US20080253900A1 - Gas compressor with pulsation absorber for reducing cylinder nozzle resonant pulsation - Google Patents
Gas compressor with pulsation absorber for reducing cylinder nozzle resonant pulsation Download PDFInfo
- Publication number
- US20080253900A1 US20080253900A1 US11/734,116 US73411607A US2008253900A1 US 20080253900 A1 US20080253900 A1 US 20080253900A1 US 73411607 A US73411607 A US 73411607A US 2008253900 A1 US2008253900 A1 US 2008253900A1
- Authority
- US
- United States
- Prior art keywords
- absorber
- pulsation
- nozzle
- compressor
- cylinder
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Abandoned
Links
Images
Classifications
-
- 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
-
- 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
-
- 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
- F04B39/0066—Pulsation and noise damping means with a special shape of fluid passage, e.g. bends, throttles, diameter changes, pipes using sidebranch resonators, e.g. Helmholtz resonators
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49229—Prime mover or fluid pump making
- Y10T29/49236—Fluid pump or compressor making
- Y10T29/49238—Repairing, converting, servicing or salvaging
Definitions
- This invention relates to large positive displacement compressors for transporting fluids, and more particularly to an improved method for reducing cylinder nozzle pulsations in large positive displacement compressors.
- Reciprocating compressors are a type of positive displacement compressor that compress gas by using a piston in a cylinder and a back-and-forth motion.
- a suction valve in the cylinder receives input gas, which is compressed, and discharged through a discharge valve.
- Reciprocating compressors inherently generate transient pulsating flows, and various devices and control methods have been developed to control these pulsations.
- a proper pulsation control design reduces system pulsations to acceptable levels without compromising compressor performance.
- Cylinder nozzle pulsations are one challenge to high-horsepower, high-speed, variable-speed units.
- the cylinder nozzle is the section of pipe that connects the cylinder to the suction or discharge side of the compressor, typically to a filter bottle. This section of pipe can provide significant resonance responses.
- FIG. 1 illustrates an integrated (low speed) compressor system.
- FIG. 2 illustrates a separable (low or high speed) compressor system.
- FIGS. 3A and 3B illustrate a nozzle pulsation absorber installed at alternative locations.
- FIG. 4 illustrates test data of cylinder nozzle pulsations without a nozzle pulsation absorber.
- FIG. 5 illustrates test data of cylinder nozzle pulsations with a nozzle pulsation absorber installed on the valve cap.
- FIG. 6 illustrates test data of cylinder nozzle pulsations with a nozzle pulsation absorber installed on the cylinder nozzle.
- FIGS. 7-9 illustrate how the cylinder nozzle resonance is altered when the pulsation absorber is installed near the compressor valves.
- the following description is directed to a “nozzle pulsation absorber” which when properly designed, can significantly reduce the cylinder nozzle resonant pulsations.
- the nozzle pulsation absorber can absorb cylinder nozzle resonant pulsations such that the maximum pulsations are drastically reduced, eliminating the need for an orifice. Unlike a conventional orifice, the nozzle pulsation absorber does require additional horsepower.
- the nozzle pulsation absorber can be easily installed on an existing system at valve up. It can also be installed in the cylinder nozzle near the cylinder flange, but for existing systems this is a more costly alternative.
- FIG. 1 illustrates a reciprocating gas compressor system 100 .
- Compressor system 100 is an “integrated” compressor system in the sense that its engine 11 and compressor 12 share the same crankshaft 13 .
- the engine 11 is represented by three engine cylinders 11 a - 11 c .
- engine 11 is a two-stroke engine.
- the compressor 12 is represented by four compressor cylinders 12 a - 12 d .
- engine 11 and compressor 12 may each have fewer or more cylinders.
- FIG. 2 illustrates a reciprocating gas compressor system 200 in which the engine 21 and compressor 22 are separate units.
- This engine/compressor configuration is referred to in the natural gas industry as a “separable” compressor system.
- the respective crankshafts 23 of engine 21 and compressor 22 are mechanically joined at a coupling 24 , which permits engine 21 to drive the compressor 22 .
- System 100 is typically a low speed system
- system 200 can be a low or high speed system.
- the trend in the last decade is toward separable (high speed) systems, which have a smaller footprint and permit coupling to either an engine or electric motor.
- Both systems 100 and 200 are characterized by having a reciprocating compressor 12 or 22 , which has one or more internal combustion cylinders. Both systems have a controller 17 for control of parameters affecting compressor load and capacity. Both systems can exhibit the residual frequency problems discussed above.
- the compressor systems operate between two gas transmission lines.
- a first line at a certain pressure, is referred to as the suction line.
