CN102032147B - Gas pulsation vibration damper - Google Patents
Gas pulsation vibration damper Download PDFInfo
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- CN102032147B CN102032147B CN 201010546888 CN201010546888A CN102032147B CN 102032147 B CN102032147 B CN 102032147B CN 201010546888 CN201010546888 CN 201010546888 CN 201010546888 A CN201010546888 A CN 201010546888A CN 102032147 B CN102032147 B CN 102032147B
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- housing
- gas
- expansion chamber
- vibration damper
- shell
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Abstract
The invention discloses a gas pulsation vibration damper for a reciprocating compressor outlet pipe in pipeline transportation. The outside of the gas pulsation vibration damper is a cylindrical shell; a gas inlet is arranged near the side wall of the left end of the shell; the right end of the shell is a gas outlet; the gas inlet is provided with a transition section; the bottom of the transition section extends into the shell and is fixedly communicated with a tapered nozzle; a throttle plate is fixed on the cross section of a shell inner chamber located between the gas inlet and the gas outlet; the throttle plate is provided with a plurality of throttle through holes; a left expansion chamber is formed between the left end of the shell and the throttle plate; a right expansion chamber is formed between the throttle plate and the gas outlet; and the volume of the left expansion chamber accounts for 3/5 of the total volume of the whole shell inner chamber. The invention changes the sound wave propagation characteristic through the two expansion chambers and the throttle plate between the two expansion chambers to damp incident waves, thus, the sound wave strength is reduced; and the gas pulsation vibration damper has good damping effect for vibration caused by pulse gas flow. The invention has the advantages of simple structure, low cost, strong adaptability and the like.
Description
Technical field
The present invention relates to a kind of vibration suppressor, relate in particular to gas pulsation vibration damper, be applicable to the pipe vibration that in the pipeline conveying, the reciprocating compressor outer pipe is caused by gas.
Background technique
The industry such as oil, chemical industry is widely used pipeline and carries, and the reciprocal compressor power source that normally pipeline is carried, be important machinery in oil refining and chemical plant installations, and pipe vibration is one of common fault of reciprocating compressor outlet pipeline.If the mobile of reciprocal compressor gas in pipelines is certain, in pipeline, the pressure of specified point and speed and density are time-independent, but, because reciprocal compressor is inhaled, the intermittence of exhaust, make the pressure of air-flow become cyclically-varying with speed, this phenomenon is called gas.Gas causes that the pressure, speed, density of medium in pipe etc. is not only with change in location but also intercropping cyclically-varying at any time.When the air-flow of pulsation carries along pipeline elements such as running into elbow, reducer, control valve, blind plate, can produce time dependent excitation force, be subject to this excitation force effect, pipe-line system just produces certain mechanical vibration response.The gas meeting causes much harm, such as: reduce the reciprocal compressor volumetric efficiency, cause that extra power consumpiton, air valve operating mode degenerate, control instrument is malfunctioning and cause pipe vibration etc.The reciprocating compressor vibration is that gas causes mostly, and gas excites pipeline to do mechanical vibration, and pipe vibration causes again unit vibration conversely, so will eliminate pipe vibration, primary problem is to eliminate gas in pipeline.
For controlling the vibration of reciprocating compressor outlet piping, publication number is that the internals that CN 1755070A, name are called " pulsing airflow vibration damping device " is provided with changeover portion and nozzle, form a flow expansion space between internals and external casing, but this device changes the shape of pulsing airflow and the weak effect of speed, attenuating to gas is undesirable, can't reach the purpose of subduing piping and accessory excitation force.
Summary of the invention
The objective of the invention is for overcoming the deficiencies in the prior art, the vibrations that provide a kind of paired pulses air-flow to cause have the gas pulsation vibration damper of better attenuating.
The technical solution used in the present invention is: outside is a Cylinder Shell, have suction port near on the sidewall of housing left end, it on right-hand member, is air outlet, suction port is provided with changeover portion, the changeover portion bottom is stretched in housing and the fixing gradual shrinkage nozzle that is communicated with, fix a Rectifier plate on the housing intracavity section between suction port and air outlet, Rectifier plate is provided with several throttling through holes; Form left expansion chamber between housing left end and Rectifier plate, form right expansion chamber between Rectifier plate and air outlet, the volume of left expansion chamber accounts for 3/5 of whole housing inner chamber total volume.
