TWI479076B - Engine variable valve lift mechanism - Google Patents
Engine variable valve lift mechanism Download PDFInfo
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- TWI479076B TWI479076B TW100131684A TW100131684A TWI479076B TW I479076 B TWI479076 B TW I479076B TW 100131684 A TW100131684 A TW 100131684A TW 100131684 A TW100131684 A TW 100131684A TW I479076 B TWI479076 B TW I479076B
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Description
本發明有關一種引擎的可變汽門揚程機構,尤指可使可使引擎在低速運轉狀態及高速運轉狀態下,獲得最適動力之運用的引擎可變汽門揚程機構。The invention relates to a variable valve head mechanism of an engine, in particular to an engine variable valve head mechanism capable of obtaining an optimum power for an engine in a low speed running state and a high speed running state.
已知的構造請參閱圖一,是在汽門閥2上方設置第一及第二搖臂21、22,其中該第二搖臂22為一多連桿式構件,藉由第一及第二搖臂21、22分別可各自推動汽門閥2,來令汽門閥2之揚程產生變化,亦即當第一搖臂21在推動汽門閥2時,該汽門閥2是為小開度揚程;當第二搖臂22在推動汽門閥2時,該汽門閥2為最大開度之揚程,藉此、以因應引擎1之高低速運轉時不同汽門閥2揚程之進、排氣閥門切換。Referring to Figure 1, the first and second rocker arms 21, 22 are disposed above the valve valve 2, wherein the second rocker arm 22 is a multi-link member, with the first and second shaking The arms 21, 22 can respectively push the valve 2 to change the head of the valve 2, that is, when the first rocker 21 is pushing the valve 2, the valve 2 is a small opening; When the two rocker arms 22 push the valve 2, the valve 2 is the head of the maximum opening degree, thereby switching between the inlet and the exhaust valves of the different valve valves 2 in response to the high and low speeds of the engine 1.
上述引擎1之汽門可變揚程機構構造,藉由於汽門閥2上方設置第一及第二搖臂21、22,來分別可各自推動汽門閥2,雖然可以達到配合引擎1高低速運轉時不同汽門閥2揚程之進、排氣閥門切換。由於,該第一及第二搖臂21、22是以質量較重的鑄鐵材質所作成,其轉動慣量較大,因此汽門彈簧23的力量亦需要設定得較強,才能克服其轉動慣量,這也使得引擎動力損耗較大;另外,該第二搖臂22為多連桿式構造,因其構造複雜及其作動時必需要有相當的作動空間,所以引擎1的汽缸頭1a相對的必需大型化,才能有足夠的空間供第二搖臂22作動;引擎1的汽缸頭1a大型化,無疑的會造成引擎1成本增加,以及引擎1設置工程設計的困難度增加,就機車而言其設置引擎1的空間本來就已有所限制。是以、如何提升較簡易的引擎1之汽門可變揚程機構構造,實為目前機車製造業者所亟待克服之課題。The valve variable head mechanism of the engine 1 is configured to respectively push the valve 2 by the first and second rocker arms 21 and 22 above the valve 2, although it can be different when the engine 1 is operated at a high speed and a low speed. The inlet and exhaust valves of the valve 2 are switched. Since the first and second rocker arms 21, 22 are made of a heavier cast iron material, the moment of inertia is larger, and therefore the force of the valve spring 23 needs to be set stronger to overcome the moment of inertia. This also causes the engine power loss to be large; in addition, the second rocker arm 22 is a multi-link type structure, and the cylinder head 1a of the engine 1 is relatively necessary because of its complicated structure and a certain working space when it is required to operate. Larger size, in order to have enough space for the second rocker arm 22 to operate; the cylinder head 1a of the engine 1 is enlarged, which undoubtedly causes an increase in the cost of the engine 1, and the difficulty in setting the engineering design of the engine 1, as far as the locomotive is concerned Setting the space for Engine 1 is inherently limited. Therefore, how to improve the structure of the valve variable head mechanism of the relatively simple engine 1 is an urgent problem for the locomotive manufacturers.
本發明主要乃在提供一種引擎的可變汽門揚程機構,該引擎具有一汽缸頭,該汽缸頭上設有進氣埠及進氣閥,排氣埠及排氣閥,於該進氣埠與排氣埠之間設有一凸輪軸座,該凸輪軸座樞設有一凸輪軸,其特徵在於:該凸輪軸上設有長進氣凸輪、短進氣凸輪及排氣凸輪,於凸輪軸轉動時,可推頂進氣閥搖臂及排氣閥搖臂,使進氣閥及排氣閥作動;該進氣閥搖臂及排氣閥搖臂為輕金屬合金材質,因此能有效降低該進氣閥搖臂及排氣閥搖臂的轉動慣量,故能減少引擎之動力消耗。The present invention mainly provides an engine variable valve lift mechanism having a cylinder head having an intake port and an intake valve, an exhaust port and an exhaust valve, and the intake port A camshaft seat is disposed between the exhaust rafts, and the camshaft seat is pivotally provided with a camshaft, wherein the camshaft is provided with a long intake cam, a short intake cam and an exhaust cam, when the camshaft rotates The intake valve rocker arm and the exhaust valve rocker arm can be pushed to make the intake valve and the exhaust valve act; the rocker arm of the intake valve and the rocker arm of the exhaust valve are made of light metal alloy, thereby effectively reducing the intake air. The moment of inertia of the valve rocker arm and the exhaust valve rocker arm can reduce the power consumption of the engine.
上述的進氣閥搖臂具有一般開度搖臂及高開度搖臂,該一般開度搖臂設有軸孔、貫孔、滾子及按壓部,該高開度搖臂具有軸孔、貫孔及滾子,該排氣閥搖臂具有軸孔及滾子,該一般開度搖臂及高開度搖臂之軸孔穿設有搖臂軸,一與油控閥相通的第一驅動油路及第二驅動油路,該搖臂軸內設有用以隔開第一驅動油路及第二驅動油路的分隔壁,該一般開度搖臂之滾子則是與短進氣凸輪滾動接觸,及該一般開度搖臂之按壓部是與進氣閥相接觸,而高開度搖臂之滾子是與長進氣凸輪滾動接觸,其中,該一般開度搖臂之貫孔與高開度搖臂之貫孔的內壁面為耐磨材質,且可相連通而型成一油壓缸,上述的油壓缸內設有耐磨之高韌性材質的第一活塞與第二活塞,因此能避免以輕金屬製成的進氣搖臂之油壓缸的內壁面與第一活塞及第二活塞的磨耗,可有效防止油壓大量洩漏,避免油壓不足導致活塞無法被推送至預定位置的問題發生。The above-mentioned intake valve rocker arm has a general opening degree rocker arm and a high opening degree rocker arm, and the general opening degree rocker arm is provided with a shaft hole, a through hole, a roller and a pressing portion, and the high opening degree rocker arm has a shaft hole, The through hole and the roller, the exhaust valve rocker arm has a shaft hole and a roller, and the shaft hole of the general opening degree rocker arm and the high opening degree rocker arm is provided with a rocker arm shaft, and the first one is connected with the oil control valve a driving oil passage and a second driving oil passage, wherein the rocker arm shaft is provided with a partition wall for separating the first driving oil passage and the second driving oil passage, and the roller of the general opening degree rocker arm is connected with the short intake air The cam rolling contact, and the pressing portion of the general opening rocker arm is in contact with the intake valve, and the roller of the high opening degree rocker arm is in rolling contact with the long intake cam, wherein the general opening degree of the rocker arm The inner wall surface of the through hole of the hole and the high opening degree rocker arm is wear-resistant material, and can be connected to form a hydraulic cylinder, and the first hydraulic piston has the first piston and the second with wear-resistant high toughness material. The piston can avoid the wear of the inner wall surface of the hydraulic cylinder of the intake rocker arm made of light metal and the first piston and the second piston, thereby effectively preventing oil pressure The amount of leakage to avoid problems due to insufficient hydraulic piston can not be pushed to a predetermined position occurs.