- a second line at a higher pressure, is referred to as the discharge line.
- the suction pressure and discharge pressure are measured in psi (pounds per square inch).
- FIGS. 3A and 3B illustrate a nozzle pulsation absorber 30 installed at alternative locations, namely, the cylinder valve cap 32 ( FIG. 3A ) and the cylinder nozzle 35 ( FIG. 3B ). Only a single cylinder 31 is represented, shown as an elevation view toward its valve cap 32 . Cylinder 31 could be one of the cylinders from either system shown in FIG. 1 or FIG. 2 .
- the cylinder nozzle 35 is the section of pipe that connects the cylinder 31 to the discharge or suction side of the compressor.
- the cylinder nozzle 35 is labeled on the discharge side of the compressor, and the nozzle pulsation absorber 30 is on the discharge side of cylinder 31 .
- the nozzle pulsation absorber 30 may be on either the suction or discharge side of the cylinder 31 .
- the cylinder 31 is connected to filter bottles 33 and 34 at both the suction input and discharge outlet.
- These filter bottles 33 and 34 are installed as a common method for pulsation control, and are placed between the compressor and the attached piping systems.
- These filter bottles 33 and 34 operate with surge volumes, and are commonly implemented as volume-choke-volume devices. They function as low-pass acoustic filters, and attenuate pulsations on the basis of a predetermined Helmholtz response.
- Each nozzle pulsation absorber 30 operates like a side branch absorber, and has a choke tube 30 a and surge volume 30 b .
- Choke tube 30 a is a span of piping connecting the valve cap 32 or cylinder nozzle 35 to the surge volume 30 b .
- nozzle pulsation absorber 30 reduces pulsations by altering the frequency of the responses in the cylinder nozzle 35 .
- choke tube 30 a and surge volume 30 b are not the same as their acoustic dimensions.
- the desired acoustic dimensions and the resulting physical dimensions are determined by various known calculation and acoustic modeling techniques.
- the acoustic dimensions of pulsation absorber 30 vary depending on the pulsation frequency to be dampened.
- the resonant frequency to be damped may be determined by various measurement or predictive techniques.
- the connecting piping 30 a is attached to the valve cap 32 or nozzle 35 , such that pulsations corresponding to the acoustic natural frequency of the pulsation absorber 30 are absorbed from the compressor system.
- the diameter and size of the connecting piping 30 a and the size of the surge volume 30 b determine the acoustic natural frequency of the pulsation absorber 30 .
- nozzle pulsation absorber 30 controls cylinder nozzle pulsations, with significant reduction of peak pulsation amplitudes and pulsations at resonance. Its design is simple, and it is easy to install on an existing system.
- FIG. 4 illustrates test data from a compressor having a 8.5 inch bore and 3 inch stroke, running at 500 to 1000 rpm, without a nozzle pulsation absorber. As illustrated, the cylinder nozzle response has a significant peak at approximately 50 Hz.
- FIG. 5 illustrates test data from the same compressor, under the same operating conditions as FIG. 4 , but with a nozzle pulsation absorber 30 installed on the valve cap 32 . As illustrated, the cylinder nozzle response is split, to approximately 43 and 58 Hz.
- FIG. 6 illustrates test data from the same compressor, under the same operating conditions as FIG. 4 , but with a nozzle pulsation absorber 30 installed on the cylinder nozzle 35 . As illustrated, the cylinder nozzle response is split, to approximately 42 and 56 Hz.
- FIGS. 7-9 illustrate how the cylinder nozzle resonance is altered when the pulsation absorber is installed near the compressor valves.
- FIG. 7 depicts the velocity profile that is typically associated with a cylinder nozzle resonance.
- FIG. 8 depicts the velocity profile that is typically associated with a side branch resonator.
- FIG. 9 by installing the pulsation absorber near the compressor valves, a gas velocity “maximum” is generated at the location where a velocity “minimum” would typically form when the pulsation absorber is not installed.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressor (AREA)
Abstract
Description
- This invention relates to large positive displacement compressors for transporting fluids, and more particularly to an improved method for reducing cylinder nozzle pulsations in large positive displacement compressors.
- Most natural gas consumed in the United States is not produced close to where it is used. To transport gas from increasingly remote production sites to consumers, pipeline companies operate and maintain hundreds of thousands of miles of natural gas transmission lines. The gas is then sold to local distribution companies, who deliver it to consumers, using a network of more than a million miles of local distribution lines. This vast underground transmission and distribution system is capable of moving billions of cubic feet of gas each day.
