131044⑦pifdoc 九、發明說明： 【發明所屬之技術領域】 、曰本發明關於-種用於控制溫水、冷水 電動閥(motor valve)或風門 致動态。 d寺的電動 【先前技術】 電動流或風_度進行調整的 訊號進行.、減速齒輪=達使==邹的驅動 至作為控制對象的閥門或風門等的=逮 作角檢測機構，檢測上述旋轉麵當前卫作 从及工 ⑽扣）（或者動作範圍）（例如，參 （per_g :乍為電動致動器的減速齒輪機構，眾所上 多段疊層多個正齒輪而構成者，或者使用揭示= ^文獻1中純太陽齒輪（sungea小行星齒輪 回輪（annular gear)的行星齒輪機 1 專利文獻！所揭示的電動致動器，將藉由多 =陽齒輪、行錢輪及錢基座（Geafbase)= 輪=而構成的行星齒輪機構收納於内壁中形成有内齒車^ ^ :内，將上迷套管裝人致動器的箱體内，並藉 j機構而使驅動馬達的旋轉減速。箱體包括收納驅動馬 體、以及收納套管的下謎，上箱體與下箱體之 由^板隔開，使軸騎___ 的仃星齒輪單元的太陽齒輪。> 取 I31_r 又，構成如下，藉由減速齒輪機構而使驅動馬達的旋 轉減速旅傳遞至閥門的轉動軸（旋轉軸），但該閥門的轉動 軸連結於行星齒輪機構的最後段的齒輪基座，並經由傳動 齒輪將該軸的旋轉進而傳遞至桿(rod)，且藉由包含凸輪與 限制開關（limit switch )的工作角檢測機構而檢測該桿的 旋轉，由此間接地檢測上述轉動軸的工作角，且根據工作 角檢測的偵測訊號而驅動控制上述驅動馬達。 【專利文獻1】日本專利特開2002 — 31259號公報 然而，先别的使用有二段正齒輪的減速齒輪機構存在 如下問題：因於一處嚙合使負荷變大故而選擇由成本較高 的高強度材料構成的正齒輪，使收納驅動馬達、減速齒輪 機構等的外叙憂彳寸大型化，因此無法使致動器變得小型、 輕量化。 另〆方面，因上述專利文獻1所揭示的電動致動器使 用行星齒輪機構，故較之使用有二段正齒輪的減速齒:機 構玎分散負荷’因此可使齒輪變得小型化。 然而’存在有由於上述減速齒輪機構僅是將輸入侧與 輸出側的減速比元全相同的行I齒輪單元疊層為所需要的 段數而構成，故而導致零件數增加以及變得重量化、大型 化的問題。即，施加於構成減速齒輪機構的各段行星齒輪 單元的行星齒輪的負荷並不相同，而是自驅^ 闕門的旋轉軸側變大。故而，較理想的是，== 時’根據各段的負荷來設計行呈齒輪單元。然而貝所 有行星齒輪機構均設計為相同時，由於必須以最後段的負 131 〇44^pif doc $為基準而設計，故而對於除負荷變小的最後段以外的行 星齒輪單元來說，負荷能力變得多餘，導致成為減少零件 件數、使之變得輕量化及小型化的較大障礙。 又無論驅動馬達侧是否可因負荷較小而使行星齒輪 白數增加，使太陽齒輪的齒數減少，均與最後段行星窗 輪的齒數相-致’由此減賴輪機構整體喊速比將變得 低效、，導致增加電動致動器的重量、大小、零件件數。 顔進Z ’上逑專利讀1所揭*的鶴致動肖存在如下 檢測，故:工作角作為機械軸的工作角，進行間接 2化？且使致動器本身變得大;量== 下問題.若零件件數越多則僅此將 ，、子 差，使誤差變大，導致由凸#盥、。们令件的公 置精声的泣… 制開關所規定的停止位 示：度的决是變大，故而將導撕顯示板的工止立 y、。、差擴大，可靠性降低。 作角的顯 【發明内容】 =發明是為解決上述先前_研“ 2 财將零雜肖1域實關化、巧彳卜 在 ，作角度的檢測誤差較小且可靠二;電動致動 並且旋轉 二輪機構由太陽齒輪及行星齒輪多段A =輪機構。行星 輪早元及上述行星齒輪㈣合的内齒行星齒 又精由行星 13104403^doc 齒輪機構而使上述驅動馬達的旋轉減速並傳遞至旋轉軸， 且上述行星齒輪單元包括共用内齒輪且愈接近上述驅動馬 達的單元則行星齒輪的個數愈少的至少2種行星齒輪單 元。 第2發明為如下之一種電動致動器’包括配設於箱體 内的驅動馬達、以及行星齒輪機構。行星齒輪機構包括太 陽齒輪及行星齒輪多段疊層而形成的行星齒輪單元及上述 行星齒輪所嚙合的内齒輪所構成。藉由行星齒輪機構而使 上述驅動馬達的旋轉滅速並傳遞至旋轉軸。上述行星齒輪 單元包括使減速比變大的至少2種行星齒輪單元，共用内 齒輪且愈靠近該驅動馬達的行星齒輪單元的行星齒輪的齒 數愈大，且太陽齒輪的齒數愈少。 第3 %；月為如下者，包括齒輪箱（明虹case )，設兮吿 成有内齒輪並作為收納驅動馬達與行星^ 执構的相體，亚且構成致動器的外殼。 π献in明包括連結旋轉軸與行星齒輪機構，且與上述 工作角檢測機二工作角檢測機構，且將上述 第5♦明f 述行星齒輪機構的箱體内。 置偵測裝置，於上，測機構包括：最大轉動位 1輸出，且於除此大轉動位置·h，產生第 產生第1衿屮， ；u連結構件的最小轉動位置上， 月'’且於除此以外的轉動位置上產生第2輸出； 13104 妙1f doc 以及自由搖動的搖桿構件，當上述連結構件轉動至最大轉 動位置時藉由該連結構件而受到擠壓力，且將該播厚力傳 遞至上述最大轉動位置偵測裝置，並且當上述連件轉 動至最小轉動位置時藉由該連結構件而受到擠魔力，並^ έ亥擠壓力傳遞至上述最小轉動位置彳貞測裝置。 ^， 第6發明中，上述最大轉動位置偵測裝置與上述最小 轉動位置偵測裝置包括以夾持上述搖桿構件而對向之方式 配設的2個限制開關。 第1發明中 考眼於她加於行星齒輪中的負荷越接近 驅動馬達的驅動轴則變得越低的情況，而使愈接近驅動馬 達側的行星齒輪單元的各段行星齒輪數愈少，故可削減行 星齒，數，由此實現致動器變得輕量化及成本降低。 的行=數3使愈接近驢動馬達的行星靖元 二:輪太陽齒輪的齒數，故可實 成致收納驅動馬達的箱體並且構 身小型輕量化。又，容t轉的制化，並可使外殼本 第4發明中，因^測部或旋轉轴等的位置對準。 偵測直接連結於卿^ :置於彳目體的工作角檢測機構而 轉軸與工作角檢測&構件的轉動，故無插入於旋 可削減零件數，又可试,S的令件，不存在零件數，從而 第5發明中，；，檢測誤差、提高可靠性。 轉動傳遞至最大轉動的搖桿構件兼用將連結構件的 動位置偵測裝置的構件與傳遞至最小轉 1310443sPif d〇c 動位置偵測裝置的構件。 2個限制開關以及自由 構。 第6發明中’可由彼此對向的 搖動的搖桿構件構成工作角檢測機 【實施方式】 以下，根腳式騎的實_轉細說明本發明。 圖！是表示本發明的電動致動器的 圖’圖2是相同，的主要構成零件的分解立體圖1 4 a〜3 C)疋相體的正視圖、俯視圖及右側視圖，圖 $ a〜4 :c)是接合部的俯視圖、正視圖及仰視圖，圖 ,的接通斷開狀恶的俯視圖及正視圖，圖“a) ==閥Η _為5 〇 %時的轉動位置檢測機構的接 t狀態的俯視圖及正視圖，《7(a)、7⑴是表示闕^ 巧為100%時的轉動位置檢測機構的接通、斷 俯視圖及正視圖。 圖1中1疋作為控制對象的球閥，2是驅動控制球 並凋整閥門間隙的電動致動器。 上述球閥1是先前眾所周知的兩通球閥，包括貫通--地突设於閥門本體4上部的圓筒部4A的旋轉轴3，其上 端部連結於上述電動致動器2 ，於下端侧設置有控制流動 ;、f閱1内的流體的流量的球塞（ball plug)(未圖示）。 球基的全工作角為9〇。，全閉角為_45。，全開角為+45。。 圖1、圖2、圖3⑻〜3(c)、圖4⑻〜4(c)中，上述電動 致動益2包括：外殼6，介隔磁軛5可裝卸地設置於上述 I310424Spifd〇c 圓筒部4A上；以及工作角檢測機構13，檢測收納於上述 外殼6内的驅動馬達^、減速齒輪機構12、上述旋轉軸3 的工作角等。 上述磁輕5以定位於一體地設置於上述圓筒部4Α上 端的凸緣部4Β上之方式進行設置，且藉由扣合元件15而 可裝卸地固定。於磁輛5底面，一體地突設有多個定位銷 16，且藉由將上述多個定位銷16嵌合於形成於凸緣部4β 上面的凹部17，而將磁輥5定位於凸緣部4Β上。1310447pifdoc IX. Description of the invention: [Technical field to which the invention pertains] The invention relates to the control of warm water, cold water motor valves or damper dynamics. The electric power of the d temple [prior art] The signal of the electric flow or the wind _ degree is adjusted. The reduction gear = the yaw == Zou's drive to the control valve or the damper, etc. The current surface of the rotating surface is deducted from the work (10) (or the range of motion) (for example, the per-g: 乍 is the reduction gear mechanism of the electric actuator, which is composed of a plurality of spur gears stacked in multiple stages, or used Revealing = ^ The pure sun gear in the literature 1 (sungea planetary gear returning wheel (annular gear) planetary gear machine 1 patent document! The electric actuator disclosed by the multi-positive gear, the