200920632 九、發明說明： -【發明所屬之技術領域】 - 本發明提供一種可變槓桿比之踏板裝置，特別是涉及 一種車輛用之槓桿式煞車踏板，具可變換槓桿上一樞軸與 踏板間之力臂長度的技術。 【先前技術】 傳統車輛之煞車系統大致上可分為兩種，一種為機械 r, 式煞車系統，另一種為油壓式煞車系統。前者是指只用機 4 械裝置如桿件、鋼索等將能量傳至車輪制動器；後者為利 用液體介質將能量傳送至車輪制動器。兩者皆是經由駕駛 人本身踩踏煞車踏板來決定煞車程度。 為了提高煞車效率、擁有較佳之靈敏度及有效縮短煞 車距離，線控式煞車系統(Brake-by-Wire)因此被發展出來。 目前線控式煞車系統的發展趨勢可區分為電子液壓式煞車 系統（Electro-Hydraulic，EHB)與電子機械式煞車系統 (Electro-Mechanical，EMB)，線控式煞車系統包含煞車踏板 ’ 位置感應器、電子控制單元(ECU)及馬達；其中，煞車踏板 與車輪制動器之運作係各自獨立，當駕駛人踩踏煞車踏板 時，煞車踏板位置感應器會將訊號傳送至電子控制單元， 經由電子控制單元運算後回傳訊息至馬達，再經由馬達控 制EHB之系統油壓或直接驅動車輪制動器運作（EMB)，且 二款線控煞車系統皆不使用增壓器。 線控式煞車系統最令人擔心的是它的可靠度，因為電 子系統較容易受外在環境侵襲而故障，一旦線控式煞車系 5 200920632 統出現故障，可能會直接影響車輛的行駛安全。針對這個 問題，電子機械式煞車系統之改善方法，是參考線控系統 在飛機上的應用，採用多套的EMB系統，當一套EMB系 統故障時還有備用EMB系統可正常運作；而電子液壓式煞 車系統之改善方法，係設有備用之機械式煞車裝置，於Ε Η B 系統故障時，該備用之機械式煞車裝置能使煞車踏板與液 壓管路重新結合，但由於缺少增壓器之補助力量，致使同 樣的踏板踩踏力量，ΕΗΒ系統故障時建立之油路壓力，約 略只有ΕΗΒ系統正常時之三分之一，踏板行程減為約二分 之一，導致煞車力量降低，且煞車距離延長。 為了克服上述電子液壓式煞車系統因缺少增壓器之補 助力量而造成煞車力量降低的問題，現有較為先進之技術 中，已揭露有可改變煞車踏板之槓桿比，以提升駕駛人踩 踏踏板所產生之煞車力量的技術，舉如美國第7,219,576號 專利案所揭示，其煞車踏板係為樞軸固定式，於採下踏板 時，可隨著踏板行程的移動而改變煞車推桿與煞車踏板之 相對位置，藉以改變槓桿比；然而，其缺點在於組成構件 較為繁多，故亟待加以改善。 【發明内容】 本發明之目的旨在提供一種可變槓桿比之踏板裝置， 作為線控式煞車系統之機械式備用煞車裝置，尤其是能以 移動樞軸位置的方式來改變煞車踏板之槓桿比，在線控式 煞車系統故障時，能藉由改變槓桿比，以提升駕駛人踩踏 踏板所產生之煞車力量，並能簡化構件而提升其在使用上 的可靠性。 200920632 為能實現上述目的，本發明可變槓桿比之踏板裝置， 包含： 一煞車用槓桿，底端具一踏板，頂端滑設一樞轴； 一推桿，樞設於樞軸與踏板之間的槓桿上，一端延伸 至一制動煞車用之出力端；及 一驅動器，設於樞軸上方，驅動樞軸垂向位移，以改 變推桿與踏板各自相對於樞軸之間的槓桿比。 據此，於車輛之線控式煞車系統故障時，能調整踏板 之樞軸位置，藉以改變槓桿比而提升煞車力量，進而提升 線控式煞車系統之可靠度，以減少交通事故的發生。 此外，本發明也包含： 所述樞軸旁侧具一垂向滑軌，且槌軸滑設於垂向滑軌 内。 所述樞軸底部形成一桿部，與槓桿頂端相互套接，以 導引枢轴滑設於損桿頂端。 所述出力端係為煞車液壓管路或機械裝置；所述驅動 器係為電磁閥或其他具電驅動能力的等效元件。 除此之外，所述驅動器亦可設於樞軸近侧，而與枢軸 之間連結一連桿，且樞軸上方具一橫向滑軌，驅動器與連 桿之一樞接端滑設於橫向滑執内，且驅動器經由連桿驅動 樞軸垂向位移；或者，於樞轴與槓桿頂端之間設一肘節單 元，具一樞設於樞軸上的上擺桿，以及一樞設於槓桿頂端 的下擺桿，上、下擺桿之間具一柩接部相連結，藉由驅動 器驅動上擺桿、樞接部、下擺桿而帶動枢軸垂向位移，且 200920632 係靠住驅動器，上擺桿與下擺桿 元4驅動器之驅動力大於彈 施的内容 上 έ：幺 然而，為能再加詳述本發明可供具體 配合圖式說明如後： 【實施方式】 首觀圖1，揭示出本發明第—款實施例的配置干 況明本發明可變槓桿比之踏板裝置，包含： W圖 -煞車用槓桿i，設於車輛之—車體39㈣ 端具一踏板3，頂端滑設一樞軸2 ; 、彳干底 一推桿4，-端樞設於樞軸2與踏板3之間 另-端延伸至-制動煞車用之出力端 Ί 一煞車用車輪制動器；及 /出力立而6可驅動 一驅動器5，設於樞軸2上方，驅動 以改變推桿4與踏板3各自相對於樞 在更加具體的實施上，所述抱袖 執7,且樞軸2滑設於垂向滑執7内(如固：门有―垂向滑 所述枢軸2底部形成—桿部幻， ，、）。 接’以導引樞軸2滑設於槓桿1頂端。、十、端相互套 所述出力端6係為煞車液愿管路 例所應用之線控式煞車系統係為電子液承本實施 述驅動:5係為-電磁閥或其他具電驅 猎由上述構件組成，可供據以實施本發明在 200920632 車輛之電子液屋式煞車系統故障時，能經由驅動哭 閥）驅動樞軸2進行垂向位移（如圖2所示），^ ^電磁 2位置，並改變推桿4與踏板3各自相對於樞軸2:二樞軸 桿比；且駕駛人能以較小的力#踩踏踏板3，使1的槓 下移的框軸2擺動，促使槓桿1帶動推桿4去驅動^繞山著 (如圖3所不）’即可產生與電子液愿式煞車系 、6 車力量，以控制車輪制動器制動車輪進行敦車。^的煞 發明能以機_ 2位置的方絲改變煞車踏板^二本 比’而提升駕駛人踩踏踏板3所產生之 、相# 升線控式煞車系統之可靠度， 里進而提 此間化構件而提升其在使用上的可靠性。 ^生，亚 此外’本發明之踏板裝置可提 的額外煞車力量；為能證明本發明使用驅動^少2〇% 驅動樞軸2改變位置，以經由 ：“磁閥） 少20%額外敦車力| γ α 棱七、車輪制動器至 動分析i 的可诚，係藉由下觸缺置之運 當電子液壓式煞車系統故障時，踏 液壓管路壓力乃可由方程式丨決定： p產生之煞車 、方_ (式中-煞車主缸横截面面積，·尸= 板槓桿比’U板槓桿機械效率）。'’ /p-踏 由圖4可知原煞車踏板3之槓桿比^可表示成方程式2: 200920632200920632 IX. Description of the invention: - [Technical field to which the invention pertains] - The present invention provides a pedal device with a variable lever ratio, and more particularly to a lever type brake pedal for a vehicle having a pivot and a pedal between the convertible levers The technique of the arm length. [Prior Art] The brake system of the conventional vehicle can be roughly divided into two types, one is a mechanical r, a brake system, and the other is a hydraulic brake system. The former refers to the transfer of energy to the wheel brakes only by mechanical devices such as rods, cables, etc.; the latter uses a liquid medium to transfer energy to the wheel brakes. Both of them determine the degree of braking by pedaling the pedals of the driver himself. In order to improve braking efficiency, have better sensitivity and effectively shorten the braking distance, the Brake-by-Wire system was developed. At present, the development trend of the wire-controlled brake system can be divided into Electro-Hydraulic (EHB) and Electro-Mechanical (EMB), and the wire-controlled brake system includes the brake pedal' position sensor. The electronic control unit (ECU) and the motor; wherein the brake pedal and the wheel brake are independent of each other. When the driver steps on the brake pedal, the brake pedal position sensor transmits the signal to the electronic control unit, and is operated via the electronic control unit. After the message is sent back to the motor, the EHB system oil pressure is directly controlled by the motor or the wheel brake operation (EMB) is directly driven, and the second line control brake system does not use the supercharger. The most worrying aspect of the wire-controlled brake system is its reliability, because the electrical system is more susceptible to external environment failure and failure, once the wire-controlled brake system 5 200920632 system failure, it may directly affect the driving safety of the vehicle. In response to this problem, the improvement method of the electromechanical brake system is to refer to the application of the line control system on the aircraft, and adopt multiple sets of EMB systems. When an EMB system fails, the standby EMB system can operate normally; and the electrohydraulic The improvement method of the brake system is to provide a spare mechanical brake device. When the system is faulty, the spare mechanical brake device can recombine the brake pedal and the hydraulic circuit, but due to the lack of a supercharger The subsidy force, the same pedal pedaling force, the oil pressure established when the system is faulty, is only about one-third of the normal system, and the pedal stroke is reduced by about one-half, resulting in reduced braking force and braking distance. extend. In order to overcome the problem that the above-mentioned electro-hydraulic brake system has reduced the braking force due to the lack of the