Further, shell length L of the present invention is its inside diameter D
05 ~ 10 times, inside diameter D
0it is the suction port inner diameter d
03 ~ 5 times; The air outlet internal diameter equals the suction port inner diameter d
0; Transition section length l
04 ~ 7 times of its internal diameter; The converging transition length l of nozzle
1it is its outlet diameter
3 ~ 5 times; The throttling through hole is arranged in parallel or annular array or star-likely disperse arrangement on Rectifier plate or by a line spacing; Every two throttling through hole center distance are suction port inner diameter d
00.4 ~ 0.6 times.
The present invention changes the sound wave transmission characteristics by two expansion chambers and Rectifier plate therebetween, and incoming wave is decayed, and has reduced intensity of acoustic wave, and the vibrations that cause for pulsing airflow have good attenuating.There are simple in structure, the advantages such as cost is low, strong adaptability.
The accompanying drawing explanation
Fig. 1 is structural representation of the present invention;
Fig. 2 is changeover portion 2 and nozzle 3 structure for amplifying schematic diagram in Fig. 1;
Fig. 3 is the sectional view of Rectifier plate 6 in Fig. 1;
In figure: 1. suction port; 2. changeover portion; 3. nozzle; 4. left expansion chamber; 5. housing; 6. Rectifier plate; 7. right expansion chamber; 8. air outlet; 9. throttling through hole.
Embodiment
Referring to Fig. 1-2, outside of the present invention is the housing 5 of a cylinder type, and housing 5 two ends are standard oval or dome head.The internal diameter of housing 5 is D
0, length is L
.having suction port 1 near on the sidewall of housing 5 left ends, the internal diameter of suction port 1 is d
0, housing 5 inside diameter D
0it is suction port 1 inner diameter d
03 ~ 5 times, length L is inside diameter D
05 ~ 10 times.The changeover portion 2 of the tubulose matched with suction port 1 size is installed on suction port 1, and the length of changeover portion 2 is l
0, the internal diameter of changeover portion 2 is d, l
04 ~ 7 times of d.The bottom of changeover portion 2 is stretched in housing 5, in the bottom of changeover portion 2, is fixedly connected with gradual shrinkage nozzle 3, and nozzle 3 communicates with changeover portion 2, and the inlet diameter of nozzle 3 equates with the inner diameter d of changeover portion 2, and the inlet diameter of nozzle 3 is than nozzle 3 outlet diameters
greatly; The converging transition length l of nozzle 3
1for outlet diameter
3 ~ 5 times.The exit flow of reciprocating compressor is entered in housing 5 by changeover portion 2 and nozzle 3.On housing 5 right-hand members, be air outlet 8, air outlet 8 internal diameters equal suction port 1 inner diameter d
0, the air-flow in housing 5 is discharged to follow-up pipe by air outlet 8.
In housing 5 inner chambers, fix a Rectifier plate 6 on the cross section between suction port 1 and air outlet 8, the wall thickness of Rectifier plate 6 equates with the wall thickness of reciprocating compressor outlet piping, Rectifier plate 6 is round structure, this circular external diameter equates with housing 5 internal diameters, Rectifier plate 6 is fixed on the inwall of housing 5.Several throttling through holes 9 are set on Rectifier plate 6.Like this, in housing 5 inner chambers, formed left expansion chamber 4 between housing 5 left ends and Rectifier plate 6, nozzle 3 is communicated with left expansion chamber 4.Formed right expansion chamber 7 between Rectifier plate 6 and air outlet 8, by the throttling through hole 9 on Rectifier plate 6, left expansion chamber 4 and right expansion chamber 7 have been communicated with.The volume of left expansion chamber 4 and left expansion chamber 7 is unequal, and the volume of left expansion chamber 4 accounts for 3/5 of whole housing 5 inner chamber total volumies.The spacing at every two throttling through hole 9 centers is suction port 1 inner diameter d
00.4 ~ 0.6 times.Referring to Fig. 3, throttling through hole 9 has multiple in the distribution mode of Rectifier plate 6, can be arranged in parallel or disperse arrangement by the annular array shown in Fig. 3 (b) or by Fig. 3 (c) star-like according to the line spacing shown in Fig. 3 (a).
