200914714 九、發明說明： 【發明所屬之技術領域】 本發明係關於-種機構之切換結構，尤指—種適用於 可變閥揚程機構之切換結構，以使進、排氣闕門對應切換 5於引擎高轉時的高開度、及低轉速時的低開度。 【先前技術】 傳統習知之内燃機已經使用有多閥門機構，並以複數 支搖臂分別控制不同進/排氣閥門之開閉時序。例如第今圖 10顯示咼速搖臂8 一端抵靠於高速凸輪80上，低速搖臂9 一端 抵靠於低速凸輪90上，藉由不同形狀之高、低速凸輪8〇,9〇 以分別驅動二支閥門連桿81,91之閥揚程動作。 由於高、低速凸輪80,90之凸輪形狀一旦固定，其所職 司高、低速搖臂8,9之閥揚程動作即被固定。因此，為能因 15 應高低轉速時不同進氣（或棑氣）需求，習知乃藉由一種 切換結構適時地將高、低速搖臂8,9予以連結或解除連結， 〇 藉以使二支閥門連桿81，91形成可變閥揚程機構。 第10圖顯示，該習知切換結構係於高速搖臂8内部設一 彈簧82以推抵一帽蓋83，低速搖臂9内部滑設一結合塊93。 2〇 如圖所示結合塊93長度約等於低速搖臂9寬度，因此油壓油 路92未加壓時’該結合塊93受對面彈簧82與帽蓋83之頂抵 而内縮至底部，形成高、低速搖臂8,9未連結狀態，故可依 其個別之高、低速凸輪80,90形狀分別驅動以作閥揚程動 作，適用於低轉速場合。 200914714 第11圖顯示高、低速搖臂8,9彼此連結狀態，其係由油 壓油路92加壓以推動結合塊％向前，並克服彈簧82與帽蓋 83之頂抵彈力，因此結合塊93插入高速搖臂8而加以連結， 故而高、低速搖臂8,9均依據凸輪形狀較高之高速凸輪8〇以 同步驅動作閥揚程動作’適用於較大進氣（或排氣）需求 之而轉速場合。 然而，習知當油壓油路92開始加壓初期，由於結合塊 93的周緣表面與油廢室94之壁面所相對產生的磨擦力，及 、口 口塊93其本身之慣性質量較大導致油壓升壓反應較慢， 再加上此時面、低速搖臂8,9相對運動十分快速，導致結合 塊93插入高速搖臂8動作不迅速確實，致使結合塊％經常跳 脫，並產生異音，均非十分理想。200914714 IX. Description of the Invention: [Technical Field] The present invention relates to a switching structure of a mechanism, and more particularly to a switching structure suitable for a variable valve head mechanism, so that the inlet and exhaust valves correspond to each other. High opening at high engine speed and low opening at low speed. [Prior Art] The conventional internal combustion engine has used a multi-valve mechanism, and controls the opening and closing timing of different intake/exhaust valves by a plurality of rocker arms. For example, Fig. 10 shows that one end of the idle rocker arm 8 abuts against the high speed cam 80, and one end of the low speed rocker arm 9 abuts against the low speed cam 90, and is driven by different shapes of high and low speed cams 8 〇, 9 分别 respectively. The valve head movement of the two valve connecting rods 81, 91. Since the cam shapes of the high and low speed cams 80, 90 are fixed, the valve head movements of the high and low speed rocker arms 8, 9 are fixed. Therefore, in order to be able to respond to different intake (or helium) requirements at high and low speeds, it is customary to connect or uncouple the high and low speed rocker arms 8, 9 in a timely manner by means of a switching structure. The valve links 81, 91 form a variable valve lift mechanism. Fig. 10 shows that the conventional switching structure is provided with a spring 82 inside the high speed rocker arm 8 for pushing against a cap 83, and a coupling block 93 is slid inside the low speed rocker arm 9. 2, as shown, the length of the joint block 93 is approximately equal to the width of the low speed rocker arm 9, so that when the oil pressure oil passage 92 is not pressurized, the joint block 93 is retracted to the bottom by the abutment of the opposite spring 82 and the cap 83. The high and low speed rocker arms 8 and 9 are not connected, so they can be driven separately for their valve head movement according to their individual high and low speed cams 80, 90, which is suitable for low speed applications. 