US20120003106A1 - Tunable choke tube for pulsation control device used with gas compressor - Google Patents
Tunable choke tube for pulsation control device used with gas compressor Download PDFInfo
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- US20120003106A1 US20120003106A1 US13/231,868 US201113231868A US2012003106A1 US 20120003106 A1 US20120003106 A1 US 20120003106A1 US 201113231868 A US201113231868 A US 201113231868A US 2012003106 A1 US2012003106 A1 US 2012003106A1
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- choke tube
- compressor
- choke
- side branch
- conduits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/12—Casings; Cylinders; Cylinder heads; Fluid connections
- F04B39/123—Fluid connections
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0027—Pulsation and noise damping means
- F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/0027—Pulsation and noise damping means
- F04B39/0055—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes
- F04B39/0061—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using muffler volumes
Definitions
- This invention relates to reciprocating compressors for transporting natural gas, and more particularly to an improved method for controlling pulsations in the piping system associated with such compressors.
- Natural gas pipeline networks connect production operations with local distribution companies through thousands of miles of gas transmission lines.
- reciprocating gas compressors are used as the prime mover for pipeline transport operations because of the relatively high pressure ratio required.
- Reciprocating gas compressors may also be used to compress gas for storage applications or prior to transport in processing plant applications.
- Reciprocating gas compressors are a type of compressor that compresses gas using a piston in a cylinder connected to a crankshaft.
- the crankshaft may be driven by an electric motor.
- a suction valve in the compressor cylinder receives input gas, which is then compressed by the piston and discharged through a discharge valve.
- Reciprocating gas compressors inherently generate transient pulsating flows because of the piston motion and alternating valve motion.
- Various devices and control methods have been developed to control these pulsations.
- An ideal pulsation control design reduces system pulsations to acceptable levels without compromising compressor performance.
- a common method for pulsation control is the use of “filter bottles”, also called “pulsation filters”, placed between the compressor and the pipeline headers. These filters are typically implemented as volume-choke-volume devices. They function as low-pass acoustic filters, and attenuate pulsations on the basis of a predetermined Helmholtz response.
- FIG. 1 is a block diagram of a “generic” reciprocating gas compressor system.
- FIG. 2 is a perspective view of the cylinders and pulsation filter bottles (suction side and discharge side) of a six-cylinder reciprocating gas compressor.
- FIG. 3 illustrates the internal elements of a filter bottle having a multi-conduit internal choke tube.
- FIG. 4 illustrates the internal elements of a filter bottle having an internal choke tube in accordance with another embodiment of the invention.
- FIG. 5 illustrates a filter bottle having a multi-conduit external choke tube.
- FIG. 6 illustrates the internal elements of a filter bottle serving two cylinders and having multiple volume-choke-volume components.
- FIG. 7 illustrates a side branch absorber having a multi-conduit internal choke tube.
- FIG. 8 illustrates a side branch absorber having a multi-conduit external choke tube.
- FIGS. 9A and 9B illustrate a side branch absorber having a variable diameter internal choke tube.
- FIGS. 10A and 10B illustrate a side branch absorber having a variable diameter external choke tube.
- the pulsation control device may have an internal or external choke tube.
- the choke tube diameter may be effectively variable in the sense that the choke tube has multiple conduits that can be selectively opened and closed.
- the choke tube may have a single conduit, but may be made from a material or otherwise designed so that the conduit's cross-sectional area is capable of changing along its length.
- these choke tubes are deemed to have a “variable cross section”, whether by means of using multiple conduits or by actually varying the diameter of a single conduit.
- the first type is a filter bottle, which is a “flow through” device.
- the second type is a side branch absorber (SBA), which may be placed at various locations along the path of the gas within the compressor system including its lateral piping. Examples of SBA's used with compressor systems are described in U.S. Patent Pub. Nos. 2007/0289653 and 2007/0101706 and in U.S. patent application Ser. No. 11/734,116, all incorporated herein by reference.
- FIG. 1 is a block diagram of the basic elements of a typical (“generic”) reciprocating gas compressor system 100 .
- Compressor system 100 has a driver 11 , compressor 12 , suction filter bottle 18 a , discharge filter bottle 18 b , suction and discharge piping connections 19 , and a controller 17 .
- compressor 12 has three compressor cylinders 12 a - 12 c .
- compressor 12 may have fewer or more (often as many as six) cylinders. Further, it may have either an integral or separate engine or motor driver 11 .
- a typical application of compressor system 100 is in the gas transmission industry.
- the compressor system 100 operates between two gas transmission lines.
- the first line, at an initial pressure, is referred to as the suction line.
- the second line, at the exit pressure for the station, is referred to as the discharge line.
- the suction and discharge lines are also referred to in the industry as the “lateral piping”.
- the pressure ratio discharge pressure divided by suction pressure may vary between 1.25-4.0, depending on the pipeline operation requirements and the application.
- filter bottles 18 a and 18 b are used to reduce compressor system pulsations. These filter bottles are placed between the compressor and the lateral piping, on the suction or discharge side or on both sides. The effectiveness of filters of this type is dependent on the pulsation frequencies that need to be controlled due to the speed of the compressor. Tunable choke tubes used in connection with filter bottles are described below in connection with FIGS. 2-6 .
- compressor system 100 may also have any number of side branch absorbers in various locations. Tunable choke tubes used in connection with side branch absorbers are described below in connection with FIGS. 7-10 .
- Controller 17 is used for control of parameters affecting compressor load and capacity.
- the pipeline operations will vary based on the flow rate demands and pressure variations.
- the compressor must be capable of changing its flow capacity and load according to the pipeline operation.
- the controller may include control circuitry and programming for controlling choke tubes associated with filter bottles 18 a and 18 b.
- FIG. 2 is a partial perspective view of a six-cylinder reciprocating gas compressor 300 , showing its cylinders and filter bottles. Each set of three cylinders 31 is connected to both a suction-side pulsation filter bottle 32 and a discharge-side pulsation filter bottle 33 . The suction piping 36 and discharge piping 37 are also shown.