在該油壓缸的兩端附近分別設有與上述第一油通路及第二油通路相連通的端口,該第一活塞與第二活塞可藉由油控閥所輸出的油壓而移動,於是當引擎處於高速運轉狀態時,該第一活塞與第二活塞是移至高開度搖臂之貫孔與一般開度搖臂之貫孔內的結合位置,而令高開度搖臂與一般開度搖臂成連動之模式;當引擎處於低速運轉狀態時,該第一活塞與第二活塞是各自位於高開度搖臂之貫孔與一般開度搖臂之貫孔內之分離位置,而令高開度搖臂與一般開度搖臂成各自作動之模式,藉此可使引擎在低速運轉狀態及高速運轉狀態下,獲得最適動力之運用。Ports communicating with the first oil passage and the second oil passage are respectively disposed near both ends of the hydraulic cylinder, and the first piston and the second piston are movable by the oil pressure output by the oil control valve. Therefore, when the engine is in a high-speed running state, the first piston and the second piston are moved to a joint position of the through hole of the high opening degree rocker arm and the through hole of the general opening degree rocker arm, and the high opening degree rocker arm is generally The opening rocker arm is in a linkage mode; when the engine is in a low speed running state, the first piston and the second piston are respectively separated from each other in the through hole of the high opening degree rocker arm and the through hole of the general opening degree rocker arm. The high-opening rocker arm and the general opening rocker arm are in a mode of operation, thereby enabling the engine to obtain the optimum power in the low-speed running state and the high-speed running state.
該高開度搖臂與一般開度搖臂及排氣閥搖臂的輕金屬選用含有鋁或镁之至少一種金屬作為主成分;該高開度搖臂之貫孔與一般開度搖臂之貫孔內壁面的耐磨材質選用為高碳鋼;該第一活塞與第二活塞具耐磨之高韌性材質選用為工具鋼,因此可有效防止磨耗的產生,而導致油壓大量洩漏。The high-opening rocker arm and the light metal of the general opening rocker arm and the exhaust valve rocker arm are selected from at least one metal containing aluminum or magnesium as a main component; the through hole of the high opening degree rocker arm and the general opening degree rocker arm The wear-resistant material of the inner wall of the hole is selected as high-carbon steel; the high-toughness material of the first piston and the second piston is made of tool steel, so that the wear can be effectively prevented, and the oil pressure is largely leaked.
該高開度搖臂與一般開度搖臂,和高開度搖臂之貫孔與一般開度搖臂之貫孔的內壁面是由不同製程的襯套所成;該位於高開度搖臂之貫孔與一般開度搖臂之貫孔的襯套為嵌入、壓合、射包之至少一種所成;該高開度搖臂之軸孔及一般開度搖臂之軸孔的孔壁為耐磨材質所成。The high opening degree rocker arm and the general opening degree rocker arm, and the inner wall surface of the through hole of the high opening degree rocker arm and the through hole of the general opening degree rocker arm are formed by bushings of different processes; The bushing of the arm through hole and the through hole of the general opening rocker arm are formed by at least one of embedding, pressing and punching; the shaft hole of the high opening rocker arm and the hole of the shaft hole of the general opening rocker arm The wall is made of wear-resistant material.
該凸輪軸為同軸設置有長進氣凸輪、短進氣凸輪及排氣凸輪的單凸輪軸,可使汽缸頭內的零件配置更緊湊,避免汽缸頭巨大化,有益於汽缸頭在整車上的空間配置。The camshaft is a single camshaft coaxially provided with a long intake cam, a short intake cam and an exhaust cam, which can make the components in the cylinder head more compact, avoiding the huge cylinder head, and benefiting the cylinder head on the whole vehicle. Space configuration.
該汽缸頭更設有抵頂高開度搖臂及一般開度搖臂之腳撐機構,該腳撐機構包括有一腳撐筒、一腳撐彈簧及一容納該腳撐筒和腳撐彈簧的腳撐孔;該高開度搖臂及一般開度搖臂更設有腳撐部,且該腳撐部是與腳撐機構之腳撐筒相接觸,可確保高開度搖臂之貫孔及一般開度搖臂之貫孔能位於設定之位置上。The cylinder head further comprises a foot support mechanism for abutting the high opening degree rocker arm and the general opening degree rocker arm, the foot support mechanism comprising a foot support tube, a foot support spring and a spring for accommodating the foot support tube and the foot support spring The foot opening hole; the high opening degree rocker arm and the general opening degree rocker arm are further provided with a foot support portion, and the foot support portion is in contact with the foot support tube of the foot support mechanism to ensure the through hole of the high opening degree rocker arm And the through hole of the general opening rocker arm can be located at the set position.
該高開度搖臂及一般開度搖臂之腳撐部是位於軸孔、與按壓部之間,故可有效使高開度搖臂及一般開度搖臂位於預定的位置上。The high opening degree rocker arm and the foot portion of the general opening degree rocker arm are located between the shaft hole and the pressing portion, so that the high opening degree rocker arm and the general opening degree rocker arm can be effectively located at a predetermined position.
該高開度搖臂之貫孔及一般開度搖臂之貫孔是位於滾子與軸孔之間,且位於滾子與軸孔中心點連線的上方,因此可抑制搖臂的總體長度,節省搖臂佔用空間,避免汽缸頭以巨大化的方式來克服空間不足的問題。The through hole of the high opening rocker arm and the through hole of the general opening rocker arm are located between the roller and the shaft hole and are located above the line connecting the center point of the roller and the shaft hole, thereby suppressing the overall length of the rocker arm It saves space for the rocker arm and avoids the problem of insufficient space in the cylinder head in a huge way.