auxiliary force of the supercharger, the prior art has revealed that the lever ratio of the brake pedal can be changed to improve the driver's pedaling. The technology of the brake force, as disclosed in the U.S. Patent No. 7,219,576, the brake pedal is pivotally fixed, and when the pedal is taken, the relative position of the brake pedal and the brake pedal can be changed as the pedal stroke moves. Position, in order to change the leverage ratio; however, the disadvantage is that the components are more numerous and therefore need to be improved. SUMMARY OF THE INVENTION The object of the present invention is to provide a variable lever ratio pedal device as a mechanical backup brake device for a wire-controlled brake system, in particular to change the lever ratio of the brake pedal by moving the pivot position. When the online controlled brake system fails, the lever ratio can be changed to improve the braking force generated by the driver to step on the pedal, and the component can be simplified to improve the reliability of the use. 200920632 In order to achieve the above object, the variable lever ratio pedal device of the present invention comprises: a lever for a vehicle, a pedal at the bottom end, and a pivot at the top end; a push rod pivoted between the pivot and the pedal On the lever, one end extends to the output end of a brake car; and a driver is disposed above the pivot to drive the vertical displacement of the pivot to change the leverage ratio between the push rod and the pedal relative to the pivot. According to this, when the vehicle's wire-controlled brake system fails, the pivot position of the pedal can be adjusted, thereby changing the lever ratio and improving the braking force, thereby improving the reliability of the wire-controlled braking system to reduce the occurrence of traffic accidents. In addition, the present invention also includes: the pivot side has a vertical sliding rail, and the stern shaft is slidably disposed in the vertical sliding rail. A bottom portion of the pivot shaft is formed to be sleeved with the top end of the lever to guide the pivot shaft to be disposed at the top end of the damage rod. The output end is a brake hydraulic circuit or a mechanical device; the drive is a solenoid valve or other equivalent component having an electric drive capability. In addition, the driver may also be disposed on the proximal side of the pivot, and a link is connected between the pivot shaft and a horizontal slide rail above the pivot shaft, and the pivotal end of the driver and the connecting rod is slidably disposed in the lateral direction. In the sliding, and the drive is vertically displaced by the connecting rod driving pivot; or a toggle unit is provided between the pivot and the top end of the lever, a pivoting