- To provide force to move the gas, operators install large gas compressors at transport stations along the pipelines. Reciprocating compressors are a type of positive displacement compressor that compress gas by using a piston in a cylinder and a back-and-forth motion. A suction valve in the cylinder receives input gas, which is compressed, and discharged through a discharge valve. Reciprocating compressors inherently generate transient pulsating flows, and various devices and control methods have been developed to control these pulsations. A proper pulsation control design reduces system pulsations to acceptable levels without compromising compressor performance.
- The state of the art in pulsation design and control technology has evolved as compressor technology has changed. Designs for low-speed compressors are more mature, with fewer critical issues. However, relatively recent high-speed, high-horsepower compressor designs are placing significant challenges on pulsation control design.
- Cylinder nozzle pulsations are one challenge to high-horsepower, high-speed, variable-speed units. The cylinder nozzle is the section of pipe that connects the cylinder to the suction or discharge side of the compressor, typically to a filter bottle. This section of pipe can provide significant resonance responses.
- Currently, one solution to attenuating cylinder nozzle pulsations is the installation of an orifice in the cylinder nozzle. For example, a plate with a flow restricting hole may be placed across the circumference of the nozzle. However, a downside of the orifice is that it causes a pressure drop that requires the supply of additional horsepower. This burden can be significant on large horsepower units.
- 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 illustrates an integrated (low speed) compressor system. -
FIG. 2 illustrates a separable (low or high speed) compressor system. -
FIGS. 3A and 3B illustrate a nozzle pulsation absorber installed at alternative locations. -
FIG. 4 illustrates test data of cylinder nozzle pulsations without a nozzle pulsation absorber. -
FIG. 5 illustrates test data of cylinder nozzle pulsations with a nozzle pulsation absorber installed on the valve cap. -
FIG. 6 illustrates test data of cylinder nozzle pulsations with a nozzle pulsation absorber installed on the cylinder nozzle. -
FIGS. 7-9 illustrate how the cylinder nozzle resonance is altered when the pulsation absorber is installed near the compressor valves. - As explained in the Background, large reciprocating compressors used in the gas and processing industries generate cylinder nozzle pulsations that can cause poor compressor performance, poor valve life, and significant vibration issues. The conventional approach to reducing nozzle pulsation is the installation of an orifice.
- The following description is directed to a “nozzle pulsation absorber” which when properly designed, can significantly reduce the cylinder nozzle resonant pulsations. The nozzle pulsation absorber can absorb cylinder nozzle resonant pulsations such that the maximum pulsations are drastically reduced, eliminating the need for an orifice. Unlike a conventional orifice, the nozzle pulsation absorber does require additional horsepower.
- Similar to the conventional orifice, the nozzle pulsation absorber can be easily installed on an existing system at valve up. It can also be installed in the cylinder nozzle near the cylinder flange, but for existing systems this is a more costly alternative.
-
FIG. 1 illustrates a reciprocatinggas compressor system 100.Compressor system 100 is an “integrated” compressor system in the sense that itsengine 11 andcompressor 12 share thesame crankshaft 13. Theengine 11 is represented by threeengine cylinders 11 a-11 c. Typically,engine 11 is a two-stroke engine. Thecompressor 12 is represented by fourcompressor cylinders 12 a-12 d. In practice,engine 11 andcompressor 12 may each have fewer or more cylinders. -
FIG. 2 illustrates a reciprocatinggas compressor system 200 in which theengine 21 andcompressor 22 are separate units. This engine/compressor configuration is referred to in the natural gas industry as a “separable” compressor system. Therespective crankshafts 23 ofengine 21 andcompressor 22 are mechanically joined at acoupling 24, which permitsengine 21 to drive thecompressor 22. - As indicated in the Background, a typical application of
gas compressor systems System 100 is typically a low speed system, whereassystem 200 can be a low or high speed system. The trend in the last decade is toward separable (high speed) systems, which have a smaller footprint and permit coupling to either an engine or electric motor. - Both
systems compressor controller 17 for control of parameters affecting compressor load and capacity. Both systems can exhibit the residual frequency problems discussed above. - As shown in
FIG. 1 , the compressor systems operate between two gas transmission lines. A first line, at a certain pressure, is referred to as the suction line. A second line, at a higher pressure, is referred to as the discharge line. Typically, the suction pressure and discharge pressure are measured in psi (pounds per square inch). - The following description is written in terms of the
separable system 200. However, the same concepts are applicable tosystem 100; as indicated inFIGS. 1 and 2 , thesame controller 17 may be used with either type of system. -
FIGS. 3A and 3B illustrate a nozzle pulsation absorber 30 installed at alternative locations, namely, the cylinder valve cap 32 (FIG. 3A ) and the cylinder nozzle 35 (FIG. 3B ). Only asingle cylinder 31 is represented, shown as an elevation view toward itsvalve cap 32.Cylinder 31 could be one of the cylinders from either system shown inFIG. 1 orFIG. 2 . - The
cylinder nozzle 35 is the section of pipe that connects thecylinder 31 to the discharge or suction side of the compressor. In the embodiment ofFIGS. 3A and 3B , thecylinder nozzle 35 is labeled on the discharge side of the compressor, and thenozzle pulsation absorber 30 is on the discharge side ofcylinder 31. However, thenozzle pulsation absorber 30 may be on either the suction or discharge side of thecylinder 31. - In the embodiments of
FIGS. 3A and 3B , thecylinder 31 is connected to filterbottles filter bottles filter bottles - Each
nozzle pulsation absorber 30 operates like a side branch absorber, and has a choke tube 30 a and surge volume 30 b. Choke tube 30 a is a span of piping connecting thevalve cap 32 orcylinder nozzle 35 to the surge volume 30 b. In accordance with the invention,nozzle pulsation absorber 30 reduces pulsations by altering the frequency of the responses in thecylinder nozzle 35. - As is known in the art of side branch absorbers (also known as Helmholtz resonators) for other applications, the physical dimensions of choke tube 30 a and surge volume 30 b are not the same as their acoustic dimensions. The desired acoustic dimensions and the resulting physical dimensions are determined by various known calculation and acoustic modeling techniques.