油壓缸二端分別封設有塞蓋,以及該塞蓋朝油壓缸內側凸設有凸柱,藉此使油壓缸與驅動油路之間保有一定的推動空間,避免活塞無法被推動的問題發生。The two ends of the hydraulic cylinder are respectively provided with a plug cover, and the plug cover protrudes from the inner side of the hydraulic cylinder, so that a certain pushing space is maintained between the hydraulic cylinder and the driving oil passage, so that the piston cannot be pushed. The problem has happened.
該一般開度搖臂之貫孔內容置有復歸彈簧,該復歸彈簧與第一活塞接觸,藉此第一驅動油路之油壓力無須設定得太高,即可推動活塞移動,如此做法可節省機油泵的動能,以及該第一活塞設有第一凹槽及第二凹槽,因此能使活塞更輕更容易被油壓或彈簧來推動。The through hole of the general opening rocker is provided with a return spring, and the return spring is in contact with the first piston, so that the oil pressure of the first driving oil passage does not need to be set too high, so that the piston can be moved, thereby saving The kinetic energy of the oil pump, and the first piston are provided with a first groove and a second groove, thereby making the piston lighter and more easily pushed by oil pressure or spring.
有關本發明之結構及所能達成之功效,茲配合圖式說明如后:Regarding the structure of the present invention and the achievable effects, the following description is in conjunction with the following:
請參閱圖二所示,本發明之引擎3具有一曲軸箱31、一組設於曲軸箱31上之汽缸本體32、一組設於汽缸本體32上之汽缸頭33;該曲軸箱31,內部設有一曲軸(圖示中未繪出),及一機油泵311,該機油泵311是將機油送至一主供油道312,該主供油道312是由曲軸箱31通過汽缸本體32後連通至設置於汽缸頭33之油控閥4;該汽缸本體32是設置於曲軸箱31之上方,並可供正時鏈條5通過,其中,該汽缸本體32於汽缸頭33之進氣埠331側設有一正時鏈條張緊器51。Referring to FIG. 2, the engine 3 of the present invention has a crankcase 31, a set of cylinder bodies 32 disposed on the crankcase 31, and a plurality of cylinder heads 33 disposed on the cylinder body 32; the crankcase 31, the interior A crankshaft (not shown) is provided, and an oil pump 311 is provided to deliver the oil to a main oil supply passage 312 which is passed through the cylinder body 32 through the crankcase 31. It is connected to the oil control valve 4 disposed on the cylinder head 33; the cylinder body 32 is disposed above the crankcase 31 and is configured to pass the timing chain 5, wherein the cylinder body 32 is in the intake port 331 of the cylinder head 33. A timing chain tensioner 51 is provided on the side.
該汽缸頭33,設有一位於進氣側之進氣埠331及進氣閥332,以及一位於排氣側之排氣埠333及排氣閥334,請配合圖二、三、四、五參閱,該汽缸頭33於該進氣埠331與排氣埠333之間一體成形設有一凸輪軸座335,該凸輪軸座335設有一可被正時鏈條5帶動之凸輪軸336,該凸輪軸336上分別設有長進氣凸輪3361(高揚程凸輪)、短進氣凸輪3362(低揚程凸輪)及排氣凸輪3363,藉由該長進氣凸輪3361、短進氣凸輪3362及排氣凸輪3363,可令凸輪軸336於轉動時可推頂進氣閥332及排氣閥334之進氣閥搖臂6及排氣閥搖臂7作開閉之動作;該進氣閥搖臂6及排氣閥搖臂7為輕金屬合金材質,該輕金屬合金的主成分為鋁,亦或者可以鎂作為主成分;如此所成的搖臂,其質量輕轉動慣量較小,因此進氣閥332及排氣閥334的汽門彈簧33a的力量無需設定得太高,即能克服轉動慣量,故能減少引擎之動力消耗,有效避免動能的損失;另外,將該長進氣凸輪3361、短進氣凸輪3362及排氣凸輪3363同軸設置於單一凸輪軸336上,可使汽缸頭33內的零件配置更緊湊,避免汽缸頭33巨大化,有益於汽缸頭33在整車上的空間配置。The cylinder head 33 is provided with an intake port 331 and an intake valve 332 on the intake side, and an exhaust port 333 and an exhaust valve 334 on the exhaust side. Please refer to Figures 2, 3, 4 and 5 for reference. The cylinder head 33 is integrally formed between the intake port 331 and the exhaust port 333. A cam shaft seat 335 is provided. The cam shaft base 335 is provided with a cam shaft 336 that can be driven by the timing chain 5, and the cam shaft 336. The upper intake cam 3361 (high lift cam), the short intake cam 3362 (low lift cam) and the exhaust cam 3363 are respectively provided by the long intake cam 3361, the short intake cam 3362 and the exhaust cam 3363. The camshaft 336 can push the intake valve rocker arm 6 and the exhaust valve rocker arm 7 of the intake valve 332 and the exhaust valve 334 to open and close when rotating; the intake valve rocker arm 6 and the exhaust valve The valve rocker arm 7 is made of a light metal alloy, and the light metal alloy has a main component of aluminum or magnesium as a main component; the rocker arm thus formed has a light mass and a small moment of inertia, so the intake valve 332 and the exhaust valve The force of the valve spring 33a of 334 need not be set too high, that is, the moment of inertia can be overcome, so that the power consumption of the engine can be reduced. Therefore, the loss of kinetic energy is effectively avoided; in addition, the long intake cam 3361, the short intake cam 3362 and the exhaust cam 3363 are coaxially disposed on the single camshaft 336, so that the parts in the cylinder head 33 can be more compactly arranged and the cylinder can be avoided. The head 33 is enlarged to benefit the space configuration of the cylinder head 33 on the entire vehicle.
請配合圖三、五、六參閱,該排氣閥搖臂7具有一供排氣搖臂軸74穿設的軸孔712,其中該排氣閥搖臂7之一端是為按壓部71,該按壓部71是與排氣閥334相接觸,該按壓部71端頭具有間隙調整件711,另一端則為滾子72,其是與排氣凸輪3363滾動接觸,該排氣閥搖臂7的一側一體延設有形成軸孔712的管套73,可供搖臂軸74穿設,藉由搖臂軸74來令排氣閥搖臂7可以穩定的定位於凸輪軸座335上,藉此可由凸輪軸336之排氣凸輪3363推動滾子72,俾使按壓部71來抵壓排氣閥334,進而使原本關閉的排氣汽門打開來令廢氣排出,按壓部71與排氣閥334之間隙可藉由間隙調整件711來調整,藉此可確保排氣閥334之揚程。Referring to FIG. 3, FIG. 5 and FIG. 6, the exhaust valve rocker arm 7 has a shaft hole 712 through which the exhaust rocker arm shaft 74 is disposed. One end of the exhaust valve rocker arm 7 is a pressing portion 71. The pressing portion 71 is in contact with the exhaust valve 334, and the end of the pressing portion 71 has a gap adjusting member 711, and the other end is a roller 72 which is in rolling contact with the exhaust cam 3363, and the exhaust valve rocker arm 7 A sleeve 73 forming a shaft hole 712 is integrally formed on one side for the rocker shaft 74 to pass through, and the rocker arm shaft 74 is used to stably position the exhaust valve rocker arm 7 on the cam shaft seat 335. The roller 72 can be pushed by the exhaust cam 3363 of the cam shaft 336 to press the pressing portion 71 against the exhaust valve 334, thereby opening the exhaust valve that is normally closed to discharge the exhaust gas, and the pressing portion 71 and the exhaust valve The gap of 334 can be adjusted by the gap adjusting member 711, whereby the head of the exhaust valve 334 can be ensured.