- Pulsation filter bottles 32 and 33 are “internal choke tube” filter bottles. As explained below, the filter bottles have two or more internal chamber volumes, separated by baffles. Each pair of chamber volumes is connected with an internal choke tube for carrying gas from one chamber to the other.
- FIG. 3 illustrates the internal elements of a pulsation filter bottle 40 having an internal choke tube 45 .
- filter bottle 40 is a suction-side filter bottle 40 , like the bottle 32 of FIG. 2 .
- bottle 40 is installed between the suction piping and the cylinder intake.
- the concepts described herein also may be applied to a discharge-side pulsation filter bottle.
- the filter bottle 40 operates in conjunction with a single cylinder, and has two volumes separated by a tunable (two-conduit) choke tube 45 .
- a typical filter bottle serves multiple cylinders and has multiple primary volumes that are connected with individual choke tubes to a single secondary volume.
- Filter bottle 40 has a rigid external shell 40 a .
- port 40 b receives gas from the suction piping.
- a second port 40 c delivers gas into the compressor cylinder.
- Filter bottle 40 has two chamber volumes 40 d and 40 e separated by a baffle 43 .
- Choke tube 45 has a plurality of conduits, which permit the two volumes to be in fluid communication.
- choke tube 45 has two conduits, but the concepts described herein could be extended to any number of choke tube conduits.
- the conduits of choke tube 45 may be, but are not necessarily, the same length.
- pulsation filter bottles have a single-conduit choke tube with a fixed cross-sectional area.
- a given filter bottle has a Helmholtz response, which depends on the dimensions of its two volumes and the connecting choke tube. The acoustic dimensions and the resulting physical dimensions are determined by acoustic modeling, and depend on the pulsation frequencies to be dampened (controlled).
- filter bottle 40 is “tunable”. That is, the response of filter bottle 40 can be made to vary depending on the compressor operating conditions. This is accomplished by changing the diameter of the choke tube 45 , more specifically, by opening and closing its conduits.
- one choke tube conduit has a different diameter than the other.
- One or both conduits can be opened or closed using valves 46 .
- the term “valve” is used here in a most general sense to mean any sort of mechanism operable to open and close one end of a conduit.
- FIG. 4 illustrates a second embodiment of a filter bottle 50 having a multi-conduit choke tube 55 .
- the conduits are arranged in a “honeycomb” type design, with the conduits being attached along their axial length. That is, one or more of the conduits may have shared walls.
- choke tube 55 has four conduits 56 . Three of the conduits 56 have a valve 57 at their input end.
- Each of the other conduits is a “secondary” conduit, which may be opened or closed by means of its associated valve 57 .
- One conduit of choke tube 55 is open at the lower operating speeds of the compressor. As the compressor increases speed, the first order excitation frequency increases. In response, the effective diameter of choke tube 55 is increased by opening additional conduits, using valves 57 . The conduits can be incrementally opened as the compressor speed increases. In this manner, the filter bottle response (its filtered frequency) tracks the compressor operation. At the high end of the compressor speed range, the filter frequency may be increased to allow for a larger choke tube diameter. The larger diameter reduces the differential pressure losses in the volume-choke-volume filter.
- the same concepts apply to various designs of multiple conduits, and the choke tube can have any number of conduits. Each conduit or subset of conduits could be matched to a specific operating speed of the compressor.
- a single choke tube could be used, but made of a material that can expand or contract to provide a variable cross sectional area of the choke tube.
- Embodiments of this nature, used in connection with side branch absorbers, are discussed below in connection with FIGS. 9 and 10 .
- FIG. 5 illustrates a filter bottle 60 having an external choke tube 65 .
- Filter bottle has two volumes 60 a and 60 b and choke tube 65 operates in a manner similar to the choke tubes of FIGS. 3 and 4 .
- choke tube 65 is a multi-conduit choke tube like that of FIG. 4 , but it could alternatively have conduits that are physically separate (like those of FIG. 3 ) or it could be a variable cross-sectional area choke tube.
- filter bottle 60 can be either a suction-side or discharge-side filter bottle, and choke tube 65 has valves (not shown) for opening and closing its conduits 66 .
- FIG. 6 illustrates a filter bottle 70 , which is like the filter bottle of FIG. 3 except that it serves two cylinders.
- tunable choke tube concepts could be applied to filter bottles having any number of volumes, each pair of volumes having a tunable choke tube (multi-conduit or variable cross-section) in accordance with the invention.
- a tunable choke tube may be installed for each gas compressor cylinder and corresponding volume-choke-volume components.
- filter bottle 70 has a volume-choke-volume for each cylinder.
- a multi-conduit choke tube 75 serves each volume-choke-volume, and has a valve 76 that operates to open or close one of the conduits.
- side branch absorbers may be placed at various locations within compressor system 100 and its associated piping. Examples, described in the patent applications referenced above, are side branch absorbers ported into lateral piping, a cylinder nozzle, or a manifold. In the figures described below, the side branch absorbers are illustrated in the generalized context of a port into a “surface” which may be the side of piping, a cylinder nozzle, a manifold housing, or any other surface that contains a gas volume or flow.
- FIG. 7 illustrates a side branch absorber 70 having a multi-conduit internal choke tube 75 .
- Side branch absorber 70 comprises a rigid housing 70 a for a gas volume in fluid communication with a “surface” of piping or a gas volume as described above, via choke tube 75 .
- Choke tube 75 has a plurality of conduits.
- choke tube 75 has two conduits, but the concepts described herein could be extended to any number of choke tube conduits.
- the conduits of choke tube 75 may be, but are not necessarily, the same length or diameter.