When the present invention works, the exit flow of reciprocating compressor enters from suction port 1, the changeover portion 2 of flowing through, by nozzle 3, be ejected in housing 5, enter left expansion chamber 4 formation and flow to the complicated vortex system such as whirlpool, stretching whirlpool, left expansion chamber 4 is similar to low-pass filter, and when the Pulse wave of high frequency enters left expansion chamber 4, its transmission factor is close to zero; Then the throttling through hole 9 that complicated vortex system is flowed through on Rectifier plate 6 flows out and becomes air-flow stably and enter right expansion chamber 7, the approximate high-pass filter of Rectifier plate 6, the Pulse wave of low frequency is after Rectifier plate, transmission factor is close to zero, simultaneously, the various complex vortex structures that Rectifier plate 6 also forms left expansion chamber 4 gases play the effect of throttling; Finally by air outlet 8, enter follow-up pipe.The present invention changes the sound wave transmission characteristics by left and right expansion chamber 4,7 and Rectifier plate 6, incoming wave is carried out to reflection loss, the transmitted wave of a part continues to propagate Pulse wave, when transmitted wave, in whole incoming wave, account for ratio close to zero the time, just reach the purpose of eliminating gas, fundamentally eliminated vibration.
Take model as V-0.12/8 secondary air reciprocating compressor outer pipe be the example, the reciprocating compressor air displacement is 0.12 m
3/ min, rotating speed is 1000 r/min; Reciprocating compressor outlet piping internal diameter is 15mm; Sensor adopts the CA-YD-103 type, and reference sensitivity is 2.15pC/ms
-2, frequency range is 0.5-10KHz.Adopt vibration and dynamic signal acquisition analytical system software CRAS successively to reciprocating compressor outlet piping of the present invention not being installed and 8 test points on piping of the present invention being installed and having carried out vibration displacement and waveform testing, the vibration amplitude of measuring is all dulble vibration amplitude values, and result is as shown in table 1.
Table 1 reciprocating compressor outlet piping test result (mm)
By table 1, known, the amplitude measurement result that each measuring point of piping of the present invention is not installed is far longer than has installed test result of the present invention, the amplitude that each test point of piping of the present invention is not installed is all larger, the amplitude of measuring point 1,2,3 particularly, and being installed, all significantly reduced each measuring point amplitude of piping of the present invention, the test result of several test points particularly, the amplitude of pipeline reduces by 25 times of left and right.
Claims (3)
1. a gas pulsation vibration damper, outside is a Cylinder Shell (5), have suction port (1) near on the sidewall of housing (5) left end, on right-hand member, be air outlet (8), suction port (1) is provided with changeover portion (2), changeover portion (2) bottom is stretched in housing (5) and the fixing gradual shrinkage nozzle (3) that is communicated with, it is characterized in that: fix a Rectifier plate (6) on housing (5) intracavity section be positioned between suction port (1) and air outlet (8), Rectifier plate (6) is provided with several throttling through holes (9); Form left expansion chamber (4) between housing (5) left end and Rectifier plate (6), form right expansion chamber (7) between Rectifier plate (6) and air outlet (8), the volume of left expansion chamber (4) accounts for 3/5 of whole housing (5) inner chamber total volume.
2. gas pulsation vibration damper according to claim 1, it is characterized in that: housing (5) length L is its inside diameter D
05 ~ 10 times, housing (5) inside diameter D
0it is changeover portion (2) inner diameter d
03 ~ 5 times; Air outlet (8) internal diameter equals changeover portion (2) inner diameter d
0; Changeover portion (2) length l
04 ~ 7 times of its internal diameter; The converging transition length l of nozzle (3)
1it is its outlet diameter
3 ~ 5 times.