再請配合圖三、五、七所示,該進氣閥搖臂6具有高開度搖臂61及一般開度搖臂62,該高開度搖臂61前方具有軸孔611,於軸孔611之前下方凸設有腳撐部612,而於軸孔611之後方設有貫孔613,另於貫孔613的後方設有滾子614;該一般開度搖臂62與高開度搖臂61相對應依序設有腳撐部622、軸孔621、貫孔623及滾子624,另一般開度搖臂62於腳撐部622的前端緣延設有按壓部625,該按壓部625之前端設有間隙調整件6251;該高開度搖臂61之滾子614是與凸輪軸336之長進氣凸輪3361滾動接觸,而一般開度搖臂62之滾子624則是與凸輪軸336之短進氣凸輪3362滾動接觸,另該一般開度搖臂62之按壓部625是與進氣閥332相接觸,該按壓部625與進氣閥332之間隙可藉由間隙調整件6251來調整,藉此可確保進氣閥332之揚程,另藉由一搖臂軸63穿設於軸孔611、621上,藉此可使高開度搖臂61及一般開度搖臂62被穩固的定位於凸輪軸座335上,使該高開度搖臂61及一般開度搖臂62能以搖臂軸63為中心進行擺動,該搖臂軸63係定位於該凸輪軸座335上,又、如圖三所示,該高開度搖臂61及一般開度搖臂62之腳撐部612、622皆是位於軸孔611、621與按壓部625之間,該高開度搖臂61及一般開度搖臂62之貫孔613、623是位於滾子614、624與軸孔611、621之間,且是位於滾子614、624分別與軸孔611、621之中心點連線A之上方,進而可抑制進氣搖臂6的總體長度,節省佔用空間,避免汽缸頭33以巨大化的方式來克服空間不足的問題;次請配合圖五、七、八、九參閱,該高開度搖臂61之貫孔613及一般開度搖臂62之貫孔623相連通而可形成一油壓缸64,其中,該一般開度搖臂62之貫孔623與高開度搖臂61之貫孔613的內壁面613a為耐磨材 質,該耐磨材質可選用高碳鋼;上述具耐磨材質的內壁面613a可以電鍍或熱處理或披覆方式形成;該耐磨材質的內壁面613a也可以是由不同製程的襯套所成;該襯套可以嵌入、壓合、射包之至少一種方式與高開度搖臂61之貫孔613與一般開度搖臂62之貫孔623相結合,因此能避免以輕金屬製成的進氣搖臂6之油壓缸64內壁的磨耗,可有效防止油壓大量洩漏,另外,該耐磨之高韌性材質亦可僅形成於活塞表面643a.644a;該油壓缸64二端分別封設有塞蓋641a.641b,該塞蓋641a.641b朝油壓缸內64凸設有凸柱6411a.6411b,該油壓缸64內設有一可被油壓推動之第一活塞643與第二活塞644,該第一活塞643與第二活塞644具耐磨之高韌性材質,該耐磨之高韌性材質可選用工具鋼,因此能避免與進氣搖臂之油壓缸64內壁的磨耗,可有效防止油壓大量洩漏;該油壓缸64是藉由第一及第二驅動油路65、66而與油控閥4連通,藉此獲得動力油源,另第一活塞643之二側設有第一凹槽6431及第二凹槽6432,藉此可減輕第一活塞643之重量,俾能增進第一活塞643於油壓缸64內的活動度,該第一凹槽6431恰可供塞蓋641a之凸柱6411a容置,即該第一凹槽6431是與塞蓋641a的凸柱6411a相配合,又塞蓋641b之凸柱6411b是抵於第二活塞644之一側,藉此 來令第一活塞643與第二活塞644與油壓缸64二端形成有間距,進而可令由第一及第二驅動油路65、66進入油壓缸64內之動力油源,能順暢的推動第一活塞643與第二活塞644,藉由塞蓋641a.641b之凸柱6411a.6411b,可令第一活塞643與第二活塞644於作動時可以被定位於預定之位置,藉此更能確保第一活塞643及第二活塞644於油壓缸64內的活動度;另於腳撐部612、622下方之汽缸頭33上設腳撐機構337,該腳撐機構337包括有一腳撐筒3371、一腳撐彈簧3372及腳撐孔3373所構成,藉由腳撐機構337來供腳撐部612、622之接觸,可確保高開度搖臂61之貫孔613及一般開度搖臂62之貫孔623能位於設定之位置上,另如腳撐機構337受到腳撐部612、622過度的抵頂力時,該腳撐孔3373可適時釋放壓力,藉此來確保油壓缸64內之第一活塞643與第二活塞644的活動性。Referring to FIG. 3, FIG. 5 and FIG. 7, the intake valve rocker arm 6 has a high opening rocker arm 61 and a general opening rocker arm 62. The high opening degree rocker arm 61 has a shaft hole 611 in front of the shaft hole. Before the 611, the foot support portion 612 is convexly disposed, and the through hole 613 is disposed behind the shaft hole 611, and the roller 614 is disposed behind the through hole 613; the general opening degree rocker arm 62 and the high opening degree rocker arm 61 is correspondingly provided with a foot support portion 622, a shaft hole 621, a through hole 623 and a roller 624. Further, the general opening degree rocker arm 62 extends a front end edge of the foot support portion 622 with a pressing portion 625. The pressing portion 625 The front end is provided with a gap adjusting member 6251; the roller 614 of the high opening degree rocker arm 61 is in rolling contact with the long intake cam 3361 of the cam shaft 336, and the roller 624 of the general opening degree rocker arm 62 is a cam shaft The short intake cam 3362 of the 336 is in rolling contact, and the pressing portion 625 of the general opening rocker 62 is in contact with the intake valve 332. The gap between the pressing portion 625 and the intake valve 332 can be obtained by the gap adjusting member 6251. Adjustment, thereby ensuring the lift of the intake valve 332, and passing through the rocker shaft 63 through the shaft holes 611, 621, thereby enabling the high opening rocker arm 61 and the general opening rocker arm 62 The high-opening rocker arm 61 and the general opening rocker arm 62 are swingably centered on the rocker arm shaft 63, and the rocker arm shaft 63 is positioned on the camshaft seat 335. As shown in FIG. 3, the high-opening rocker arm 61 and the foot support portions 612 and 622 of the general opening degree rocker arm 62 are located between the shaft holes 611 and 621 and the pressing portion 625. The through holes 613, 623 of the arm 61 and the general opening rocker arm 62 are located between the rollers 614, 624 and the shaft holes 611, 621, and are located at the center points of the roller holes 614, 621 and the shaft holes 611, 621, respectively. Above the line A, the overall length of the intake rocker arm 6 can be suppressed, space is saved, and the cylinder head 33 can be prevented from overcoming the problem of insufficient space in a huge manner; please refer to Figure 5, 7, 8, and 9 for details. The through hole 613 of the high opening degree rocker arm 61 and the through hole 623 of the general opening degree rocker arm 62 communicate with each other to form a hydraulic cylinder 64, wherein the general opening degree rocker arm 62 has a through hole 623 and a high opening degree. The inner wall surface 613a of the through hole 613 of the rocker arm 61 is wear-resistant material The inner surface 613a of the wear-resistant material may be formed by electroplating or heat treatment or coating; the inner wall surface 613a of the wear-resistant material may also be made of bushings of different processes. The bushing can be combined with the through hole 613 of the high opening degree rocker arm 61 and the through hole 623 of the general opening degree rocker arm 62 in at least one manner of embedding, pressing, and projecting, thereby avoiding the progress made of light metal. The wear of the inner wall