives the valve stem 220 of the regulator body 202.

To control or regulate the flow rate of the loading fluid flowing to the loading chamber 312 via the loading fluid passageway 314, the actuator 300 of the illustrated example includes a flow restrictor 336. For example, the flow restrictor 336 may implement the example speed control device 252 of the example fluid regulator 102 of fig. 1 and 2. A flow restrictor 336 is inserted in the second portion 326 of the loading fluid passageway 314 to control or restrict fluid flow between the inlet port 316 and the loading chamber 312 (e.g., between the first portion 324 of the loading fluid passageway 314 and the first outlet 320). The flow restrictor 336 of the illustrated example is adjustable via an access port 338 accessible from an exterior surface 340 of the actuator 300 or the first housing portion 304. As shown, the access port 338 is recessed relative to an outer surface 340 of the first housing portion 304. Additionally, the inlet port 316 of the loading fluid passage 314 is positioned between about 30 degrees and 90 degrees from the inlet port 338 relative to the longitudinal axis 330. The flow restrictor 336 is described in more detail in connection with FIG. 4.

Referring to fig. 3A and 3B, a solenoid valve 342 (e.g., a three-way solenoid valve) fluidly couples the inlet port 316 and the loading fluid via a conduit or line 344. The solenoid valve 342 of the illustrated example is positioned near the actuator 300 or upstream of the inlet port 316. In other words, the solenoid valve 342 is positioned outside the dimensional envelope of the actuator 300. The solenoid valve 342 may receive a command (e.g., from the combustor management system 104 of fig. 1) to move between a first position and a second position to enable a flow of a loading fluid from a loading fluid line 346 (e.g., coupled to the loading line 120 of fig. 1) to the inlet port 316 of the actuator 300 via a conduit 344.

To remove the loading fluid from the loading chamber 312, the example actuator 300 includes a fluid control device 348. The fluid control device 348 of the illustrated example is positioned between the loading chamber 312 and the inlet 316 of the loading fluid passageway 314. Specifically, the fluid control device 348 has a second inlet 350 in fluid communication with the loading chamber 312 and a second outlet 352 in fluid communication with the inlet port 316 via the first portion 324 of the loading fluid passageway 314. The solenoid valve 342 may receive a command (e.g., from the combustor management system 104 of fig. 1) to move between the second position and the third position to fluidly couple the inlet port 316 to the exhaust line 354 via the conduit 344. When the solenoid valve 342 is in the third position, loading fluid from the loading fluid line 346 is blocked to prevent the flow of loading fluid to the inlet port 316 via the conduit 344. Instead, the loading fluid passage 314 is fluidly coupled to the exhaust line 354 via conduit 344 to provide a (e.g., reverse) flow path to exhaust the loading fluid from the loading chamber 312. Specifically, the absence of loading fluid in the first portion 324 of the loading fluid path 314 and the presence of loading fluid in the loading chamber 312 causes a pressure differential across the fluid control device 348 that is greater than a threshold pressure differential. Accordingly, the fluid control device 348 moves to the open position to exhaust the loading chamber 312 via the conduit 344 and the exhaust line 354.

On the other hand, when the first portion 324 of the loading fluid passageway 314 is fluidly coupled to the loading fluid line 346 via the conduit 344, the pressure differential across the fluid control device 348 is less than the pressure differential threshold, thereby causing the fluid control device 348 to move to the closed position and preventing fluid flow across the fluid control device 348 between the loading chamber 312 and the loading fluid passageway 314. The fluid control device 348 is discussed in more detail in connection with fig. 5A and 5B.

