M352581 五、新型說明： 【新型所屬之技術領域】 本新型疋有關於一種排氣管，特別是指一種用於導引 一内燃機之排氣之排氣管。 【先前技術】 一般排氣管適用於接引内燃機之排氣，並排放至空氣 之中，由於汽車或機車之引擎等内燃機於運作過程中是利 用燃料爆炸產生之能量推動活塞運作，所以排放之排氣是 具有間歇形式之脈衝衝力。 故於排氣過程中需謹慎處理上述之脈衝衝力，以避免 形成噪音，且如果適當運用上述之脈衝衝力還可增加内燃 機之效率，提升内燃機之輸出馬力及扭力。 α此中華民國專利公告號第326241號、第奶綱號 且書號第M331G4G號及第Μ265464號專利案都是揭露螺 旋管形狀之排氣管，且由上述案件之說明中可明瞭以螺旋 管導引排氣碎實有改善燃燒效率與降低噪音的功效，但是 上述螺旋官之旋度與管縮比例影響燃燒效率與噪音降低程 度甚大。 【新型内容】 因此，本新型之目的即在提供一種利用良好的排氣效 率使内燃錢體馬力與扭力輸出特在高效率的排氣管。 ^於是’本新型排氣管適用於導弓卜内燃機之排氣，排 虱官包含：依序銜接之_進氣段、一螺旋段及一排氣段。 該進氣段銜接所述内燃機並呈中空之圓管狀。該螺旋 M352581 段前端軸向銜接該進氣段，螺旋段具有至少三由内周面往 内螺旋凸設且相互間隔的螺旋條，該等螺旋條之旋度是介 於100度〜165度，也就是螺旋條的螺旋線與徑向直線的夾 角疋介於100度〜165度間，該螺旋段之内徑是小於進氣段 内徑的一半。該排氣段銜接該螺旋段之後端，且呈中空之 圓管狀。 本新型之功效在於利用螺旋段之旋度設計於1〇〇度〜 165度間，以導引所述内燃機之排氣脈衝，降低噪音，增加 内燃機效率，提升輸出馬力與扭力。 【實施方式】 有關本新型之前述及其他技術内容、特點與功效，在 、下配s參考圖式之二個較佳實施例的詳細說明中，將可 清楚的呈現。 在本新型被詳細描述之前，要注意的是，在以下的說 明内谷中，類似的元件是以相同的編號來表示。 閱圖1與圖2，本新型排氣管之第一較佳實施例適用 於銜接-内職2並導引具有間歇形式之脈衝衝力的排氣 ’排氣管包含：依序銜接之-進氣段3、一螺旋段4及-排 氣段5。 °亥進氣段3銜接所述内燃機2並呈中空之圓管狀，其 雨端連接所述内燃機2而後端連接該螺旋段4，進氣段3主 要之功能在於導引所述内燃冑2排出之排氣進人螺旋段4 中。 螺紅& 4之如端軸向銜接該進氣段3，螺旋段4具有 M352581 五條由内周面往内螺旋凸設且相互間隔的螺旋條41，該等 螺旋條41之旋度是介於100度〜165度，也就是螺旋條41 的螺旋線與徑向直線的夾角6>是介於1〇〇度〜165度間。此 外该螺旋段4之管縮比例是小於〇 5，也就是該等螺旋條41 之内側緣間的距離D小於進氣段3内徑的一半。 由於該等螺旋條41之旋度是指徑向直線方向與該等螺 灰條41間之夾角，當上述夾角是165〜180度時，排氣流 動方向幾乎與螺旋條41之延伸方向垂直，容易造成排氣流 動時之阻力較大，排氣之脈衝衝力往内燃機2回衝，形成 過间之回壓，當所述内燃機2之多數汽缸依序或交錯排氣 時，不僅容易造成排氣與回壓相互碰撞，產生更大的噪音 ，也容易造成所述内燃機2燃燒效率降低。 么另外，當上述旋度是於90〜1〇〇度時，排氣流動方向 幾乎與螺旋條41之延伸方向平行，幾乎無阻㈣氣之功能 ，容易造成排氣排放過程中之回壓過低，易造成所述内燃 機2馬力與輸出扭力的表現較差。而本創作之螺旋條41之 旋度設計於UK)〜165度間，可提供所述内燃機2適當之回 壓’使其輸出扭力有較佳表現，同㈣可適度提高燃燒效 率至於方疋度15〜80度之螺旋條41是屬於逆螺旋之螺旋 條4卜效果與⑽〜165度之螺旋條4ι相同，於此就不再 多做說明。 該排氣奴5銜接該螺旋段4之後端，且呈中空之圓管 狀以將排氣導引往外排放。本實施例中該排氣段5、螺旋: 4與進氣段3是-體成型製成，也就是排氣管是以_金屬管 M352581 直接扭轉出該螺旋段4而成。 藉此，本創作利用該螺旋段4將該所屬内燃機2排放 之排氣適當地螺旋導引，並提供適當之阻力，以使排氣造 成回壓，一方面可避免不同汽缸排放之排氣脈衝於排氣管 中相互擾机，降低噪音產生，另一方面可提升内燃機2之 馬力與扭力之輸出表現’提昇燃燒效率。 參閱圖3與圖4，本新型排氣管之第二較佳實施例主要 力用疋V引内燃機2之排氣並消除内燃機2運作時排氣產 生之本音，第二較佳實施例之構造是大致與第一較佳實施 例相同，其不同之處在於排氣管更包含一圍覆於該進氣段3 、螺旋段4與排氣段5外之外殼段6、填充於外殼段6與螺 旋焱4間之消音棉7，及多數分佈於該進氣段3、螺旋段* 與排氣段5上並貫穿内、外周面之消音孔$。 田所述内燃機2之排氣進入該進氣段3後，經過内徑 斬縮之累旋& 4 ’排氣因文阻而形成噴流效應，致使部分排 鲁 I㈣進氣段3與螺旋段4前端部上之料孔8往外流動 ' 至消音棉7中’當管内之排氣流過螺旋段4後，因管徑漸 闊壓力漸小，致使排放至吸音棉7中之部分排氣又經由螺 旋段4之後端部與排氣段5上之消音孔8進入螺旋段*盘 .減段5巾，湘螺錢4使絲之排氣分料重新組合 - 以使消音棉7發揮消除噪音的功效。 參閱圖5,本新型排氣管之第三較佳實施例之構造是大 致與第二較佳實施例相同’其不同之處在於排氣管是兩段 式設計，也就是排氣管包含二前後轴接之消音管部9、一圍 M352581 覆於消音管部9外周圍之外殼段6、多數分佈於該消音管部 〃並貫穿内、外周面之消音孔8，及填充於外般段6與螺 方疋^ 4間之消音棉7。每—消音管部9具有—進氣段3、一 if 與i氣段5。對於汽缸數較少之内燃機可藉由多 數螺旋段4以形成多數回塵，避免排氣脈衝頻率較低時回 壓隨排氣脈衝而高低不定，可穩定維持管内回壓，且兩段 式螺旋段4可形成兩次喷流效應，可大幅降低噪音產生。 本實施例中是以兩段消音管部9為例做說明，實際實 施時可依據所述_機2之汽缸數量設計消音管部9之數 量’或者設計各個螺旋段4有不同之旋度，或者各螺旋段4 分別設計為正、逆螺旋等形式，以使該等螺旋& 4有不同 導引排氣的效率，逐步消除噪音。 綜上所述，本新型排氣管利用螺旋段4之旋度設計於 100度〜165度間，可具有以下優點： 1·利用該螺旋段4將該所屬内燃機2之排氣適當地螺旋導 引’以使排氣造成回壓’改善内燃機2之馬力與扭力 之輸出表現，提昇燃燒效率。 2. 於排氣管中造成回壓可使不同汽缸排放之排氣脈衝避免 於排氣管中相互擾流，降低噪音產生。 3. 經過佈滿消音孔8且内徑漸縮之螺旋段4時，排氣因受 阻而形成噴流效應，使流動之排氣分離進入消音棉7 再重新組合，以使消音棉7發揮消除噪音的功效。 4. 多數螺旋段4串接時，可形成多數回壓，對於汽紅數較 少、排氣脈衝頻率較低之内燃機，可避免回壓隨脈衝 M352581 而高低不定’穩定維持管内回壓。 惟以上所述者，僅為本新型之較佳實施例而已，當不 能以此限定本新型實施之範圍，即大凡依本新型申請專利 fe圍及新型說明内容所作之簡單的等效變化與修飾，皆仍 屬本新型專利涵蓋之範圍内。 