- choke tube 75 results in side branch absorber being “tunable”. That is, the response of side branch absorber 70 can be made to vary depending on the compressor operating conditions. This is accomplished by changing the diameter of the choke tube 75 , more specifically, by opening and closing its conduits. In the example of FIG. 7 , the diameter of choke tube 75 is varied by opening or closing valves 76 .
- FIG. 8 illustrates a side branch absorber 80 having a multi-conduit external choke tube 85 .
- the structure of choke tube 85 is similar to that used with the filter bottle of FIG. 5 .
- the diameter of the choke tube 85 can be varied by opening or closing valves 86 .
- the multi-conduit choke tubes 75 and 85 could also have a “honeycomb” type design, sharing conduit walls.
- FIGS. 9A and 9B illustrate a side branch absorber 90 having a variable diameter internal choke tube 95 .
- choke tube 95 is made of a material that can expand or contract to provide a variable cross sectional area. The diameter variations may be continuous or incremental.
- choke tube 95 has a diameter that is smaller than that of FIG. 9B .
- controller 17 may be used to provide a control signal to activate the diameter variation.
- FIGS. 10A and 10B illustrate a side branch absorber 110 having a variable diameter external choke tube 115 .
- the diameter of choke tube 115 can be made to vary.
- choke tube 95 has a diameter that is larger than that of FIG. 10B .
- valves of the various multi-conduit choke tubes described herein may be operated manually.
- a choke tube whose cross-sectional area is variable may be manually operated.
- the choke tube may be operated automatically.
- the choke tube valves could be operated, or its diameter could vary, in mechanical response to a flow measurement device, or in response to control signals from a controller.
- controller 17 tracks changing compressor operating conditions, and provides pulsation control optimization for changing pulsation frequencies.
- controller 17 is a comprehensive system control unit, but controller 17 could also a smaller separate controller especially for controlling the diameter of the filter bottle choke tube.
- Pulsation values within the system may be measured with one or more vibration sensing devices 19 .
- An example of a suitable sensing device 19 has a tap into the lateral piping and a pressure-to-voltage transducer, which measures dynamic pressure of the flowing gas within the lateral piping.
- Various measurement devices are known for direct measurement of pulsation within piping. In other embodiments, it may be possible to measure vibration or to infer pulsation changes from changes in other operating conditions.
- Data acquisition signals, representing pulsation frequency and/or amplitude, from sensor 19 may be delivered to controller 17 .
- controller 17 may be programmed to respond simply to changes in compressor speed or flow. Readouts from controller 17 may be used to determine when and how to operate the choke tube, or the data may be used to generate signals for automatic control.
- controller 17 determines control values, and delivers control signals to actuators that adjust the diameter of choke tube 45 or 55 .
- the pulsation control devices described herein may be self-tuning in the sense that programming of controller 17 causes changes in pulsations to result in changes in the diameter of their choke tubes. Dimension adjustments of the choke tubes are accomplished with appropriate mechanisms, controlled by signals from controller 17 .
- Controller 17 is equipped with processing and memory devices, appropriate input and output devices, and an appropriate user interface. It is programmed to perform the various control tasks and deliver control parameters to the compressor system. Given appropriate input data, output specifications, and control objectives described herein, algorithms for programming controller 17 may be developed and executed.
- the tunable choke tube filters described above provide efficiency advantages.
- Conventional filters operate at a single cut-off frequency, hence the filter must be designed for the lowest running speed of the compressor.
- Modern reciprocating compressors operate over a wide speed range, spanning 300-1100 RPM. This relationship between the compressor speed range and the required filter design frequency imposes efficiency losses on the compressor at the higher running speeds.
- the tunability of the various choke tubes described herein reduces total differential pressure, which increases the power for gas compression.
- Differential pressure losses in the filter system are directly related to losses in horsepower and compressor efficiency.
- High speed compressors may operate more efficiently at the higher end of their speed range due to the increase in the filter choke tube diameter.
- a tunable choke tube can be designed to accommodate smaller filter bottles, which are more cost effective and permit smoother compressor operation.
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Abstract
A method and system for reducing pulsation in a gas compressor system. A pulsation control device, such as a filter bottle or side branch absorber, is installed at a port into some location on the compressor system. The pulsation control device has a choke tube with a variable cross-sectional area, such as by having multiple conduits that may be opened or closed or a diameter that may be varied. In operation, the cross sectional area of the choke tube is varied depending on the compressor speed.
Description
- This invention relates to reciprocating compressors for transporting natural gas, and more particularly to an improved method for controlling pulsations in the piping system associated with such compressors.
- To transport natural gas from production sites to consumers, pipeline operators install large compressors at transport stations along the pipelines. Natural gas pipeline networks connect production operations with local distribution companies through thousands of miles of gas transmission lines. Typically, reciprocating gas compressors are used as the prime mover for pipeline transport operations because of the relatively high pressure ratio required. Reciprocating gas compressors may also be used to compress gas for storage applications or prior to transport in processing plant applications.
- Reciprocating gas compressors are a type of compressor that compresses gas using a piston in a cylinder connected to a crankshaft. The crankshaft may be driven by an electric motor. A suction valve in the compressor cylinder receives input gas, which is then compressed by the piston and discharged through a discharge valve.
- Reciprocating gas compressors inherently generate transient pulsating flows because of the piston motion and alternating valve motion. Various devices and control methods have been developed to control these pulsations. An ideal pulsation control design reduces system pulsations to acceptable levels without compromising compressor performance.
- A common method for pulsation control is the use of “filter bottles”, also called “pulsation filters”, placed between the compressor and the pipeline headers. These filters are typically implemented as volume-choke-volume devices. They function as low-pass acoustic filters, and attenuate pulsations on the basis of a predetermined Helmholtz response.
