CN103062569A - Pressure-auto-balance hydrodynamic noise silencer - Google Patents
Pressure-auto-balance hydrodynamic noise silencer Download PDFInfo
- Publication number
- CN103062569A CN103062569A CN2013100093571A CN201310009357A CN103062569A CN 103062569 A CN103062569 A CN 103062569A CN 2013100093571 A CN2013100093571 A CN 2013100093571A CN 201310009357 A CN201310009357 A CN 201310009357A CN 103062569 A CN103062569 A CN 103062569A
- Authority
- CN
- China
- Prior art keywords
- perforated pipe
- internal layer
- silencing apparatus
- perforation
- spring member
- 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.)
- Granted
Links
Images
Landscapes
- Pipe Accessories (AREA)
- Exhaust Silencers (AREA)
Abstract
The invention aims to provide a pressure-auto-balance hydrodynamic noise silencer comprising an inner perforated tube, an end face flange and a barrel casing. The end face flange is respectively hermetically connected with the inner perforated tube and the barrel casing to form a cavity. A compressible elastic component is filled in the cavity. One end of the inner perforated tube is connected with an inlet tube, and the other end of the inner perforated tube is connected with an outlet tube. The inner perforated tube is provided with perforated holes. The pressure-auto-balance hydrodynamic noise silencer is compact in structure, and can automatically balance along with changes of system static pressure during working, and a conventional energy accumulator inflating and deflating device is omitted. Besides, the noise silencer combines advantages of a resistant noise silencer and an energy accumulator, and is high in adjustability of silencing frequency and capable of effectively suppressing broadband hydrodynamic noise.
Description
Technical field
What the present invention relates to is a kind of silencing apparatus, specifically is used for suppressing the silencing apparatus of pipeline system water kinetic noise.
Background technique
Pipe-line system is common device in the every field of national economy and the daily life, all be prevalent in various ships such as domestic water pipeline and cooling water pipeline etc., but the vibration noise of water lines also is not well controlled so far, how to reduce a difficult problem that the pipe-line system noise remains the puzzlement people.
The impact of charging line noise be noise in the pipeline by tube wall to external radiation and the directly radiation in the environment in the outlet port, people's work and life produced considerable influence.Pressure pulsation also directly causes stress fluctuation and the mechanical vibration of pipeline, particularly when the natural frequency of ripple frequency and pipe-line system near the time, have very large destruction.Airplane hydraulic pipeline for example all occured both at home and abroad break and cause the event of engine combustion, air crash, the oil transport pipeline break accident also once repeatedly occured.A kind of special circumstances of pipeline pressure pulsation are water hammers common in the water lines, and the line rupture protection valve accident that is caused by water hammer both at home and abroad is a lot.
The general vibration and noise reducing measure that the charging line system is often taked mainly contains following several: the one, reduce the flow pulsation of the pipeline components such as pump, valve; The 2nd, from the angle of load system, reduce the input resistance of system, then in the same corresponding minimizing of flow pulsation downforce pulsation meeting; The 3rd, the supplementary equipment such as liquid silencing apparatus are installed in pipeline, pressure pulsation is decayed and filtering.Wherein in pipeline the liquid silencing apparatus being installed is most widely used a kind of method.
Existing hydrodynamic noise silencing apparatus mainly contains by air silencer and develops and the expanssion type come, inner-intubation, reactive muffling structure and the accumulator such as resonant.
There is following difficulty in reactive muffling structured liquids muffler desing: at first, the airborne wavelength of wavelength ratio of sound wave is large more than four times in the frequency one timing liquid medium, the size of silencing apparatus certainly will increase under the identical frequency of noise elimination, but the size increase can be subject to the restriction of installing space; Secondly, sound absorption, sound insulating material commonly used in the air dielectric all are entrant sound basically in liquid medium, and water liquid medium silencing apparatus should not design by the perforation structure that often adopts in the air silencer design.
Accumulator is to go out to send decay pressure pulsation from load system, accumulator is installed is effectively reduced pipeline fluid pulsation and noise, but the general volume of existing accumulator is larger, frequency of noise elimination is single, thereby is difficult to suppress the hydrodynamic force noise of wideband, and the Environmental Conditions that changes for system static pressure power, accumulator need to add aerating and exhaust device with the balance sysmte static pressure, this has further increased its volume, has increased the complexity of its structure, has limited its application in the confined space.
Summary of the invention
The object of the present invention is to provide saved traditional accumulator aerating and exhaust device and can be with the change of system static pressure power a kind of pressure self-balancing hydrodynamic noise silencing apparatus of self balancing.
The object of the present invention is achieved like this:
A kind of pressure self-balancing hydrodynamic noise of the present invention silencing apparatus, it is characterized in that: comprise internal layer perforated pipe, end face flange, barreled housing, thereby the end face flange is connected with the barreled housing to be connected with the internal layer perforated pipe respectively and is formed chamber, fill compressible spring member in the chamber, internal layer perforated pipe one end connects inlet tube, the other end connection outlet pipe, is provided with the perforation of internal layer perforated pipe on the internal layer perforated pipe.