lever pivoted on the pivot, and a pivoting The hem of the top end of the lever has a splicing joint between the upper and lower sway rods, and the vertical displacement of the pivot is driven by the driver driving the upper swing lever, the pivoting portion and the hem lever, and the 200920632 is fastened to the driver and the upper swing The driving force of the rod and the hem rod 4 driver is greater than that of the spring application. However, in order to be able to further detail the present invention, the specific cooperation diagram can be used as follows: [Embodiment] Figure 1 reveals The configuration of the first embodiment of the present invention shows that the variable lever ratio pedal device of the present invention comprises: a W-bike lever i, which is disposed on the vehicle body 39 (four) end has a pedal 3, and the top end slides a Pivot 2; 彳 dry bottom a push rod 4, the end is pivoted on the pivot 2 and the pedal 3 extend to the other end of the brake to the brake end of the vehicle, a brake wheel for the vehicle; and/or the output 6 can drive a driver 5, which is arranged above the pivot 2 and is driven to change the push rod 4 In a more specific implementation with respect to the pedals 3 relative to the pivot, the cuffs are held 7 and the pivot 2 is slidably disposed within the vertical slide 7 (eg, the solid: the door has a vertical sliding formation of the bottom of the pivot 2) - Rod illusion, ,,). Connected to guide the pivot 2 to slide on the top of the lever 1. The ten-end and the end-to-end sets of the output end 6 are the brake-type hydraulic brakes. The wire-operated brake system applied to the electronic liquid bearing system is described as driving: 5 series is - solenoid valve or other electric drive The above-mentioned component composition can be used to implement the present invention. In the case of the failure of the electronic liquid house brake system of the vehicle in 200920632, the vertical displacement of the pivot 2 can be driven via the driving crying valve (as shown in FIG. 2), ^^2 Positioning, and changing the ratio of the push rod 4 and the pedal 3 relative to the pivot 2: two pivot rods; and the driver can pedal the pedal 3 with a small force #, causing the frame shaft 2 of the downward movement of the 1 to swing The lever 1 drives the push rod 4 to drive the motor around the mountain (as shown in Fig. 3), which can generate the power with the electronic liquid brake system and the 6-car power to control the wheel brake brake wheel. ^The invention can change the reliability of the phase-up control brake system generated by the driver pedaling the pedal 3 with the square wire of the machine _ 2 position, and then improve the reliability of the phase-controlled brake system. And improve its reliability in