- A more complete understanding of the present embodiments and advantages thereof may be acquired by referring to the following description taken in conjunction with the accompanying drawings, in which like reference numbers indicate like features, and wherein:
-
FIG. 1 is a block diagram of a “generic” reciprocating gas compressor system. -
FIG. 2 is a perspective view of the cylinders and pulsation filter bottles (suction side and discharge side) of a six-cylinder reciprocating gas compressor. -
FIG. 3 illustrates the internal elements of a filter bottle having a multi-conduit internal choke tube. -
FIG. 4 illustrates the internal elements of a filter bottle having an internal choke tube in accordance with another embodiment of the invention. -
FIG. 5 illustrates a filter bottle having a multi-conduit external choke tube. -
FIG. 6 illustrates the internal elements of a filter bottle serving two cylinders and having multiple volume-choke-volume components. -
FIG. 7 illustrates a side branch absorber having a multi-conduit internal choke tube. -
FIG. 8 illustrates a side branch absorber having a multi-conduit external choke tube. -
FIGS. 9A and 9B illustrate a side branch absorber having a variable diameter internal choke tube. -
FIGS. 10A and 10B illustrate a side branch absorber having a variable diameter external choke tube. - The following description is directed to various embodiments of pulsation control devices that are used with a compressor system and that have “tunable” choke tubes. As explained below, the pulsation control device may have an internal or external choke tube. The choke tube diameter may be effectively variable in the sense that the choke tube has multiple conduits that can be selectively opened and closed. Alternatively, the choke tube may have a single conduit, but may be made from a material or otherwise designed so that the conduit's cross-sectional area is capable of changing along its length. For purposes of this description, these choke tubes are deemed to have a “variable cross section”, whether by means of using multiple conduits or by actually varying the diameter of a single conduit.
- Two types of pulsation control devices are described herein. The first type is a filter bottle, which is a “flow through” device. The second type is a side branch absorber (SBA), which may be placed at various locations along the path of the gas within the compressor system including its lateral piping. Examples of SBA's used with compressor systems are described in U.S. Patent Pub. Nos. 2007/0289653 and 2007/0101706 and in U.S. patent application Ser. No. 11/734,116, all incorporated herein by reference.
-
FIG. 1 is a block diagram of the basic elements of a typical (“generic”) reciprocatinggas compressor system 100.Compressor system 100 has adriver 11,compressor 12,suction filter bottle 18 a,discharge filter bottle 18 b, suction anddischarge piping connections 19, and acontroller 17. - In the example of
FIG. 1 ,compressor 12 has threecompressor cylinders 12 a-12 c. In practice,compressor 12 may have fewer or more (often as many as six) cylinders. Further, it may have either an integral or separate engine ormotor driver 11. - The following description is written in terms of the “generic”
compressor system 100. However, the same concepts are applicable to other compressor configurations. - A typical application of
compressor system 100 is in the gas transmission industry. Thecompressor system 100 operates between two gas transmission lines. The first line, at an initial pressure, is referred to as the suction line. The second line, at the exit pressure for the station, is referred to as the discharge line. The suction and discharge lines are also referred to in the industry as the “lateral piping”. The pressure ratio (discharge pressure divided by suction pressure) may vary between 1.25-4.0, depending on the pipeline operation requirements and the application. - As explained in the Background,
filter bottles FIGS. 2-6 . - Although not shown in
FIG. 1 ,compressor system 100 may also have any number of side branch absorbers in various locations. Tunable choke tubes used in connection with side branch absorbers are described below in connection withFIGS. 7-10 . -
Controller 17 is used for control of parameters affecting compressor load and capacity. The pipeline operations will vary based on the flow rate demands and pressure variations. The compressor must be capable of changing its flow capacity and load according to the pipeline operation. As explained below, the controller may include control circuitry and programming for controlling choke tubes associated withfilter bottles - Tunable Choke Tube for Filter Bottles
-
FIG. 2 is a partial perspective view of a six-cylinderreciprocating gas compressor 300, showing its cylinders and filter bottles. Each set of threecylinders 31 is connected to both a suction-sidepulsation filter bottle 32 and a discharge-sidepulsation filter bottle 33. Thesuction piping 36 and discharge piping 37 are also shown. -
Pulsation filter bottles -
FIG. 3 illustrates the internal elements of apulsation filter bottle 40 having aninternal choke tube 45. In the example ofFIG. 3 ,filter bottle 40 is a suction-side filter bottle 40, like thebottle 32 ofFIG. 2 . In other words,bottle 40 is installed between the suction piping and the cylinder intake. However, the concepts described herein also may be applied to a discharge-side pulsation filter bottle. - In the example of
FIG. 3 , thefilter bottle 40 operates in conjunction with a single cylinder, and has two volumes separated by a tunable (two-conduit) choketube 45. As explained below in connection withFIG. 6 , in practice, for a multi-cylinder compressor, a typical filter bottle serves multiple cylinders and has multiple primary volumes that are connected with individual choke tubes to a single secondary volume. -
Filter bottle 40 has a rigidexternal shell 40 a. In the embodiment ofFIG. 3 , wherebottle 40 is a suction-side bottle,port 40 b receives gas from the suction piping. Asecond port 40 c delivers gas into the compressor cylinder. -
Filter bottle 40 has twochamber volumes baffle 43. Choketube 45 has a plurality of conduits, which permit the two volumes to be in fluid communication. In the example of this description, choketube 45 has two conduits, but the concepts described herein could be extended to any number of choke tube conduits. The conduits ofchoke tube 45 may be, but are not necessarily, the same length. - Conventionally, pulsation filter bottles have a single-conduit choke tube with a fixed cross-sectional area. As is known in the art of compressor pulsation control, a given filter bottle has a Helmholtz response, which depends on the dimensions of its two volumes and the connecting choke tube. The acoustic dimensions and the resulting physical dimensions are determined by acoustic modeling, and depend on the pulsation frequencies to be dampened (controlled).