of the hydraulic cylinder 64 of the air rocker arm 6 can effectively prevent a large amount of oil pressure from leaking. In addition, the high-toughness material of the wear resistance can be formed only on the piston surface 643a.644a; the two ends of the hydraulic cylinder 64 are respectively A plug cover 641a.641b is disposed, and the plug cover 641a.641b protrudes from the hydraulic cylinder 64 with a protrusion 6411a.6411b. The hydraulic cylinder 64 is provided with a first piston 643 and a hydraulic pump The second piston 644, the first piston 643 and the second piston 644 have a wear-resistant high toughness material, and the wear-resistant high toughness material can be selected from tool steel, thereby avoiding the inner wall of the hydraulic cylinder 64 with the intake rocker arm. The abrasion can effectively prevent a large amount of oil pressure leakage; the hydraulic cylinder 64 is driven by the first and second driving oil passages 6 5, 66 and communicate with the oil control valve 4, thereby obtaining a power oil source, and the first side of the first piston 643 is provided with a first groove 6431 and a second groove 6432, thereby reducing the weight of the first piston 643 The first groove 6431 can be accommodated in the boss 6411a of the plug cover 641a, that is, the first groove 6431 is the plug cover 641a. The protrusions 6411a are matched, and the protrusions 6411b of the cover 641b are opposite to one side of the second piston 644. The first piston 643 and the second piston 644 are formed at a distance from the two ends of the hydraulic cylinder 64, so that the first and second driving oil passages 65 and 66 can enter the power oil source in the hydraulic cylinder 64, and the smooth flow can be smoothly performed. Pushing the first piston 643 and the second piston 644 by the bosses 6411a.6411b of the plug cover 641a.641b, the first piston 643 and the second piston 644 can be positioned at a predetermined position when actuating The movement of the first piston 643 and the second piston 644 in the hydraulic cylinder 64 can be ensured. The cylinder head 33 below the foot support portions 612 and 622 is provided with a foot support mechanism 337. The foot support mechanism 337 includes a foot. The support tube 3371, the one foot support spring 3372 and the foot support hole 3373 are formed by the foot support mechanism 337 for contacting the foot support portions 612 and 622, thereby ensuring the through hole 613 of the high opening degree rocker arm 61 and the general opening degree. The through hole 623 of the rocker arm 62 can be located at a set position. When the foot support mechanism 337 is subjected to an excessive abutting force of the foot support portions 612 and 622, the foot support hole 3373 can release the pressure in time to ensure the oil pressure. The mobility of the first piston 643 and the second piston 644 within the cylinder 64.
本發明於實施時,請參閱圖八、九所示,該搖臂軸63內設有用以隔開第一驅動油路65及第二驅動油路66的分隔壁631,其中,該分隔壁631是由該搖臂軸63一體延設,因此無需再額外裝設其他止擋分隔元件,可有效減少零件數量及免除組裝工程;請參閱圖二、三、八、九所示,藉由曲軸箱31內設置之機油泵311將機油送至一主供油道31 2,該主供油道312由曲軸箱31通過汽缸本體32後連通至設置於汽缸頭33之油控閥4,其中,該油控閥4再將機油送入於汽缸頭33的第一驅動油路65及第二驅動油路66內後再進入油壓缸64內,此外,請配合圖八、九參閱,藉由引擎3之控制中心ECU(圖示中未繪出)感測車輛的行車狀態後,如只需引擎為低速運轉狀態時,引擎3之控制中心ECU即可令油控閥4將機油由驅動油路65進入油壓缸64內,如圖八所示,藉由油壓力之作用來將第一活塞643與第二活塞644向高開度搖臂61方向推移,該機油由驅動油路65進入一般開度搖臂62之貫孔621後,由塞蓋641a之凸柱6411a與第一活塞643之導引進入第一活塞643的凹槽6431內,同時位於高開度搖臂61的機油會由驅動油路66流出,藉此來令第二活塞644是位於高開度搖臂61內的分離位置,並可藉由高開度搖臂61側的塞蓋6411b之凸柱6411b限制而定位於適當之位置,而第一活塞643則可被定位於一般開度搖臂62內的分離位置,此時高開度搖臂61及一般開度搖臂62是成各自作動模式,由於一般開度搖臂62其前端的按壓部625與進氣閥332相接觸,且一般開度搖臂62後方的滾子624是與凸輪軸336之短進氣凸輪3362(即低揚程凸輪)滾動接觸,因此、此時引擎3進氣汽閥332是為低揚開度狀態;另當引擎3因 行車狀態改變為高速運轉狀態時,引擎3之控制中心ECU即可令油控閥4將機油由驅動油路66進入油壓缸64內,如圖九所示,機油會由驅動油路66流入高開度搖臂6的貫孔613內,同時一般開度搖臂62之貫孔623內之機油流出,藉由機油油壓力之作用來將第一活塞643與第二活塞644向一般開度搖臂62方向推移,俾使第一活塞643是位於一般開度搖臂62內,並可藉由一般開度搖臂62的塞蓋641a之凸柱6411a限制,該第一活塞643與第二活塞644被定位於適當之位置,而使第二活塞644被定位於高開度搖臂61及一般開度搖臂62之間的結合位置,此時高開度搖臂61及一般開度搖臂62是成連動模式,由於高開度搖臂61後方的滾子614是與凸輪軸336之長進氣凸輪3361(即高揚程凸輪)滾動接觸,而一般開度搖臂62其前端的按壓部625與進氣閥332相接觸,因此一般開度搖臂62被高開度搖臂61所帶動,即會以長進氣凸輪3361(即高揚程凸輪)之揚程度將進氣閥332達成預定的引擎高速運轉狀態,藉此即可達成引擎3可變汽門揚程之目的;另外,亦可在該一般開度搖臂62之貫孔623內容置復歸彈簧642,該復歸彈簧642與第一活塞643接觸,藉此第一驅動油路65之油壓力無須設定得太高,即可推動活塞移動,如此做法可節省機油泵311的動能,亦避免僅單獨使用復歸彈簧 642造成彈力衰減後,無法使活塞643、644移動至預定位置的弊病;在實施上,該高開度搖臂61之軸孔611及一般開度搖臂62之軸孔621及排氣搖臂7軸孔712的孔壁為耐磨材質所成,該耐磨材質可選用高碳鋼;上述的孔壁可以電鍍或熱處理或披覆方式形成;該耐磨材質的孔壁也可以是由不同製程的襯套所成;該襯套可以嵌入、壓合、射包之至少一種方式與軸孔611、621、712相結合,因此能避免以輕金屬製成的進氣搖臂6及排氣搖臂7之軸孔611、621、712壁面與搖臂軸63、74的磨耗,可有效增進耐用性。When the present invention is implemented, as shown in FIG. 8 and FIG. 9, the rocker arm shaft 63 is provided with a partition wall 631 for separating the first driving oil passage 65 and the second driving oil passage 66. The partition wall 631 is disposed. It is integrally extended by the rocker shaft 63, so there is no need to additionally install other stop separating elements, which can effectively reduce the number of parts and eliminate the assembly work; please refer to the second, third, eighth and ninth, by the crankcase The oil pump 311 provided in 31 sends the oil to a main oil supply passage 31. 