Fig. 4 is a side partial cross-sectional view of the example actuator 300 of fig. 3A and 3B. The flow restrictor 336 of the illustrated example includes a screw 402, the screw 402 having an axis 404 substantially perpendicular to the axis 332 of the second portion 326 of the loading fluid passageway 314. The restrictor 336 includes a threaded portion 406, the threaded portion 406 being threaded within an inlet port 338 of the first housing portion 304 such that the position of the restrictor 336 is movable between a first position (e.g., a fully open position) and a second position (e.g., a fully closed position) to vary or adjust the fluid flow rate of the loading fluid flowing to the loading chamber 312 via the loading fluid passageway 314 (e.g., a second portion thereof). Specifically, the flow rate through the loading fluid passageway 314 may be adjusted between a first flow rate (e.g., a maximum flow rate) when the restrictor 336 is in a first position (e.g., a fully open position) and a second flow rate (e.g., a minimum flow rate) less than the first flow rate when the restrictor 336 is in a second position (e.g., a fully closed position). The flow restrictor 336 includes a seal 408 to prevent the loading fluid in the second portion 326 of the loading fluid passageway 314 from flowing through the opening 410 of the inlet port 338. The locking pin 412 retains the restrictor 336 within the access port 338 and prevents the restrictor 336 from being removed (e.g., completely removed) from the access port 338. In some examples, the locking pin 412 limits or prevents the restrictor 336 from moving beyond the first position. In the example shown, end 414 of restrictor 336 moves within transition portion 416 of loading fluid passage 314, which transition portion 416 fluidly couples first portion 324 and second portion 326. The transition portion 416 may include a stop 418 to limit or prevent movement of the restrictor 336 (e.g., the end 414 of the restrictor 336) beyond the second position. Specifically, the stop 418 of the transition portion 416 includes a profile or shape that is complementary to the profile or shape of the end 414 of the restrictor 336.

The restrictor 336 may be moved to a first position by rotating the restrictor 336 in a first direction about the axis 404, and the restrictor 336 may be moved to a second position by rotating the restrictor 336 in a second direction about the axis 404, opposite the first direction. In the first position, at least a portion of end 414 of restrictor 336 positioned in transition portion 416 is spaced apart from opening 420 of second portion 326 of loading fluid passageway 314 to enable fluid flow between first portion 324 and second portion 326 of loading fluid passageway 314. Thus, in the first position, the end 414 of the restrictor 336 exposes at least a portion of the opening 420 to increase the flow rate of the loading fluid flowing to the loading chamber 312 via the second portion 326 of the loading fluid passageway 314. In the second position, end 414 of restrictor 336 is positioned adjacent to opening 420 such that end 414 blocks (e.g., at least partially obstructs) or at least partially covers opening 420 of second portion 326 of loading fluid passageway 314. Thus, in the second position, the end 414 of the restrictor 336 blocks or obstructs at least a portion of the opening 420 of the second portion 326 to reduce the flow rate of the loading fluid flowing to the loading chamber 312 via the second portion 326 of the loading fluid passageway 314. In some examples, when the restrictor 336 is in the second position, the restrictor 336 completely blocks or covers the opening 420 to prevent fluid flow through the second portion 326 of the loading fluid passage 314. When the restrictor 336 is in the first position, the increased fluid flow rate of the loading fluid through the second portion 326 increases the speed at which the flow control member 216 (fig. 1) moves to the open position. When the restrictor 336 is in the second position, the reduced flow rate of the loading fluid through the second portion 326 reduces the speed at which the flow control member 216 (fig. 1) moves to the open position. When positioned in the first or second position, the restrictor 336 causes the flow control member 216 to move from the closed position to the open position at a speed or time that is less than the speed or time that the flow control member 216 moves from the open position to the closed position.

In some examples, the restrictor 336 may be a fluid control device and/or a solenoid that moves between the first position and the second position. For example, during a loading operation, when implemented via a solenoid valve, the restrictor 336 may receive a signal to move to a first position, allowing loading fluid to flow into the loading chamber 312. When the loading chamber 312 is vented, such as when implemented via a solenoid valve, the restrictor 336 may receive a signal to move to the second position, thereby preventing or substantially restricting fluid flow through the second portion 326 of the loading fluid passage 314.

Fig. 5A is a cross-sectional view of the example actuator 300 and the regulator body 202 of fig. 3A, 3B, and 4. Fig. 5B is an enlarged portion of a cross-sectional view of the example actuator 300 of fig. 5A. Referring to fig. 5A and 5B, the example fluid control device shown is a one-way fluid valve (e.g., a check valve). For example, the fluid control device 348 may be a ball check valve. In some examples, the fluid control device 348 may be a solenoid valve and/or any other fluid control device(s) to evacuate the loading chamber 312.