- In the present invention, however, where
filter bottle 40 has amulti-conduit choke tube 45,filter bottle 40 is “tunable”. That is, the response offilter bottle 40 can be made to vary depending on the compressor operating conditions. This is accomplished by changing the diameter of thechoke tube 45, more specifically, by opening and closing its conduits. - In the example embodiment of
FIG. 3 , one choke tube conduit has a different diameter than the other. One or both conduits can be opened or closed usingvalves 46. The term “valve” is used here in a most general sense to mean any sort of mechanism operable to open and close one end of a conduit. -
FIG. 4 illustrates a second embodiment of afilter bottle 50 having amulti-conduit choke tube 55. The conduits are arranged in a “honeycomb” type design, with the conduits being attached along their axial length. That is, one or more of the conduits may have shared walls. In the example ofFIG. 4 , choketube 55 has fourconduits 56. Three of theconduits 56 have avalve 57 at their input end. A “primary” conduit, used at the lowest compressor operating speed, need not have a valve. Each of the other conduits is a “secondary” conduit, which may be opened or closed by means of its associatedvalve 57. - One conduit of
choke tube 55 is open at the lower operating speeds of the compressor. As the compressor increases speed, the first order excitation frequency increases. In response, the effective diameter ofchoke tube 55 is increased by opening additional conduits, usingvalves 57. The conduits can be incrementally opened as the compressor speed increases. In this manner, the filter bottle response (its filtered frequency) tracks the compressor operation. At the high end of the compressor speed range, the filter frequency may be increased to allow for a larger choke tube diameter. The larger diameter reduces the differential pressure losses in the volume-choke-volume filter. - Referring to both
FIGS. 3 and 4 , the same concepts apply to various designs of multiple conduits, and the choke tube can have any number of conduits. Each conduit or subset of conduits could be matched to a specific operating speed of the compressor. - In still other embodiments, a single choke tube could be used, but made of a material that can expand or contract to provide a variable cross sectional area of the choke tube. Embodiments of this nature, used in connection with side branch absorbers, are discussed below in connection with
FIGS. 9 and 10 . -
FIG. 5 illustrates afilter bottle 60 having anexternal choke tube 65. Filter bottle has twovolumes tube 65 operates in a manner similar to the choke tubes ofFIGS. 3 and 4 . In the example ofFIG. 5 , choketube 65 is a multi-conduit choke tube like that ofFIG. 4 , but it could alternatively have conduits that are physically separate (like those ofFIG. 3 ) or it could be a variable cross-sectional area choke tube. As indicated,filter bottle 60 can be either a suction-side or discharge-side filter bottle, and choketube 65 has valves (not shown) for opening and closing itsconduits 66. -
FIG. 6 illustrates afilter bottle 70, which is like the filter bottle ofFIG. 3 except that it serves two cylinders. It should be understood that above-described tunable choke tube concepts could be applied to filter bottles having any number of volumes, each pair of volumes having a tunable choke tube (multi-conduit or variable cross-section) in accordance with the invention. For modern reciprocating compressors, a tunable choke tube may be installed for each gas compressor cylinder and corresponding volume-choke-volume components. - Thus, in
FIG. 6 ,filter bottle 70 has a volume-choke-volume for each cylinder. Amulti-conduit choke tube 75 serves each volume-choke-volume, and has avalve 76 that operates to open or close one of the conduits. - Tunable Choke Tube for Side Branch Absorbers
- As stated above, side branch absorbers may be placed at various locations within
compressor system 100 and its associated piping. Examples, described in the patent applications referenced above, are side branch absorbers ported into lateral piping, a cylinder nozzle, or a manifold. In the figures described below, the side branch absorbers are illustrated in the generalized context of a port into a “surface” which may be the side of piping, a cylinder nozzle, a manifold housing, or any other surface that contains a gas volume or flow. -
FIG. 7 illustrates aside branch absorber 70 having a multi-conduitinternal choke tube 75.Side branch absorber 70 comprises arigid housing 70 a for a gas volume in fluid communication with a “surface” of piping or a gas volume as described above, viachoke tube 75. - Choke
tube 75 has a plurality of conduits. In the example of this description, choketube 75 has two conduits, but the concepts described herein could be extended to any number of choke tube conduits. The conduits ofchoke tube 75 may be, but are not necessarily, the same length or diameter. - The operational principles of
choke tube 75 are similar to those of the internal choke tube discussed above in connection withFIG. 3 . That is,choke tube 75 results in side branch absorber being “tunable”. That is, the response ofside branch absorber 70 can be made to vary depending on the compressor operating conditions. This is accomplished by changing the diameter of thechoke tube 75, more specifically, by opening and closing its conduits. In the example ofFIG. 7 , the diameter ofchoke tube 75 is varied by opening or closingvalves 76. -
FIG. 8 illustrates aside branch absorber 80 having a multi-conduitexternal choke tube 85. The structure ofchoke tube 85 is similar to that used with the filter bottle ofFIG. 5 . Like other multi-conduit choke tubes described herein, the diameter of thechoke tube 85 can be varied by opening or closingvalves 86. - As with the choke tubes for filter bottles, the
multi-conduit choke tubes -
FIGS. 9A and 9B illustrate aside branch absorber 90 having a variable diameterinternal choke tube 95. Rather than having multiple conduits, choketube 95 is made of a material that can expand or contract to provide a variable cross sectional area. The diameter variations may be continuous or incremental. InFIG. 9A , choketube 95 has a diameter that is smaller than that ofFIG. 9B . Although not explicitly illustrated,controller 17 may be used to provide a control signal to activate the diameter variation. -
FIGS. 10A and 10B illustrate aside branch absorber 110 having a variable diameter external choke tube 115. As inFIGS. 9A and 9B , the diameter of choke tube 115 can be made to vary. InFIG. 10A , choketube 95 has a diameter that is larger than that ofFIG. 10B . - Choke Tube Operation and Control
- The valves of the various multi-conduit choke tubes described herein may be operated manually. Similarly, a choke tube whose cross-sectional area is variable may be manually operated. Alternatively, the choke tube may be operated automatically. For example, the choke tube valves could be operated, or its diameter could vary, in mechanical response to a flow measurement device, or in response to control signals from a controller.