money wheel and the money base The planetary gear mechanism formed by the base (=============================================================================================== The rotation of the box is reduced. The box body includes a lower armhole for accommodating the driving horse body and the storage sleeve, and the upper box body and the lower box body are separated by the board, so that the shaft rides the sun gear of the comet gear unit of the ___. Take I31_r again, the following is made by the reduction gear machine And the rotation deceleration brigade of the drive motor is transmitted to the rotation shaft (rotation shaft) of the valve, but the rotation shaft of the valve is coupled to the gear base of the last stage of the planetary gear mechanism, and the rotation of the shaft is transmitted to the rotation gear via the transmission gear to a rod, and detecting the rotation of the rod by a working angle detecting mechanism including a cam and a limit switch, thereby indirectly detecting an operating angle of the rotating shaft, and detecting a detection signal according to the working angle In the case of the reduction gear mechanism using the two-stage spur gear, there is a problem in that the load is increased due to one meshing, and the above-described drive motor is used. By selecting a spur gear made of a high-strength high-strength material, the size of the drive motor, the reduction gear mechanism, and the like is increased, so that the actuator cannot be made smaller or lighter. The electric actuator disclosed in the above Patent Document 1 uses a planetary gear mechanism, so that a reduction gear having a two-stage spur gear is used: the mechanism 玎 disperses negative 'Therefore, the gear can be miniaturized. However, there is a case where the reduction gear mechanism is formed by laminating only the row I gear units having the same reduction ratio elements on the input side and the output side as the required number of stages. There is a problem in that the number of parts is increased and the weight is increased and the size is increased. That is, the load applied to the planetary gears of the respective stages of the planetary gear units constituting the reduction gear mechanism is not the same, but is changed from the rotation axis side of the drive door. Therefore, it is desirable that when == 'the gear unit is designed according to the load of each segment. However, all the planetary gear mechanisms are designed to be the same, because the negative of the last segment must be 131 〇 44 ^ pif doc Since it is designed based on the reference, the planetary gear unit other than the last stage in which the load is reduced has an excessive load capacity, which is a major obstacle to reducing the number of parts, making it lighter and smaller. Regardless of whether the drive motor side can increase the white number of the planetary gear due to the small load, and reduce the number of teeth of the sun gear, both of which are in phase with the number of teeth of the last planetary wheel, thereby reducing the overall speed ratio of the wheel mechanism. It becomes inefficient, resulting in an increase in the weight, size, and number of parts of the electric actuator. Yan Jin Z ’ 逑 逑 逑 逑 逑 逑 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤 鹤And the actuator itself becomes large; the quantity == the next problem. If the number of parts is larger, the difference will be only the difference, and the error will become larger, resulting in the convexity. The order of the pieces is sobbing... The stop position specified by the switch means that the degree is greater, so the work of tearing the display panel is set to y. The difference is expanded and the reliability is lowered. The invention of the angle is invented. In order to solve the above-mentioned previous problems, the detection error of the angle is small and reliable; the electric actuation is The rotating two-wheel mechanism consists of a sun gear and a planetary gear multi-stage A = wheel mechanism. The planetary gear early element and the inner gear planetary tooth of the above planetary gear (four) are refined