【圖式簡單說明】M352581 V. New description: [New technical field] The present invention relates to an exhaust pipe, and more particularly to an exhaust pipe for guiding the exhaust of an internal combustion engine. [Prior Art] Generally, the exhaust pipe is suitable for receiving the exhaust gas of the internal combustion engine and discharging it into the air. Since the internal combustion engine such as the engine of the automobile or the locomotive uses the energy generated by the fuel explosion to drive the piston to operate, the discharge is performed. Exhaust gas is a pulsed impulse with intermittent forms. Therefore, the above-mentioned pulse impulse should be carefully handled during the exhaust process to avoid noise, and if the pulse force is properly applied, the efficiency of the internal combustion engine can be increased, and the output horsepower and torque of the internal combustion engine can be improved. The patents of the Republic of China Patent No. 326241, the Milk No. and the No. M331G4G and the No. 265464 are all disclosed as the exhaust pipe in the shape of a spiral tube, and the description of the above case can be seen as a spiral guide. Exhaust gas has the effect of improving combustion efficiency and reducing noise, but the above-mentioned spiral rotation and tube shrinkage ratio affect combustion efficiency and noise reduction. [New content] Therefore, the purpose of the present invention is to provide an exhaust pipe which is highly efficient in utilizing good exhaust efficiency to make the internal combustion engine horsepower and torque output. ^ So, the new exhaust pipe is suitable for the exhaust of the internal combustion engine, and the exhaustor includes: the intake section, the spiral section and the exhaust section. The intake section engages the internal combustion engine and has a hollow circular tube shape. The front end of the spiral M352581 section axially engages the air inlet section, and the spiral section has at least three spiral strips which are spirally protruded from the inner circumferential surface and are spaced apart from each other, and the spiralness of the spiral strips is between 100 degrees and 165 degrees. That is, the angle between the spiral of the spiral strip and the radial straight line is between 100 degrees and 165 degrees, and the inner diameter of the spiral section is less than half of the inner diameter of the air inlet section. The exhaust section engages the rear end of the spiral section and has a hollow circular tube shape. The utility model has the advantages that the rotation degree of the spiral section is designed to be between 1 〜 and 165 degrees to guide the exhaust pulse of the internal combustion engine, reduce noise, increase the efficiency of the internal combustion engine, and improve the output horsepower and torque. [Embodiment] The foregoing and other technical contents, features, and advantages of the present invention will be apparent from the detailed description of the preferred embodiments of the accompanying drawings. Before the present invention is described in detail, it is noted that in the following description, similar elements are denoted by the same reference numerals. Referring to Figures 1 and 2, the first preferred embodiment of the novel exhaust pipe is adapted to engage - internal 2 and direct the exhaust having an intermittent impulse of the 'exhaust pipe comprising: sequentially connected - intake Section 3, a spiral section 4 and an exhaust section 5. The air inlet section 3 is connected to the internal combustion engine 2 and has a hollow circular tube. The rain end is connected to the internal combustion engine 2 and the rear end is connected to the spiral section 4. The main function of the air inlet section 3 is to guide the internal combustion chamber 2 to discharge. The exhaust enters the spiral section 4. The spiral red & 4 is axially connected to the air inlet section 3, and the spiral section 4 has M352581 five spiral strips 41 which are spirally protruded from the inner circumferential surface and are spaced apart from each other, and the spiralness of the spiral strips 41 is Between 100 degrees and 165 degrees, that is, the angle between the spiral of the spiral strip 41 and the radial straight line is between 1 and 165 degrees. Further, the ratio of the tube length of the spiral section 4 is smaller than 〇 5, that is, the distance D between the inner edges of the spiral strips 41 is smaller than half the inner diameter of the inlet section 3. Since the curl of the spiral strips 41 refers to the angle between the radial straight line direction and the spiral strips 41, when the angle is 165 to 180 degrees, the flow direction of the exhaust gas is almost perpendicular to the extending direction of the spiral strips 41. It is easy to cause a large resistance when the exhaust gas flows, and the pulse impulse of the exhaust gas is backflushed to the internal combustion engine 2 to form a back pressure. When most of the cylinders of the internal combustion engine 2 are sequentially or staggered, it is not only easy to cause exhaust. Colliding with the back pressure, generating more noise, is also liable to cause a decrease in the combustion efficiency of the internal combustion engine 2. In addition, when the above-mentioned curl is 90 to 1 degree, the flow direction of the exhaust gas is almost parallel to the extending direction of the spiral strip 41, and the function of the gas is almost unimpeded (four), which easily causes the back pressure in the exhaust gas discharge process to be too low. It is easy to cause the performance of the internal combustion engine 2 horsepower and output torque to be poor. The spiral of the spiral strip 41 of the present design is designed to be between 165 degrees and 165 degrees, and the proper back pressure of the internal combustion engine 2 can be provided to make the output torque better, and the fourth (4) can appropriately improve the combustion efficiency to the squareness. The spiral strip 41 of 15 to 80 degrees is the same as the spiral strip 4 of the inverse spiral and the spiral strip 4 of the (10) to 165 degree, and will not be described here. The exhaust slave 5 is connected to the rear end of the spiral section 4 and has a hollow circular tube to guide the exhaust gas to the outside. In this embodiment, the exhaust section 5, the spiral: 4 and the intake section 3 are formed by body molding, that is, the exhaust pipe is formed by directly twisting the spiral section 4 by the metal pipe M352581. Thereby, the present invention