- Referring again to
FIG. 1 , for variable speed compressor systems,controller 17 tracks changing compressor operating conditions, and provides pulsation control optimization for changing pulsation frequencies. In the example ofFIG. 1 ,controller 17 is a comprehensive system control unit, butcontroller 17 could also a smaller separate controller especially for controlling the diameter of the filter bottle choke tube. - Pulsation values within the system may be measured with one or more
vibration sensing devices 19. An example of asuitable sensing device 19 has a tap into the lateral piping and a pressure-to-voltage transducer, which measures dynamic pressure of the flowing gas within the lateral piping. Various measurement devices are known for direct measurement of pulsation within piping. In other embodiments, it may be possible to measure vibration or to infer pulsation changes from changes in other operating conditions. - Data acquisition signals, representing pulsation frequency and/or amplitude, from
sensor 19 may be delivered tocontroller 17. In other embodiments,controller 17 may be programmed to respond simply to changes in compressor speed or flow. Readouts fromcontroller 17 may be used to determine when and how to operate the choke tube, or the data may be used to generate signals for automatic control. - For automatic choke tube control,
controller 17 determines control values, and delivers control signals to actuators that adjust the diameter ofchoke tube controller 17 causes changes in pulsations to result in changes in the diameter of their choke tubes. Dimension adjustments of the choke tubes are accomplished with appropriate mechanisms, controlled by signals fromcontroller 17. -
Controller 17 is equipped with processing and memory devices, appropriate input and output devices, and an appropriate user interface. It is programmed to perform the various control tasks and deliver control parameters to the compressor system. Given appropriate input data, output specifications, and control objectives described herein, algorithms for programmingcontroller 17 may be developed and executed. - As compared to conventional volume-choke-volume filters, the tunable choke tube filters described above provide efficiency advantages. Conventional filters operate at a single cut-off frequency, hence the filter must be designed for the lowest running speed of the compressor. Modern reciprocating compressors operate over a wide speed range, spanning 300-1100 RPM. This relationship between the compressor speed range and the required filter design frequency imposes efficiency losses on the compressor at the higher running speeds.
- Furthermore, the tunability of the various choke tubes described herein reduces total differential pressure, which increases the power for gas compression. Differential pressure losses in the filter system are directly related to losses in horsepower and compressor efficiency. High speed compressors may operate more efficiently at the higher end of their speed range due to the increase in the filter choke tube diameter. Additionally, a tunable choke tube can be designed to accommodate smaller filter bottles, which are more cost effective and permit smoother compressor operation.
Claims (8)
1-18. (canceled)
19. A side branch absorber for reducing pulsations associated with a gas compressor system, the compressor system having one or more cylinders connected to lateral piping, the side branch absorber comprising:
a rigid shell, having at least one part for receiving transmission of gas to or from the compressor system;
a choke tube for providing fluid communication between the shell and the compressor system;
wherein the choke tube has a diameter that is variable in response to operating conditions of the compressor.
20. The side branch absorber of claim 19 , wherein the choke tube is internal to the shell.
21. The side branch absorber of claim 19 , wherein the choke tube is external to the shell.
22. The side branch absorber of claim 19 , wherein the choke tube has a primary conduit and one or more secondary conduits, each secondary conduit having a valve for opening and closing the conduit, and wherein the stop of varying the diameter is performed by operating the valves.
23. The side branch absorber of claim 22 , wherein the conduits are axially connected.
24. The side branch absorber of claim 22 , wherein the conduits are physically separate
25. The side branch absorber of claim 19 , wherein the cross-sectional area of the choke tube may be varied along its length, and wherein the step of varying the diameter of the choke tube is performed by activating a change in the cross-sectional area.
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US13/231,868 US20120003106A1 (en) | 2008-01-24 | 2011-09-13 | Tunable choke tube for pulsation control device used with gas compressor |
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US13/231,868 US20120003106A1 (en) | 2008-01-24 | 2011-09-13 | Tunable choke tube for pulsation control device used with gas compressor |
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Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9909577B2 (en) | 2014-01-22 | 2018-03-06 | Jared W. ADAIR | Dynamic variable orifice for compressor pulsation control |
US10487812B2 (en) | 2014-01-22 | 2019-11-26 | Jared W. ADAIR | Dynamic variable orifice for compressor pulsation control |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20110243761A1 (en) * | 2010-03-31 | 2011-10-06 | Rusty Darsey | Pulsation Dampener for Gas Compressors Having Selectable Size Choke Openings |