by the planetary gear 13104403^doc gear mechanism to decelerate and transmit the rotation of the above-mentioned drive motor to a rotating shaft, wherein the planetary gear unit includes a common internal gear and the closer to the drive motor, the less the number of the planetary gears is at least two types of planetary gear units. The second invention is as follows: a drive motor disposed in the casing and a planetary gear mechanism. The planetary gear mechanism includes a planetary gear unit formed by stacking a plurality of stages of a sun gear and a planetary gear, and an internal gear meshed by the planetary gear. The planetary gear mechanism is used. The rotation of the drive motor is extinguished and transmitted to the rotating shaft. The planetary gear unit includes at least two kinds of planetary teeth that increase the reduction ratio. The unit, the internal gear and the planetary gear unit closer to the drive motor, the larger the number of teeth of the planetary gear, and the smaller the number of teeth of the sun gear. The third month; the month is as follows, including the gear box (Minghong case), The inner gear is formed as a phase body for accommodating the drive motor and the planet, and constitutes an outer casing of the actuator. The π-in-in combination includes a rotating shaft and a planetary gear mechanism, and the working angle detecting machine The working angle detecting mechanism and the fifth detecting body of the planetary gear mechanism are disposed. The detecting device includes: a maximum rotating position 1 output, and a large rotating position·h, Producing the first 衿屮, u u at the minimum rotational position of the connecting member, the month '' and generating a second output at the other rotational position; 13104 妙1f doc and the freely rocking rocker member, when the above link When the member is rotated to the maximum rotational position, the pressing force is received by the connecting member, and the thickening force is transmitted to the maximum rotational position detecting device, and when the connecting member is rotated to the minimum rotational position The connecting member is subjected to the squeezing force, and the squeezing force is transmitted to the minimum rotational position detecting device. ^ In the sixth invention, the maximum rotational position detecting device and the minimum rotational position detecting device include In the first invention, the two limit switches are disposed to face the rocker member. The smaller the number of the planetary gears of the planetary gear unit closer to the drive motor side, the smaller the number of planetary teeth can be, and the smaller the number of the planetary gears can be, and the lower the cost. The planetary motor Yasuk 2 of the moving motor: the number of teeth of the sun gear, so that it can be used to house the casing of the drive motor and the structure is small and lightweight. Moreover, the system can be adjusted and can be made into the fourth invention. , because the position of the measuring part or the rotating shaft is aligned. The detection is directly connected to the Qing ^: placed in the working angle detection mechanism of the eyepiece and the rotation axis and the working angle detection & the rotation of the member, so there is no insertion in the rotation to reduce the number of parts, and can be tested, the S component, not In the fifth invention, the number of parts is present, and the error is detected and the reliability is improved. The rocker member that transmits the rotation to the maximum rotation also uses the member that moves the moving position detecting device of the connecting member and the member that transmits the minimum position to the 1310443s Pif d〇c moving position detecting device. 