The present invention can also comprise:
1, is positioned at outer perforated pipe is installed on the internal layer perforated pipe outer wall of chamber one side, be provided with outer perforated pipe perforation on the outer perforated pipe, link to each other by adjusting screw, the perforation of internal layer perforated pipe, the perforation of outer perforated pipe between internal layer perforated pipe and the outer perforated pipe, can regulate the relative position of internal layer perforated pipe and outer perforated pipe by adjusting screw, the perforation of internal layer perforated pipe, the perforation of outer perforated pipe.
2, on the outer perforated pipe wire gaze is installed, the size of wire gaze mesh can't be passed as the upper limit take compressible spring member.
3, the punching rate of internal layer perforated pipe is 50%, and internal layer perforated pipe penetration hole diameter is 10mm.
4, the punching rate of internal layer perforated pipe and outer perforated pipe is 50%, and the diameter of the perforation of internal layer perforated pipe and the perforation of outer perforated pipe is 10mm.
5, described compressible spring member is regular spheroid or the irregular spheroid of the inflation of sealing, and the size between the compressible spring member and material are all inconsistent.
Advantage of the present invention is: compact structure of the present invention, saved traditional accumulator aerating and exhaust device, can be with the change of system static pressure power during its work self balancing; This silencing apparatus combines the advantage of anti-formula silencing apparatus and accumulator, and the frequency of noise elimination adjustability is strong, can effectively suppress wideband hydrodynamic force noise.
Description of drawings
Fig. 1 is structural representation of the present invention;
Fig. 2 is that single inflation bead is positioned over the transmission loss figure that causes in the chamber;
Fig. 3 is that the size of inflation bead is to the influence curve figure of transmission loss peak value;
Fig. 4 is the schematic representation one that punching rate is regulated;
Fig. 5 is the schematic representation two that punching rate is regulated;
Fig. 6 is perforation schematic representation one;
Fig. 7 is perforation schematic representation two.
Embodiment
For example the present invention is described in more detail below in conjunction with accompanying drawing:
In conjunction with Fig. 1~7, the present invention has the outer perforated pipe 2 of cylindrical shape of a cylindrical shape internal layer perforated pipe 1, a coaxial placement, and internal layer perforated pipe 1 is connected with its end face flange 13 sealings, and outer perforated pipe 2 is coated with wire gaze 22; Outer perforated pipe 2 consists of a chamber with its end face flange 13, tubular shell 3, chamber interior is filled with a plurality of inflation beads or other shape, sealing, compressible spring member 4, bead or other shape, sealing, compressible spring member 4 is of different sizes; Relative position between internal layer perforated pipe 1 and the outer perforated pipe 2 can change by adjusting screw 23; Left side 51 is connected by bolt 35 connections in the right side 34 of tubular shell 3 with outlet pipe section, whole silencing apparatus is connected to water piping system by the entry end flange 24 of internal layer perforated pipe and the right-hand member flange 52 of outlet pipe section.
Chamber interior is placed inflation bead or other shape, sealing, compressible spring member 4, because the compressibility of elastic element 4 is good, therefore the velocity of sound in the elastic element 4 is significantly less than the velocity of sound in the water, the structural parameter of suitable selection elastic element, the incident sound impedance levels off to 0 when making the incident acoustic wave of certain frequency be applied to the bead surface, reach the purpose of noise elimination, since each elastic element be the sealing and independently, its enclosed, outer surface was subject to well-distributed pressure when elastic element placed working fluid, so when the system static pressure power of charging line changes, the compressible spring member of sealing expands or shrinks and balance outside system static pressure power, the material of elastic element or physical dimension are different, thereby make silencing apparatus have a plurality of different frequency of noise elimination, reach the purpose that wideband is eliminated the noise.
The outer perforated pipe 2 of cylindrical shape internal layer perforated pipe 1 and cylindrical shape is the punch block at the middle part, do not bore a hole near two-end part, the punching rate of perforated pipe is 50%, the penetration hole diameter of each perforated pipe is 10mm, two coaxial placements of perforated pipe, thereby change the space contact ratio (such as Fig. 4 and shown in Figure 6) of two perforation pipeline sections by the relative axial position that adjusting screw 23 is regulated two perforated pipes, thereby change the punching rate of whole silencing apparatus, and then change the frequency of noise elimination of silencing apparatus.
Outer perforated pipe 2 is coated with wire gaze 22, and the mesh of wire gaze 22 is not to make perforation that elastic element 4 can be by perforated pipe as upper dimension bound, so that the elastic element 4 that the fluid of internal layer perforated pipe 1 inside can fully touch in the chamber is lower size limit.The effect of wire gaze is: protection elastic element 4 is not cut by sharp-pointed perforated edge when the fluctuation of the rapid drawdown of system static pressure power or piping flow is larger, stops that simultaneously elastic element makes it can not pass perforated pipe and flow in the pipe-line system.