2, the main oil supply passage 312 is communicated from the crankcase 31 through the cylinder body 32 to the oil control valve 4 disposed in the cylinder head 33, wherein the oil control valve 4 then feeds the oil to the first drive of the cylinder head 33. After entering the oil passage 65 and the second driving oil passage 66, the hydraulic cylinder 64 is again inserted into the hydraulic cylinder 64. In addition, please refer to FIG. 8 and FIG. 9 to sense the vehicle by the control center ECU (not shown) of the engine 3. After the driving state, if only the engine is running at a low speed, the control center ECU of the engine 3 can cause the oil control valve 4 to enter the oil from the driving oil passage 65 into the hydraulic cylinder 64, as shown in FIG. The pressure acts to move the first piston 643 and the second piston 644 toward the high-opening rocker arm 61. After the oil enters the through hole 621 of the general opening rocker arm 62 from the driving oil passage 65, the convexity is blocked by the plug cover 641a. The guide 6411a and the first piston 643 are guided into the recess 6431 of the first piston 643, while the oil located at the high opening rocker 61 is discharged from the drive oil passage 66, thereby causing the second piston 644 to be at a high position. The separation position in the rocker arm 61 is opened and can be positioned by the protrusion 6411b of the plug cover 6411b on the side of the high opening rocker 61. Position, and the first piston 643 can be positioned in a separate position within the general opening rocker arm 62. At this time, the high opening degree rocker arm 61 and the general opening degree rocker arm 62 are in respective actuation modes due to the general opening degree rocker arm. The front end pressing portion 625 is in contact with the intake valve 332, and the roller 624 behind the general opening degree rocker arm 62 is in rolling contact with the short intake cam 3362 (ie, the low lift cam) of the cam shaft 336. When the engine 3 intake steam valve 332 is in a low lift state; When the driving state is changed to the high-speed running state, the control center ECU of the engine 3 can cause the oil control valve 4 to enter the oil from the driving oil passage 66 into the hydraulic cylinder 64. As shown in FIG. 9, the oil will flow from the driving oil passage 66. In the through hole 613 of the high opening degree rocker arm 6, while the oil in the through hole 623 of the general opening degree rocker arm 62 flows out, the first piston 643 and the second piston 644 are driven to the general opening by the action of the oil pressure of the oil. The rocker arm 62 is displaced in the direction, so that the first piston 643 is located in the general opening rocker arm 62, and can be restrained by the boss 6411a of the plug cover 641a of the general opening rocker arm 62, the first piston 643 and the second piston 643 The piston 644 is positioned at an appropriate position, so that the second piston 644 is positioned at a combined position between the high opening rocker arm 61 and the general opening rocker arm 62, at which time the high opening rocker arm 61 and the general opening degree are shaken. The arm 62 is in the interlocking mode, because the roller 614 behind the high opening rocker arm 61 is in rolling contact with the long intake cam 3361 (ie, the high lift cam) of the cam shaft 336, and the front end of the general opening rocker 62 is pressed. The portion 625 is in contact with the intake valve 332, so that the general opening degree rocker arm 62 is driven by the high opening degree rocker arm 61, that is, The degree of raising of the intake cam 3361 (ie, the high lift cam) causes the intake valve 332 to reach a predetermined high-speed engine running state, thereby achieving the purpose of the engine 3 variable valve head; and, in addition, the general opening degree The through hole 623 of the rocker arm 62 is disposed to return to the spring 642. The return spring 642 is in contact with the first piston 643, whereby the oil pressure of the first driving oil passage 65 does not need to be set too high to push the piston to move. Save the kinetic energy of the oil pump 311 and avoid using only the return spring alone 642 causes the piston 643, 644 to move to a predetermined position after the elastic force is attenuated; in practice, the shaft hole 611 of the high opening rocker arm 61 and the shaft hole 621 of the general opening rocker arm 62 and the exhaust rocker arm The hole wall of the 7-axis hole 712 is made of wear-resistant material, and the wear-resistant material can be made of high-carbon steel; the above-mentioned hole wall can be formed by electroplating or heat treatment or coating; the hole wall of the wear-resistant material can also be different The bushing of the process is formed; the bushing can be combined with the shaft holes 611, 621, and 712 in at least one manner of being embedded, pressed, and shot, thereby avoiding the intake rocker arm 6 and the exhaust shake made of light metal. The wear of the wall faces 611, 621, and 712 of the arm 7 and the rocker shafts 63 and 74 can effectively improve durability.