2 limit switches and freewheeling. In the sixth invention, the rocker member that can be tilted toward each other constitutes an operating angle detecting machine. [Embodiment] Hereinafter, the present invention will be described in detail. Figure! FIG. 2 is an exploded perspective view of the main components of the present invention. FIG. 2 is an exploded perspective view of the main components. FIG. 2 is a front view, a plan view, and a right side view of the 疋 phase body. FIG. ) is a plan view, a front view, and a bottom view of the joint portion, and a plan view and a front view of the open and closed view of the joint, and Fig. "a) == valve Η is 5 〇% of the rotational position detecting mechanism The top view and the front view of the state, "7(a), 7(1) are the on and off top view and front view of the rotational position detecting mechanism when the 阙^ is 100%. In Fig. 1, 1球 is the ball valve to be controlled, 2 The electric actuator that drives the control ball and withstands the valve clearance. The ball valve 1 is a previously known two-way ball valve, and includes a rotary shaft 3 that penetrates through the cylindrical portion 4A of the upper portion of the valve body 4, and the upper end thereof The part is connected to the electric actuator 2, and is provided with a ball plug (not shown) for controlling the flow rate of the fluid in the lower end side. The total working angle of the ball base is 9 〇. The full angle of closure is _45. The full opening angle is +45. Figure 1, Figure 2, Figure 3 (8) ~ 3 (c), Figure 4 (8) ~ 4 (c) The electric actuator 2 includes a housing 6, a yoke 5 detachably disposed on the I310424 Spifd〇c cylindrical portion 4A, and a working angle detecting mechanism 13 for detecting a driving motor housed in the housing 6. The reduction gear mechanism 12, the operating angle of the rotating shaft 3, etc. The magnetic light 5 is disposed so as to be integrally provided on the flange portion 4 of the upper end of the cylindrical portion 4, and is fastened by the engaging member 15. Removably fixed. A plurality of positioning pins 16 are integrally protruded from the bottom surface of the magnetic vehicle 5, and the magnetic roller is assembled by fitting the plurality of positioning pins 16 to the concave portion 17 formed on the flange portion 4β. 5 is positioned on the flange portion 4Β.
上述扣合元件15欲入固定於上述磁輛5内部，且具備 有：扣合部，與設置於凸緣部4Β側的扣合部（未圖示） 扣合；以及操作把手18，相對於凸緣部4Β制動扣合元件 15。操作把手18自形成於磁軛5下部的開口部2〇突出至 外°卩’若於水平方向轉動操作該操作把手18而解除凸緣部 4Β與扣合元件15的扣合狀態，則可自凸緣部4Β拆磁 車厄5。 ”The fastening element 15 is intended to be fixed to the inside of the magnetic vehicle 5, and includes a fastening portion that is engaged with a fastening portion (not shown) provided on the flange portion 4Β side, and an operation handle 18 that is opposite to the handle The flange portion 4 Β brakes the fastening member 15. The operation knob 18 protrudes from the opening portion 2 formed at the lower portion of the yoke 5 to the outside. When the operation handle 18 is rotated in the horizontal direction to release the engagement state of the flange portion 4 and the fastening member 15, the operation handle 18 can be self-retained. The flange portion 4 is demagnetized. ”
上述外殼6包括：上箱體21，收納上述驅動馬達u 外^乍角檢測機構13 ;環22，絲於該上箱體21下端部 °面二以及嵩輪箱23 ’收納上述減速齒輪機構12。 述磁與環22及齒輪箱23 一起可裝卸地固定於上 去… 下面側開口部由上述齒輪箱23覆蓋。 部收納有上述減速齒輪機構 24堵塞。齒Μ ^ 5上面’上端側開口部B由安裝板 方式Μ; T I端側開口部挪形成以自由旋轉的 飞轴支下述承载器（carrier) 43的轴孔。 C S > 12 I3104435p if.doc 上述驅動馬達11藉由設置於上述齒輪箱23的安裝板 24上’而位於上箱體21内。又，將藉由驅動馬達11朝向 下方設置於安裝板24上，而使驅動軸25貫通設置於安震 板24的插通孔且插入齒輪箱23内，於該插入端部固定有 將驅動軸25的旋轉傳遞至上述減速齒輪機構12的小齒輪 (pinion) 26。 上述減速齒輪機構12包括疊層為二段的第1、第2行 星齒輪單元U卜U2以及上述承載器43等，且其收納於上 述齒輪箱23。 位於上方且接近於驅動馬達n的驅動轴25的第]行 星齒輪單元U1包括太陽齒輪30、3個行星齒輪31、承載 ，32、以及内齒輪4〇 (圖3 (b))等。驅動馬達u至行 星齒輪單元υι的嚙合的傳遞中，介隔有二段齒輪27 (27a、27b)、以及齒輪29。二段齒輪27的第1齒輪27 ，合於上述小齒輪26，於第2齒輪27b上响合有上 陽齒輪30與絲29形·—體，並分㈣合= w輪31。各仃星齒輪分別由突設於第1承載哭32面 ΐ 33以自由旋轉的方式軸支。又，於第1承載 的軸銷34。 °又有以自由旋轉的方式軸支上述齒輪29 星齒輪單元4且 輪38的4個行星齒輪f 38、分別嚙合於上述太陽] 上述内齒輪40、以及$ 述夕個行星齒輪39所嚙合t 乂及弟2承载器43等。太陽齒輪％ 一彳 13 1310443^ d°c ^承载器32下面。各行星齒輪39分別由 支。又，行星齒輪44以自*旋轉的方式轴 齒輪31齒寬較厚的方式二弟^丁星齒輪單元U1的行星 的旋轉軸3的行星齒輪單^力因在:越接近球間i 大，故而設行星絲 齒輪的負荷越 面壓）。上述内餘40」回見Μ由此可承受負荷（降低 定齒輪，且上述^星^ 7成於上述齒輪箱23内壁的固 上述承載ί 39共同嗜合於其。 43Α，該軸部43Α由:成也突设於下面的圓筒狀軸部 以白絲从、由也成於上述齒輪箱23下面的軸孔23h 槽46，^栓槽！又了轴部43A内面侧形成有栓 合部47的花上侧箱23下方的接 輪機構12，與上述減速齒 旋轉傳遞至旋轉轴3 構減速的驅動馬達11的 嵌合於設置於上述旋構件’以限制旋轉的方式 央部設置有上述花鍵:48全而的角柱部3a’且於上面中 動使上述旋轉車由3轉建:二二丄部-，設置有於手 50、以及使上述:作角時所使用的操作手柄 2個操作部51、52。操; 的圓筒部47A的階差m d又置於接合部47 之方式設置於圓筒與52以相一 I作角仏測機構13包括：上述搖桿構件54、以 131044+if d〇c 及藉由該搖桿構件 檢測機構60、61。轉動位置檢而:通、斷開的2個轉動位置 微動開關。