The fluid control apparatus 348 defines an exhaust passage 502 between a second inlet 350 in fluid communication with the loading chamber 312 and a second outlet 352 in fluid communication with the first portion 324 of the loading fluid passageway 314. The discharge passage 502 of the example fluid control apparatus 348 defines an axis 504 that is substantially parallel and/or substantially perpendicular to the axis 328 of the first portion 324 of the loading fluid passageway 314 relative to the longitudinal axis 330. In the example shown, the axis 504 of the fluid control device 348 is spaced apart or laterally offset relative to the longitudinal axis 330 and/or the central opening 334 of the first housing portion 304. The axis 504 is laterally offset from the axis 332 of the second portion 326 of the loading fluid passageway 314.

Referring to fig. 5B, the fluid control device 348 defines a body 506 that is positioned within the bore 508 of the first housing portion 304. One or more seals 510 are positioned within bore 508 between the outer surface of body 506 and the inner surface of bore 508 to prevent loading fluid in loading chamber 312 from leaking into first portion 324 of loading fluid passageway 314. The fluid control apparatus 348 of the illustrated example includes a flow control member 512 (e.g., a ball) biased toward a seat surface 514 via a biasing element 516 (e.g., a spring). Thus, when the fluid control apparatus 348 is in the closed position, the biasing element 516 biases the flow control member 512 to sealingly engage the seating surface 514, thereby preventing fluid flow through the discharge passage 502 between the second inlet 350 and the second outlet 352.

When the force or pressure provided on a first side 518 of the flow control member 512 (e.g., downward direction 522 in the orientation of fig. 5B) is less than the force or pressure provided on a second side 520 of the flow control member 512 opposite the first side (e.g., upward direction 524 in the orientation of fig. 5B), the fluid control apparatus 348 moves to the closed position to prevent fluid flow through the drain channel 502. For example, the loading fluid flowing through the loading fluid passageway 314 and the loading fluid in the loading chamber 312 provide substantially equal pressures or forces on the first and

second sides

518, 520 of the flow control member 512 such that the force of the biasing element 516 moves the flow control member 512 into sealing engagement with the seat surface 514. Thus, when the loading fluid is fluidly coupled to the loading chamber 312, the fluid control apparatus 348 is in a closed position to prevent the loading fluid in the loading chamber 312 from flowing toward the first portion 324 of the loading fluid passageway 314.

When the force or pressure on the first side 518 of the flow control member 512 is greater than the force or pressure on the second side 520 of the flow control member 512 (e.g., the pressure provided by the biasing element 516 and in the first portion 324 of the loading fluid passageway 314), the fluid control apparatus 348 moves to the open position to allow the loading fluid in the loading chamber 312 to flow to the first portion 324 of the loading fluid passageway 314. When the loading fluid is removed or prevented from flowing through the first portion 324 of the loading fluid passageway 314, the pressure of the loading fluid in the loading chamber 312 exerts a force on the actuation member 310 that overcomes the force of the biasing element 516. Thus, the fluid control apparatus 348 of the illustrated example allows fluid in the loading chamber 312 to vent when the pressure in the loading chamber 312 is substantially greater than the pressure in the loading fluid passageway 314 (e.g., the first portion of the loading fluid passageway). For example, referring also to fig. 3A, to move the flow control member 512 to the open position and discharge the loading chamber 312, the solenoid valve 342 is moved between the second position and the third position to couple the inlet port 316 to the drain line 354 via conduit 344. When the solenoid valve 342 is in the third position, loading fluid from the loading fluid line 346 is blocked from flowing to the inlet port 316 via the conduit 344. Instead, the loading fluid passage 314 is fluidly coupled to the drain line 354 via conduit 344. When the drain line 354 is coupled to the main line downstream of the outlet 210 (e.g., as shown in fig. 1 and 2), the pressure of the supply fluid downstream of the outlet 210 is less than the pressure of the loading fluid. Thus, if the first portion 324 of the loading fluid passageway 314 records the pressure of the downstream supply fluid via the drain line 354, the force of the biasing element 516 and the pressure of the downstream supply fluid (e.g., recorded in the first portion 324) are insufficient to overcome the force provided to the second side 520 of the flow control member 512 by the loading fluid in the loading chamber 312, thereby causing the flow control member 512 to move away from the seat surface 514 to the open position until the loading fluid is discharged from the loading chamber 312. The fluid control device 348 discharges the loading fluid from the loading chamber 312 relatively quickly compared to the rate at which the flow restrictor 336 fills the loading chamber 312 with the loading fluid. In this manner, the fluid control device 348 causes the flow control member 216 to move from the open position to the closed position substantially faster (e.g., almost instantaneously, less than one second, less than 3 seconds, etc.) than the speed or time (e.g., greater than 3 seconds, between about 3 seconds and 10 seconds, etc.) that the restrictor 336 causes the flow control member 216 to move from the closed position to the open position.