Internal layer perforated pipe 1 is connected with 13 sealings of end face flange; Internal layer perforated pipe end face flange 13 is bolted with tubular shell 3, and seal arrangement is set between them; Outer perforated pipe 2 consists of a chamber with internal layer perforated pipe end face flange 13, tubular shell 3, and left side 51 is connected by bolt 35 connections in the right side 34 of tubular shell 3 with outlet pipe section, seal arrangement 36 is set between them; Whole silencing apparatus is connected to water piping system by the entry end flange 24 of internal layer perforated pipe 1 and the right-hand member flange 52 of outlet pipe section.
Using perforated pipe that the import and export of silencing apparatus are coupled together is in order to reduce the fluid resistance losses of fluid.Sound wave enters into chamber by the aperture on the wall of perforated pipe, reflects, interferes at the front/rear end place of chamber, realizes eliminating the noise.For flowing of tube fluid, the introducing of perforated pipe is equivalent to increase a guiding bridge, makes the current can be with for waltzing through, thereby reduces fluid resistance losses.
The punching rate of double-deck perforated pipe can be regulated, two coaxial placements of perforated pipe, thus change the space contact ratio of two perforation pipeline sections by the relative axial position that adjusting screw 23 is regulated two perforated pipes, thus the punching rate of whole silencing apparatus changed; Thereby punching rate and piercing aperture have changed the perforation impedance makes its acoustical behavior adjustable.
When the punching rate of perforated pipe is hanged down, the introducing of perforated pipe is less to the influence of them of silencing apparatus, the intermediate frequency acoustic attenuation performance is improved a lot, limited on the impact of high frequency acoustic attenuation performance, punching rate is lower, the fluid impedance losses of silencing apparatus is less, and particularly the effect of perforated pipe is more obvious when velocity in pipes is larger; Along with the increase of punching rate, effectively noise elimination frequency band increases.When total punching rate〉25% the time, perforated pipe can not consider that on the impact of acoustical behavior whole silencing apparatus embodies and is the expansion chamber characteristic.
After incident acoustic wave entered into silencing apparatus, at first in the 13 places flow area sudden contraction of entrance face flange and impedance mismatch reflects, impedance mismatch occured in the right side 34 places flow area sudden expansion of outlet tubular shell in the part incident acoustic wave, reflects; Superpose in the process that this two-part reflected wave is upstream propagated, when the axial length of tubular shell equals the odd-multiple of 1/4 incident acoustic wave wavelength, the phase phase difference 180o of two-part reflected wave and destructive interference occurs, at this moment has maximum noise reduction under the frequency that incoming wave is corresponding, when the axial length of tubular shell equals the even-multiple of 1/4 incident acoustic wave wavelength, has minimum noise reduction under frequency corresponding to incoming wave; Simultaneously because inflation bead or other shape, sealing, the velocity of sound of compressible spring member 4 inside is significantly less than the velocity of sound in the flowing medium, impedance mismatching when being delivered to the elastic element surface, incident acoustic wave occurs, the corresponding intrinsic frequency of noise elimination of each elastic element, particularly when the natural frequency of incident sound wave frequency and elastic element is coincide, fluid particle is at inflation bead or other elastic element surface high vibration, the incident impedance of sound wave on surface of contact levels off to 0, the acoustic pressure of namely inflating bead or other elastic element 4 surfaces levels off to 0, and incident acoustic wave strong reflection has occured and made that silencing apparatus has had maximum noise reduction under this frequency.
Putting into of using that finite element software the calculates transmission loss that single inflation bead causes as shown in Figure 2.Can see in the drawings, can introduce at bead natural frequency place a transmission loss peak value behind the interpolation inflation bead in the chamber.The size of inflation bead on the impact of transmission loss as shown in Figure 3.If the physical dimension of a plurality of elastic elements of putting into is different, thereby make silencing apparatus have a plurality of different frequency of noise elimination, just can reach the purpose that wideband is eliminated the noise.
The aperture 11 that is covered with aperture φ 10mm on the internal layer perforated pipe 1, punching rate 50%, internal layer perforated pipe 1 and its inlet tube flange 24 welding, internal layer perforated pipe 1 welds with its end face flange 13 simultaneously, and there are 8 bolts hole the part on the end face flange 13.The internal diameter of outer perforated pipe 2 is identical with the external diameter of internal layer perforated pipe 1, and penetration hole diameter, punching rate are identical with internal layer perforated pipe 1, and the right-hand member of outer perforated pipe 2 is processed with adjustment hole 24 as shown in Figure 6; The periphery of outer perforated pipe 2 is coated with layer of metal silk screen 22 and prevents that elastic element 4 from passing perforated pipe; Outer perforated pipe 2 coaxial sleeves are on internal layer perforated pipe 1, and the axial relative displacement of regulating two perforated pipes just changes the coincidence factor in the space of two-layer perforated pipe.
Be evenly equipped with 8 bolts hole on the left side flange 31 of tubular shell, corresponding with 8 uniform bolt hole on the internal layer perforated pipe end face 13.Perforated pipe gos deep into to the through hole of the right side 34 of tubular shell 3, and the end face flange 13 of internal and external layer perforated pipe is connected left side flange 31 by bolt 33 connections with tubular shell, seal arrangement 32 is housed on the junction surface.