本發明之功效在於,藉由凸輪軸336上分別設有長進氣凸輪3361、短進氣凸輪3362及排氣凸輪3363,以及進氣閥搖臂6具有高開度搖臂61及一般開度搖臂62,再藉由該高開度搖臂61之貫孔613及一般開度搖臂62之貫孔623相連通而可形成一油壓缸64,於油壓缸64內設一可被油壓推動之第一活塞643與第二活塞644,藉此來令高開度搖臂61及一般開度搖臂62可成各自擺動或成連動模式,來使引擎3進汽門332的揚程改變,進而可使引擎3汽門閥332可變揚程之工程簡易化。由於該進氣閥搖臂6及排氣閥搖臂7為質量較輕的輕金屬合金材質所成的搖臂,其轉動慣量較小因此進氣閥332及排氣閥334的汽門彈簧 33a力量無需設定得太高,即能克服轉動慣量,故能減少引擎之動力消耗,有效避免動能的損失。再者,本案的一般開度搖臂62之貫孔623與高開度搖臂61之貫孔613的內壁面613a為耐磨材質,以及該第一活塞643與第二活塞644具耐磨之高韌性材質,因此能避免以輕金屬製成的進氣搖臂6之油壓缸64的內壁面613a與第一活塞643及第二活塞644的磨耗,可有效防止油壓大量洩漏,避免油壓不足導致活塞643、644無法被推送至預定位置的問題發生。以及,本案在搖臂軸63內一體延設有用以隔開第一驅動油路65及第二驅動油路66的分隔壁631,因此無需再額外裝設其他止擋分隔元件,可有效減少零件數量及免除額外的組裝工程。再者、藉由該高開度搖臂61及一般開度搖臂62之腳撐部612、622皆是位於軸孔611、621與按壓部625之間,該高開度搖臂61及一般開度搖臂62之貫孔613、623是位於滾子614、624與軸孔611、621之間,且是位於滾子614、624與軸孔611、621之中心點連線A之上方,進而可抑制進氣搖臂6的總體長度,節省佔用空間,避免汽缸頭33以巨大化的方式來克服空間不足的問題。以及,該長進氣凸輪3361、短進氣凸輪3362及排氣凸輪3363同軸設置於單一凸輪軸336上,可使汽缸頭33內的零件配置更緊湊,避免汽缸頭33巨 大化,有益於汽缸頭33在整車上的空間配置。The utility model has the advantages that the camshaft 336 is provided with a long intake cam 3361, a short intake cam 3362 and an exhaust cam 3363, respectively, and the intake valve rocker arm 6 has a high opening rocker arm 61 and a general opening degree. The rocker arm 62 is connected to the through hole 613 of the high opening degree rocker arm 61 and the through hole 623 of the general opening degree rocker arm 62 to form a hydraulic cylinder 64, and a hydraulic cylinder 64 is provided in the hydraulic cylinder 64. The hydraulic pressure pushes the first piston 643 and the second piston 644, so that the high opening rocker arm 61 and the general opening rocker arm 62 can be oscillated or interlocked to make the head of the engine 3 into the valve 332. The change can further simplify the engineering of the variable lift of the engine 3 valve 332. Since the intake valve rocker arm 6 and the exhaust valve rocker arm 7 are rocker arms made of light weight light metal alloy material, the moment of inertia is small, so the valve springs of the intake valve 332 and the exhaust valve 334 The 33a force does not need to be set too high, that is, it can overcome the moment of inertia, so it can reduce the power consumption of the engine and effectively avoid the loss of kinetic energy. Furthermore, the inner hole surface 623 of the general opening degree rocker arm 62 and the inner wall surface 613a of the through hole 613 of the high opening degree rocker arm 61 are wear-resistant materials, and the first piston 643 and the second piston 644 are wear-resistant. The high-toughness material can avoid the wear of the inner wall surface 613a of the hydraulic cylinder 64 of the intake rocker arm 6 made of light metal and the first piston 643 and the second piston 644, thereby effectively preventing a large amount of oil pressure leakage and avoiding oil pressure. The problem that the pistons 643, 644 cannot be pushed to the predetermined position occurs. Moreover, in the present invention, the partition wall 631 for partitioning the first driving oil passage 65 and the second driving oil passage 66 is integrally extended in the rocker shaft 63, so that it is unnecessary to additionally install another stopper separating member, thereby effectively reducing the number of parts. Quantity and exemption from additional assembly work. Furthermore, the foot support portions 612 and 622 of the high opening degree rocker arm 61 and the general opening degree rocker arm 62 are located between the shaft holes 611 and 621 and the pressing portion 625. The high opening degree rocker arm 61 and the general The through holes 613, 623 of the opening rocker arm 62 are located between the rollers 614, 624 and the shaft holes 611, 621, and are located above the center point connecting line A of the rollers 614, 624 and the shaft holes 611, 621. Further, the overall length of the intake rocker arm 6 can be suppressed, space is saved, and the cylinder head 33 can be prevented from overcoming the problem of insufficient space in a huge manner. And the long intake cam 3361, the short intake cam 3362 and the exhaust cam 3363 are coaxially disposed on the single cam shaft 336, so that the parts in the cylinder head 33 can be more compactly arranged, and the cylinder head 33 is prevented from being huge. The enlargement is beneficial to the space configuration of the cylinder head 33 on the whole vehicle.
綜上所述,本發明藉由上述之構造,的確能改善習用之缺失,進而達成所訴求之目的與功效,已符合發明專利所述之實用性、新穎性,以及進步性之要件,爰依法提出發明專利之申請。In summary, the present invention, by the above configuration, can indeed improve the lack of use, and thereby achieve the purpose and effect of the claim, has met the practicality, novelty, and progressive requirements described in the invention patent, An application for an invention patent is filed.
惟以上所述者,僅為本發明之較佳實施例而已,當不能以此限定本發明實施之範圍,即大凡依本發明申請專利範圍及發明說明內容所作之簡單的等效變化與修飾,皆仍屬本發明專利涵蓋之範圍內。The above is only the preferred embodiment of the present invention, and the scope of the invention is not limited thereto, that is, the simple equivalent changes and modifications made by the scope of the invention and the description of the invention are All remain within the scope of the invention patent.