Fig. 6 illustrates another example actuator 600 configured in accordance with the teachings of the present disclosure. For example, the example actuator 600 may implement the example fluid regulator 102 of fig. 1 and 2. The example actuator 600 of the illustrated example includes a first housing portion 602 coupled to a second housing portion 604. The first housing portion 602 includes a velocity control device or restrictor 606 to control the flow rate of the loading fluid flowing between the inlet port 608 and the loading chamber defined by the actuator 600. Additionally, the actuator 600 includes a flow control device 610 (e.g., a check valve similar to the fluid control device 348) within the actuator 600 to vent the loading chamber of the actuator 600. The loading chamber may be exhausted through the inlet port 608 or another exhaust path that does not pass through the inlet port 608. Additionally, a solenoid valve 612 (e.g., solenoid valve 258) is positioned inside the actuator 600 between the inlet port 608 and the loading chamber (e.g., second chamber 230 or 312). In other words, the solenoid valve 612 is positioned within the size envelope of the actuator 600.

In some examples, the

example actuators

204, 300, and/or 600 disclosed herein may be factory assembled with the regulator body 202. In some examples, the

example actuators

204, 300, and/or 600 and/or the example second housing 226 or the first housing portion 304 and/or 602 may retrofit existing regulators and/or fluid control devices in the field. Accordingly, the

example actuators

204, 300, and/or 600 and/or the example second housing 226 or first housing portion 304 and/or 602 disclosed herein may be provided as components for retrofitting existing fluid regulators and/or other fluid control devices.

Fig. 7 and 8 illustrate another example fluid regulator 700 and actuator 702 configured in accordance with the teachings of the present disclosure. The example fluid regulator 700 and the actuator 702 are substantially identical to the fluid regulator 102 and the actuator 300 described above, and those components of the example fluid regulator 700 and the actuator 702 that are substantially similar or identical to the components of the example fluid regulator 102 and the actuator 300 described above and that have functions that are substantially similar or identical to the functions of those components will not be described in detail below. Instead, the interested reader is referred to the corresponding description above. To facilitate this process, like reference numerals will be used for like structures.

In some of these examples, the fluid regulator 700 may be a failed closed valve, a failed open valve, or any other classification of valves and/or regulators depending on the particular orientation of the components of the valve. The fluid regulator 700 has a regulator body 202 defining an inlet 208, an outlet 210, and an inlet port 316, an inlet port 338, a loading chamber 312 disposed within the regulator body 202 and coupled to the inlet port 338, a valve assembly disposed at least partially between the inlet 208 and the outlet 210 and in communication with the loading chamber 312 to regulate fluid flow at the outlet 210 by regulating a fluid flow rate between the inlet 208 and the outlet 210, and a flow restrictor 710 disposed at least partially within the inlet port 338.

The loading chamber 312 and valve assembly are adapted to respond to changes in loading pressure such that a modified rate is achieved. The restrictor 710 is adapted to adjust the response speed to achieve the modified rate.