US8613607B2 (en) * | 2010-03-31 | 2013-12-24 | Fred Rusty Darsey | Pressure pulsation dampener |
US9388712B2 (en) | 2010-10-13 | 2016-07-12 | Southwest Research Institute | Methods and apparatus for an oxy-fuel based power cycle |
US8453788B2 (en) * | 2010-11-10 | 2013-06-04 | International Business Machines Corporation | Implementing dynamic noise elimination with acoustic frame design |
US9790934B2 (en) * | 2011-07-07 | 2017-10-17 | Performance Pulsation Control, Inc. | Pump pulsation discharge dampener with curved internal baffle and pressure drop feature creating two internal volumes |
CN105715327B (en) * | 2016-04-07 | 2018-06-26 | 北京化工大学 | To spraying formula gas attenuator |
US20210222594A1 (en) * | 2020-01-17 | 2021-07-22 | Advanced Flow Engineering Inc. | Tunable Exhaust System |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4546733A (en) * | 1983-03-22 | 1985-10-15 | Nippondenso Co., Ltd. | Resonator for internal combustion engines |
US5894823A (en) * | 1996-12-13 | 1999-04-20 | Hyundai Motor Company | Variable suction resonator system for internal combustion engines |
US5930371A (en) * | 1997-01-07 | 1999-07-27 | Nelson Industries, Inc. | Tunable acoustic system |
US6453695B1 (en) * | 2002-01-18 | 2002-09-24 | Carrier Corporation | Dual length inlet resonator |
US6609489B1 (en) * | 2002-05-07 | 2003-08-26 | General Motors Corporation | Apparatus and method for reducing engine noise |
US6792907B1 (en) * | 2003-03-04 | 2004-09-21 | Visteon Global Technologies, Inc. | Helmholtz resonator |
US20070289653A1 (en) * | 2006-05-23 | 2007-12-20 | Harris Ralph E | Gas Compressor With Side Branch Absorber For Pulsation Control |
US7690478B2 (en) * | 2006-09-15 | 2010-04-06 | Visteon Global Technologies, Inc. | Continuously variable tuned resonator |
Family Cites Families (62)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3181648A (en) * | 1965-05-04 | Adjustable muffler | ||
US734116A (en) * | 1902-12-30 | 1903-07-21 | John Blair | Fountain-pen. |
US2198021A (en) | 1938-04-09 | 1940-04-23 | Westinghouse Air Brake Co | Compressor discharge silencer |
US2501751A (en) * | 1946-03-15 | 1950-03-28 | Fluor Corp | Pulsation and flow control system for gas lines |
US2570241A (en) | 1948-10-09 | 1951-10-09 | Fish Engineering Corp | Pulsation dampener |
US2919715A (en) | 1954-07-02 | 1960-01-05 | Edward A Rockwell | Accumulating apparatus and system |
US2951638A (en) | 1955-05-31 | 1960-09-06 | Southern Gas Ass | Gas pumping system analog |
US2973132A (en) | 1958-10-20 | 1961-02-28 | Worthington Corp | Unloading means for reciprocating compressor |
US3114430A (en) * | 1961-03-06 | 1963-12-17 | Burgess Manning Co | Pulsation snubber or silencer |
US3219141A (en) * | 1963-08-30 | 1965-11-23 | Gen Motors Corp | Compressor muffler having adjustable baffle means controlled by thermally responsive element |
US3936606A (en) | 1971-12-07 | 1976-02-03 | Wanke Ronald L | Acoustic abatement method and apparatus |
DE2318538B2 (en) | 1973-04-12 | 1975-12-04 | Siemens Ag, 1000 Berlin Und 8000 Muenchen | Distributor for a liquid ring gas compressor |
JPS5544404Y2 (en) | 1974-05-09 | 1980-10-18 | ||
US4359134A (en) | 1980-12-05 | 1982-11-16 | American Hospital Supply Corporation | Sound suppressor for fluid flow lines |
US4523612A (en) | 1983-04-15 | 1985-06-18 | The United States Of America As Represented By The United States Department Of Energy | Apparatus and method for suppressing vibration and displacement of a bellows |
US4557349A (en) | 1983-08-10 | 1985-12-10 | Crump Herschel W | Sound-muffling system |
US4570745A (en) | 1984-03-02 | 1986-02-18 | Southern Gas Association | Method and apparatus for minimizing pulsations in fluid transmission systems |
US4658634A (en) * | 1986-02-11 | 1987-04-21 | Piedmont Natural Gas Company | Meter prover |
US5082421A (en) * | 1986-04-28 | 1992-01-21 | Rolls-Royce Plc | Active control of unsteady motion phenomena in turbomachinery |
US4779415A (en) | 1986-11-26 | 1988-10-25 | Arvin Industries, Inc. | Manifold tuning structure |
US5119427A (en) | 1988-03-14 | 1992-06-02 | Hersh Alan S | Extended frequency range Helmholtz resonators |
US4927342A (en) | 1988-12-12 | 1990-05-22 | General Electric Company | Compressor noise attenuation using branch type resonator |
US5189266A (en) | 1989-06-09 | 1993-02-23 | Nissan Motor Co., Ltd. | Vehicular exhaust resonance suppression system and sensing means therefore |
KR920007624B1 (en) | 1990-10-22 | 1992-09-09 | 대우캐리어 주식회사 | Muffler for hermetic rotary compressor |
US5288212A (en) | 1990-12-12 | 1994-02-22 | Goldstar Co., Ltd. | Cylinder head of hermetic reciprocating compressor |
US5183974A (en) * | 1992-04-03 | 1993-02-02 | General Motors Corporation | Gas pulsation attenuator for automotive air conditioning compressor |
US5621656A (en) | 1992-04-15 | 1997-04-15 | Noise Cancellation Technologies, Inc. | Adaptive resonator vibration control system |
US5354185A (en) * | 1992-10-05 | 1994-10-11 | Aura Systems, Inc. | Electromagnetically actuated reciprocating compressor driver |
US5377629A (en) | 1993-10-20 | 1995-01-03 | Siemens Electric Limited | Adaptive manifold tuning |
US5471400A (en) | 1994-05-24 | 1995-11-28 | Gas Research Institute | Method for detecting and specifying compressor cylinder leaks |
CH691465A5 (en) | 1995-04-20 | 2001-07-31 | Dornier Gmbh | Soundproofing for payload fairings in launch vehicles and a method for producing soundproofing. |
DE69724050T8 (en) | 1996-01-23 | 2005-09-15 | Matsushita Refrigeration Co., Higashiosaka | ELECTRICALLY DRIVEN HERMETICALLY CAPSUED COMPRESSOR |