- The acoustic dimensions of
pulsation absorber 30 vary depending on the pulsation frequency to be dampened. The resonant frequency to be damped may be determined by various measurement or predictive techniques. - The connecting piping 30 a is attached to the
valve cap 32 ornozzle 35, such that pulsations corresponding to the acoustic natural frequency of thepulsation absorber 30 are absorbed from the compressor system. The diameter and size of the connecting piping 30 a and the size of the surge volume 30 b determine the acoustic natural frequency of thepulsation absorber 30. - Advantages of the above-described
nozzle pulsation absorber 30 are that it controls cylinder nozzle pulsations, with significant reduction of peak pulsation amplitudes and pulsations at resonance. Its design is simple, and it is easy to install on an existing system. -
FIG. 4 illustrates test data from a compressor having a 8.5 inch bore and 3 inch stroke, running at 500 to 1000 rpm, without a nozzle pulsation absorber. As illustrated, the cylinder nozzle response has a significant peak at approximately 50 Hz. -
FIG. 5 illustrates test data from the same compressor, under the same operating conditions asFIG. 4 , but with anozzle pulsation absorber 30 installed on thevalve cap 32. As illustrated, the cylinder nozzle response is split, to approximately 43 and 58 Hz. -
FIG. 6 illustrates test data from the same compressor, under the same operating conditions asFIG. 4 , but with anozzle pulsation absorber 30 installed on thecylinder nozzle 35. As illustrated, the cylinder nozzle response is split, to approximately 42 and 56 Hz. -
FIGS. 7-9 illustrate how the cylinder nozzle resonance is altered when the pulsation absorber is installed near the compressor valves.FIG. 7 depicts the velocity profile that is typically associated with a cylinder nozzle resonance.FIG. 8 depicts the velocity profile that is typically associated with a side branch resonator. As shown inFIG. 9 , by installing the pulsation absorber near the compressor valves, a gas velocity “maximum” is generated at the location where a velocity “minimum” would typically form when the pulsation absorber is not installed.