200914714 Fig. 11 shows the state in which the high and low speed rocker arms 8, 9 are connected to each other, which is pressurized by the oil pressure oil passage 92 to push the joint block % forward, and overcomes the spring force of the spring 82 and the cap 83, thus combining The block 93 is inserted into the high-speed rocker arm 8 and connected. Therefore, the high- and low-speed rocker arms 8 and 9 are all driven by the high-speed cam 8〇 with a high cam shape for the valve lift action to apply to the larger intake (or exhaust). Demand and speed occasions. However, it is known that when the hydraulic oil passage 92 starts to pressurize, the frictional force generated by the peripheral surface of the joint block 93 and the wall surface of the oil waste chamber 94, and the inertial mass of the orifice block 93 itself are large. The oil pressure boosting reaction is slower, and the relative movement of the low-speed rocker arms 8,9 at this time is very fast, so that the action of the joint block 93 inserted into the high-speed rocker arm 8 is not performed quickly, so that the joint block% often jumps and generates The abnormal sound is not very ideal.
軸呈未連結狀態時， 凹槽，當第一搖臂、 一 狀態時，係… 臂別相應於樞 …3由油路自油壓室洩放油壓，使彈 200914714 性儿件所提供的彈性預力得以推動結合塊、及活塞，使其 分別容設於第―、第二容室内。相對地，當第一、第二搖 ’相應於樞軸呈連結狀態_，係藉由油路供油使油壓室產 生一恆壓，將結合塊推出第一容室外而形成。 如此，即可使第一搖臂、及第二搖臂於連結狀態以對 應引擎南速運轉時，進、排氣油門開啟的高開度；或使第 一搖臂、及第二搖臂於未連結狀態以對應引擎低速運轉 時’進、排氣油門開啟的低開度。When the shaft is in the unconnected state, the groove, when the first rocker arm, a state, is... the arm corresponds to the pivot... 3 is drained from the oil pressure chamber by the oil passage, so that the spring 200914714 The elastic pre-force pushes the coupling block and the piston to be accommodated in the first and second chambers, respectively. In contrast, when the first and second shakes are in a connected state corresponding to the pivot, the oil pressure is generated by the oil passage to generate a constant pressure, and the joint block is pushed out of the first chamber. In this way, the first rocker arm and the second rocker arm can be opened in a connected state to correspond to the engine opening at a south speed, and the intake and exhaust throttles are opened at a high opening; or the first rocker arm and the second rocker arm are The unconnected state is the low opening of the intake and exhaust throttle opening when the engine is running at a low speed.
10 15 其中’複數軸向凹槽可開設於結合塊之外壁；或複數 軸向凹槽亦可開設於第一容室之内壁。而且，複數軸向凹 槽可為等間距設置。同時’結合塊其軸心凹設有一軸向槽 孔’用以減輕結合塊的重量。此可變閥揚程機構之切換結 構的油壓控制包括一引擎轉速感測器、一控制器、及一電 磁閥。引擎轉速感測器與控制器電性連結，並且控制器再 與電磁閥電性連結’控制器接收引擎轉速感測器之訊號進 而控制該油壓電磁閥開啟或關閉，用以控制油路的油量進 出。 藉由上述之油壓控制機制可在引擎高轉速時開啟電磁 閥以提供油壓促使結合塊連結第一搖臂、及第二搖臂而帶 動進、排氣油門的高開合度，並在引擎低轉速時關閉電磁 閥以排出油壓使結合塊分離第一搖臂、及第二搖臂之間， 而以搖臂帶動進、排氣油門的低開合度。 【實施方式】 20 200914714 p請同時參閱，、圖2、及圖3β 係本發明第一較佳 實施例之剖視圖，其用以顯示本實施例之元件位於引擎中 之相對位置關係、、圖2係、本發明第—較佳實施例之分解圓、 及圖3係本發明第—較佳實施例結合塊之放大圖。 5 &圖所不’本實施例為—種可變閥揚程機構之切換結 ，’主要係於—樞軸17上同軸插設有相互比鄰之一第一^ f卜及一第二搖臂2 ’ 一凸輪組3包括有一低速凸輪η、一 @速凸輪32、及—排氣凸輪33 4中’低速凸輪31相應接 〇 冑於搖臂1的接觸面112,使得第-搖臂！帶動—進氣閥 10門連桿5進而開、閉進氣閥門，於本例中，進氣閥門連桿5 包括一左閥門連桿51、及一右閥門連桿52，其由第一搖臂i 同時帶動。高速凸輪32相應接觸於第二搖臂2的接觸面 222，由於高速凸輪32高於低速凸輪31之揚程，因此第二搖 臂2广擺動弧度大於第一搖臂i。排氣凸輪33相應接觸於一 15排氣搖臂4之接觸面42 ’使得排氣搖臂4帶動一排氣閥門連 桿6進而開、閉排氣閥門。 