CN1163668C (en) | 1996-06-14 | 2004-08-25 | 松下冷机株式会社 | Hermetic compressor |
TW318529U (en) * | 1996-12-06 | 1997-10-21 | Chen Jen Shiung | Structure of exhaust pipe with pressure adjustment and sound volume adjustment functions |
US6295363B1 (en) | 1997-03-20 | 2001-09-25 | Digisonix, Inc. | Adaptive passive acoustic attenuation system |
US6308694B1 (en) | 1999-01-11 | 2001-10-30 | Ford Global Technologies, Inc. | Flow measurement and control |
JP2003512568A (en) | 1999-10-20 | 2003-04-02 | デーウー・エレクトロニクス・カンパニー・リミテッド | Noise reduction device for reciprocating compressor using side branch silencer |
WO2001044681A2 (en) | 1999-11-17 | 2001-06-21 | Board Of Trustees Operating Michigan State University | Hybrid digital-analog controller |
DE10026121A1 (en) | 2000-05-26 | 2001-11-29 | Alstom Power Nv | Device for damping acoustic vibrations in a combustion chamber |
DE10058688B4 (en) | 2000-11-25 | 2011-08-11 | Alstom Technology Ltd. | Damper arrangement for the reduction of combustion chamber pulsations |
US6684633B2 (en) | 2001-04-27 | 2004-02-03 | Marion Barney Jett | Exhaust device for two-stroke internal combustion engine |
US20020059959A1 (en) | 2002-01-08 | 2002-05-23 | Qatu Mohamad S. | System and apparatus for noise suppression in a fluid line |
US7055484B2 (en) | 2002-01-18 | 2006-06-06 | Carrier Corporation | Multiple frequency Helmholtz resonator |
JP4236878B2 (en) | 2002-07-04 | 2009-03-11 | 株式会社神戸製鋼所 | Damping constant measuring device and damping constant measuring method for hydraulic pulsation absorbing device |
US6799657B2 (en) | 2002-10-02 | 2004-10-05 | Carrier Corporation | Absorptive/reactive muffler for variable speed compressors |
US6698390B1 (en) | 2003-01-24 | 2004-03-02 | Visteon Global Technologies, Inc. | Variable tuned telescoping resonator |
US6814041B1 (en) | 2003-01-31 | 2004-11-09 | Fleetguard, Inc. | Multi-frequency engine intake resonator |
US6935848B2 (en) | 2003-05-19 | 2005-08-30 | Bristol Compressors, Inc. | Discharge muffler placement in a compressor |
NZ526361A (en) | 2003-05-30 | 2006-02-24 | Fisher & Paykel Appliances Ltd | Compressor improvements |
US7275916B2 (en) | 2003-11-24 | 2007-10-02 | Southwest Research Institute | Integrated engine/compressor control for gas transmission compressors |
US20050194207A1 (en) | 2004-03-04 | 2005-09-08 | York International Corporation | Apparatus and method of sound attenuation in a system employing a VSD and a quarter-wave resonator |
US7337877B2 (en) | 2004-03-12 | 2008-03-04 | Visteon Global Technologies, Inc. | Variable geometry resonator for acoustic control |
US7246680B2 (en) | 2004-07-01 | 2007-07-24 | General Motors Corporation | Sound dampening assembly for automotive exhaust system |
US7299894B2 (en) | 2004-07-02 | 2007-11-27 | Anest Iwata Corporation | Acoustic fluid machine |
JP4576944B2 (en) | 2004-09-13 | 2010-11-10 | パナソニック株式会社 | Refrigerant compressor |
US7866147B2 (en) | 2005-09-30 | 2011-01-11 | Southwest Research Institute | Side branch absorber for exhaust manifold of two-stroke internal combustion engine |
US8147211B2 (en) * | 2006-01-03 | 2012-04-03 | General Electric Company | Method and system for monitoring a reciprocating compressor valve |
JP4127292B2 (en) * | 2006-05-18 | 2008-07-30 | トヨタ自動車株式会社 | Muffler |
US7762521B2 (en) * | 2006-05-23 | 2010-07-27 | Southwest Research Institute | Semi-active compressor valve |
US20080023264A1 (en) * | 2006-07-27 | 2008-01-31 | Pacini Larry W | Muffler having adjustable butterfly valve for improved sound attenuation and engine performance |
US20080253900A1 (en) | 2007-04-11 | 2008-10-16 | Harris Ralph E | Gas compressor with pulsation absorber for reducing cylinder nozzle resonant pulsation |
US7757808B1 (en) | 2009-02-04 | 2010-07-20 | Gm Global Technology Operations, Inc. | Noise reduction system |
-
2008
- 2008-01-24 US US12/019,462 patent/US8123498B2/en not_active Expired - Fee Related
-
2011
- 2011-09-13 US US13/231,868 patent/US20120003106A1/en not_active Abandoned
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4546733A (en) * | 1983-03-22 | 1985-10-15 | Nippondenso Co., Ltd. | Resonator for internal combustion engines |
US5894823A (en) * | 1996-12-13 | 1999-04-20 | Hyundai Motor Company | Variable suction resonator system for internal combustion engines |
US5930371A (en) * | 1997-01-07 | 1999-07-27 | Nelson Industries, Inc. | Tunable acoustic system |
US6453695B1 (en) * | 2002-01-18 | 2002-09-24 | Carrier Corporation | Dual length inlet resonator |
US6609489B1 (en) * | 2002-05-07 | 2003-08-26 | General Motors Corporation | Apparatus and method for reducing engine noise |
US6792907B1 (en) * | 2003-03-04 | 2004-09-21 | Visteon Global Technologies, Inc. | Helmholtz resonator |
US20070289653A1 (en) * | 2006-05-23 | 2007-12-20 | Harris Ralph E | Gas Compressor With Side Branch Absorber For Pulsation Control |
US7946382B2 (en) * | 2006-05-23 | 2011-05-24 | Southwest Research Institute | Gas compressor with side branch absorber for pulsation control |
US7690478B2 (en) * | 2006-09-15 | 2010-04-06 | Visteon Global Technologies, Inc. | Continuously variable tuned resonator |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9909577B2 (en) | 2014-01-22 | 2018-03-06 | Jared W. ADAIR | Dynamic variable orifice for compressor pulsation control |
US10487812B2 (en) | 2014-01-22 | 2019-11-26 | Jared W. ADAIR | Dynamic variable orifice for compressor pulsation control |
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US20090191076A1 (en) | 2009-07-30 |
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