CN1755070A - Pulsation air current vibration-damping arrangement - Google Patents
Pulsation air current vibration-damping arrangement Download PDFInfo
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- CN1755070A CN1755070A CN 200410060551 CN200410060551A CN1755070A CN 1755070 A CN1755070 A CN 1755070A CN 200410060551 CN200410060551 CN 200410060551 CN 200410060551 A CN200410060551 A CN 200410060551A CN 1755070 A CN1755070 A CN 1755070A
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- nozzle
- flow
- vibration damping
- damping device
- changeover portion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
- F16L55/00—Devices or appurtenances for use in, or in connection with, pipes or pipe systems
- F16L55/02—Energy absorbers; Noise absorbers
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Pipe Accessories (AREA)
Abstract
The invention discloses a pulse air-flow damping device in the vibration damping and damageproof technique domain, which comprises the following parts: outer case, inside component and air-flow expansion space, wherein the inside component contains transition section and injector whose exit connects the air-flow expansion space between inside component and outer case; the cross-section shape of injector is periodic plane curve structure in space along the circle direction or quadrangle, triangle and regular polygon direction to extend arrangement, which is composed of straightway, arc segment or parabolic segment or hyperbolic segment or expansion segment; forming a closed plane curve in space; stretching the section shape along the axial direction of outer case; forming hollow channel with two end opening; the outlet of condenser sprays out through transition section and forms current direction vortex, extension vortex structure in the gas flow expansion space, which turns the pulse air-flow as stable air-flow.
Description
Affiliated technical field
The invention belongs to vibration damping and prevention technique field, relate generally to a kind of pulse pneumatic vibration damping device.
Background technique
Piping is in industrial production, particularly use quite extensive in petrochemical industry, electric power, chemical industry, usually pipeline that stream-liquid two-phase flow piping, pressure reduction are bigger and pulse pneumatic piping etc. are in operation and can produce vibration, particularly in the conveying piping of reciprocal compressor.The work characteristics of reciprocal compressor is that suction, blast air are periodically and/or intermittence, therefore inevitably will excite the air-flow of the inlet/outlet piping of compressor to be pulse state, and this phenomenon is called gas.The flow parameter of pulse pneumatic (as pressure, speed, density) is periodic variation with position and time.When pulse pneumatic flows along piping, run into elements such as elbow, reducer, branched pipe, valve, blind plate and will produce time dependent excitation force, be subjected to the effect of this excitation force, piping just produces certain mechanical vibration response.Pressure pulsation is bigger, and the vibration amplitude of piping and stress intensity are bigger.Strong pulse pneumatic can seriously influence the normal switching of air valve, causes improper the closing of valve in the piping, the damage of instrumentation and conduit, and the misoperation of control system, also can cause the pipe fitting fatigue ruption, leak, even cause major accidents such as fire, blast.In addition, the vibration of piping also can produce sizable noise, and environment is on every side produced noise pollution.
Second reason of piping vibration is resonance.Gas in the pipeline constitutes an aeroelastic system, is called gas column.The hydroacoustics frequency that gas column itself has is called the gas column natural frequency.The suction and discharge frequency that the reciprocal compressor piston motion causes is called excitation frequency.Piping and annex thereof are formed a system, and the frequency that this system's solid structure itself has is called mechanical natural frequency.On engineering often the frequency range of (0.8-1.2) f (f is mechanical natural frequency or gas column natural frequency) as resonance region.When the gas column natural frequency drops on the resonance region of excitation frequency, air column resonance (standing wave) takes place, produce bigger stream pressure pulsation.When mechanical natural frequency drops on the resonance region of excitation frequency, recurring structure resonance.
Current, to the control of piping vibration, mainly research and solve from the excitation force of subduing piping and these two aspects of vibration characteristics of improving piping.Subduing excitation force, just to subdue vibration source be best bet, possible in theory, but actual conditions are never to find effective solution both at home and abroad.For the vibration characteristics of improving piping, to study morely, existing achievement in research all is at the appropriate location of pipeline reload buffer jar basically, perhaps the position and the form of pipe clamp in the piping is improved design.
Summary of the invention
The objective of the invention is to propose a kind of pulse pneumatic vibration damping device, its sound wave transmission characteristics and reduction intensity of acoustic wave by changing gas circuit in piping and the accessory thereof, thus reach the excitation force of subduing piping and accessory thereof.
Device proposed by the invention mainly is made up of external casing, internals and flow expansion space; Internals is made of changeover portion and nozzle; Form the flow expansion space between internals and the external casing; Flow expansion spatial communication between the outlet of nozzle and internals, the external casing; The sectional shape of nozzle---by straightway or circular arc line segment or parabolic segment or hyperbolic line segment or launch line segment and by straightway and circular arc line segment or with parabolic segment or the periodic space plane curvilinear structures formed with the hyperbolic line segment or with the expansion line segment along the circumferential direction, or along quadrilateral, triangle and regular polygon direction extension arrangement thereof, the space plane curve of a sealing of formation; Then the axial direction of this sectional shape along external casing stretched, form hollow channel---the nozzle of both ends open; The exit flow of compressor is entered by the suction port of this device, spray by nozzle through changeover portion, enter described flow expansion space, form and flow to complex vortex structures such as vortex system, stretching vortex system, pulse pneumatic is become stable air-flow, enter follow-up pipeline by the air outlet then.