Claims (6)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/734,116 US20080253900A1 (en) | 2007-04-11 | 2007-04-11 | Gas compressor with pulsation absorber for reducing cylinder nozzle resonant pulsation |
US13/400,849 US20120144671A1 (en) | 2007-04-11 | 2012-02-21 | Gas compressor with pulsation absorber for reducing cylinder nozzle resonant pulsation |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/734,116 US20080253900A1 (en) | 2007-04-11 | 2007-04-11 | Gas compressor with pulsation absorber for reducing cylinder nozzle resonant pulsation |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/400,849 Division US20120144671A1 (en) | 2007-04-11 | 2012-02-21 | Gas compressor with pulsation absorber for reducing cylinder nozzle resonant pulsation |
Publications (1)
Publication Number | Publication Date |
---|---|
US20080253900A1 true US20080253900A1 (en) | 2008-10-16 |
Family
ID=39853880
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/734,116 Abandoned US20080253900A1 (en) | 2007-04-11 | 2007-04-11 | Gas compressor with pulsation absorber for reducing cylinder nozzle resonant pulsation |
US13/400,849 Abandoned US20120144671A1 (en) | 2007-04-11 | 2012-02-21 | Gas compressor with pulsation absorber for reducing cylinder nozzle resonant pulsation |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US13/400,849 Abandoned US20120144671A1 (en) | 2007-04-11 | 2012-02-21 | Gas compressor with pulsation absorber for reducing cylinder nozzle resonant pulsation |
Country Status (1)
Country | Link |
---|---|
US (2) | US20080253900A1 (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20070101706A1 (en) * | 2005-09-30 | 2007-05-10 | Harris Ralph E | Side branch absorber for exhaust manifold of two-stroke internal combustion engine |
US20070289653A1 (en) * | 2006-05-23 | 2007-12-20 | Harris Ralph E | Gas Compressor With Side Branch Absorber For Pulsation Control |
US20100329899A1 (en) * | 2009-06-24 | 2010-12-30 | Southwest Research Institute | Multi-frequency pulsation absorber at cylinder valve cap |
US20110116940A1 (en) * | 2009-11-17 | 2011-05-19 | Cameron International Corporation | Viscoelastic compressor pulsation dampener |
US20110243760A1 (en) * | 2010-03-30 | 2011-10-06 | Southern Gas Association Gas Machinery Research Council | Pressure Recovery Insert for Reciprocating Gas Compressor |
US20110243761A1 (en) * | 2010-03-31 | 2011-10-06 | Rusty Darsey | Pulsation Dampener for Gas Compressors Having Selectable Size Choke Openings |
US8123498B2 (en) | 2008-01-24 | 2012-02-28 | Southern Gas Association Gas Machinery Research Council | Tunable choke tube for pulsation control device used with gas compressor |
Citations (62)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 |
US2573536A (en) * | 1951-07-02 | 1951-10-30 | Jr Albert G Bodine | Engine detonation control by acoustic methods and apparatus |
US2919715A (en) * | 1954-07-02 | 1960-01-05 | Edward A Rockwell | Accumulating apparatus and system |
US2936041A (en) * | 1955-06-10 | 1960-05-10 | Southern Gas Ass | Pulsation dampening apparatus |
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 |
US3181648A (en) * | 1965-05-04 | Adjustable muffler | ||
US3219141A (en) * | 1963-08-30 | 1965-11-23 | Gen Motors Corp | Compressor muffler having adjustable baffle means controlled by thermally responsive element |
US3884596A (en) * | 1973-04-12 | 1975-05-20 | Siemens Ag | Distributor with separate suction and pressure nozzles for a liquid-ring gas compressor |
US3936606A (en) * | 1971-12-07 | 1976-02-03 | Wanke Ronald L | Acoustic abatement method and apparatus |
US3940721A (en) * | 1974-05-09 | 1976-02-24 | Nippon Electric Company, Ltd. | Cavity resonator having a variable resonant frequency |
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 |
US4779415A (en) * | 1986-11-26 | 1988-10-25 | Arvin Industries, Inc. | Manifold tuning structure |
US4927342A (en) * | 1988-12-12 | 1990-05-22 | General Electric Company | Compressor noise attenuation using branch type resonator |
US5005353A (en) * | 1986-04-28 | 1991-04-09 | Rolls-Royce Plc | Active control of unsteady motion phenomena in turbomachinery |
US5119427A (en) * | 1988-03-14 | 1992-06-02 | Hersh Alan S | Extended frequency range Helmholtz resonators |
US5183974A (en) * | 1992-04-03 | 1993-02-02 | General Motors Corporation | Gas pulsation attenuator for automotive air conditioning compressor |
US5189266A (en) * | 1989-06-09 | 1993-02-23 | Nissan Motor Co., Ltd. | Vehicular exhaust resonance suppression system and sensing means therefore |