The fluid regulator 700 may also include a valve seat 214 at the orifice 212 and a flow control member 216 of the valve assembly. The flow control member 216 is urged toward contact with the valve seat 214 by a biasing element 236 (e.g., a spring) contained in the first chamber 228. The biasing element 236 engages the diaphragm plate 222 to operably couple to the valve stem 220, which in turn operably couples to the flow control member 216.

As described above, when the loading pressure received at the inlet port 316 is at a steady state value, the pressure in the loading chamber 312 is also at a steady state value. The biasing element 236 applies a force equal to the pressure within the loading chamber 312 to maintain the flow control member 216 in an equilibrium position relative to the valve seat 214. In this way, the fluid flow between the inlet 208 and the outlet 210 is at a constant rate. As the loading pressure received at the inlet port 316 changes, the pressure at the loading chamber 312 also changes and causes the biasing element 236 to adjust to apply an adjusted force equal to the pressure within the loading chamber 312. Thus, the flow control member 216 is repositioned and the fluid flow between the inlet 208 and the outlet 210 is at a different rate.

A restrictor 710 is disposed within the inlet port 338 to regulate the rate at which the loading chamber 312 experiences pressure changes. The occluder 710 includes a screw 712 having a longitudinal axis 714, the longitudinal axis 714 being substantially perpendicular to the axis 332 of the second portion 326 of the loading fluid passageway 314. The restrictor 710 includes a threaded portion 716 that is threaded within the inlet port 338 of the first housing portion 304 to enable the position of the restrictor 710 to be moved between a first position (e.g., a fully open position) and a second position (e.g., a fully closed position) to change or adjust the fluid flow rate of the loading fluid flowing to the loading chamber 312 via the loading fluid passageway 314. In particular, the flow rate through the loading fluid passageway 314 may be adjusted to be at various different flow rates between a first flow rate (e.g., a maximum flow rate) when the restrictor 710 is in a first position (e.g., a fully open position) and a second flow rate (e.g., a minimum flow rate) that is less than the first flow rate when the restrictor 710 is in a second position (e.g., a fully closed position). In some examples, the restrictor 710 may be friction fit into the entry port 338 and/or the restrictor 710 may include a channel that extends the length of the restrictor 710 to allow an amount of fluid to flow between the entry port 338 and the loading chamber 312. The flow restrictor 710 includes a seal 718 to prevent the loading fluid in the second portion 326 of the loading fluid passageway 314 from flowing through the opening 410 of the inlet port 338. The locking pin 720 may retain the occluder 710 within the entry port 338 and prevent the occluder 710 from being removed (e.g., completely removed) from the entry port 338. In some examples, the locking pin 720 may limit or prevent the occluder 710 from moving beyond the first position. In the illustrated example, the tapered end 725 of the restrictor 710 moves within a cylindrical transition portion 730 of the loading fluid passage 314 that fluidly couples the first portion 324 and the second portion 326.

The occluder 710 may be moved toward a first position by rotating the occluder 710 in a first direction about the axis 714, and the occluder 710 may be moved toward a second position by rotating the occluder 710 in a second direction opposite the first direction about the axis 714. In the first position, the restrictor 710 is positioned such that the tapered end 725 is spaced from the transition portion 730, thereby enabling fluid flow between the first portion 324 and the second portion 326 of the loading fluid passageway 314. Thus, in the first position, the tapered end 725 of the restrictor 710 exposes at least a portion of the transition portion 730 to increase the flow rate of the loading fluid flowing to the loading chamber 312 via the second portion 326 of the loading fluid passageway 314. In the second position, the tapered end 725 of the occluder 710 is positioned to extend completely into the transition portion 730, such that the tapered end 725 obstructs the transition portion 730. Thus, in the second position, the tapered end 725 of the restrictor 710 blocks or obstructs the transition portion 730 to prevent the flow of loading fluid to the loading chamber 312 via the second portion 326 of the loading fluid passageway 314. The flow restrictors 710 may also be positioned at various locations between the first and second positions to at least partially restrict flow between the first and second portions 324, 326 of the loading fluid passageway 314. As the occluder 710 moves away from the second position, the flow area provided between the first portion 324 and the second portion 326 slowly increases due to the decreasing cross-sectional area of the tapered end 725 and the constant cross-sectional area of the cylindrical transition portion 730. Accordingly, the flow restrictor 710 is adapted to be at least partially disposed within the transition portion 730 to adjustably restrict the flow rate of the fluid.