〇 圖2所示，第一、第一搖臂1，2於相鄰内側分別凹設有 對應之一第 第二容室im第---第二㈣ 孔16,22,第一容室11内部容設有一結合塊12,而第二容室 20 21内部容設有一活塞13，其與第二容室21底部之間組設有 彈〖生元件15，同時活塞13也凹設有一容室131以容設此彈 性元件15，於本例中，彈性元件15係指一壓縮彈簧。又， 第一谷室11其連通至一油路14，此油路14凹設於第一樞接 孔丨6内’而棍軸17樞設於第一、第二樞接孔16,22之間，因 200914714 此，油路14得以與樞軸1 7的樞軸油路丨73相通，再連通至外 部（圖未示）。 5 Ο 10 15 Ο 如圖3所示，結合塊12其外壁開設有複數個軸向凹槽 121，此軸向凹槽121係為等間距設置，同時為了減輕結合 塊12的重量，其於軸心處凹設有一軸向凹槽，如此，除 了可以減少結合塊12與第一容室11之接觸面間之磨擦力外 更可減輕結合塊12之重量。因此，結合塊12可更迅速的滑 移於第-容室11與第二容室21之間’以改善習知之結合塊 插入高速搖臂動作不迅速確實的問題。 請參閱圖4,其係本發明第一較佳實施例之油壓控制系 統之示意圖。如圖所示此油壓控制系統包括一引擎轉速感 測益70、-控制器71、_電磁閥72。引擎轉速感測器顺 控制器71電性連結，而且控制器71再與電磁閥72電性連 結，控制器71接收引擎轉速感測器7〇之訊號進而控制油壓 電磁閥72開啟或關閉。例如，當引擎進入高轉速運轉時， 引擎轉速感測器70發送一高轉速指令給控制器7丨，之後， 控制器71送出一控制訊號命令電磁閥72開啟，以使機油73 得以經由電磁閥72而流入油路14;反之，當引擎進入低轉 速運轉時’引擎轉速感測H 7〇發送—低轉速指令給控制器 71之後控制器71送出一控制訊號命令電磁閥72關閉， 以使機油73得以經由電磁閥72而流出油路14。 請參閱圖5-併參閱圖2，其係本發明第一較佳實施例 未連結狀態之立體圖。當引擎進入低轉速運轉時，藉由油 路14使油壓室U1自樞軸油路173浅放，再經由彈性^件15 20 200914714 所提供的彈性預力得以推動結合塊12、及活塞13，使其分 別容設於第-、第二容室U，21内。此時，第-搖臂卜^ 二搖臂2分別相應於樞軸17呈未連結狀態，因此，第一搖臂 5 10 1、及第二搖臂2由低速凸輪31與高速凸輪32分別控制其揚 程，使得進氣閥門連桿5呈低開合度。 請參閱圖6並請一併參閲圖2及圖4,其係本發明第一較 佳實施例連結狀態之立體圖’如圖所示，#引擎進入高轉 速運轉時，油壓自樞軸油路173進人，經由油路_使油壓 室111充滿機油73以產生-恆壓’此恆壓可克服使彈性元件 15所提供的彈性預力而將結合塊12推出第一容室丨丨外，而 使第一、第二搖臂丨，2相應於樞軸17呈連結狀態，此時，第 一搖臂1、及第二搖臂2由高速凸輪32控制其揚程，使得進 氣閥門連桿5呈高開合度。 請參閲圖7,其係本發明第二較佳實施例部份元件之立 體圖’其與第-較佳實施例之結構大致相同，唯不同處在 於複數軸向凹槽113係等間距地開設於第一容室u之内 ) 壁，且以一表面平滑之結合塊23替代上一實例之結合塊Η。 請參閲圖8，其係本發明第三較佳實施例之立體圖。其 結構與第一較佳實施例大致相同，唯不同處在於第一搖臂 20 19係連動一左閥門連桿丨91 ’第二搖臂18係連動一右閥門連 桿 181。 上述實施例僅係為了方便說明而舉例而已，本發明所 主張之權利範圍自應以申請專利範圍所述為準，而非僅限 於上述實施例。 ^ 200914714 【圖式簡單說明】 圖1係本發明第一較佳實施例之剖視圖。 圖2係本發明第一較佳實施例之分解圖。 5圖3係本發明第一較佳實施例結合塊之放大圖。 圖4係本發明第一較佳實施例之油壓控制系統之示意圖。 圖5係本發明第一較佳實施例未連結狀態之立體圖。 圖6係本發明第一較佳實施例連結狀態之立體圖。 圖7係本發明第二較佳實施例部份元件之立體圖。 10圖8係本發明第三較佳實施例之立體圖。 圖9係習知之剖視圖。 圖10係習知之未連結狀態之剖視圖。 圖Π係習知之連結狀態之剖視圖。 15 【主要元件符號說明】 第一搖臂1，19 接觸面 112,222,42 軸向槽孔122,231 油路14 樞軸17 第二容室21 低速凸輪31 排氣搖臂4 右閥門連桿52，181 第一容室11 軸向凹槽113,121 活塞13 彈性元件15,24 樞軸油路173 第一植接孔2 2 高速凸輪32 進氣閥門連桿5 排氣閥門連桿6 油壓室111，94 結合塊12,23,93 容室131 第一樞接孔16 第二搖臂2,18 凸輪組3 排氣凸輪33 左閥門連桿51，191 引擎轉速感測器70 200914714 控制器71 電磁閥72 機油73 兩速搖臂8 高速凸輪80 閥門連桿81,91 彈簧82 帽蓋83 低速搖臂9 低速凸輪90 油壓油路9210 15 wherein 'the plurality of axial grooves may be formed on the outer wall of the joint block; or the plurality of axial grooves may be formed on the inner wall of the first chamber. Moreover, the plurality of axial grooves can be equally spaced. At the same time, the 'joint block has an axial groove recessed in its axial recess to reduce the weight of the joint block. The oil pressure control of the switching structure of the variable valve lift mechanism includes an engine speed sensor, a controller, and an electromagnetic valve. The engine speed sensor is electrically connected to the controller, and the controller is electrically connected to the solenoid valve, and the controller receives the signal of the engine speed sensor to control the oil pressure solenoid valve to be turned on or off to control the oil passage. The amount of oil in and out. By the above-mentioned oil pressure control mechanism, the solenoid valve can be opened at a high engine speed to provide oil pressure to cause the coupling block to connect the first rocker arm and the second rocker arm to drive the high opening