use. ^生,亚其他'The pedal device of the present invention can provide additional braking force; in order to prove that the invention uses the driving force 2%% to drive the pivot 2 to change position, to pass: "magnetic valve" less 20% extra car Force | γ α 七 七, wheel brake to dynamic analysis i can be honest, by the under-touch operation When the electro-hydraulic brake system fails, the hydraulic pressure of the step can be determined by the equation :: p generated car , square _ (in the middle - cross-sectional area of the master cylinder of the car, corpse = plate lever ratio 'U plate lever mechanical efficiency.'' /p- step by Figure 4 shows that the lever ratio of the original pedal 3 can be expressed as an equation 2: 200920632
P C 方程式2P C Equation 2
F~A 藉由驅動器5 (電磁閥）改變樞軸2位置（配合圖2所 示），使樞軸2向下移動Y距離，此時煞車踏板2之槓桿比 冬可更改為方程式3 : r P ^(A + B-Y)2 +D2 p p (A-Y) 方程式3 其中，D = ^C2-(A + B)2 本發明希望於線控式煞車系統故障時，可經由出力端6 提供車輪制動器額外增加20%的煞車力量，可由方程式4 成立：F~A changes the position of the pivot 2 by the driver 5 (solenoid valve) (as shown in Fig. 2), so that the pivot 2 moves downward by the Y distance. At this time, the lever ratio of the brake pedal 2 can be changed to the equation 3: r P ^(A + BY)2 +D2 pp (AY) Equation 3 where D = ^C2-(A + B)2 The present invention is intended to provide additional wheel brakes via the output end 6 in the event of a fault in the brake system An increase of 20% of the braking force can be established by Equation 4:
4(A + B-Yf + C2-{A + Bf C =L2xj 方程式4 量測部分車種之煞車踏板尺寸（如表1所示），並將其 數據帶入(3)式中，可得知欲加大20%之煞車力量，該樞轴 需向下移動之距離，如表2所示。 A B C TOYOTA Premio 8.5 cm 23.5cm 33cm CHRYSLER Spirit 9 cm 27.5cm 39cm GM Saturn 8.5 cm 16cm 27 cm 表1 10 200920632 表2 r 樞軸所需位移量γ TOYOTA Premio __________1.79cm CHRYSLER Spirit _____ 1.83cm GM Saturn 1.86cm 义攸表2可知一般車種樞軸所需之位移量約2公分，目 販售之電磁閥的驅動行程約3公分，可滿足本 言:計二、°依f上述’本發明可在不改變原油壓系統之 設叶，在钤用踏板槓桿比之概念進行備用煞車裝置的 I的效庫、，丨ί、車系統故障時，能使踏板3槓桿比有放 力量 ㈣力❻車液壓管路之壓力，提供額外之煞車 械式煞車系^明所應用之線控式煞車系統亦可為電子機 請參閱圖5所示，揭 I:所示)，其餘構件叙成及實施;“ 示意圖，說明所述驅叙… I明第二款實施例的配置 轴2之間連結—連桿&亦可設於樞軸2近侧，而與樞 71 ,驅動器5a與連椁^且樞軸2上方設有一橫向滑軌 71内，且驅動器-5a、緩區接端52&滑設於橫向滑軌 圖6所示}，其餘構株“ 驅動枢轴2垂向位移（如 款實 請參閱圖7所示，揭Μ 示意圖，說明所述樞軸2d乐一执見轭例的配置 (ToggleMeCha_)，具，於拖轴 ：即早凡8 一樞設於檟桿1頂端的下擺桿δ2 =干81 ’以及 間具一樞接部83相連結， 、卜鉍#81及82之 "由驅動器5b驅動上擺桿81、 200920632 框接部δ3、下擺桿82而 其餘構件組成等同於—袖2堂向位私（如圖8所示）， 形下，框軸2位於垂向:7—款實施例；據此，在—般情 3 8 =失效時，驅動器5b ( 工式，車 部83、下擺桿82， U㈢推動上扳柃81、樞接 促使槓桿】繞著下移=ΓΤ移至垂向滑軌7之下死點， 上述第-款實施例。夕…2擺動，其餘實施方式等同於 卜為了避免肘節單元8因行車震動 性力量而有所偏移，故肘節單元8之上時因慣 下擺桿Μ的初始位置，係向驅動哭區接部83、 形成-初始角度“如圖7及圖9:-:方向偏移 3踩踏之力量，只會使財_ ，&軸2承党踏板 而不會向驅動哭5b出力方：：向驅動器5b方向偏移， 導出方程式5。 不夕卿圖9及圖10可推 弋=/sin么 少0 = 2(/-/cos〇 y+y〇= 2(/ - / c〇s φ) χ = 1ύηφ 方程式5 (式中/ =上、下擺桿長度；$ =雷 一 軸向下移動量）。 &而行程、夕=樞 以CHRYSLER Spint為例，其樞轴所 3-U3(cm)，其電磁閥（驅動器）作動行程私量 3 _。將不同之初始角度“入式(5)後，可求得？π/約為 12 200920632 Ο 上、下擺#i莩的關係，如表 初始 3 (cm) 3.5(cm) 4(cm) 4.5 (cm) =1° χ〇—0.05 尤〇二0.06 而二 0.07 χ〇=0·08 ^2.16 X =2·36 ^=2.55 χ =2.72 Φ〇=2° Χο^ΟΛΙ χ〇==〇Λ2 -^(9^0.14 χ〇=0.16 x^2.