3. gas pulsation vibration damper according to claim 1 is characterized in that: throttling through hole (9) is upper or be arranged in parallel or annular array or star-likely disperse arrangement by a line spacing at Rectifier plate (6); Every two described throttling through holes (9) center distance is changeover portion (2) inner diameter d
00.4 ~ 0.6 times.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010546888 CN102032147B (en) | 2010-11-17 | 2010-11-17 | Gas pulsation vibration damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201010546888 CN102032147B (en) | 2010-11-17 | 2010-11-17 | Gas pulsation vibration damper |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102032147A CN102032147A (en) | 2011-04-27 |
| CN102032147B true CN102032147B (en) | 2013-01-16 |
Family
ID=43885465
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201010546888 Active CN102032147B (en) | 2010-11-17 | 2010-11-17 | Gas pulsation vibration damper |
Country Status (1)
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| CN (1) | CN102032147B (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103438323B (en) * | 2013-08-30 | 2015-07-01 | 西安交通大学 | L-type impact air flow attenuator |
| CN103758798B (en) * | 2014-01-21 | 2016-01-20 | 华中科技大学 | Broad-frequency pressure-variable pressure pulsation attenuator |
| CN104989622B (en) * | 2014-03-03 | 2018-04-27 | 刘友宏 | Compressor and its piping vibration-damping energy-saving device |
| CN104033374B (en) * | 2014-06-12 | 2015-09-16 | 浙江大学 | Be integrated in the multi-freedom degree adjustable pressure pulsation dampening in plunger pump shell |
| CN106335642B (en) * | 2016-09-27 | 2018-10-19 | 中国空气动力研究与发展中心高速空气动力研究所 | A kind of noise suppression device for weapon bay based on environmental gas jet flow |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4122914A (en) * | 1976-04-30 | 1978-10-31 | Nihon Radiator Co., Ltd. | Muffler |
| US4360076A (en) * | 1976-03-24 | 1982-11-23 | Nihon Rajieeta Kabushiki Kaisha (Nihon Radiator Co., Ltd.) | Muffler |
| SU1483058A2 (en) * | 1987-10-06 | 1989-05-30 | В.ВоОвечкин | Exhaust silencer for ic-engine |
| DE20212354U1 (en) * | 2002-08-10 | 2002-12-12 | Weiershaeuser Volker | Exhaust of a two-stroke engine |
| CN2818812Y (en) * | 2005-07-13 | 2006-09-20 | 林辉江 | Electroplating gasoline purification silencer of vehicle |
| CN201184226Y (en) * | 2008-04-14 | 2009-01-21 | 贾永康 | Automobile energy-saving silencer |
| CN201412208Y (en) * | 2009-06-09 | 2010-02-24 | 郑邑明 | Muffler |
-
2010
- 2010-11-17 CN CN 201010546888 patent/CN102032147B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4360076A (en) * | 1976-03-24 | 1982-11-23 | Nihon Rajieeta Kabushiki Kaisha (Nihon Radiator Co., Ltd.) | Muffler |
| US4122914A (en) * | 1976-04-30 | 1978-10-31 | Nihon Radiator Co., Ltd. | Muffler |
| SU1483058A2 (en) * | 1987-10-06 | 1989-05-30 | В.ВоОвечкин | Exhaust silencer for ic-engine |
| DE20212354U1 (en) * | 2002-08-10 | 2002-12-12 | Weiershaeuser Volker | Exhaust of a two-stroke engine |
| CN2818812Y (en) * | 2005-07-13 | 2006-09-20 | 林辉江 | Electroplating gasoline purification silencer of vehicle |
| CN201184226Y (en) * | 2008-04-14 | 2009-01-21 | 贾永康 | Automobile energy-saving silencer |
| CN201412208Y (en) * | 2009-06-09 | 2010-02-24 | 郑邑明 | Muffler |
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|---|---|
| CN102032147A (en) | 2011-04-27 |
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Effective date of registration: 20150928 Address after: Daitou town of Liyang City Ferry Street 213311 Jiangsu city of Changzhou province 8-2 No. 7 Patentee after: Liyang Chang Technology Transfer Center Co., Ltd. Address before: Gehu Lake Road Wujin District 213164 Jiangsu city of Changzhou province No. 1 Patentee before: Changzhou University |