搖桿構# 彳機構60、61，使用常閉型 接合部47的操作部5卜52中的任一^向）’於未與上述 為大致垂直，且維m 丄個抵接的狀態下立起 60、61均處於非接觸狀:上述轉動位置檢測機構 由轉動的方式如此般之搖桿構件％以自 中點位詈^1支 且藉由轉性構件簡於通常 U位置而構成自動恢復式搖捍。 W一 t述轉動位置檢測機構60、61於相同上述齒 方述搖桿構件54且接近並對向於其傾斜方向的 式配。又。又’2個轉動位置檢測機構6〇、61中， =右側的轉動位置檢測機構60 ’於上述接合；4二 所示的最小轉動位置（閥門的間門間隙成為 的轉動位置）上，由上述搖桿構件54#壓成為斷開， 猎此停止向朝向間隙減少方向的馬達u的通電。於除此之 外的轉動位置’於接通狀態下構成最小轉動位㈣測裝 置。此時’位於左側的轉動位置檢測機構61保 位於左侧的上述轉動位置檢測機構61於上述接合部 47的圖7(a)、7(b)所示的最大轉動位置（閥門間^: 時的轉動位置上述搖桿構件54 _成為成斷為開4 此切斷向朝向間隙增加方向的馬達U的通電。於除此之外 的轉動位置，於接通狀態卞構成最大轉動位置偵測裝置。 此時，右侧的轉動位置檢測機構60保持接通（導、通）狀離。 15 再者，於閥門間隙為除全閉、全開以外的中間間隙時，藉 由接合部47的操作部51、52中的任一個而均無法使搖桿 構件54傾斜，故轉動位置檢測機構60、61均保持接通（導 通）狀態。 其次，就具有如此般之構造的電動致動器2的動作加 以說明。 若藉由來自控制部的驅動訊號而驅動驅動馬達11，則 上述驅動軸25的旋轉藉由減速齒輪機構12而減速後，將 經由接合部47傳遞至球閥1的旋轉軸3。即，若驅動馬達 11進行驅動則其驅動軸25的旋轉將經由小齒輪26傳遞至 二段齒輪27。又，二段齒輪27的旋轉將經由齒輪29傳遞 至太陽齒輪30，由此太陽齒輪30旋轉，從而使3個行星 齒輪31旋轉。 行星齒輪31若因太陽齒輪30旋轉而旋轉，則將沿内 齒輪40公轉且使第1承載器32旋轉，以此使太陽齒輪30 的旋轉減速。又，若行星齒輪31沿内齒輪40公轉，則太 陽齒輪38亦將旋轉，並使4個行星齒輪39旋轉。此等行 星齒輪39沿内齒輪40公轉，使第2承載器43旋轉從而使 太陽齒輪38的旋轉減速。進而，由於上述第2承載器43 的旋轉經由栓槽46與花鍵齒48傳遞至接合部47，故接合 部47與旋轉軸3整體地轉動，藉此調整球閥1的閥門開 度。再者，將減速齒輪機構12之減速比設為’輸入側與輸 出侧的減速比為997 : 1，2個行星齒輪單元Ul、U2為 1/6x1/5.3=1/32。 16 13104妙1f doc 動，則接合部47亦與旋韓細^ 軸3轉動财角度（_ —體地轉動。*且，若旋轉 部51將抵接於搖桿構件54’、=合部47的其中-個操作 54如圖5(b)所示傾* 士而#亚擠遷其，使搖桿構件 置檢測機構60的射减^此’搖桿構件54_轉動位 切斷全閉方向側的通6〇斷開，藉此 此時，球間!為二一動馬達，的一 Η方Ϊ =面，如旋轉軸3自閥門間隙為5〇%的狀態於打 轉動預定角度（45。），則接合部47的操作部以口 ，7 (b)所不，擠壓搖桿構件54而使之傾斜。由此，搖 桿構件54擠壓轉動位置檢測機構61的按鈕使轉動位置檢 測機構61斷開’藉此切斷全開方向側的通電，使驅動馬達 U的驅動停止。此時，球閥1為全開狀態。 如此，本發明中，因施加於各行星齒輪單元、u2 的行星齒輪31、39的負荷於驅動馬達u侧變小、朝向球 閥1側變大，故以球閥1側的行星齒輪單元U2為標基準 而進行設計，因設驅動馬達11側的行星齒輪單元Π1與第 2行星齒輪單元U2共用内齒輪且該行星齒輪單元^^的減 速比變大，並且行星齒輪31的齒寬薄於行星齒輪單元U2 的行星齒輪39的齒寬’行星齒輪31的個數為3個比行星 齒輪39的個數少1個，故可提高減速齒輪機構12整體的 減速效率並且削滅行星齒輪32的個數，又藉此可實現致動 器本身的小型化與重ϊ減輕。 又，收納減速齒輪機構12的齒輪箱23與收納驅動馬 18 131 〇443if d〇c 達11的上箱體21 —起構成致動器2的外殼6，由此可實 現零件的共用化，並可易於實現與接合部47的軸對準，而 且無需連結部，故可實現小型化。 進而，本發明以藉由設置於箱體23中的2個限制開關 60、61而偵測安裝於球閥1的旋轉軸3的接合部47的轉 動的方式構成，故與上述專利文獻1所揭示的電動致動器 相比構造簡單，可削減插入於自旋轉軸3至工作角檢測機 構13的中間的零件，提高工作角檢測機構13的檢測精度 及可靠性。 又，本發明中，於1根搖桿構件54兼用將接合部47 的轉動傳遞至2個限制開關60、61的構件，將箱體23兼 用於減速齒輪機構12的收納、及工作角檢測機構13的安 裝，由此根據此點亦可削減零件數。 再者，上述之實施形態中，表示有使用行星齒輪數不 同的2種行星齒輪單元U1、U2的例示，但並非限定於此， 亦可適用大於等於2種的行星齒輪單元。 雖表示有本發明的電動致動器適用於球閥的示例，但 並非限定於此，亦可適用於各種閥門，又無需多說亦可用 於除閥門以外的裝置、例如開關燃燒裝置或導管的排氣口 的風門等，亦可作為減速機構一體的齒輪電動機的齒輪單 元單體而使用。 【圖式簡單說明】 圖1是表示本發明的電動致動器的一實施形態的剖面 圖。 19 131 〇44^pifd〇c 圖 =是相同致動器的主要構成零件的分解立體圖。 ° a) 3 (c)是箱體的正視圖、俯視圖及右側視 圖 4 (a) 0疋接合部的俯視圖、正視圖及仰視 檢剩機槿拉_ (b)疋表不閥門間隙為Q%時的轉動位置 冓的接通、斷開狀態的俯視圖及正視圖。 置撿ma)、6 (b)是表示㈣間隙為5Q%時的轉動位 則铋構的接通、斷開狀態的俯視圖及正視圖。動 置7 (a)、7 (b)是表示閥門間隙為，/。時的韩叙私 r Μ機構的接通、斷開狀態的俯視圖及正視圖。'動位 L主要元件符號說明、 。 圖 圖The outer casing 6 includes an upper casing 21 that houses the drive motor u and an angle detecting mechanism 13; a ring 22 on which the lower end portion of the upper casing 21 and the wheel box 23' accommodate the reduction gear mechanism 12 . The magnet is detachably fixed to the upper end together with the ring 22 and the gear case 23. The lower side opening portion is covered by the gear case 23. The portion of the reduction gear mechanism 24 is blocked. The upper end portion B of the upper end of the tooth Μ ^ 5 is mounted by a mounting plate; the opening portion of the T I end side is formed by a shaft hole of a carrier 43 which is supported by a freely rotatable flying shaft. C S > 12 I3104435p if.doc The above-described drive motor 11 is located in the upper casing 21 by being disposed on the mounting plate 24 of the gear case 23. Further, the drive motor 11 is disposed downward on the mounting plate 24, and the drive shaft 25 is inserted through the insertion hole of the sound-absorbing plate 24, and inserted into the gear case 23, and the drive shaft is fixed to the insertion end. The rotation of 25 is transmitted to the pinion 26 of the above-described reduction gear mechanism 12. The reduction gear mechanism 12 includes first and second planetary gear units Ub, U2, and the like, which are stacked in two stages, and are housed in the gear case 23. The first planetary gear unit U1 located above and close to the drive shaft 25 of the drive motor n includes a sun gear 30, three planetary gears 31, a carrier 32, and an internal gear 4 (Fig. 3(b)). In the transmission of the meshing of the drive motor u to the planetary gear unit ,, the two-stage gear 27 (27a, 27b) and the gear 29 are interposed. The first gear 27 of the second-stage gear 27 is coupled to the pinion 26, and the second gear 27b is coupled to the upper gear 30 and the wire 29, and is divided into four (four) = w wheels 31. Each of the comet gears is pivotally supported by a crying 32 face ΐ 33 protruding from the first load. Further, the pin 34 is placed on the first carrier. ° Further, the gears 29 are mounted in a freely rotatable manner, and the four planetary gears f 38 of the wheel 38 are engaged with the sun, the internal gear 40, and the planetary gears 39.