\6 χ =2.36 χ ^2.55 χ =2.72 Α = 3° 义〇二〇.16 ^~0.18 -^0=0.21 χ〇=0.24 χ ^2.16 x=237 ^=2.55 χ =2.73 -—---__. Φ〇=^° ^0^0.24 ^0=0.28 χ〇-031 ^:=2.16 x=2.37 ^=2.56 χ =2.73 表3 其中當桿長/ 移動行程>3 (cm) >4.5(cm)且初始角度么 ，與本發明之電嵫間1 4 < » «s 24° 時， 法配合， 則電磁閥 所示 .當線控式煞車系統正常時，根據實車驗證發現，財節 13 200920632 早7G 8在煞車情況中仍有可能產生向驅動器5b •干上下擺桿82之間設—彈簧84(如圖U所示）；； !=即早7G 8 ’且_器5b (電磁閥）之驅動力係大^ :的拉力，·據此，當線控式煞樣统失、: :推動肘節單元8,促卿2下移至垂向滑軌j;5b -占，以增加煞車踏板3的槓桿比。 之下死 經由圖12及圖13可推導出方程式6。 F = 2(mg㈣。—ma_Rx+〇J 方程式 6 其中，\吗-〇々么—〇.5w(iZ + gtan《） 憤性力(式：F=電磁閥推力財節機構重量；•教車0± ^性力’知B點固定支座之反力）。 …、車蚪 在圖13之肘節單元8上加入—彈箬+ 出方程式7。 泮尹、84弹力，可推導 X : 〇々“·5(™㈣+构。)方 (式中Λ，簧拉力）。 柱式7 再將（7)式代回（6)式中，可推導屮强竺私a 式8所示。 V出弓平！拉力Λ，如方程 ° 方程式8 假設（8)式中F為兩 寓最大值，如夺“:、♦，求付在四種么角度下彈簧拉力 ΊΧ Η所示。 14 200920632 ^車種 初始角度^\ ]~ TOYOTA Premio CHRYSLER Spirit GM Saturn Φο = 1〇 Λ 二246.2 Λ = 175.2 Λ，3 Φ〇 =2° ------- Λ =129.4 Λ =58.4 ---— Λ =76.2 Φ〇 =3° fs ^90.6 Λ =19.4 Λ =37.3 ^0=4° fs '70.9 '~~---- 1 Λ ~〇_ Λ =17.8 表4 拉力為零’表示可不必安裝定箬 ^中之彈菁84拉力代回⑻式，反推出電磁間推力大小， 如表5所示。 ^車種 初始角度^ Φο =1° 一· — j-------- TOYOTA Premio ~~——__ CHRYSLER Spirit GM Saturn F=4.7 F=3.8 F=5 5 Φ〇 =2° F=ll.l F=7.7 F=11 1 Φο =3° F=14.〇 F=11.6 丄 i. I . 1 F— λ f\ Φ〇=^° F=18.7 J F=15.5 丄 JL 0.0 F=22.2 表5 上販心==::=即可推_，市面 性;為認本發明在實際應用上的可行 的寺效修飾或置換，均應包含於後述申^而完成 15 200920632 【圖式簡單說明 圖1 :為本發明第一款實施例之配置示意圖。 圖2 .為圖1之—實施狀態圖。 圖3 :為圖1之另一實施狀態圖。 圖4:為圖1之配置位置幾何圖。 圖5 ·為本發明第二款實施例之配置示意圖。 圖6 :為圖5之實施狀態圖。 r 圖7:為本發明第三款實施例之—配置示意圖。 圖8 :為圖7之實施狀態圖。 =為圖7驅動器未動作時肘節單元之位置圖。 圖11 .為圖7驅動器動作時肘節單元之位置圖。 二.為本發明第三款實 圖…為本發明財節單:配置〜圖 圖13:為本發明包含彈菁 ^圖。 主要元件符號說明】 的自由體圖 1 2 21 3 4 5、5a、5b 5la 52a .......槓桿 樞軸 -------桿部 -------踏板 ......推桿 ......驅動器 ......連桿 枢接蠕 16 200920632 6 - ------- 出力端 7、71 - -------骨軌 8 - ------- 肘$單天 81 - -------上擺桿 82 - -------下擺桿 83 - -------樞接部 84 - -------彈簧 9 - -------車體 ί 174(A + B-Yf + C2-{A + Bf C = L2xj Equation 4 Measure the brake pedal size of some models (as shown in Table 1), and bring the data into (3), you can know To increase the braking force by 20%, the distance the pivot needs to move downwards, as shown in Table 2. ABC TOYOTA Premio 8.5 cm 23.5cm 33cm CHRYSLER Spirit 9 cm 27.5cm 39cm GM Saturn 8.5 cm 16cm 27 cm Table 1 10 200920632 Table 2 r Pivotal required displacement γ TOYOTA Premio __________1.79cm CHRYSLER Spirit _____ 1.83cm GM Saturn 1.86cm 攸 攸 Table 2 shows that the displacement of the general vehicle type pivot is about 2 cm, the solenoid valve sold The driving stroke is about 3 cm, which can satisfy the present statement: 计二, °依f The above-mentioned invention can change the setting of the crude oil pressure system, and the utility model of the spare brake device is used in the concept of pedal lever ratio. ,, 丨ί, when the vehicle system is faulty, the pedal 3 lever can be used to release the force (4) to force the hydraulic