utilizes the spiral section 4 to properly guide the exhaust gas discharged from the internal combustion engine 2, and provides appropriate resistance to cause back pressure of the exhaust gas, and on the other hand, avoid exhaust pulses of different cylinder discharges. Mutual interference in the exhaust pipe to reduce noise generation, on the other hand, can improve the output performance of the internal combustion engine 2 horsepower and torsion to improve combustion efficiency. Referring to Figures 3 and 4, the second preferred embodiment of the present novel exhaust pipe mainly utilizes the exhaust of the internal combustion engine 2 and eliminates the local sound generated by the exhaust gas during operation of the internal combustion engine 2. The construction of the second preferred embodiment It is substantially the same as the first preferred embodiment, except that the exhaust pipe further comprises an outer casing segment 6 surrounding the air inlet section 3, the spiral section 4 and the exhaust section 5, and is filled in the outer casing section 6. The muffler cotton 7 between the spiral cymbal 4 and most of the muffling hole $ distributed on the air inlet section 3, the spiral section* and the exhaust section 5 and passing through the inner and outer peripheral surfaces. After the exhaust gas of the internal combustion engine 2 enters the intake section 3, the jet flow effect is formed by the entanglement of the inner diameter and the 4' exhaust gas, so that part of the exhaust I (four) intake section 3 and the spiral section 4 The material hole 8 on the front end portion flows outward' to the sound-absorbing cotton 7'. When the exhaust gas in the pipe flows through the spiral segment 4, the pressure gradually decreases due to the pipe diameter, so that part of the exhaust gas discharged into the sound-absorbing cotton 7 is again Via the rear end of the spiral section 4 and the sound-absorbing hole 8 on the exhaust section 5, enter the spiral section * disk. Reduce the section 5 towel, Xiangluo Qian 4 re-combines the exhaust material of the wire - so that the muffler cotton 7 can eliminate noise The effect. Referring to FIG. 5, the configuration of the third preferred embodiment of the present novel exhaust pipe is substantially the same as that of the second preferred embodiment. The difference is that the exhaust pipe is a two-stage design, that is, the exhaust pipe includes two The muffling pipe portion 9 and the M352581 which are axially connected to each other are disposed on the outer casing segment 6 around the outer portion of the muffling pipe portion 9, and the muffling holes 8 which are distributed in the muffling pipe portion and penetrate the inner and outer peripheral faces, and are filled in the outer segment. 