乂 弟 2 2 carrier 43 and so on. Sun gear % 彳 13 1310443^ d°c ^ below the carrier 32. Each of the planetary gears 39 is branched. Further, the planetary gear 44 is in a self-rotating manner, and the shaft gear 31 has a relatively large tooth width. The planetary gear of the planetary shaft of the second planetary gear unit U1 has a planetary gear unit force: the closer to the ball i is, Therefore, the load of the planetary gear is more surface pressure. The inner circumference 40" is returned to the load so as to be able to withstand the load (the fixed gear is reduced, and the above-mentioned metal ball 7 is formed on the inner wall of the gear box 23, and the above-mentioned bearing member 39 is commonly associated with it. 43Α, the shaft portion 43Α The cylindrical shaft portion which is also protruded from the lower side is formed by the white wire, the shaft hole 23h which is also formed in the lower surface of the gear case 23, the groove 46, and the bolt groove is formed on the inner surface side of the shaft portion 43A. The pick-up mechanism 12 at the lower side of the flower upper side box 47 is fitted to the drive motor 11 that is rotated by the reduction gear and transmitted to the rotary shaft, and is mounted on the central portion of the rotary member to restrict rotation. Spline: 48 full corner post 3a' and moving in the upper side to make the above-mentioned rotating car from 3: two-two-part, provided with the hand 50, and the operation handle 2 used to make the above: The step portion md of the cylindrical portion 47A of the operating portion 51, 52 is disposed in the manner of the engaging portion 47, and the angle detecting mechanism 13 is disposed at the same angle as the cylinder. With 131044+if d〇c and by the rocker member detecting mechanisms 60, 61. The rotational position is detected: two rotation positions of on and off The micro switch, the rocker mechanism # 彳 mechanism 60, 61, using any one of the operation portions 5, 52 of the normally closed joint portion 47 is not substantially perpendicular to the above, and the dimension m is abutted. In the state, the standing 60, 61 are in a non-contact state: the above-mentioned rotating position detecting mechanism is rotated in such a manner that the rocker member % is from the center point and is rotated by the rotating member to the normal U position. It constitutes an automatic recovery shake. The rotational position detecting means 60, 61 are described in the same manner as the above-described crank member 54 and are close to and in the direction in which they are inclined. also. Further, in the 'two rotational position detecting mechanisms 6', 61, the right rotational position detecting mechanism 60' is in the above-described engagement; the minimum rotational position shown in Fig. 2 (the rotational position at which the door gap of the valve becomes) is The rocker member 54# is pressed to be off, and the hunting is stopped to energize the motor u toward the gap reducing direction. The rotational position other than this constitutes the minimum rotational position (four) measuring device in the on state. At this time, the rotational position detecting means 61 on the left side holds the rotational position detecting means 61 on the left side at the maximum rotational position shown in Figs. 7(a) and 7(b) of the engaging portion 47 (between the valves: In the rotational position, the rocker member 54_ is turned into the opening 4, and the cutting is performed to energize the motor U in the direction in which the