Be evenly equipped with 8 bolts hole on the right side 34 of tubular shell 3, corresponding with 8 uniform bolts hole on the left side 51 of outlet pipe section.Tubular shell 3 is connected with outlet pipe section by bolt 35 connections, and seal arrangement 36 is housed on the junction surface.
The periphery of outer perforated pipe 2 and the internal surface of tubular shell 3 and former and later two end faces 13,34 consist of a chamber, are filled with inflation bead or other shape, sealing, compressible spring member 4 in chamber.
Whole silencing apparatus is linked in the pipe-line system by inlet flange 24 and outlet(discharge) flange 52, during work, the liquid of line upstream enters into silencing apparatus inside by suction flange 24, partially liq enters into chamber by perforated pipe, when the static pressure of system changes, sealing, compressible spring member 4 is by expanding or shrinking the outside system static pressure power that balances.
Liquid carries hydrodynamic noise, and hydrodynamic noise is subdued by two kinds of mechanism in chamber interior.One is: incident-noise the sudden enlargement of inlet channel cross section locate dwindle suddenly the place with the outlet flow cross section and all reflect, when the axial length of chamber equals the even-multiple of 1/4 incident acoustic wave wavelength, cancelling out each other of two row reflective sound waves, be reflected to the peak value of the corresponding transmission loss of upper this frequency of transmission loss curve, when the axial length of chamber equals the odd-multiple of 1/4 incident acoustic wave wavelength, 0 value of corresponding transmission loss.The at this moment transmission loss of whole silencing apparatus has the expansion chamber characteristic of arch; When regulating punching rate to smaller value, the transmission loss of whole silencing apparatus has resonant characteristic.The mechanism two of noise reduction is: when the hydrodynamic noise of characteristic frequency incides bead, the incident impedance levels off to 0, be that fluid particle is being inflated bead or other elastic element surface high vibration, but the acoustic pressure on surface level off to 0, reaches the purpose of eliminating the noise at the characteristic frequency place with this.Since a plurality of sealings, compressible spring member has a plurality of different frequency of noise elimination, reaches the purpose of eliminating the noise at wideband with this.
Claims (8)
1. pressure self-balancing hydrodynamic noise silencing apparatus, it is characterized in that: comprise internal layer perforated pipe, end face flange, barreled housing, thereby the end face flange is connected with the barreled housing to be connected with the internal layer perforated pipe respectively and is formed chamber, fill compressible spring member in the chamber, internal layer perforated pipe one end connects inlet tube, the other end connection outlet pipe, is provided with the perforation of internal layer perforated pipe on the internal layer perforated pipe.
2. a kind of pressure self-balancing hydrodynamic noise silencing apparatus according to claim 1, it is characterized in that: be positioned at outer perforated pipe is installed on the internal layer perforated pipe outer wall of chamber one side, be provided with outer perforated pipe perforation on the outer perforated pipe, link to each other by adjusting screw, the perforation of internal layer perforated pipe, the perforation of outer perforated pipe between internal layer perforated pipe and the outer perforated pipe, can regulate the relative position of internal layer perforated pipe and outer perforated pipe by adjusting screw, the perforation of internal layer perforated pipe, the perforation of outer perforated pipe.
3. a kind of pressure self-balancing hydrodynamic noise silencing apparatus according to claim 2, it is characterized in that: on the outer perforated pipe wire gaze is installed, the size of wire gaze mesh can't be passed as the upper limit take compressible spring member.
4. a kind of pressure self-balancing hydrodynamic noise silencing apparatus according to claim 1, it is characterized in that: the punching rate of internal layer perforated pipe is 50%, internal layer perforated pipe penetration hole diameter is 10mm.
5. according to claim 2 or 3 described a kind of pressure self-balancing hydrodynamic noise silencing apparatuss, it is characterized in that: the punching rate of internal layer perforated pipe and outer perforated pipe is 50%, and the diameter that the perforation of internal layer perforated pipe and outer perforated pipe are bored a hole is 10mm.
6. arbitrary described a kind of pressure self-balancing hydrodynamic noise silencing apparatus according to claim 1-3, it is characterized in that: described compressible spring member is regular spheroid or the irregular spheroid of the inflation of sealing, and the size between the compressible spring member and material are all inconsistent.
7. a kind of pressure self-balancing hydrodynamic noise silencing apparatus according to claim 4 is characterized in that: described compressible spring member is regular spheroid or the irregular spheroid of the inflation of sealing, and the size between the compressible spring member and material are all inconsistent.