Sectional dimension at each axial position of nozzle equates with former busbar cross-section size, or equal proportion enlarges or scaled down.
The sectional shape of changeover portion is circular, equates with former busbar cross-section size in the sectional dimension of each axial position of changeover portion, or equal proportion expansion or scaled down.
Pulse pneumatic vibration damping device proposed by the invention will be sprayed by nozzle through changeover portion by the pulse pneumatic that compressor outlet enters, in the flow expansion space, form and flow to complex vortex structures such as vortex system, stretching vortex system, pulse pneumatic is become stable air-flow, enter follow-up pipeline by the air outlet then.Sound wave transmission characteristics and the reduction intensity of acoustic wave of the present invention by changing gas circuit in piping and the accessory thereof, thus reach the excitation force of subduing piping and accessory thereof, have the better damping effect.
Description of drawings
Fig. 1 is the structural representation of apparatus of the present invention.
Fig. 2-Fig. 5 is the sectional shape schematic representation of nozzle among the present invention.
Fig. 6 is one section piping schematic representation of calculating machine natural frequency in the specific embodiment.
Fig. 7 is the one section piping schematic representation that calculates the gas column natural frequency in the specific embodiment.
Among the figure: 1, suction port, 2, changeover portion, 3, nozzle, 4, external casing, 5, the air outlet, 6, the expansion space.
Embodiment
The embodiment who provides is in conjunction with the accompanying drawings further specified the present invention: shown in accompanying drawing 1, apparatus of the present invention mainly are made up of external casing 4, internals and flow expansion space 6; Internals is made of changeover portion 2 and nozzle 3; External casing has air outlet 5; Form flow expansion space 6 between internals and the external casing 4; Flow expansion spatial communication between the outlet of nozzle 3 and internals, the external casing 4.
The sectional shape of nozzle---by straightway or circular arc line segment or parabolic segment or hyperbolic line segment or launch line segment and by straightway and circular arc line segment or with parabolic segment or the periodic space plane curvilinear structures formed with the hyperbolic line segment or with the expansion line segment along the circumferential direction, or along quadrilateral, triangle and regular polygon direction extension arrangement thereof, the space plane curve of a sealing of formation; Then the axial direction of this sectional shape along external casing stretched, form hollow channel---the nozzle of both ends open.
By shown in Figure 2, the sectional shape of nozzle is that the periodic space plane curvilinear structures that straightway and circular arc line segment are formed along the circumferential direction extends arrangement, the space plane curve of a sealing of formation.
By shown in Figure 3, the sectional shape of nozzle is that the periodic space plane curvilinear structures that circular arc line segment and parabolic segment are formed along the circumferential direction extends arrangement, the space plane curve of a sealing of formation.
By shown in Figure 4, the sectional shape of nozzle is that the periodic space plane curvilinear structures that straightway and hyperbolic line segment are formed along the circumferential direction extends arrangement, the space plane curve of a sealing of formation.
By shown in Figure 5, the sectional shape of nozzle is that straightway along the circumferential direction extends arrangement, the space plane curve of a sealing of formation with the periodic space plane curvilinear structures that launches the line segment composition.
The exit flow of compressor is entered by the suction port 1 of this device, spray by nozzle 3 through changeover portion 2, enter described flow expansion space 6, formation flows to vortex system, the stretching vortex system (flows to a plurality of vortexs that vortex system causes owing to the jet area has velocity circulation, intensity changes along the injection stream direction, the stretching vortex system is to have speed difference owing to outflow in the jet area, thereby in mixing shear layer because a plurality of vortexs that the effect of entrainmenting forms) etc. the complex vortex structure, pulse pneumatic is become stable air-flow, enter follow-up pipeline by air outlet 5 then.
To certain specified inlet flow rate is 17800Nm
3/ h, speed of crankshaft 300rpm, inlet pressure are that 2.4MPa, inlet temperature are that 40 ℃, outlet pressure are that 9.8MPa, outlet temperature are the piping at 2 sections double-action reciprocal compressor places of certain gas of 110 ℃, select a certain section typical pipeline as research object, the mechanical natural frequency limited element calculation model of this pipeline section of setting up as shown in Figure 6, the mechanical calculation on Natural Frequency of this pipeline section the results are shown in (excitation frequency of reciprocal compressor is 10Hz) shown in the following table-1.
Table-1
A same compressor piping selection segment pipe as shown in Figure 7 as research object, has been set up the gas column natural frequency limited element calculation model of this pipeline section, and the gas column calculation on Natural Frequency of this pipeline section the results are shown in shown in the following table-2.
Table-2
By comparing with excitation frequency, table-1 (mechanical natural frequency of pipeline section) and table-2 (the gas column natural frequencys of pipeline section) have all been avoided the excitation frequency of compressor from far away, and visible selection all is safe as the mechanical resonance and the air column resonance of the pipeline section of research object.Other pipeline section to piping is all made same FEM (finite element) calculation, all is mechanical resonance and air column resonance safety with the piping that guarantees whole compressor workshop section.