gap is increased. In addition to the rotating position, the turning position constitutes the maximum rotational position detecting device. At this time, the rotational position detecting mechanism 60 on the right side is kept in an ON state. In addition, when the valve clearance is an intermediate gap other than the fully closed and fully open, the operation portion of the joint portion 47 is used. In either of 51 and 52, the rocker member 54 cannot be tilted, so that the rotational position detecting mechanisms 60 and 61 are kept in an ON state. Next, the action of the electric actuator 2 having such a configuration is obtained. When the drive motor 11 is driven by the drive signal from the control unit, the rotation of the drive shaft 25 is decelerated by the reduction gear mechanism 12, and then transmitted to the rotary shaft 3 of the ball valve 1 via the joint portion 47. If the drive horse When the drive 11 is driven, the rotation of the drive shaft 25 thereof is transmitted to the two-stage gear 27 via the pinion gear 26. Further, the rotation of the two-stage gear 27 is transmitted to the sun gear 30 via the gear 29, whereby the sun gear 30 rotates, thereby making 3 When the planetary gears 31 rotate by the rotation of the sun gears 30, the planetary gears 31 revolve along the internal gear 40 and rotate the first carrier 32, thereby decelerating the rotation of the sun gear 30. Further, if the planetary gears 31 are rotated, the planetary gears 31 are rotated. When the internal gear 40 revolves, the sun gear 38 also rotates and rotates the four planetary gears 39. These planetary gears 39 revolve along the internal gear 40 to rotate the second carrier 43 to decelerate the rotation of the sun gear 38. Further, since the rotation of the second carrier 43 is transmitted to the joint portion 47 via the pin groove 46 and the spline teeth 48, the joint portion 47 rotates integrally with the rotary shaft 3, thereby adjusting the valve opening degree of the ball valve 1. The reduction ratio of the reduction gear mechanism 12 is set to 'the reduction ratio of the input side and the output side is 997: 1, and the two planetary gear units U1 and U2 are 1/6x1/5.3=1/32. 16 13104 Wonder 1f doc , the joint portion 47 is also rotated with the rotary shaft 3 The angle (__ body rotation. * and, if the rotating portion 51 will abut against the rocker member 54', = the joint portion 47 of the operation 54 as shown in Figure 5 (b) Moved to the rocker member to detect the mechanism 60. The 'rocker member 54_rotation position cuts off the 6th turn of the fully closed direction side. At this time, the ball is a two-one motor. , a square Ϊ = face, such as the rotation axis 3 from the valve clearance of 5 〇% state in the rotation of the predetermined angle (45.), the operation of the joint 47 is the mouth, 7 (b) does not squeeze The rocker member 54 is tilted by the rocker member 54. Thereby, the rocker member 54 presses the button of the rotational position detecting mechanism 61 to turn off the rotational position detecting mechanism 61, thereby cutting off the energization of the fully open direction side, thereby driving the motor U. The drive stops. At this time, the ball valve 1 is in the fully open state. In the present invention, since the load applied to the planetary gears 31 and 39 of the planetary gear units and u2 is smaller on the side of the drive motor u and larger toward the ball valve 1 side, the planetary gear unit U2 on the side of the ball valve 1 is used as the standard. Designed by the reference, the planetary gear unit Π1 on the side of the drive motor 11 shares the internal gear with the second planetary gear unit U2, and the reduction ratio of the planetary gear unit becomes large, and the tooth width of the planetary gear 31 is thinner than the planetary gear Since the number of the planetary gears 39 of the unit U2, the number of the planetary gears 31, is three less than the number of the planetary gears 39, the reduction efficiency of the entire reduction gear mechanism 12 can be increased and the number of the planetary gears 32 can be eliminated. In this way, miniaturization