US5203679A (en) * | 1990-10-22 | 1993-04-20 | Daewoo Carrier Corporation | Resonator for hermetic rotary compressor |
US5288212A (en) * | 1990-12-12 | 1994-02-22 | Goldstar Co., Ltd. | Cylinder head of hermetic reciprocating compressor |
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 |
US5621656A (en) * | 1992-04-15 | 1997-04-15 | Noise Cancellation Technologies, Inc. | Adaptive resonator vibration control system |
US5760349A (en) * | 1995-04-20 | 1998-06-02 | Dornier Gmbh | Acoustic absorber having a slotted horn arranged in a pot |
US5866860A (en) * | 1996-12-06 | 1999-02-02 | Chen; Ching Long | Muffler having a pressure adjusting device |
US5930371A (en) * | 1997-01-07 | 1999-07-27 | Nelson Industries, Inc. | Tunable acoustic system |
US6012908A (en) * | 1996-01-23 | 2000-01-11 | Matsushita Refrigeration Company | Electrically operated seal compressor having a refrigerant flow branch tube with a chamber disposed in the vicinity of a suction port |
US6152703A (en) * | 1996-06-14 | 2000-11-28 | Matsushita Refrigeration Company | Hermetic-type compressor |
US6295363B1 (en) * | 1997-03-20 | 2001-09-25 | Digisonix, Inc. | Adaptive passive acoustic attenuation system |
US20020059959A1 (en) * | 2002-01-08 | 2002-05-23 | Qatu Mohamad S. | System and apparatus for noise suppression in a fluid line |
US6453695B1 (en) * | 2002-01-18 | 2002-09-24 | Carrier Corporation | Dual length inlet resonator |
US6533064B1 (en) * | 1999-10-20 | 2003-03-18 | Daewoo Electronics Corporation | Noise reduction device for use in reciprocating compressor using a side-branch silencer |
US6546729B2 (en) * | 2000-11-25 | 2003-04-15 | Alstom (Switzerland) Ltd | Damper arrangement for reducing combustion-chamber pulsations |
US20030136119A1 (en) * | 2002-01-18 | 2003-07-24 | Marks Patrick C. | Multiple frequency helmholtz resonator |
US6634457B2 (en) * | 2000-05-26 | 2003-10-21 | Alstom (Switzerland) Ltd | Apparatus for damping acoustic vibrations in a combustor |
US6698390B1 (en) * | 2003-01-24 | 2004-03-02 | Visteon Global Technologies, Inc. | Variable tuned telescoping resonator |
US20040065303A1 (en) * | 1998-06-04 | 2004-04-08 | Russell John D. | System and method for air flow and EGR flow estimation |
US6792907B1 (en) * | 2003-03-04 | 2004-09-21 | Visteon Global Technologies, Inc. | Helmholtz resonator |
US6799657B2 (en) * | 2002-10-02 | 2004-10-05 | Carrier Corporation | Absorptive/reactive muffler for variable speed compressors |
US6814041B1 (en) * | 2003-01-31 | 2004-11-09 | Fleetguard, Inc. | Multi-frequency engine intake resonator |
US20050008512A1 (en) * | 2003-05-30 | 2005-01-13 | Mcgill Ian Campbell | Compressor improvements |
US20050111997A1 (en) * | 2003-11-24 | 2005-05-26 | Southwest Research Institute | Integrated engine/compressor control for gas transmission compressors |
US6935848B2 (en) * | 2003-05-19 | 2005-08-30 | Bristol Compressors, Inc. | Discharge muffler placement in a compressor |
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 |
US20060275158A1 (en) * | 2004-09-13 | 2006-12-07 | Takahide Nagao | Refrigerating compressor |
US20070101706A1 (en) * | 2005-09-30 | 2007-05-10 | Harris Ralph E | Side branch absorber for exhaust manifold of two-stroke internal combustion engine |
US20070130926A1 (en) * | 2001-04-27 | 2007-06-14 | Jett Marion B | Exhaust device for two-stroke internal combustion engine |
US20070154325A1 (en) * | 2006-01-03 | 2007-07-05 | General Electric Company | Method and system for monitoring a reciprocating compressor valve |
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 |
US20070272178A1 (en) * | 2006-05-23 | 2007-11-29 | Klaus Brun | Semi-Active Compressor Valve |
US20070289653A1 (en) * | 2006-05-23 | 2007-12-20 | Harris Ralph E | Gas Compressor With Side Branch Absorber For Pulsation Control |
US20080023264A1 (en) * | 2006-07-27 | 2008-01-31 | Pacini Larry W | Muffler having adjustable butterfly valve for improved sound attenuation and engine performance |
US7337877B2 (en) * | 2004-03-12 | 2008-03-04 | Visteon Global Technologies, Inc. | Variable geometry resonator for acoustic control |
US20100193283A1 (en) * | 2009-02-04 | 2010-08-05 | Gm Global Technology Operations, Inc. | Noise reduction system |
-
2007
- 2007-04-11 US US11/734,116 patent/US20080253900A1/en not_active Abandoned
-
2012
- 2012-02-21 US US13/400,849 patent/US20120144671A1/en not_active Abandoned
Patent Citations (63)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3181648A (en) * | 1965-05-04 | Adjustable muffler | ||
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 |