and closing of the intake and exhaust throttles, and in the engine When the engine speed is low, the solenoid valve is closed to discharge the oil pressure, so that the coupling block is separated between the first rocker arm and the second rocker arm, and the rocker arm drives the low opening degree of the intake and exhaust throttles. [Embodiment] 20 200914714 p Please also refer to, FIG. 2 and FIG. 3β are cross-sectional views of the first preferred embodiment of the present invention, which are used to show the relative positional relationship of the components of the embodiment in the engine, FIG. The exploded circle of the first preferred embodiment of the present invention, and FIG. 3 is an enlarged view of the combined block of the first preferred embodiment of the present invention. 5 & Figure is not a 'switching junction of a variable valve head mechanism, 'mainly on the pivot 17 is coaxially inserted with one of the first adjacent to each other and a second rocker arm 2' A cam group 3 includes a low speed cam η, a @ speed cam 32, and an 'exhaust cam 33'. The low speed cam 31 is correspondingly connected to the contact surface 112 of the rocker arm 1, so that the first rocker arm! The intake valve 10 door connecting rod 5 further opens and closes the intake valve. In this example, the intake valve connecting rod 5 includes a left valve connecting rod 51 and a right valve connecting rod 52, which are firstly shaken Arm i is driven at the same time. The high speed cam 32 is in contact with the contact surface 222 of the second rocker arm 2, and since the high speed cam 32 is higher than the head of the low speed cam 31, the second rocker arm 2 has a larger swinging arc than the first rocker arm i. The exhaust cam 33 is in contact with a contact surface 42' of a 15 exhaust rocker arm 4 such that the exhaust rocker arm 4 drives an exhaust valve link 6 to open and close the exhaust valve. As shown in FIG. 2, the first and first rocker arms 1, 2 are respectively recessed with adjacent ones of the second chambers im---second (four) holes 16, 22, and the first chamber 11 A piston block 13 is disposed inside the second chamber 20 21 , and a piston 13 is disposed between the bottom of the second chamber 21 and the bottom portion of the second chamber 21 . To accommodate the elastic member 15, in this example, the elastic member 15 is referred to as a compression spring. Moreover, the first trough 11 is connected to an oil passage 14 which is recessed in the first pivot hole 6 and the rod shaft 17 is pivoted to the first and second pivot holes 16, 22 Between, as in 200914714, the oil passage 14 is in communication with the pivot oil passage 73 of the pivot shaft 17 and is connected to the outside (not shown). 