When the restrictor 710 is in the first position, the increased fluid flow rate of the loading fluid through the second portion 326 increases the speed at which the flow control member 216 (fig. 1) moves to the open position. When the restrictor 710 is in the second position, the flow control member 216 (fig. 1) is prevented from moving. The reduced flow rate of the loading fluid through the second portion 326 compared to the first position reduces the speed at which the flow control member 216 (fig. 1) moves to the open position when the restrictor 710 is positioned between the first position and the second position. Depending on the location of the occluder 710 within the transition portion 730, different portions of the taper of the tapered end 725 are disposed within the transition portion 730. As the cross-sectional diameter of the tapered end 725 of the flow restrictor 710 disposed within the transition portion 730 increases, the flow path velocity through the transition portion 730 decreases as the open volume of the flow path decreases. Thus, the rate at which the loading chamber 312 receives the load pressure may be varied or controlled.

Because the outer profile of the flow restrictor 710 contains a tapered end 725, the unit can be easily inspected to ensure that there is no damage. Furthermore, because the flow rate adjustment is housed within the flow restrictor 710, no complex arrangement and/or structure is required.

While various embodiments have been described above, the present disclosure is not intended to be so limited. Those skilled in the art will recognize that a wide variety of modifications, alterations, and combinations can be made with respect to the above described embodiments without departing from the scope of the invention, and that such modifications, alterations, and combinations are to be viewed as being within the ambit of the inventive concept.

Claims

1. A fluid regulator, comprising:

a valve body defining an inlet, an outlet, a loading port, and an entry port;

a loading chamber disposed within the valve body and coupled to the loading port;

a valve assembly disposed at least partially between the inlet and the outlet and in communication with the loading chamber, the valve assembly adapted to cooperate with the loading chamber to regulate fluid flow at the outlet by regulating a fluid flow rate between the inlet and the outlet; and

a flow restrictor at least partially disposed within the inlet port;

wherein the loading chamber and the valve assembly are adapted to respond to changes in loading pressure such that a modified rate is reached, and the flow restrictor is adapted to adjust the speed of response to the modified rate.

2. The fluid regulator of claim 1, wherein the flow restrictor comprises a tapered end that is adjustable to achieve a plurality of response speeds.

3. A fluid regulator of claim 2, wherein the flow restrictor further comprises a threaded portion adapted to be threadably inserted into the inlet port.

4. A fluid regulator of claim 3, wherein the loading chamber is adapted to undergo a pressure change as the loading pressure changes, the pressure change causing the valve assembly to urge to the modified rate.

5. The fluid regulator of claim 1, further comprising a transition portion positioned between the first portion and the second portion of the loading fluid passageway, wherein the flow restrictor is adapted to be at least partially disposed within the transition portion to adjustably restrict a flow rate of fluid propagating through the loading fluid passageway.

6. The fluid regulator of claim 1, wherein the flow restrictor comprises a threaded portion.

7. A fluid regulator of claim 1, further comprising a diaphragm disposed at least partially within the loading chamber, wherein the diaphragm is adapted to move in response to a change in the loading pressure to equalize the loading pressure in the loading chamber with a force applied by a biasing element.

8. A fluid regulator of claim 2, wherein the flow restrictor comprises a seal for sealing the flow restrictor within the inlet port.

9. An apparatus for regulating a flow rate into a loading chamber of a fluid regulator, the apparatus comprising:

a flow restrictor adapted to be at least partially disposed in an entry port and a loading fluid passageway, the flow restrictor comprising a screw extending along a longitudinal axis and a tapered end having a cross-section wherein the cross-sectional area decreases along the length of the tapered end, wherein the flow restrictor limits the flow rate propagating through the loading fluid passageway based on insertion depth when the flow restrictor is inserted into the entry port.

10. The apparatus of claim 9, wherein the flow restrictor comprises a threaded portion such that the flow restrictor is threadably coupled to the access port.