8. a kind of pressure self-balancing hydrodynamic noise silencing apparatus according to claim 5 is characterized in that: described compressible spring member is regular spheroid or the irregular spheroid of the inflation of sealing, and the size between the compressible spring member and material are all inconsistent.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201310009357.1A CN103062569B (en) | 2013-01-10 | 2013-01-10 | A kind of Pressure-auto-balanchydrodynamic hydrodynamic noise silencer |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201310009357.1A CN103062569B (en) | 2013-01-10 | 2013-01-10 | A kind of Pressure-auto-balanchydrodynamic hydrodynamic noise silencer |
Publications (2)
Publication Number | Publication Date |
---|---|
CN103062569A true CN103062569A (en) | 2013-04-24 |
CN103062569B CN103062569B (en) | 2015-09-30 |
Family
ID=48105338
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
CN201310009357.1A Active CN103062569B (en) | 2013-01-10 | 2013-01-10 | A kind of Pressure-auto-balanchydrodynamic hydrodynamic noise silencer |
Country Status (1)
Country | Link |
---|---|
CN (1) | CN103062569B (en) |
Cited By (38)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103307198A (en) * | 2013-06-28 | 2013-09-18 | 江苏大学 | Pump pool inherent frequency self-adapting method and device |
CN104089139A (en) * | 2014-07-02 | 2014-10-08 | 上海市计量测试技术研究院 | Water pipe silencer |
CN104632792A (en) * | 2014-12-12 | 2015-05-20 | 燕山大学 | Pipe type variable-damping filter provided with multiple holes with different parameters and applied to opening of hydraulic pump |
CN105736522A (en) * | 2016-05-12 | 2016-07-06 | 沈兴华 | Whole-frequency-band work condition self-adaptive filtering, magnetizing, magnetic field and centrifugation oil filter |
CN105736521A (en) * | 2016-05-12 | 2016-07-06 | 徐燚超 | Oil filtering method adopting filter for magnetizing, adsorbing and centrifuging |
CN105736524A (en) * | 2016-05-12 | 2016-07-06 | 徐燚超 | Oil filtering method adopting full-frequency-band working condition self-adaptive filtering, magnetization, rotary magnetic field and centrifuging |
CN105757061A (en) * | 2016-05-12 | 2016-07-13 | 谢阿招 | Filter device adopting wave suppression, magnetization, adsorption and centrifugation |
CN105782170A (en) * | 2016-05-12 | 2016-07-20 | 谢阿招 | Full-band variable-structure working condition-adaptive filtering, magnetizing and centrifuging oil filter |
CN105782169A (en) * | 2016-05-12 | 2016-07-20 | 陈连萍 | Filtering method adopting wave suppression, magnetization, adsorption and centrifugation |
CN105840594A (en) * | 2016-05-12 | 2016-08-10 | 李�昊 | Oil filtering method for full-band variable structure working condition self-adaptive filtering, electrifying and adsorbing |
CN105840593A (en) * | 2016-05-12 | 2016-08-10 | 徐燚超 | Filter method for filtering, magnetization, magnetic field rotation and centrifugation by full-band variable structure |
CN105840590A (en) * | 2016-05-12 | 2016-08-10 | 谢阿招 | Filter tank for filtering, magnetizing, adsorbing and centrifuging through full-band variable structure |
CN105840591A (en) * | 2016-05-12 | 2016-08-10 | 沈兴华 | Filtering device adopting wave suppression, magnetization, adsorption, rotating magnetic field and centrifugation |
CN105864221A (en) * | 2016-05-12 | 2016-08-17 | 李�昊 | Filtering method adopting filter, electrification, separation, adsorption and rotating magnetic field |
CN105864119A (en) * | 2016-05-12 | 2016-08-17 | 张华芳 | Method for treating hydraulic oil through magnetization, cyclone centrifugation and adsorption |
CN105864184A (en) * | 2016-05-12 | 2016-08-17 | 李�昊 | Method for filtering by adoption of full-band variable structure working condition self-adaptive wave filtering, electrification and adsorption |
CN105864196A (en) * | 2016-05-12 | 2016-08-17 | 陈连萍 | Filtering method using wave filter, magnetization, adsorption, rotating magnetic field and centrifugation |
CN105864200A (en) * | 2016-05-12 | 2016-08-17 | 谢阿招 | Filter tank adopting work-condition-adaptive filtering, magnetization, rotary magnetic field and centrifugation |
CN105889210A (en) * | 2016-05-12 | 2016-08-24 | 浙江工业职业技术学院 | Oil filtering method based on full-band variable-structure working condition self-adaptive filtration, electrification and centrifugation |
CN105889232A (en) * | 2016-05-12 | 2016-08-24 | 浙江工业职业技术学院 | Filtering device using wave restraint, electrifying, separating, absorbing and centrifuging |
CN105889213A (en) * | 2016-05-12 | 2016-08-24 | 浙江工业职业技术学院 | Filtering method based on full-band variable-structure filtration, electrification, separation and centrifugation |
CN105909619A (en) * | 2016-05-12 | 2016-08-31 | 李�昊 | Oil filtering method adopting variable-structure filtering, electrification, separation, adsorption and rotating magnetic field |