and weight reduction of the actuator itself can be achieved. Further, the gear case 23 accommodating the reduction gear mechanism 12 and the upper case 21 accommodating the drive horse 18 131 〇 443if d〇c 11 constitute the outer casing 6 of the actuator 2, whereby the parts can be shared, and The alignment with the axis of the joint portion 47 can be easily realized, and the joint portion is not required, so that downsizing can be achieved. Further, the present invention is configured to detect the rotation of the joint portion 47 attached to the rotary shaft 3 of the ball valve 1 by the two limit switches 60 and 61 provided in the casing 23, and thus disclosed in Patent Document 1 The electric actuator is simpler in structure, and the components inserted in the middle of the self-rotating shaft 3 to the working angle detecting mechanism 13 can be reduced, and the detection accuracy and reliability of the working angle detecting mechanism 13 can be improved. Further, in the present invention, the one rocker member 54 also serves as a member for transmitting the rotation of the joint portion 47 to the two limit switches 60 and 61, and the casing 23 is also used for the storage of the reduction gear mechanism 12 and the working angle detecting mechanism. The installation of 13 can also reduce the number of parts according to this point. In the above-described embodiment, the two kinds of planetary gear units U1 and U2 having different numbers of planetary gears are used. However, the present invention is not limited thereto, and two or more planetary gear units may be applied. Although the electric actuator of the present invention is applied to an example of a ball valve, it is not limited thereto, and may be applied to various valves, and it is also needless to say that it can also be used for a device other than a valve, such as a switch burning device or a row of a catheter. The damper of the air port or the like can also be used as a gear unit of the gear motor integrated with the speed reduction mechanism. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a cross-sectional view showing an embodiment of an electric actuator according to the present invention. 19 131 〇44^pifd〇c Fig. = An exploded perspective view of the main components of the same actuator. ° a) 3 (c) is the front view, top view and right side view of the box. 4 (a) 0疋 Top view of the joint, front view and upside down check _ (b) 不 No valve clearance is Q% A top view and a front view of the on and off states of the rotational position 时 at the time.捡 捡 ma), 6 (b) is a plan view and a front view showing the state in which the (four) gap is 5Q%. Actuators 7 (a) and 7 (b) indicate that the valve clearance is /. The top view and the front view of the ON and OFF state of the Korean public. 'Movement L main component symbol description, . Figure
A 1 : 球閥 2 : 電動致動器 3 : 旋轉軸 3a :角柱部 4 : 閥門本體 4Λ :圓筒部 4B .凸緣部 5 :磁車厄 6 ·外殼 驅動馬達 減速齒輪機構 工作角檢測機構 11 12 13 20 131 〇443pf d〇c 15 :扣合元件 16 :定位銷 17 :凹部 18 :操作把手 20 :開口部 21 :上箱體 22 :環 23 :齒輪箱 23a :開口部 23b :開口部 24 :安裝板 25 :驅動軸 26 :小齒輪 27、24a、27b :二段齒輪 29 :齒輪 30、 38 :太陽齒輪 31、 39 :行星齒輪 33 :支持銷 34、44 :軸銷 40 :内齒輪 43 :承載器 43A :軸部 46 :栓槽 47 :接合部（連結構件） 21 47A :圓筒部 48 :花鍵齒 50 :操作手柄 51、52 :操作部 54 :搖桿構件 60、61 :限制開關A 1 : Ball valve 2 : Electric actuator 3 : Rotary shaft 3a : Corner column 4 : Valve body 4 Λ : Cylinder portion 4B . Flange portion 5 : Magnetic car 6 · Case drive motor reduction gear mechanism Working angle detecting mechanism 11 12 13 20 131 〇443pf d〇c 15 : fastening element 16 : positioning pin 17 : recess 18 : operating handle 20 : opening 21 : upper case 22 : ring 23 : gear case 23 a : opening 23 b : opening 24 Mounting plate 25: Drive shaft 26: Pinion gears 27, 24a, 27b: Two-stage gear 29: Gears 30, 38: Sun gears 31, 39: Planetary gears 33: Support pins 34, 44: Shaft pin 40: Internal gear 43 : carrier 43A : shaft portion 46 : bolt groove 47 : joint portion (joining member) 21 47A : cylindrical portion 48 : spline tooth 50 : operation handle 51 , 52 : operation portion 54 : rocker member 60 , 61 : restriction switch
Ul、U2 :行星齒輪單元Ul, U2: planetary gear unit
1310443^do 221310443^do 22