US2573536A (en) * | 1951-07-02 | 1951-10-30 | Jr Albert G Bodine | Engine detonation control by acoustic methods and apparatus |
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 |
US2936041A (en) * | 1955-06-10 | 1960-05-10 | Southern Gas Ass | Pulsation dampening apparatus |
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 |
US3884596A (en) * | 1973-04-12 | 1975-05-20 | Siemens Ag | Distributor with separate suction and pressure nozzles for a liquid-ring gas compressor |
US3940721A (en) * | 1974-05-09 | 1976-02-24 | Nippon Electric Company, Ltd. | Cavity resonator having a variable resonant frequency |
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 |
US5005353A (en) * | 1986-04-28 | 1991-04-09 | 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 |
US5203679A (en) * | 1990-10-22 | 1993-04-20 | Daewoo Carrier Corporation | Resonator 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 |
US5760349A (en) * | 1995-04-20 | 1998-06-02 | Dornier Gmbh | Acoustic absorber having a slotted horn arranged in a pot |
US6012908A (en) * | 1996-01-23 | 2000-01-11 | Matsushita Refrigeration Company | Electrically operated seal compressor having a refrigerant flow branch tube with a chamber disposed in the vicinity of a suction port |
US6152703A (en) * | 1996-06-14 | 2000-11-28 | Matsushita Refrigeration Company | Hermetic-type compressor |
US5866860A (en) * | 1996-12-06 | 1999-02-02 | Chen; Ching Long | Muffler having a pressure adjusting device |
US5930371A (en) * | 1997-01-07 | 1999-07-27 | Nelson Industries, Inc. | Tunable acoustic system |
US6295363B1 (en) * | 1997-03-20 | 2001-09-25 | Digisonix, Inc. | Adaptive passive acoustic attenuation system |
US20040065303A1 (en) * | 1998-06-04 | 2004-04-08 | Russell John D. | System and method for air flow and EGR flow estimation |
US6533064B1 (en) * | 1999-10-20 | 2003-03-18 | Daewoo Electronics Corporation | Noise reduction device for use in reciprocating compressor using a side-branch silencer |
US6634457B2 (en) * | 2000-05-26 | 2003-10-21 | Alstom (Switzerland) Ltd | Apparatus for damping acoustic vibrations in a combustor |
US6546729B2 (en) * | 2000-11-25 | 2003-04-15 | Alstom (Switzerland) Ltd | Damper arrangement for reducing combustion-chamber pulsations |
US20070130926A1 (en) * | 2001-04-27 | 2007-06-14 | Jett Marion B | 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 |
US6453695B1 (en) * | 2002-01-18 | 2002-09-24 | Carrier Corporation | Dual length inlet resonator |
US20030136119A1 (en) * | 2002-01-18 | 2003-07-24 | Marks Patrick C. | Multiple frequency helmholtz resonator |
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 |
US6792907B1 (en) * | 2003-03-04 | 2004-09-21 | Visteon Global Technologies, Inc. | Helmholtz resonator |
US6935848B2 (en) * | 2003-05-19 | 2005-08-30 | Bristol Compressors, Inc. | Discharge muffler placement in a compressor |
US20050008512A1 (en) * | 2003-05-30 | 2005-01-13 | Mcgill Ian Campbell | Compressor improvements |
US20050111997A1 (en) * | 2003-11-24 | 2005-05-26 | 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 |
US20060275158A1 (en) * | 2004-09-13 | 2006-12-07 | Takahide Nagao | Refrigerating compressor |
US20070101706A1 (en) * | 2005-09-30 | 2007-05-10 | Harris Ralph E | Side branch absorber for exhaust manifold of two-stroke internal combustion engine |
US20070154325A1 (en) * | 2006-01-03 | 2007-07-05 | General Electric Company | Method and system for monitoring a reciprocating compressor valve |
US20070272178A1 (en) * | 2006-05-23 | 2007-11-29 | Klaus Brun | Semi-Active Compressor Valve |
US20070289653A1 (en) * | 2006-05-23 | 2007-12-20 | Harris Ralph E | Gas Compressor With Side Branch Absorber For Pulsation Control |
US20080023264A1 (en) * | 2006-07-27 | 2008-01-31 | Pacini Larry W | Muffler having adjustable butterfly valve for improved sound attenuation and engine performance |
US20100193283A1 (en) * | 2009-02-04 | 2010-08-05 | Gm Global Technology Operations, Inc. | Noise reduction system |
Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20070101706A1 (en) * | 2005-09-30 | 2007-05-10 | Harris Ralph E | Side branch absorber for exhaust manifold of two-stroke internal combustion engine |
US7866147B2 (en) | 2005-09-30 | 2011-01-11 | Southwest Research Institute | Side branch absorber for exhaust manifold of two-stroke internal combustion engine |
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 |
US8123498B2 (en) | 2008-01-24 | 2012-02-28 | Southern Gas Association Gas Machinery Research Council | Tunable choke tube for pulsation control device used with gas compressor |