Claims (8)
1, a kind of pulse pneumatic vibration damping device, this device mainly is made up of external casing (4), internals and flow expansion space (6); It is characterized in that: described internals is made of changeover portion (2), nozzle (3); Form flow expansion space (6) between internals and the external casing (4); Flow expansion spatial communication between the outlet of nozzle (3) and internals, the external casing; The sectional shape of described nozzle---by straightway or circular arc line segment or parabolic segment or hyperbolic line segment or launch line segment and by straightway and circular arc line segment or with parabolic segment or the periodic space plane curvilinear structures formed with the hyperbolic line segment or with the expansion line segment along the circumferential direction, or along quadrilateral, triangle and regular polygon direction extension arrangement thereof, the space plane curve of a sealing of formation; Then the axial direction of this sectional shape along external casing stretched, form hollow channel---the nozzle of both ends open; The exit flow of compressor is entered by the suction port (1) of this device, the changeover portion (2) of flowing through is sprayed by nozzle (3), enter described flow expansion space (6), formation flows to complex vortex structures such as vortex system, stretching vortex system, pulse pneumatic is become stable air-flow, enter follow-up pipeline by air outlet (5) then.
2, pulse pneumatic vibration damping device according to claim 1 is characterized in that, equates with former busbar cross-section size in the sectional dimension of each axial position of nozzle.
3, pulse pneumatic vibration damping device according to claim 1 is characterized in that, in the sectional dimension of each axial position of nozzle and the contraction that former busbar cross-section size is an equal proportion.
4, pulse pneumatic vibration damping device according to claim 1 is characterized in that, in the sectional dimension of each axial position of nozzle and the expansion that former busbar cross-section size is an equal proportion.
5, pulse pneumatic vibration damping device according to claim 1 is characterized in that, the sectional shape of described changeover portion is circular, equates with former busbar cross-section size in the sectional dimension of each axial position of changeover portion.
6, pulse pneumatic vibration damping device according to claim 1 is characterized in that, the sectional shape of described changeover portion is circular, in the sectional dimension of each axial position of changeover portion and the expansion that former busbar cross-section size is an equal proportion.
7, pulse pneumatic vibration damping device according to claim 1 is characterized in that, the sectional shape of described changeover portion is circular, in the sectional dimension of each axial position of changeover portion and the contraction that former busbar cross-section size is an equal proportion.
8, pulse pneumatic vibration damping device according to claim 1 is characterized in that, described external casing (4) has air outlet (5).
Priority Applications (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200410060551 CN1755070A (en) | 2004-09-30 | 2004-09-30 | Pulsation air current vibration-damping arrangement |
| PCT/CN2005/001363 WO2006034623A1 (en) | 2004-09-30 | 2005-08-30 | A device of reducing pulsating airflow and vibration |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 200410060551 CN1755070A (en) | 2004-09-30 | 2004-09-30 | Pulsation air current vibration-damping arrangement |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN1755070A true CN1755070A (en) | 2006-04-05 |
Family
ID=36118566
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 200410060551 Pending CN1755070A (en) | 2004-09-30 | 2004-09-30 | Pulsation air current vibration-damping arrangement |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN1755070A (en) |
| WO (1) | WO2006034623A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104801435A (en) * | 2014-01-23 | 2015-07-29 | 刘友宏 | Chrysanthemum-shaped nozzle water injecting and air pumping device and an injection type mixer |
| CN105715327A (en) * | 2016-04-07 | 2016-06-29 | 北京化工大学 | Counter jet type airflow pulsation attenuator |
| CN106335642A (en) * | 2016-09-27 | 2017-01-18 | 中国空气动力研究与发展中心高速空气动力研究所 | Weapon bay noise suppression device based on environment gas jet |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN87216191U (en) * | 1987-12-11 | 1988-07-27 | 北京机械工业管理学院 | Pulsation eliminater of liquid pressure |
| JPH06191766A (en) * | 1992-12-28 | 1994-07-12 | Hitachi Ltd | Hydraulic muffler |
| CN2289122Y (en) * | 1997-06-16 | 1998-08-26 | 广东美的集团股份有限公司 | Noise silencer for fluide pipeline |
-
2004
- 2004-09-30 CN CN 200410060551 patent/CN1755070A/en active Pending
-
2005
- 2005-08-30 WO PCT/CN2005/001363 patent/WO2006034623A1/en active Application Filing
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104801435A (en) * | 2014-01-23 | 2015-07-29 | 刘友宏 | Chrysanthemum-shaped nozzle water injecting and air pumping device and an injection type mixer |
| CN105715327A (en) * | 2016-04-07 | 2016-06-29 | 北京化工大学 | Counter jet type airflow pulsation attenuator |
| CN106335642A (en) * | 2016-09-27 | 2017-01-18 | 中国空气动力研究与发展中心高速空气动力研究所 | Weapon bay noise suppression device based on environment gas jet |
| 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 |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2006034623A1 (en) | 2006-04-06 |
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