CN105909615A (en) * | 2016-05-12 | 2016-08-31 | 张国云 | Filtering method adopting magnetization, adsorption and rotating magnetic field for hydraulic system |
CN105971997A (en) * | 2016-05-12 | 2016-09-28 | 浙江工业职业技术学院 | Filtering method adopting working condition self-adaptive filtering, electrification, centrifugation and rotating magnetic field |
CN105971998A (en) * | 2016-05-12 | 2016-09-28 | 浙江工业职业技术学院 | Oil filtering method adopting full-band working condition self-adaptive filtering, electrification and centrifugation |
CN105971996A (en) * | 2016-05-12 | 2016-09-28 | 张华芳 | Method adopting magnetization, centrifuging and electric shock hammer adsorption for treating hydraulic oil |
CN105971992A (en) * | 2016-05-12 | 2016-09-28 | 浙江工业职业技术学院 | Oil filtering method using variable-structure filtering, electrification, separation, centrifuging and rotating magnetic field |
CN106197578A (en) * | 2014-09-23 | 2016-12-07 | 微动公司 | magnetic flowmeter flow tube assembly |
CN106402093A (en) * | 2016-05-12 | 2017-02-15 | 谢阿招 | Oil filtering device achieving full-band-working-condition self-adapted filtering, magnetization, adsorption and centrifugation |
CN107244397A (en) * | 2017-05-12 | 2017-10-13 | 哈尔滨工程大学 | A kind of heat dissipation type acoustic hood of gravity flow under water with noise elimination structure |
CN107420680A (en) * | 2017-08-23 | 2017-12-01 | 武汉理工大学 | A kind of artificial cochlea's silencer for air pipeline Noise measarement |
CN112628516A (en) * | 2019-10-09 | 2021-04-09 | 东台市东方船舶装配有限公司 | Frequency adjustable water pipeline silencer |
CN112648463A (en) * | 2019-10-09 | 2021-04-13 | 东台市东方船舶装配有限公司 | Frequency-adjustable resonance type water pipeline silencer |
CN113251233A (en) * | 2021-04-28 | 2021-08-13 | 北京理工大学 | Liquid pipeline sound attenuation system based on underwater wide and low frequency sound insulation metal-based metamaterial design |
CN114110291A (en) * | 2021-11-24 | 2022-03-01 | 江苏科技大学 | Elastic plate type straight-through perforated pipe water muffler with static pressure balance cavity and assembling method |
CN114215669A (en) * | 2021-12-24 | 2022-03-22 | 安徽江淮汽车集团股份有限公司 | Method for eliminating air inlet broadband noise and expansion cavity structure |
CN114321552A (en) * | 2022-01-04 | 2022-04-12 | 中国海洋大学 | Magnetorheological energy accumulator for water hammer protection and installation method and control system thereof |
CN114704703A (en) * | 2022-03-15 | 2022-07-05 | 中国船舶重工集团公司第七一一研究所 | Water pipeline silencing device, silencing method and ship |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN109209565A (en) * | 2018-07-26 | 2019-01-15 | 福建省汽车工业集团云度新能源汽车股份有限公司 | A kind of adjustable noise-reducing structure and its application and application method |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2952600A1 (en) * | 1979-12-28 | 1981-07-02 | Juval Dr.-Ing. 8000 München Mantel | Pipe noise damping equipment - comprises resilient outer or inner pipe section with breathing action |
SU1196601A2 (en) * | 1984-06-07 | 1985-12-07 | Харьковский авиационный институт им.Н.Е.Жуковского | Noise silencer |
CN2089112U (en) * | 1991-02-07 | 1991-11-20 | 宋振华 | Noise and wave absorbers for hydraulic system |
US5732741A (en) * | 1996-09-25 | 1998-03-31 | Aeroquip Corporation | Noise suppressor |
US20110120584A1 (en) * | 2009-11-26 | 2011-05-26 | Hyundai Motor Company | Low-noise plastic intercooler pipe having multi-layered structure |
CN102226491A (en) * | 2011-06-08 | 2011-10-26 | 浙江大学 | Fluid pulsation eliminating and noise reducing device for liquid transportation pipeline |
CN202149020U (en) * | 2011-07-18 | 2012-02-22 | 潍坊大明生物科技有限公司 | Noise reduction damping device for high pressure measuring pump |
-
2013
- 2013-01-10 CN CN201310009357.1A patent/CN103062569B/en active Active
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2952600A1 (en) * | 1979-12-28 | 1981-07-02 | Juval Dr.-Ing. 8000 München Mantel | Pipe noise damping equipment - comprises resilient outer or inner pipe section with breathing action |
SU1196601A2 (en) * | 1984-06-07 | 1985-12-07 | Харьковский авиационный институт им.Н.Е.Жуковского | Noise silencer |
CN2089112U (en) * | 1991-02-07 | 1991-11-20 | 宋振华 | Noise and wave absorbers for hydraulic system |
US5732741A (en) * | 1996-09-25 | 1998-03-31 | Aeroquip Corporation | Noise suppressor |
US20110120584A1 (en) * | 2009-11-26 | 2011-05-26 | Hyundai Motor Company | Low-noise plastic intercooler pipe having multi-layered structure |
CN102226491A (en) * | 2011-06-08 | 2011-10-26 | 浙江大学 | Fluid pulsation eliminating and noise reducing device for liquid transportation pipeline |
CN202149020U (en) * | 2011-07-18 | 2012-02-22 | 潍坊大明生物科技有限公司 | Noise reduction damping device for high pressure measuring pump |