5 Ο 10 15 Ο As shown in FIG. 3, the outer wall of the joint block 12 is provided with a plurality of axial grooves 121 which are arranged at equal intervals, and at the same time, in order to reduce the weight of the joint block 12, The axial recess is provided with an axial groove, so that the weight of the joint block 12 can be reduced in addition to reducing the friction between the joint surface of the joint block 12 and the first chamber 11. Therefore, the joint block 12 can be more smoothly slid between the first chamber 11 and the second chamber 21 to improve the problem that the conventional joint block is not quickly and accurately inserted into the high-speed rocker arm. Referring to Figure 4, there is shown a schematic view of a hydraulic control system in accordance with a first preferred embodiment of the present invention. As shown, the hydraulic control system includes an engine speed sensing benefit 70, a controller 71, and a solenoid valve 72. The engine speed sensor is electrically connected to the controller 71, and the controller 71 is electrically connected to the solenoid valve 72. The controller 71 receives the signal of the engine speed sensor 7 to control the oil pressure solenoid valve 72 to open or close. For example, when the engine enters high speed operation, the engine speed sensor 70 sends a high speed command to the controller 7A. Thereafter, the controller 71 sends a control signal to command the solenoid valve 72 to open, so that the oil 73 can be passed through the solenoid valve. 72 flows into the oil passage 14; conversely, when the engine enters the low speed operation, the engine speed sensing H 7 is sent - the low speed command is sent to the controller 71, and the controller 71 sends a control signal to command the solenoid valve 72 to close, so that the oil 73 is able to flow out of the oil passage 14 via the solenoid valve 72. Referring to Figure 5 - and to Figure 2, there is shown a perspective view of the uncoupled state of the first preferred embodiment of the present invention. When the engine enters the low-speed operation, the oil pressure chamber U1 is shallowed from the pivot oil passage 173 by the oil passage 14, and the coupling block 12 and the piston 13 are pushed by the elastic pre-force provided by the elastic member 15 20 200914714. , respectively, is accommodated in the first and second chambers U, 21. At this time, the first rocker arm 2 and the second rocker arm 2 are respectively unconnected with respect to the pivot shaft 17, and therefore, the first rocker arm 5 10 1 and the second rocker arm 2 are respectively controlled by the low speed cam 31 and the high speed cam 32. Its head makes the intake valve connecting rod 5 have a low opening degree. Please refer to FIG. 6 and FIG. 2 together, which is a perspective view of the connected state of the first preferred embodiment of the present invention. As shown in the figure, when the engine enters a high-speed operation, the hydraulic pressure is self-pivoting oil. The road 173 enters, and the oil pressure chamber 111 is filled with the oil 73 through the oil passage _ to generate a constant pressure. This constant pressure overcomes the elastic preload force provided by the elastic member 15 to push the coupling block 12 out of the first chamber. In addition, the first and second rocker arms 2 are connected to each other corresponding to the pivot 17, and at this time, the first