6 with the square 疋 ^ 4 between the muffler cotton 7. Each of the muffling pipe sections 9 has an intake section 3, an if and an i section 5. For an internal combustion engine with a small number of cylinders, a majority of the spiral segments 4 can be used to form a majority of the dust return, and the back pressure can be prevented from varying with the exhaust pulse when the exhaust pulse frequency is low, and the back pressure in the tube can be stably maintained, and the two-stage spiral Segment 4 creates two jet effects that significantly reduce noise generation. In the embodiment, the two-stage silencer tube portion 9 is taken as an example for description. In actual implementation, the number of the silencer tube portions 9 may be designed according to the number of cylinders of the machine 2, or the design of each spiral segment 4 may have different degrees of rotation. Or the spiral segments 4 are respectively designed in the form of positive and negative spirals, so that the spirals & 4 have different guiding exhaust efficiencies and gradually eliminate noise. In summary, the novel exhaust pipe is designed to have a rotation between 100 degrees and 165 degrees by using the spiral segment 4, and has the following advantages: 1. The spiral portion 4 is used to properly circulate the exhaust gas of the internal combustion engine 2 The introduction of 'to make the exhaust gas back pressure' improves the output performance of the horsepower and torque of the internal combustion engine 2, and improves the combustion efficiency. 2. The back pressure caused in the exhaust pipe can prevent the exhaust pulse discharged from different cylinders from turbulence in the exhaust pipe and reduce the noise. 3. After the spiral section 4 which is covered with the muffling hole 8 and the inner diameter is tapered, the exhaust gas is blocked by the jetting effect, so that the flowing exhaust gas is separated into the muffing cotton 7 and recombined, so that the muffler cotton 7 can eliminate the noise. The effect. 4. When most of the spiral segments 4 are connected in series, most of the back pressure can be formed. For an internal combustion engine with less steam red number and lower exhaust pulse frequency, the back pressure can be avoided with the pulse M352581, and the back pressure can be stably maintained. However, the above is only the preferred embodiment of the present invention, and the scope of the present invention cannot be limited thereto, that is, the simple equivalent change and modification made by the novel patent application and the new description content. , are still within the scope of this new patent. [Simple description of the map]
疋本新型排氣管之第一較佳實施例與 m 接之側面視圖； 圖2是該第一較佳實施例的正面剖視圖； 圖3是本新型排氣管之第二較佳實施例與一内燃機銜 接之側面視圖； 圖4疋該第二較佳實施例的正面剖視圖；及 圖5是本新型排氣管之第= 接之側面視圖。 二較佳貝施例與-内燃機銜 M352581 【主要元件符號說明】 2 内燃機 6 外殼段 3 進氣段 7 消音棉 4 螺旋段 8 消音孔 41 螺旋條 9 消音管部 5 排氣段2 is a side elevational view of the first preferred embodiment of the present invention; FIG. 2 is a front cross-sectional view of the first preferred embodiment; FIG. 3 is a second preferred embodiment of the present novel exhaust pipe. A side view of an internal combustion engine; FIG. 4 is a front cross-sectional view of the second preferred embodiment; and FIG. 5 is a side view of the new exhaust pipe. The second preferred embodiment and the internal combustion engine M352581 [Main component symbol description] 2 Internal combustion engine 6 Shell section 3 Inlet section 7 Silencer cotton 4 Spiral section 8 Silencer hole 41 Spiral strip 9 Silencer section 5 Exhaust section