Cited By (43)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103307198A (en) * | 2013-06-28 | 2013-09-18 | 江苏大学 | Pump pool inherent frequency self-adapting method and device |
CN103307198B (en) * | 2013-06-28 | 2015-04-29 | 江苏大学 | Pump pool inherent frequency self-adapting device |
CN104089139A (en) * | 2014-07-02 | 2014-10-08 | 上海市计量测试技术研究院 | Water pipe silencer |
CN106197578A (en) * | 2014-09-23 | 2016-12-07 | 微动公司 | magnetic flowmeter flow tube assembly |
CN104632792A (en) * | 2014-12-12 | 2015-05-20 | 燕山大学 | Pipe type variable-damping filter provided with multiple holes with different parameters and applied to opening of hydraulic pump |
CN105889232A (en) * | 2016-05-12 | 2016-08-24 | 浙江工业职业技术学院 | Filtering device using wave restraint, electrifying, separating, absorbing and centrifuging |
CN105971997A (en) * | 2016-05-12 | 2016-09-28 | 浙江工业职业技术学院 | Filtering method adopting working condition self-adaptive filtering, electrification, centrifugation and rotating magnetic field |
CN105757061A (en) * | 2016-05-12 | 2016-07-13 | 谢阿招 | Filter device adopting wave suppression, magnetization, adsorption and centrifugation |
CN105782170A (en) * | 2016-05-12 | 2016-07-20 | 谢阿招 | Full-band variable-structure working condition-adaptive filtering, magnetizing and centrifuging oil filter |
CN105782169A (en) * | 2016-05-12 | 2016-07-20 | 陈连萍 | Filtering method adopting wave suppression, magnetization, adsorption and centrifugation |
CN105840594A (en) * | 2016-05-12 | 2016-08-10 | 李�昊 | Oil filtering method for full-band variable structure working condition self-adaptive filtering, electrifying and adsorbing |
CN105840593A (en) * | 2016-05-12 | 2016-08-10 | 徐燚超 | Filter method for filtering, magnetization, magnetic field rotation and centrifugation by full-band variable structure |
CN105840590A (en) * | 2016-05-12 | 2016-08-10 | 谢阿招 | Filter tank for filtering, magnetizing, adsorbing and centrifuging through full-band variable structure |
CN105840591A (en) * | 2016-05-12 | 2016-08-10 | 沈兴华 | Filtering device adopting wave suppression, magnetization, adsorption, rotating magnetic field and centrifugation |
CN105864221A (en) * | 2016-05-12 | 2016-08-17 | 李�昊 | Filtering method adopting filter, electrification, separation, adsorption and rotating magnetic field |
CN105864119A (en) * | 2016-05-12 | 2016-08-17 | 张华芳 | Method for treating hydraulic oil through magnetization, cyclone centrifugation and adsorption |
CN105864184A (en) * | 2016-05-12 | 2016-08-17 | 李�昊 | Method for filtering by adoption of full-band variable structure working condition self-adaptive wave filtering, electrification and adsorption |
CN105864196A (en) * | 2016-05-12 | 2016-08-17 | 陈连萍 | Filtering method using wave filter, magnetization, adsorption, rotating magnetic field and centrifugation |
CN105864200A (en) * | 2016-05-12 | 2016-08-17 | 谢阿招 | Filter tank adopting work-condition-adaptive filtering, magnetization, rotary magnetic field and centrifugation |
CN105889210A (en) * | 2016-05-12 | 2016-08-24 | 浙江工业职业技术学院 | Oil filtering method based on full-band variable-structure working condition self-adaptive filtration, electrification and centrifugation |
CN105736521A (en) * | 2016-05-12 | 2016-07-06 | 徐燚超 | Oil filtering method adopting filter for magnetizing, adsorbing and centrifuging |
CN105889213A (en) * | 2016-05-12 | 2016-08-24 | 浙江工业职业技术学院 | Filtering method based on full-band variable-structure filtration, electrification, separation and centrifugation |
CN105909619A (en) * | 2016-05-12 | 2016-08-31 | 李�昊 | Oil filtering method adopting variable-structure filtering, electrification, separation, adsorption and rotating magnetic field |
CN105909615A (en) * | 2016-05-12 | 2016-08-31 | 张国云 | Filtering method adopting magnetization, adsorption and rotating magnetic field for hydraulic system |
CN105736524A (en) * | 2016-05-12 | 2016-07-06 | 徐燚超 | Oil filtering method adopting full-frequency-band working condition self-adaptive filtering, magnetization, rotary magnetic field and centrifuging |
CN105971998A (en) * | 2016-05-12 | 2016-09-28 | 浙江工业职业技术学院 | Oil filtering method adopting full-band working condition self-adaptive filtering, electrification and centrifugation |
CN105971996A (en) * | 2016-05-12 | 2016-09-28 | 张华芳 | Method adopting magnetization, centrifuging and electric shock hammer adsorption for treating hydraulic oil |
CN105971992A (en) * | 2016-05-12 | 2016-09-28 | 浙江工业职业技术学院 | Oil filtering method using variable-structure filtering, electrification, separation, centrifuging and rotating magnetic field |
CN105736522A (en) * | 2016-05-12 | 2016-07-06 | 沈兴华 | Whole-frequency-band work condition self-adaptive filtering, magnetizing, magnetic field and centrifugation oil filter |
CN106402093A (en) * | 2016-05-12 | 2017-02-15 | 谢阿招 | Oil filtering device achieving full-band-working-condition self-adapted filtering, magnetization, adsorption and centrifugation |
CN107244397A (en) * | 2017-05-12 | 2017-10-13 | 哈尔滨工程大学 | A kind of heat dissipation type acoustic hood of gravity flow under water with noise elimination structure |
CN107244397B (en) * | 2017-05-12 | 2019-01-15 | 哈尔滨工程大学 | A kind of underwater gravity flow heat dissipation type acoustic hood with noise elimination structure |
CN107420680A (en) * | 2017-08-23 | 2017-12-01 | 武汉理工大学 | A kind of artificial cochlea's silencer for air pipeline Noise measarement |
CN112628516A (en) * | 2019-10-09 | 2021-04-09 | 东台市东方船舶装配有限公司 | Frequency adjustable water pipeline silencer |
CN112648463A (en) * | 2019-10-09 | 2021-04-13 | 东台市东方船舶装配有限公司 | Frequency-adjustable resonance type water pipeline silencer |
CN113251233A (en) * | 2021-04-28 | 2021-08-13 | 北京理工大学 | Liquid pipeline sound attenuation system based on underwater wide and low frequency sound insulation metal-based metamaterial design |
CN114110291A (en) * | 2021-11-24 | 2022-03-01 | 江苏科技大学 | Elastic plate type straight-through perforated pipe water muffler with static pressure balance cavity and assembling method |
CN114110291B (en) * | 2021-11-24 | 2023-09-19 | 江苏科技大学 | Elastic plate type straight-through perforated pipe water muffler with static pressure balance cavity and assembly method |
CN114215669A (en) * | 2021-12-24 | 2022-03-22 | 安徽江淮汽车集团股份有限公司 | Method for eliminating air inlet broadband noise and expansion cavity structure |
CN114321552A (en) * | 2022-01-04 | 2022-04-12 | 中国海洋大学 | Magnetorheological energy accumulator for water hammer protection and installation method and control system thereof |
CN114321552B (en) * | 2022-01-04 | 2023-02-10 | 中国海洋大学 | Magnetorheological energy accumulator for water hammer protection and installation method and control system thereof |
CN114704703A (en) * | 2022-03-15 | 2022-07-05 | 中国船舶重工集团公司第七一一研究所 | Water pipeline silencing device, silencing method and ship |
CN114704703B (en) * | 2022-03-15 | 2023-10-13 | 中国船舶集团有限公司第七一一研究所 | Water pipeline silencing device, silencing method and ship |
Also Published As
Publication number | Publication date |
---|---|
CN103062569B (en) | 2015-09-30 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
CN103062569B (en) | A kind of Pressure-auto-balanchydrodynamic hydrodynamic noise silencer | |
EP0196812B1 (en) | Hydraulic noise attenuators | |
CN103115214B (en) | Wave absorbing device used for eliminating and reducing noise and pulses of hydraulic system fluid | |
CN107023350A (en) | Silencer | |
CN110056737B (en) | Honeycomb rubber lining type pressure pulsation attenuator | |
CN104006260B (en) | Water lines current stabilization Broad Band Muffler | |
EP3098413B1 (en) | An acoustic attenuator for damping pressure vibrations in an exhaust system of an engine | |
US4172508A (en) | Exhaust silencers | |
US20100329899A1 (en) | Multi-frequency pulsation absorber at cylinder valve cap | |
Chai et al. | A compact design of pulsation attenuator for hydraulic pumps | |
CN203441570U (en) | Impedance composite muffler | |
CN104632792A (en) | Pipe type variable-damping filter provided with multiple holes with different parameters and applied to opening of hydraulic pump | |
CN106090523A (en) | A kind of pipeline pressure pulsation attenuator based on mass-spring system | |
CN203856544U (en) | Helmholtz resonance muffling unit | |
CN103353042A (en) | Pressure self-adaptation low-frequency broadband elastic resonance noise-abatement device | |
CN105402004B (en) | High-power agricultural machinery muffler for diesel engine | |
CN211422806U (en) | Multi-band broadband silencer capable of being rapidly applied | |
CN210069241U (en) | Self-adaptive compound pressure pulsation attenuator | |
CN114110291B (en) | Elastic plate type straight-through perforated pipe water muffler with static pressure balance cavity and assembly method | |
JPH0756254B2 (en) | Hydraulic system | |
US8740590B2 (en) | Hyperbolic horn for pulsation filter device used with gas compressor | |
CN105864209A (en) | Method for restraining pressure pulsation of hydraulic system | |
CN103438323B (en) | L-type impact air flow attenuator | |
CN210004014U (en) | honeycomb rubber lining type pressure pulsation attenuator | |
CN101975326B (en) | Pipe type hydraulic fluid muffler |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
C06 | Publication | ||
PB01 | Publication | ||
C10 | Entry into substantive examination | ||
SE01 | Entry into force of request for substantive examination | ||
C14 | Grant of patent or utility model | ||
GR01 | Patent grant |