rocker arm 1 and the second rocker arm 2 are controlled by the high speed cam 32 to make the head thereof, so that the intake valve The connecting rod 5 has a high opening degree. Please refer to FIG. 7 , which is a perspective view of some components of the second preferred embodiment of the present invention, which is substantially the same as the structure of the first preferred embodiment, except that the plurality of axial grooves 113 are equally spaced. The wall is inside the first chamber u, and the bonding block 23 of the previous example is replaced by a bonding block 23 having a smooth surface. Please refer to FIG. 8, which is a perspective view of a third preferred embodiment of the present invention. The structure is substantially the same as that of the first preferred embodiment except that the first rocker arm 20 19 is interlocked with a left valve link 丨 91 ′ and the second rocker arm 18 is coupled to a right valve link 181. The above-described embodiments are merely examples for the convenience of the description, and the scope of the claims is intended to be limited by the scope of the claims. ^ 200914714 BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a cross-sectional view showing a first preferred embodiment of the present invention. Figure 2 is an exploded view of a first preferred embodiment of the present invention. 5 is an enlarged view of a bonding block of a first preferred embodiment of the present invention. Figure 4 is a schematic illustration of a hydraulic control system in accordance with a first preferred embodiment of the present invention. Figure 5 is a perspective view showing the unconnected state of the first preferred embodiment of the present invention. Figure 6 is a perspective view showing the connected state of the first preferred embodiment of the present invention. Figure 7 is a perspective view of some of the components of the second preferred embodiment of the present invention. Figure 8 is a perspective view of a third preferred embodiment of the present invention. Figure 9 is a cross-sectional view of a conventional one. Figure 10 is a cross-sectional view showing a conventional unconnected state. The figure is a cross-sectional view of the connected state of the prior art. 15 [Description of main components] First rocker arm 1,19 Contact surface 112,222,42 Axial slot 122,231 Oil circuit 14 Pivot 17 Second chamber 21 Low speed cam 31 Exhaust rocker arm 4 Right valve link 52,181 First chamber 11 axial groove 113, 121 piston 13 elastic member 15, 24 pivot oil passage 173 first planting hole 2 2 high speed cam 32 intake valve connecting rod 5 exhaust valve connecting rod 6 hydraulic chamber 111, 94 Combination block 12, 23, 93 chamber 131 first pivot hole 16 second rocker arm 2, 18 cam group 3 exhaust cam 33 left valve link 51, 191 engine speed sensor 70 200914714 controller 71 solenoid valve 72 Oil 73 Two-speed rocker arm 8 High-speed cam 80 Valve connecting rod 81, 91 Spring 82 Cap 83 Low-speed rocker arm 9 Low-speed cam 90 Hydraulic oil line 92
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