1...引擎1. . . engine
1a...汽缸頭1a. . . Cylinder head
2...汽門閥2. . . Valve valve
21...高開度搖臂twenty one. . . High opening rocker
22...一般開度搖臂twenty two. . . General opening rocker
23...彈簧twenty three. . . spring
3...引擎3. . . engine
31...曲軸箱31. . . Crankcase
311...機油泵311. . . Oil pump
312...主供油道312. . . Main oil supply channel
32...汽缸本體32. . . Cylinder body
33...汽缸頭33. . . Cylinder head
331...進氣埠331. . . Intake
332...進氣閥332. . . Intake valve
333...排氣埠333. . . Exhaust gas
334...排氣閥334. . . Vent
335...凸輪軸座335. . . Camshaft seat
336...凸輪軸336. . . Camshaft
3361...長進氣凸輪3361. . . Long intake cam
3362...短進氣凸輪3362. . . Short intake cam
3363...排氣凸輪3363. . . Exhaust cam
337...腳撐機構337. . . Foot support mechanism
3371...腳撐筒3371. . . Foot support
3372...腳撐彈簧3372. . . Foot spring
3373...腳撐孔3373. . . Foot support
33a...汽門彈簧33a. . . Valve spring
4...油控閥4. . . Oil control valve
41...油路通道41. . . Oil passage
5...正時鏈條5. . . Timing chain
51...正時鏈條張緊器51. . . Timing chain tensioner
6...進氣閥搖臂6. . . Intake valve rocker
61...高開度搖臂61. . . High opening rocker
611...軸孔611. . . Shaft hole
612...腳撐部612. . . Foot support
613...貫孔613. . . Through hole
613a...內壁面613a. . . Inner wall
614...滾子614. . . Roller
62...一般開度搖臂62. . . General opening rocker
621...軸孔621. . . Shaft hole
622...腳撐部622. . . Foot support
623...貫孔623. . . Through hole
624...滾子624. . . Roller
625...按壓部625. . . Pressing part
6251...間隙調整件6251. . . Gap adjustment
63...搖臂軸63. . . Rocker shaft
631...分隔壁631. . . Partition wall
64...油壓缸64. . . Hydraulic cylinder
641a‧641b...塞蓋641a‧641b. . . Plug cover
6411a‧6411b...凸柱6411a‧6411b. . . Tab
642...復歸彈簧642. . . Return spring
643...第一活塞643. . . First piston
643a...活塞表面643a. . . Piston surface
6431...第一凹槽6431. . . First groove
6432...第二凹槽6432. . . Second groove
644...第二活塞644. . . Second piston
644a...活塞表面644a. . . Piston surface
65...第一驅動油路65. . . First drive oil circuit
66...第二驅動油路66. . . Second drive oil circuit
7...排氣閥搖臂7. . . Exhaust valve rocker
71...按壓部71. . . Pressing part
711...間隙調整件711. . . Gap adjustment
712...軸孔712. . . Shaft hole
72...滾子72. . . Roller
73...管套73. . . Socket
74...搖臂軸74. . . Rocker shaft
A...滾子與軸孔中心點連線A. . . The roller is connected to the center point of the shaft hole
圖一是習知汽缸頭之示意圖。Figure 1 is a schematic view of a conventional cylinder head.
圖二是本發明引擎汽缸頭之示意圖。Figure 2 is a schematic illustration of the engine cylinder head of the present invention.
圖三是本發明汽缸頭部份剖視之示意圖。Figure 3 is a schematic cross-sectional view of a portion of the cylinder head of the present invention.
圖四是本發明凸輪軸之外觀示意圖。Figure 4 is a schematic view showing the appearance of the cam shaft of the present invention.
圖五是本發明汽缸頭俯視之示意圖。Figure 5 is a schematic plan view of the cylinder head of the present invention.
圖六是本發明排氣閥搖臂之示意圖。Figure 6 is a schematic view of the rocker arm of the exhaust valve of the present invention.
圖七是本發明進氣閥搖臂之分解示意圖。Figure 7 is a schematic exploded view of the rocker arm of the intake valve of the present invention.
圖八、九是本發明之實施例。Figures 8 and 9 are embodiments of the invention.
33...汽缸頭33. . . Cylinder head
336...凸輪軸336. . . Camshaft
3361...長進氣凸輪3361. . . Long intake cam
3362...短進氣凸輪3362. . . Short intake cam
3363...排氣凸輪3363. . . Exhaust cam
6...進氣閥搖臂6. . . Intake valve rocker
61...高開度搖臂61. . . High opening rocker
613...貫孔613. . . Through hole
613a...內壁面613a. . . Inner wall
614...滾子614. . . Roller
62...一般開度搖臂62. . . General opening rocker
622...腳撐部622. . . Foot support
623...貫孔623. . . Through hole
624...滾子624. . . Roller
625...按壓部625. . . Pressing part
63...搖臂軸63. . . Rocker shaft
64...油壓缸64. . . Hydraulic cylinder
641a‧641b...塞蓋641a‧641b. . . Plug cover
6411a‧6411b...凸柱6411a‧6411b. . . Tab
642...彈簧642. . . spring
643...第一活塞643. . . First piston
6431...第一凹槽6431. . . First groove
6432...第二凹槽6432. . . Second groove
644...第二活塞644. . . Second piston
65、66...第一、第二驅動油路65, 66. . . First and second driving oil passages
7...排氣閥搖臂7. . . Exhaust valve rocker
71...按壓部71. . . Pressing part
72...滾子72. . . Roller
73...管套73. . . Socket
Claims (3)
Priority Applications (1)
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TW100131684A TWI479076B (en) | 2011-09-02 | 2011-09-02 | Engine variable valve lift mechanism |
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TW100131684A TWI479076B (en) | 2011-09-02 | 2011-09-02 | Engine variable valve lift mechanism |
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TW201311994A TW201311994A (en) | 2013-03-16 |
TWI479076B true TWI479076B (en) | 2015-04-01 |
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TW100131684A TWI479076B (en) | 2011-09-02 | 2011-09-02 | Engine variable valve lift mechanism |
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CN106401682B (en) * | 2015-07-31 | 2019-11-08 | 光阳工业股份有限公司 | Rocker arm auxiliary unit for engine cylinder head |
Citations (4)
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US4768467A (en) * | 1986-01-23 | 1988-09-06 | Fuji Jukogyo Kabushiki Kaisha | Valve operating system for an automotive engine |
JP2003049622A (en) * | 2001-08-03 | 2003-02-21 | Honda Motor Co Ltd | Rocker arm having changeover mechanism, and its manufacturing method |
JP2004019616A (en) * | 2002-06-19 | 2004-01-22 | Honda Motor Co Ltd | Hydraulic pressure control unit of valve mechanism |
TW200914714A (en) * | 2007-09-20 | 2009-04-01 | Sanyang Industry Co Ltd | Switch structure of variable valve lift mechanism |
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2011
- 2011-09-02 TW TW100131684A patent/TWI479076B/en not_active IP Right Cessation
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US4768467A (en) * | 1986-01-23 | 1988-09-06 | Fuji Jukogyo Kabushiki Kaisha | Valve operating system for an automotive engine |
JP2003049622A (en) * | 2001-08-03 | 2003-02-21 | Honda Motor Co Ltd | Rocker arm having changeover mechanism, and its manufacturing method |
JP2004019616A (en) * | 2002-06-19 | 2004-01-22 | Honda Motor Co Ltd | Hydraulic pressure control unit of valve mechanism |
TW200914714A (en) * | 2007-09-20 | 2009-04-01 | Sanyang Industry Co Ltd | Switch structure of variable valve lift mechanism |
Non-Patent Citations (1)
Title |
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Akima, K., Seko, K., Taga, W., Torii, K. et al., "Development of New Low Fuel Consumption 1.8L i-VTEC Gasoline Engine with Delayed Intake Valve Closing." SAE Technical Paper 2006-01-0192, 2006 * |
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