US20100329899A1 (en) * | 2009-06-24 | 2010-12-30 | Southwest Research Institute | Multi-frequency pulsation absorber at cylinder valve cap |
US8591208B2 (en) | 2009-06-24 | 2013-11-26 | Southwest Research Institute | Multi-frequency pulsation absorber at cylinder valve cap |
US20110116940A1 (en) * | 2009-11-17 | 2011-05-19 | Cameron International Corporation | Viscoelastic compressor pulsation dampener |
US20110243760A1 (en) * | 2010-03-30 | 2011-10-06 | Southern Gas Association Gas Machinery Research Council | Pressure Recovery Insert for Reciprocating Gas Compressor |
US8740581B2 (en) * | 2010-03-30 | 2014-06-03 | Southern Gas Association Gas Machinery Research Council | Pressure recovery insert for reciprocating gas compressor |
WO2011126754A3 (en) * | 2010-03-30 | 2015-07-09 | Southern Gas Association Gas Machinery Research Council | Pressure recovery insert for reciprocating gas compressor |
US20110243761A1 (en) * | 2010-03-31 | 2011-10-06 | Rusty Darsey | Pulsation Dampener for Gas Compressors Having Selectable Size Choke Openings |
Also Published As
Publication number | Publication date |
---|---|
US20120144671A1 (en) | 2012-06-14 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
US20120144671A1 (en) | Gas compressor with pulsation absorber for reducing cylinder nozzle resonant pulsation | |
US7946382B2 (en) | Gas compressor with side branch absorber for pulsation control | |
US9567996B2 (en) | Pulsation attenuation | |
US8123498B2 (en) | Tunable choke tube for pulsation control device used with gas compressor | |
US8591208B2 (en) | Multi-frequency pulsation absorber at cylinder valve cap | |
CN105443353A (en) | Apparatus, system, and method for improved performance of a pressurized system | |
US20140212315A1 (en) | Hyperbolic horn for pulsation filter device used with gas compressor | |
US20100126607A9 (en) | Branching Device for a Pulsation Attenuation Network | |
CN109210125B (en) | Frequency-adjustable self-adaptive airflow pulsation attenuator | |
US8740581B2 (en) | Pressure recovery insert for reciprocating gas compressor | |
US9909577B2 (en) | Dynamic variable orifice for compressor pulsation control | |
US8052398B2 (en) | Reciprocating gas compressor with speed modulation of compressor driver for pulsation avoidance | |
CN104018963B (en) | Pressure fluctuation buffer | |
CN107905982B (en) | Diaphragm type active airflow pulsation attenuation device for large reciprocating compressor | |
CN108087239B (en) | Pipeline type active airflow pulsation attenuation device for large reciprocating compressor | |
CN110939614B (en) | Broadband spring oscillator hydraulic pulsation attenuator | |
CN207673511U (en) | A kind of diaphragm type active flow pulsation damping device for large reciprocating compressor | |
CN101094982A (en) | Pressure vibration dampener for an internal combustion engine fuel injection system | |
CN212537511U (en) | Reciprocating compressor gas phase pipeline damping device for trimellitic anhydride production line | |
SU1361374A1 (en) | Method of operation of pump and pump for effecting same | |
Shade et al. | EFFICIENT BOTTLE-LESS COMPRESSOR PULSATION CONTROL EXPERIMENTAL TEST RESULTS | |
CN113446209A (en) | Fracturing equipment and vibration reduction method thereof | |
Broerman et al. | Benefits of the Virtual Orifice: Pulsations and Vibrations Reduced, Performance Improved | |
CN109798435A (en) | Mine pneumatic motor lubricating device | |
Wachel et al. | Engineering the reliability of reciprocating compressor systems |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: SOUTHWEST RESEARCH INSTITUTE, TEXAS Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BROERMAN, EUGENE L., III;SMOLIK, MITCHEL A.;REEL/FRAME:019774/0816 Effective date: 20070613 Owner name: SOUTHWEST RESEARCH INSTITUTE, TEXAS Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:HARRIS, RALPH E.;REEL/FRAME:019774/0737 Effective date: 20070615 |
|
AS | Assignment |
Owner name: SOUTHERN GAS ASSOCIATION GAS MACHINERY RESEARCH CO Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:SOUTHWEST RESEARCH INSTITUTE;REEL/FRAME:022608/0045 Effective date: 20081014 Owner name: SOUTHWEST RESEARCH INSTITUTE, TEXAS Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:BROERMAN, EUGENE L. III;SMOLIK, MITCHEL A.;REEL/FRAME:022608/0008 Effective date: 20070613 Owner name: SOUTHWEST RESEARCH INSTITUTE, TEXAS Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:HARRIS, RALPH E.;REEL/FRAME:022607/0992 Effective date: 20070615 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |