JPH11336555A - Reciprocating internal combustion engine - Google Patents
Reciprocating internal combustion engineInfo
- Publication number
- JPH11336555A JPH11336555A JP11701499A JP11701499A JPH11336555A JP H11336555 A JPH11336555 A JP H11336555A JP 11701499 A JP11701499 A JP 11701499A JP 11701499 A JP11701499 A JP 11701499A JP H11336555 A JPH11336555 A JP H11336555A
- Authority
- JP
- Japan
- Prior art keywords
- combustion engine
- internal combustion
- reciprocating internal
- exhaust
- silencer
- 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.)
- Pending
Links
- 238000002485 combustion reaction Methods 0.000 title claims description 25
- 239000002184 metal Substances 0.000 claims abstract description 26
- 230000003584 silencer Effects 0.000 claims description 39
- 238000000034 method Methods 0.000 claims description 4
- 238000005192 partition Methods 0.000 claims description 3
- 210000000056 organ Anatomy 0.000 claims 2
- 239000011148 porous material Substances 0.000 claims 1
- 238000013016 damping Methods 0.000 abstract description 8
- 230000000694 effects Effects 0.000 abstract description 6
- 238000010276 construction Methods 0.000 description 5
- 230000001419 dependent effect Effects 0.000 description 2
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 230000030279 gene silencing Effects 0.000 description 2
- 239000011810 insulating material Substances 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- XSQUKJJJFZCRTK-UHFFFAOYSA-N Urea Chemical compound NC(N)=O XSQUKJJJFZCRTK-UHFFFAOYSA-N 0.000 description 1
- 230000002238 attenuated effect Effects 0.000 description 1
- 239000004202 carbamide Substances 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000009413 insulation Methods 0.000 description 1
- 230000001902 propagating effect Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B33/00—Engines characterised by provision of pumps for charging or scavenging
- F02B33/44—Passages conducting the charge from the pump to the engine inlet, e.g. reservoirs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N1/00—Silencing apparatus characterised by method of silencing
- F01N1/003—Silencing apparatus characterised by method of silencing by using dead chambers communicating with gas flow passages
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
- F02M35/1205—Flow throttling or guiding
- F02M35/1216—Flow throttling or guiding by using a plurality of holes, slits, protrusions, perforations, ribs or the like; Surface structures; Turbulence generators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
- F02M35/1255—Intake silencers ; Sound modulation, transmission or amplification using resonance
- F02M35/1261—Helmholtz resonators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M35/00—Combustion-air cleaners, air intakes, intake silencers, or induction systems specially adapted for, or arranged on, internal-combustion engines
- F02M35/12—Intake silencers ; Sound modulation, transmission or amplification
- F02M35/1255—Intake silencers ; Sound modulation, transmission or amplification using resonance
- F02M35/1266—Intake silencers ; Sound modulation, transmission or amplification using resonance comprising multiple chambers or compartments
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B77/00—Component parts, details or accessories, not otherwise provided for
- F02B77/11—Thermal or acoustic insulation
- F02B77/13—Acoustic insulation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F7/00—Casings, e.g. crankcases or frames
- F02F2007/0097—Casings, e.g. crankcases or frames for large diesel engines
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
- Exhaust Silencers (AREA)
Abstract
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、過給空気出口が接
続管によって後置の過給空気冷却器に接続されている少
なくとも一つの排気駆動式過給機を備え、この排気駆動
式過給機に音の放出を減少するための手段が付設されて
いる往復動内燃機関、特に大形ディーゼルエンジンに関
する。BACKGROUND OF THE INVENTION The present invention comprises at least one exhaust-driven supercharger whose supercharged air outlet is connected by a connecting pipe to a downstream supercharged air cooler. The invention relates to a reciprocating internal combustion engine, in particular a large diesel engine, provided with means for reducing sound emissions in the machine.
【０００２】[0002]
【従来の技術】排気駆動式過給機で生ずる音の放出を特
に危険な構成要素の防音処置によって減少することが従
来試みられている。その配管ないしケーシングの防音処
置はこれが配管の全長ないしはケーシングの全表面にわ
たって施されるときだけしか有用な結果が得られないと
いうことに注意しなければならない。しかしこれはしば
しば構造的な理由からほとんど実施できない。即ちその
防音装置は板金で包囲された比較的厚い絶縁材料から成
っている。これは非常に大きな構造空間を必要とし、そ
のような空間はしばしば存在しない。更に危険な配管な
どは一般に接近し難いので、その防音処置の施工には非
常に経費がかかる。もう一つの特別な欠点は、排気駆動
式過給機の範囲で生ずる高い温度において絶縁材料が容
易に分解し、所定の時間経過後に防音作用が減少すると
いうことにある。2. Description of the Prior Art It has been attempted in the past to reduce the sound emissions produced by exhaust-driven superchargers by soundproofing particularly dangerous components. It should be noted that the soundproofing of the pipe or casing only yields useful results when it is applied over the entire length of the pipe or the entire surface of the casing. However, this is often hardly feasible for structural reasons. That is, the soundproofing device is made of a relatively thick insulating material surrounded by sheet metal. This requires a very large amount of structural space, and such space often does not exist. In addition, dangerous pipes and the like are generally inaccessible, so the construction of the soundproofing process is very expensive. Another particular disadvantage is that at high temperatures occurring in the region of exhaust-driven superchargers, the insulating material easily decomposes and after a certain time the sound insulation is reduced.
【０００３】ヨーロッパ特許出願公開第０７７９４１５
号明細書において、ディーゼルエンジンの排気管に組み
込まれ排気に尿素を供給する装置が前置されている反応
室に対する消音器が知られている。この公知の消音器は
大きな窓状開口を介して流路に接続されている共振室を
有し、その長さは発生する音波の波長に合わされ、奥行
きは流路の直径の約半分に相当している。この場合も非
常にかさばった構造となる。この公知の消音器は従っ
て、排気管内と全く異なった波長の音を生ずる排気駆動
式過給機の範囲には利用できない。更に僅かな摩擦損失
従って悪い減衰作用しか生じない。[0003] EP-A-0 779 415
In the specification, a silencer is known for a reaction chamber which is integrated in the exhaust pipe of a diesel engine and is upstream of a device for supplying urea to the exhaust gas. This known silencer has a resonance chamber connected to the channel via a large window-like opening, the length of which is adapted to the wavelength of the sound waves to be generated, the depth corresponding to approximately half the diameter of the channel. ing. Also in this case, the structure becomes very bulky. This known silencer cannot therefore be used in a range of exhaust driven turbochargers which produce sounds of a completely different wavelength than in the exhaust pipe. Furthermore, only small friction losses and thus poor damping effects occur.
【０００４】[0004]
【発明が解決しようとする課題】本発明の課題は、冒頭
に述べた形式の消音処置を、単純でコンパクトな構造で
実施されるだけでなく、大きな減衰作用並びに長い寿命
が得られるように改良することにある。SUMMARY OF THE INVENTION The object of the invention is to improve a silencing device of the type mentioned at the outset in such a way that not only can it be implemented in a simple and compact construction, but also that a large damping effect and a long service life are obtained. Is to do.
【０００５】[0005]
【課題を解決するための手段】この課題は本発明に基づ
いて、排気駆動式過給機の範囲における少なくとも一つ
の流れ案内構成要素が、孔開き板金によってその流路か
ら分離されている少なくとも一つの室を含んでいるホル
ムヘルツ共振器の原理に基づく少なくとも一つの消音器
を備えていることによって解決される。SUMMARY OF THE INVENTION According to the present invention, there is provided, in accordance with the present invention, at least one flow guiding component in the area of an exhaust driven turbocharger, wherein at least one flow guiding component is separated from its flow path by a perforated sheet metal. The problem is solved by providing at least one silencer based on the principle of a Holmhertz resonator containing two chambers.
【０００６】本発明に基づいて採用されるホルムヘルツ
共振器の原理で作動する消音器は、コンパクトな構造に
もかかわらず多くの音エネルギを有利に消滅できる。つ
まり孔開き板金の各孔の部位に実質的にばね・質量・振
動系が生じ、このばね・質量・振動系において孔内に存
在する流体質量が音波で励振されて振動し、その際、室
内に存在する流体容積がばねとして作用する。孔開き壁
において生ずる強い摩擦に基づいて大きな減衰が生ず
る。これと同時に、防音する場合と異なって本発明に基
づく消音器を使用する場合、配管の一部だけに本発明に
基づく消音器を備えるだけで比較的良好な作用が得られ
ることが保証される。本発明に基づく消音器は径方向に
即ち、孔開き板金に対して垂直方向に比較的僅かな構造
空間しか必要としないので、本発明に基づく消音器は有
利に周辺の配管ないしケーシングなどの範囲に限らずに
配置できる。むしろ排気駆動式過給機に直接組み込むこ
ともできる。更に本発明に基づく消音器は比較的大きな
周波数帯域が減衰されるように設計できる。A silencer operating according to the principle of a Holmhertz resonator employed according to the invention can advantageously extinguish a large amount of sound energy despite its compact construction. In other words, a spring, mass, and vibration system is generated substantially at each hole of the perforated sheet metal, and in this spring, mass, and vibration system, the fluid mass present in the hole is excited by a sound wave and vibrates. Act as a spring. Large damping occurs due to the strong friction occurring at the perforated wall. At the same time, if the silencer according to the invention is used differently from the case of soundproofing, it is assured that a relatively good operation can be obtained simply by providing the silencer according to the invention in only a part of the piping. . Since the silencer according to the invention requires relatively little structural space in the radial direction, i.e., perpendicular to the perforated sheet metal, the silencer according to the invention is advantageously used in areas such as peripheral pipes or casings. It can be arranged without being limited to. Rather, it can be incorporated directly into the exhaust-driven supercharger. Furthermore, the silencer according to the invention can be designed so that a relatively large frequency band is attenuated.
【０００７】本発明の有利な実施態様および目的に適っ
た発展例は従属請求項に記載されている。[0007] Advantageous embodiments of the invention and advantageous developments are described in the dependent claims.
【０００８】即ち排気駆動式過給機から出ている特に少
なくとも一つの管状構成要素が消音器を備えていると有
利である。本発明に基づく処置はその管状構成要素の範
囲において特に安価な費用で使用することができる。It is advantageous if at least one tubular component coming from the exhaust-driven supercharger is provided with a silencer. The procedure according to the invention can be used at a particularly low cost in the area of its tubular components.
【０００９】本発明に基づく消音器の特に有利な設置場
所は排気駆動式過給機の過給空気出口に続く接続管であ
る。この処置は、排気駆動式過給機の圧縮機内で生ずる
騒音が流れ方向に伝播することを特に簡単に防止する。A particularly advantageous installation location of the silencer according to the invention is a connection pipe following the supercharging air outlet of the exhaust-driven supercharger. This measure particularly simply prevents the noise generated in the compressor of the exhaust-driven supercharger from propagating in the flow direction.
【００１０】他の有利な処置は孔開き板金のすべての孔
が共通の室に開口していることにある。これは特に単純
で安価な実施態様を生ずる。Another advantageous measure consists in that all the holes of the perforated sheet metal are open to a common chamber. This results in a particularly simple and inexpensive implementation.
【００１１】その代わりに孔開き板金で画成された空間
を隔壁によって多数の小室に分割することが考えられ
る。この場合個々の室の範囲における減衰作用を種々の
周波数について有利に最適化することができ、これによ
って特に幅広い周波数帯域内において良好な減衰作用が
得られる。Instead, it is conceivable to divide the space defined by the perforated sheet metal into a number of small chambers by partition walls. In this case, the damping effect in the area of the individual chambers can be advantageously optimized for different frequencies, so that a good damping effect is obtained, especially in a wide frequency band.
【００１２】本発明の有利な実施態様および発展例は他
の従属請求項に記載されている。[0012] Advantageous embodiments and developments of the invention are described in the further dependent claims.
【００１３】[0013]
【発明の実施の形態】以下図に示した実施形態を参照し
て本発明を詳細に説明する。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention will be described below in detail with reference to the embodiments shown in the drawings.
【００１４】図１の基礎となっている大形ディーゼルエ
ンジン１は列を成して配置された複数のシリンダ２を有
し、これらのシリンダ２の排気口３は全シリンダ２にわ
たって延びてる排気マニホールド４に接続されている。
排気マニホールド４から排気管５が排気駆動式過給機６
に通じている。この過給機６は排気によって駆動される
タービン７およびこのタービン７で駆動されシリンダ２
に供給する過給空気を用意する圧縮機８を有している。
排気管５はタービン７の流入ノズル９に接続されてい
る。タービン７の流出ノズル１０は管路状の流出通路１
１に開口している。The large diesel engine 1 on which FIG. 1 is based has a plurality of cylinders 2 arranged in rows, the exhaust ports 3 of which cylinders 2 extend over the entire cylinder 2. 4 is connected.
The exhaust pipe 5 extends from the exhaust manifold 4 to the exhaust driven supercharger 6
Leads to. The supercharger 6 includes a turbine 7 driven by exhaust gas and a cylinder 2 driven by the turbine 7.
And a compressor 8 for preparing supercharged air to be supplied to the compressor.
The exhaust pipe 5 is connected to an inflow nozzle 9 of the turbine 7. The outflow nozzle 10 of the turbine 7 is a pipe-shaped outflow passage 1.
1 is open.
【００１５】排気駆動式過給機６の圧縮機８に過給空気
冷却器１２が後置され、この過給空気冷却器１２は圧縮
機８の吐出しノズル１３に接続管を介して接続されてい
る。この接続管は吐出しノズル１３に続いている管１４
およびこれに続き過給空気冷却器１２の中に開口してい
るディフューザ１５から成っている。A supercharged air cooler 12 is provided after the compressor 8 of the exhaust-driven supercharger 6, and the supercharged air cooler 12 is connected to a discharge nozzle 13 of the compressor 8 via a connection pipe. ing. This connecting pipe is connected to a pipe 14 following the discharge nozzle 13.
And subsequently a diffuser 15 which opens into the supercharged air cooler 12.
【００１６】排気駆動式過給機６内に、特にその圧縮機
８内に音波が生じ、この音波は流れ媒体の流れ方向に空
気内ないし排気内を伝播し、従って排気駆動式過給機６
に後置された構成要素を振動させ、従って音を放出させ
る。これを防止するために、排気駆動式過給機６の範囲
に少なくとも一つの消音器が設けられ、これは防音と異
なって音をしゃ断するだけでなく吸収もする。この消音
器は排気駆動式過給機６の中に組み込まれるか、あるい
は周辺の流れ案内構造部品に付設される。音が流れ方向
に伝播するので、まず排気駆動式過給機６から出る配管
が問題となる。この配管は消音器の組立を容易にする管
状の構成要素である。In the exhaust-driven supercharger 6, in particular in its compressor 8, sound waves are generated which propagate in the air or in the exhaust in the direction of flow of the flowing medium, and are therefore supercharged.
Vibrates the components that follow it, thus emitting sound. In order to prevent this, at least one silencer is provided in the area of the exhaust-driven supercharger 6, which, unlike soundproofing, not only cuts off sound but also absorbs it. This silencer is integrated into the exhaust driven supercharger 6 or is attached to a surrounding flow guiding structure. Since the sound propagates in the flow direction, firstly, a pipe coming out of the exhaust driven supercharger 6 becomes a problem. The tubing is a tubular component that facilitates assembly of the silencer.
【００１７】上述の消音器はコンパクトな構造容積、長
い寿命および良好な減衰作用を得るためにそれ自体公知
のホルムヘルツ共振器の原理に基づいて構成されてい
る。ホルムヘルツ共振器の原理は図２に示されている。
壁１８にある孔１７を介して流れ媒体に接続されている
室１６が設けられている。孔１７内に存在し孔１７に隣
接する流れ媒体容積２０が衝突する音波１９によって振
動させられ、この振動は孔１７の範囲で生ずる摩擦によ
って減衰される。室１６内に存在する流体容積はその場
合ばねとして作用する。従って全体が摩擦減衰形ばね・
質量・振動系となる。この振動系は振動する質量および
ばねに関係して共振し、その場合最大の振動振幅が生
じ、これは更に最大摩擦を引き起こし、これによって多
くの音エネルギが消耗させられる。The silencer described above is designed on the basis of the known form-Holtz resonator principle in order to obtain a compact construction volume, a long service life and good damping action. The principle of a Holmhertz resonator is shown in FIG.
A chamber 16 is provided which is connected to the flow medium via a hole 17 in a wall 18. The flow medium volume 20 present in the hole 17 and adjacent to the hole 17 is vibrated by the impinging sound waves 19 and this vibration is damped by the friction occurring in the region of the hole 17. The fluid volume present in the chamber 16 then acts as a spring. Therefore, the whole is a friction damping spring
It becomes a mass and vibration system. The vibrating system resonates in relation to the vibrating mass and the spring, which results in a maximum vibration amplitude, which also causes a maximum friction, which consumes a great deal of sound energy.
【００１８】排気駆動式過給機６の圧縮機８が主騒音発
生源であり、そこで発生する騒音が流れ方向に伝播する
ので、圧縮機８の吐出しノズル１３に続く過給空気冷却
器１２への接続管の部位に本発明に基づく形式の消音器
が設けられているとき、良好な結果が得られる。この消
音器は管１４に付設される。それに加えてあるいはそれ
に代えてディフューザ１５もそのような消音器を備えて
いる。その場合、消音器の作用はその長さが長くなれば
なるほど大きくなるということに注意しなければならな
い。消音器が上述したように圧縮機の近くに置かれるこ
とによって、後置された構成要素への音波の供給が防止
されるか十分に減少させられるので、その場所特有の消
音処置を省くことができる。これは特にディーゼルエン
ジン１の吸気装置に対して当てはまる。The compressor 8 of the exhaust-driven supercharger 6 is a main noise source, and the noise generated there propagates in the flow direction, so that the supercharged air cooler 12 following the discharge nozzle 13 of the compressor 8 Good results are obtained when a silencer of the type according to the invention is provided at the site of the connecting pipe to the tub. This silencer is attached to the pipe 14. Additionally or alternatively, the diffuser 15 also includes such a silencer. It must be noted that the effect of the silencer in that case increases as its length increases. By placing the silencer close to the compressor as described above, the supply of sound waves to downstream components can be prevented or substantially reduced, thus eliminating the need for site-specific silencing measures. it can. This applies in particular to the intake system of the diesel engine 1.
【００１９】図３および図４は本発明に基づく消音器２
１を備えた管１４の一部を示している。消音器２１は流
路２２を画成し孔開き板金２３として形成された壁を有
している。これは径方向に間隔を隔てて配置された外被
管２４で包囲されている。孔開き板金２３と外被管２４
との間に孔開き板金２３の孔２６を介して流路２２内の
流れ媒体に連通する室２５が形成されている。図３の実
施形態では消音器の全長にわたって通しの室２５が設け
られている。図４の実施形態では孔開き板金２３と外被
管２４との間の空間は隔壁２７によって多数の小室２５
ａに分割され、これらの小室２５ａにはそれぞれ孔開き
板金２３の幾つかの孔２６しか付属されていない。FIGS. 3 and 4 show a muffler 2 according to the present invention.
1 shows a part of a tube 14 with 1; The silencer 21 has a wall defining a flow path 22 and formed as a perforated sheet metal 23. It is surrounded by a radially spaced jacket tube 24. Perforated sheet metal 23 and jacket tube 24
A chamber 25 communicating with the flow medium in the flow path 22 through the hole 26 of the perforated sheet metal 23 is formed between the hole 25 and the hole. In the embodiment of FIG. 3, a through chamber 25 is provided over the entire length of the silencer. In the embodiment of FIG. 4, the space between the perforated sheet metal 23 and the jacket tube 24 is divided into a large number of small chambers 25 by partition walls 27.
The small chambers 25a are provided with only a few holes 26 of the perforated sheet metal 23, respectively.
【００２０】各孔２６の範囲において上述のホルムヘル
ツ共振器の作用が生ずる。孔２６の直径とその孔ピッ
チ、孔開き板金２３の厚さ従って孔長および室２５ない
し小室２５ａの奥行きは個々の事情に合わせて選定され
ねばならず、即ち予測される音波の波長に合わせねばな
らない。図示した実施形態において孔開き板金２３の孔
面積はその全面積の０．９％である。それが約０．５〜
１．５％の範囲にあるとき孔２６により顕著な強度低下
は生じない。孔ピッチ、即ち孔間隔ｔは図示の実施形態
においては約９ｍｍである。孔直径は１ｍｍである。同
様に孔開き板金２３の厚さ、従って孔長は１ｍｍであ
る。室の奥行きｋはここでは約１５ｍｍである。ここか
ら明らかなように本発明に基づく処置は特にコンパクト
な構造にできる。In the area of each hole 26, the operation of the above-described Holmhertz resonator occurs. The diameter of the hole 26 and its pitch, the thickness of the perforated sheet metal 23 and therefore the length of the hole and the depth of the chamber 25 or the small chamber 25a must be selected according to the individual circumstances, that is, to the expected wavelength of the sound wave. No. In the illustrated embodiment, the hole area of the perforated sheet metal 23 is 0.9% of the total area. About 0.5 ~
When in the range of 1.5%, no significant reduction in strength occurs due to the holes 26. The hole pitch, or hole spacing t, is about 9 mm in the illustrated embodiment. The hole diameter is 1 mm. Similarly, the thickness of the perforated sheet metal 23, and thus the length of the hole, is 1 mm. The depth k of the room is here about 15 mm. As can be seen, the treatment according to the invention can have a particularly compact construction.
【００２１】すべての孔２６が開口している通しの室２
５を備えた図３の実施形態は特に単純に実施できる。そ
れぞれ一つあるいは幾つかの孔２６しか付属されていな
い多数の小室２５ａを備えた図４の実施例の場合、種々
の室２５の範囲における減衰状態を種々の波長に合わせ
ることができるので、全体として大きな減衰帯域幅が得
られる。Through chamber 2 in which all holes 26 are open
The embodiment of FIG. 3 with 5 is particularly simple to implement. In the case of the embodiment of FIG. 4 having a number of small chambers 25a, each of which has only one or several holes 26, the attenuation in the region of the different chambers 25 can be adapted to different wavelengths, so that As a result, a large attenuation bandwidth can be obtained.
【００２２】管１４に付設された上述の消音器２１の代
わりにあるいはこれに加えて、排気駆動式過給機６の内
部あるいはその周辺における別の流れ案内構成要素に本
発明に基づく方式の消音器を付設することも勿論でき
る。図５においてそのような消音器２１は太い実線で示
されている。即ち圧縮機８の吐出しノズル１３及び／又
は圧縮機ケーシング２８及び／又は吸込みノズル２９及
び／又は圧縮機８の吸込み配管３０にもそれぞれ消音器
２１を付設できる。タービン側でも本発明に基づく消音
器の利用は有効に作用する。即ち例えば流出ノズル１０
に続く流出通路１１及び／又は流出ノズル１０及び／又
は流入ノズル９及び／又は流入ノズル９に続く排気管５
及び／又は排気駆動式過給機６のタービン７のタービン
車室３１に消音器２１が設けられる。上述の処置は既に
述べたように個々にあるいは累積して施される。Instead of or in addition to the above-described silencer 21 attached to the pipe 14, other flow guiding components inside or around the exhaust-driven supercharger 6 can be used to silence the system according to the invention. Of course, a vessel can be attached. In FIG. 5, such a silencer 21 is indicated by a thick solid line. That is, the muffler 21 can be attached to the discharge nozzle 13 of the compressor 8 and / or the compressor casing 28 and / or the suction nozzle 29 and / or the suction pipe 30 of the compressor 8 respectively. The use of the silencer according to the invention also works effectively on the turbine side. That is, for example, the outflow nozzle 10
The outlet pipe 11 following the outlet passage 11 and / or the outlet nozzle 10 and / or the inlet nozzle 9 and / or the inlet nozzle 9
A muffler 21 is provided in the turbine casing 31 of the turbine 7 of the exhaust-driven supercharger 6. The measures described above can be applied individually or cumulatively, as already mentioned.
【図１】排気駆動式過給機を備えた大形ディーゼルエン
ジンの側面図。FIG. 1 is a side view of a large diesel engine having an exhaust-driven supercharger.
【図２】ホルムヘルツ共振器の作用原理を示した概略
図。FIG. 2 is a schematic diagram showing the operation principle of a Holm Hertz resonator.
【図３】排気駆動式過給機の過給空気出口に続く本発明
に基づく消音器を備えた管の断面図。FIG. 3 is a cross-sectional view of a tube provided with a silencer according to the present invention following a supercharged air outlet of an exhaust-driven supercharger.
【図４】異なった実施形態の図３に相当した断面図。FIG. 4 is a sectional view corresponding to FIG. 3 of a different embodiment.
【図５】多数の内部および周辺の消音器を備えた排気駆
動式過給機の断面図。FIG. 5 is a cross-sectional view of an exhaust-driven supercharger provided with a number of internal and peripheral silencers.
６ 排気駆動式過給機 ７ タービン ９ 流入ノズル １０ 流出ノズル １４ 管 ２１ 消音器 ２２ 流路 ２３ 孔開き板金 ２５ 室 ２９ 吸込みノズル ３０ 吸込み管 ３１ タービン車室 Reference Signs List 6 Exhaust drive type supercharger 7 Turbine 9 Inflow nozzle 10 Outflow nozzle 14 Pipe 21 Silencer 22 Flow path 23 Perforated sheet metal 25 Chamber 29 Suction nozzle 30 Suction pipe 31 Turbine casing
───────────────────────────────────────────────────── フロントページの続き (51)Int.Cl.6 識別記号 ＦＩ Ｆ０２Ｍ 35/12 Ｆ０２Ｍ 35/12 Ｍ ──────────────────────────────────────────────────続 き Continued on the front page (51) Int.Cl. 6 Identification code FI F02M 35/12 F02M 35/12 M
Claims (22)
後置の過給空気冷却器（１２）に接続されている少なく
とも一つの排気駆動式過給機（６）を備え、この排気駆
動式過給機（６）に音の放出を減少させるための手段が
付設されている往復動内燃機関において、排気駆動式過
給機（６）の範囲における少なくとも一つの流れ案内構
成要素が、孔開き板金（２３）によってその流路（２
２）から分離されている少なくとも一つの室（２５）を
含んでいるホルムヘルツ共振器の原理に基づく少なくと
も一つの消音器（２１）を備えていることを特徴とする
往復動内燃機関。1. A supercharged air outlet (13) comprising at least one exhaust-driven supercharger (6) connected to a downstream supercharged air cooler (12) by a connecting pipe. In a reciprocating internal combustion engine in which the supercharger (6) is provided with means for reducing the emission of sound, at least one flow-guiding component in the area of the exhaust-driven supercharger (6) is provided with a bore. The channel (2) is opened by the open sheet metal (23).
A reciprocating internal combustion engine, characterized in that it comprises at least one silencer (21) based on the principle of a Holmhertz resonator including at least one chamber (25) separated from 2).
れた少なくとも一つの流れ案内構成要素が消音器（２
１）を備えていることを特徴とする請求項１記載の往復
動内燃機関。2. An exhaust-driven supercharger (6) having at least one flow-guiding component attached to the periphery of the silencer (2).
2. The reciprocating internal combustion engine according to claim 1, further comprising (1).
に管状の少なくとも一つの流れ案内構成要素が消音器
（２１）を備えていることを特徴とする請求項２記載の
往復動内燃機関。3. The reciprocating motion according to claim 2, wherein the at least one flow guiding component coming from the exhaust-driven supercharger (6) is provided with a silencer (21). Internal combustion engine.
つの内部流れ構成要素が消音器（２１）を備えているこ
とを特徴とする請求項１ないし３のいずれか１つに記載
の往復動内燃機関。4. The exhaust-driven supercharger (6) according to claim 1, wherein at least one internal flow component comprises a silencer (21). Reciprocating internal combustion engine.
（３）に続く管（１４）が消音器（２１）を備えている
ことを特徴とする請求項１ないし４のいずれか１つに記
載の往復動内燃機関。5. A muffler according to claim 1, wherein the pipe following the supercharged air outlet of the exhaust-driven supercharger is provided with a muffler. A reciprocating internal combustion engine according to any one of the preceding claims.
フューザ（１５）が消音器（２１）を備えていることを
特徴とする請求項１ないし５のいずれか１つに記載の往
復動内燃機関。6. The reciprocating motion according to claim 1, wherein the diffuser (15) opening into the supercharged air cooler (12) comprises a silencer (21). Internal combustion engine.
の、過給空気出口（３）を形成する吐出しノズルが消音
器（２１）を備えていることを特徴とする請求項１ない
し６のいずれか１つに記載の往復動内燃機関。7. A compressor (8) of an exhaust-driven supercharger (6).
7. A reciprocating internal combustion engine according to claim 1, wherein the discharge nozzle forming the supercharged air outlet (3) comprises a muffler (21).
８）が消音器（２１）を備えていることを特徴とする請
求項１ないし７のいずれか１つに記載の往復動内燃機
関。8. A compressor casing (2) of a compressor (8).
8. A reciprocating internal combustion engine according to claim 1, wherein 8) comprises a silencer (21).
消音器（２１）を備えていることを特徴とする請求項１
ないし８のいずれか１つに記載の往復動内燃機関。9. The compressor according to claim 1, wherein the suction nozzle of the compressor is provided with a muffler.
9. The reciprocating internal combustion engine according to any one of claims 8 to 8.
込み管（３０）が消音器（２１）を備えていることを特
徴とする請求項１ないし９のいずれか１つに記載の往復
動内燃機関。10. The reciprocating internal combustion engine according to claim 1, wherein the suction pipe (30) connected to the suction nozzle (29) comprises a silencer (21). organ.
流入ノズル（９）が消音器（２１）を備えていることを
特徴とする請求項１ないし１０のいずれか１つに記載の
往復動内燃機関。11. The exhaust-driven turbocharger according to claim 1, wherein the inlet nozzle (9) of the turbine (7) comprises a silencer (21). Reciprocating internal combustion engine.
（５）が消音器（２１）を備えていることを特徴とする
請求項１ないし１１のいずれか１つに記載の往復動内燃
機関。12. The reciprocating internal combustion engine according to claim 1, wherein the exhaust pipe (5) connected to the inlet nozzle (9) is provided with a silencer (21). organ.
１）の流出ノズル（１０）が消音器（２１）を備えてい
ることを特徴とする請求項１ないし１２のいずれか１つ
に記載の往復動内燃機関。13. A turbine casing (3) of a turbine (7).
Reciprocating internal combustion engine according to any of the preceding claims, characterized in that the outflow nozzle (1) of 1) comprises a silencer (21).
１）が消音器（２１）を備えていることを特徴とする請
求項１ないし１３のいずれか１つに記載の往復動内燃機
関。14. An exhaust passage (1) following an exhaust pipe (10).
14. A reciprocating internal combustion engine according to claim 1, wherein 1) comprises a silencer (21).
１）を備えていることを特徴とする請求項１ないし１４
のいずれか１つに記載の往復動内燃機関。15. A muffler (2) comprising a turbine casing (31).
15. The method according to claim 1, further comprising:
A reciprocating internal combustion engine according to any one of the preceding claims.
〜１．５％、好適には０．９％の孔面積を有しているこ
とを特徴とする請求項１ないし１５のいずれか１つに記
載の往復動内燃機関。16. A perforated sheet metal (23) having a total area of 0.5
16. A reciprocating internal combustion engine according to any one of the preceding claims, having a pore area of ~ 1.5%, preferably 0.9%.
有していることを特徴とする請求項１ないし１６のいず
れか１つに記載の往復動内燃機関。17. The reciprocating internal combustion engine according to claim 1, wherein the perforated sheet metal (23) has a thickness of 1 mm.
径が１ｍｍであることを特徴とする請求項１ないし１７
のいずれか１つに記載の往復動内燃機関。18. The perforated sheet metal (23) according to claim 1, wherein the diameter of the hole (26) is 1 mm.
A reciprocating internal combustion engine according to any one of the preceding claims.
ｍであることを特徴とする請求項１ないし１８のいずれ
か１つに記載の往復動内燃機関。19. The hole pitch of the perforated sheet metal (23) is 9 m.
The reciprocating internal combustion engine according to any one of claims 1 to 18, wherein m is m.
方向奥行きが１５ｍｍであることを特徴とする請求項１
ないし１９のいずれか１つに記載の往復動内燃機関。20. The chamber (25) to the small chamber (25a) having a radial depth of 15 mm.
20. The reciprocating internal combustion engine according to any one of claims 19 to 19.
６）が共通の室（２５）に開口していることを特徴とす
る特徴とする請求項１ないし２０のいずれか１つに記載
の往復動内燃機関。21. All holes (2) of a perforated sheet metal (23).
21. Reciprocating internal combustion engine according to claim 1, wherein 6) opens into a common chamber (25).
た室が隔壁（２７）によって複数の小室（２５ａ）に分
割されていることを特徴とする請求項１ないし２１のい
ずれか１つに記載の往復動内燃機関。22. The method according to claim 1, wherein the chamber defined by the perforated sheet metal is divided into a plurality of small chambers by a partition wall. A reciprocating internal combustion engine as described.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19818873.0 | 1998-04-28 | ||
| DE1998118873 DE19818873C2 (en) | 1998-04-28 | 1998-04-28 | Reciprocating internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPH11336555A true JPH11336555A (en) | 1999-12-07 |
Family
ID=7865993
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP11701499A Pending JPH11336555A (en) | 1998-04-28 | 1999-04-23 | Reciprocating internal combustion engine |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JPH11336555A (en) |
| DE (1) | DE19818873C2 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003519329A (en) * | 2000-01-07 | 2003-06-17 | アーベーベー ターボ システムズ アクチエンゲゼルシャフト | Silencer for exhaust gas turbocharger compressor |
| JP2005069228A (en) * | 2003-08-26 | 2005-03-17 | Abb Turbo Systems Ag | Muffler |
| JP2006348939A (en) * | 2005-06-16 | 2006-12-28 | Man Diesel Sa | Exhaust-driven supercharger of internal combustion engine |
| US20110308502A1 (en) * | 2009-02-18 | 2011-12-22 | Mitsubishi Heavy Industries, Ltd. | Turbocharger |
| JP2013527382A (en) * | 2010-06-04 | 2013-06-27 | ボーグワーナー インコーポレーテッド | Exhaust gas turbocharger compressor |
Families Citing this family (23)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2364352A (en) * | 2000-07-03 | 2002-01-23 | Draftex Ind Ltd | Noise reduction in air conduits; making perforated conduits |
| GB0018620D0 (en) * | 2000-07-28 | 2000-09-13 | Draftex Ind Ltd | Noise attenuation arrangements for pressurised-gas conduits |
| FI114332B (en) | 2000-11-08 | 2004-09-30 | Waertsilae Finland Oy | Air supply arrangement for a supercharged piston engine and method for a supercharged piston engine |
| DE10102040A1 (en) * | 2001-01-18 | 2002-07-25 | Mahle Filtersysteme Gmbh | Silencer, for a motor exhaust or turbo charger air intake, has a hollow body at the component to be suppressed containing a number of parallel Helmholtz resonators |
| US7017706B2 (en) | 2001-12-21 | 2006-03-28 | Honeywell International, Inc. | Turbine noise absorber |
| DE10243884A1 (en) * | 2002-09-21 | 2004-04-01 | Mann + Hummel Gmbh | Resonatorschalldämpfer |
| DE102004040317A1 (en) * | 2004-08-20 | 2006-02-23 | Bayerische Motoren Werke Ag | Silencer device for exhaust-gas turbocharger, has resonator chamber with silencer unit e.g. Helmholtz resonator, that is placed in proximity to source of gas pulsations at guide vanes and wheel vanes, for absorbing and reflecting noises |
| DE102004055429B3 (en) * | 2004-11-17 | 2006-08-10 | Man B & W Diesel Ag | Sealing device for a particularly lubricated at standstill bearing a rotor shaft |
| DE102004057413A1 (en) * | 2004-11-26 | 2006-06-29 | Mahle Filtersysteme Gmbh | Muffler for internal combustion engine, has housing arranged at airborne sound conveying pipe during operation of internal combustion engine and including damper body with set of hollow bodies that are connected with each other |
| JP5043686B2 (en) | 2005-02-23 | 2012-10-10 | カミンズ・ターボ・テクノロジーズ・リミテッド | Compressor |
| DE102006020334B4 (en) * | 2006-04-28 | 2008-07-10 | Man Diesel Se | filter silencer |
| EP1873364A1 (en) * | 2006-06-29 | 2008-01-02 | ABB Turbo Systems AG | Silencer |
| FR2909730B1 (en) * | 2006-12-06 | 2011-10-28 | Renault Sas | DEVICE FOR FEEDING FRESH AIR FROM AN INTERNAL COMBUSTION ENGINE OF THE SURALIMENT TYPE |
| US7794213B2 (en) | 2007-05-14 | 2010-09-14 | Honeywell International Inc. | Integrated acoustic damper with thin sheet insert |
| DE102008015353A1 (en) | 2008-03-22 | 2009-09-24 | Bosch Mahle Turbo Systems Gmbh & Co. Kg | Loading device i.e. exhaust gas turbo charger, for motor vehicle, has sound absorber including chamber, where external wall is partially extended in axial direction and formed by housing of device |
| DE102009027539A1 (en) | 2009-07-08 | 2011-01-20 | Ford Global Technologies, LLC, Dearborn | Internal combustion engine with intercooler |
| DE102011120347A1 (en) | 2011-11-30 | 2013-06-06 | Maik Hentschel | Structured multi-layer tubular air charge line for internal combustion engine, has inner layer for thermal and sound insulation which is made of thermoplastic foam layer of variable layer thickness and formed by blow molding process |
| EP2631449B1 (en) * | 2012-02-22 | 2020-07-29 | ISOLITE GmbH | Acoustic absorber |
| FR2995633B1 (en) * | 2012-09-18 | 2018-04-13 | Peugeot Citroen Automobiles Sa | ACOUSTIC ATTENUATOR FORMING THERMAL SCREEN FOR SUPERIMUM THERMAL MOTOR |
| JP6097188B2 (en) * | 2013-09-25 | 2017-03-15 | 三菱重工業株式会社 | Turbocharger |
| DE102016112333B4 (en) | 2016-07-06 | 2023-05-25 | Man Energy Solutions Se | turbocharger |
| WO2018225078A1 (en) * | 2017-06-05 | 2018-12-13 | Mahle Behr India Private Limited | Charge-air cooler for a fresh-air system of an internal combustion engine |
| DE102017124467A1 (en) | 2017-10-19 | 2019-04-25 | Abb Turbo Systems Ag | Diffuser arrangement of an exhaust gas turbine |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6136173A (en) * | 1984-07-27 | 1986-02-20 | 工業技術院長 | High temperature solid lubricating ceramics |
| JPS6276244A (en) * | 1985-09-30 | 1987-04-08 | Matsushita Electric Ind Co Ltd | Picture display device |
| JPH06207563A (en) * | 1992-06-12 | 1994-07-26 | Kuehnle Kopp Kausch Ag | Exhaust turbo-supercharger |
| JPH09144986A (en) * | 1995-11-27 | 1997-06-03 | Nissan Motor Co Ltd | Noise absorbing duct structure |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ZA783845B (en) * | 1977-07-13 | 1979-07-25 | Carrier Corp | Pressure variation absorber |
| WO1981003201A1 (en) * | 1980-04-28 | 1981-11-12 | G Koopmann | Noise reduction system |
| DE3531353A1 (en) * | 1985-09-03 | 1987-03-12 | Audi Ag | Charge air cooler for supercharged internal combustion engine |
| US5162620A (en) * | 1989-11-28 | 1992-11-10 | Allied-Signal Inc. | Dual flow turbine engine muffler |
| SE505569C2 (en) * | 1995-12-11 | 1997-09-15 | Abb Flaekt Marine Ab | Reactor chamber for catalytic purification of exhaust gas from diesel engine |
| DE19615917A1 (en) * | 1996-04-22 | 1997-10-30 | Wolf Woco & Co Franz J | Intake silencer and motor vehicle |
-
1998
- 1998-04-28 DE DE1998118873 patent/DE19818873C2/en not_active Expired - Fee Related
-
1999
- 1999-04-23 JP JP11701499A patent/JPH11336555A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6136173A (en) * | 1984-07-27 | 1986-02-20 | 工業技術院長 | High temperature solid lubricating ceramics |
| JPS6276244A (en) * | 1985-09-30 | 1987-04-08 | Matsushita Electric Ind Co Ltd | Picture display device |
| JPH06207563A (en) * | 1992-06-12 | 1994-07-26 | Kuehnle Kopp Kausch Ag | Exhaust turbo-supercharger |
| JPH09144986A (en) * | 1995-11-27 | 1997-06-03 | Nissan Motor Co Ltd | Noise absorbing duct structure |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2003519329A (en) * | 2000-01-07 | 2003-06-17 | アーベーベー ターボ システムズ アクチエンゲゼルシャフト | Silencer for exhaust gas turbocharger compressor |
| JP2005069228A (en) * | 2003-08-26 | 2005-03-17 | Abb Turbo Systems Ag | Muffler |
| JP2006348939A (en) * | 2005-06-16 | 2006-12-28 | Man Diesel Sa | Exhaust-driven supercharger of internal combustion engine |
| KR101204226B1 (en) | 2005-06-16 | 2012-11-26 | 만 디젤 앤 터보 에스이 | Exhaust gas turbosupercharger for an internal combustion engine |
| US20110308502A1 (en) * | 2009-02-18 | 2011-12-22 | Mitsubishi Heavy Industries, Ltd. | Turbocharger |
| JP2013527382A (en) * | 2010-06-04 | 2013-06-27 | ボーグワーナー インコーポレーテッド | Exhaust gas turbocharger compressor |
Also Published As
| Publication number | Publication date |
|---|---|
| DE19818873A1 (en) | 1999-11-11 |
| DE19818873C2 (en) | 2001-07-05 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JPH11336555A (en) | Reciprocating internal combustion engine | |
| JP5417610B2 (en) | High performance exhaust system | |
| US6752240B1 (en) | Sound attenuator for a supercharged marine propulsion device | |
| EP2354482B1 (en) | Exhaust muffler device | |
| JP2005256839A (en) | Reciprocating piston internal combustion engine | |
| US8136627B2 (en) | Exhaust silencer device for internal combustion engine | |
| JP2013015118A (en) | Sound absorbing structure | |
| JPH11351085A (en) | Reciprocating internal combustion engine | |
| US6722467B1 (en) | Noise attenuator for an air supply system of an internal combustion engine | |
| JP2004519575A (en) | Device for damping resonance in conduit | |
| US8936133B2 (en) | Four cycle internal combustion engine exhaust | |
| JP2006029224A (en) | Exhaust device of engine with supercharger | |
| JP2000045782A (en) | Pulsation noise silencer for supercharger | |
| RU19555U1 (en) | NOISE MUFFLER | |
| JPS58202322A (en) | Discharge silencer of internal-combustion engine | |
| KR100347305B1 (en) | Expention Chamber Silencer with extended inlet and outlet for Deasel generator | |
| KR100311132B1 (en) | Resonator for internal combustion engine | |
| KR100288234B1 (en) | Muffler for internal combustion engine | |
| SU1390391A1 (en) | Noise silencer | |
| RU2460889C1 (en) | Automotive ice exhaust gas silencer | |
| JP3448124B2 (en) | Internal combustion engine with turbocharge | |
| RU2268374C2 (en) | Exhaust silencer for internal combustion engine | |
| SU709824A1 (en) | Noise suppressor at exhaust of internal combustion engine | |
| RU33407U1 (en) | Combustion exhaust silencer | |
| RU27408U1 (en) | INTERNAL COMBUSTION ENGINE RELEASE SILENCER |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| A621 | Written request for application examination |
Effective date: 20060331 Free format text: JAPANESE INTERMEDIATE CODE: A621 |
|
| A131 | Notification of reasons for refusal |
Free format text: JAPANESE INTERMEDIATE CODE: A131 Effective date: 20090305 |
|
| A601 | Written request for extension of time |
Free format text: JAPANESE INTERMEDIATE CODE: A601 Effective date: 20090605 |
|
| A602 | Written permission of extension of time |
Free format text: JAPANESE INTERMEDIATE CODE: A602 Effective date: 20090610 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20090903 |
|
| A131 | Notification of reasons for refusal |
Effective date: 20091020 Free format text: JAPANESE INTERMEDIATE CODE: A131 |
|
| A601 | Written request for extension of time |
Free format text: JAPANESE INTERMEDIATE CODE: A601 Effective date: 20100120 |
|
| A602 | Written permission of extension of time |
Effective date: 20100125 Free format text: JAPANESE INTERMEDIATE CODE: A602 |
|
| A521 | Written amendment |
Free format text: JAPANESE INTERMEDIATE CODE: A523 Effective date: 20100416 |
|
| A02 | Decision of refusal |
Effective date: 20101109 Free format text: JAPANESE INTERMEDIATE CODE: A02 |