pressure of the vehicle, and provide an additional brake-type brake system. For the electronic machine, please refer to Figure 5, revealing I:), and the rest of the components are summarized. Implementation; "schematic diagram, explaining the description... I can see that the connection between the shafts 2 of the second embodiment - the link & can also be located on the near side of the pivot 2, and the pivot 71, the driver 5a and the connection ^ and a horizontal slide rail 71 is disposed above the pivot 2, and the driver-5a, the slow joint end 52& is slidably disposed on the lateral slide rail as shown in FIG. 6, and the rest of the structure "drives the pivot 2 to be vertically displaced (eg, Please refer to FIG. 7 for a schematic diagram illustrating the configuration of the yoke (ToggleMeCha_) of the pivot 2d, which is located on the top of the mast 1 The hem rod δ2 = dry 81 ' and the pivotal portion 83 are connected to each other, and the 铋 铋 #81 and 82 are driven by the driver 5b to drive the upper swing lever 81, the 200920632 frame joint portion δ3, and the lower swing rod 82, and the remaining members are composed of Equivalent to - sleeve 2 hall orientation (as shown in Figure 8), under the shape, the frame axis 2 is in the vertical direction: 7 - embodiment; accordingly, in the case of -3 8 = failure, the drive 5b , the car portion 83, the hem rod 82, U (three) pushes the upper rakper 81, the pivoting urging lever] moves downwards = ΓΤ to the bottom dead center of the vertical slide rail 7, the above-mentioned first embodiment In the evening, 2 swings, and the rest of the implementation is equivalent to the fact that in order to avoid the deflection of the toggle unit 8 due to the vibrational force of the vehicle, the initial position of the conventional lower swing lever is used to drive the crying area. The joint 83, forming - initial angle "as shown in Figure 7 and Figure 9: -: direction shift 3 stepping on the force, will only make the money _, & axis 2 bearing the party pedal and will not cry to the driver 5b:: It is shifted in the direction of the driver 5b, and Equation 5 is derived. Figure 9 and Figure 10 can push 弋=/sin or less 0 = 2(/-/cos〇y+y〇= 2(/ - / c〇s φ) χ = 1ύηφ Equation 5 (where / The length of the upper and lower sway rods; $ = the amount of movement under the axis of the mine.) And the stroke and the eve = the pivot of the CHRYSLER Spint, the pivot of the 3-U3 (cm), the solenoid valve (driver) actuation stroke Private quantity 3 _. Different initial angles can be obtained after entering equation (5), π/about 12 200920632 Ο relationship between upper and lower hem #i莩, as shown in the table initial 3 (cm) 3.5 (cm) 4 (cm) 4.5 (cm) =1° χ〇—0.05 尤〇二0.06 and two 0.07 χ〇=0·08 ^2.16 X =2·36 ^=2.55 χ =2.72 Φ〇=2° Χο^ΟΛΙ χ〇 ==〇Λ2 -^(9^0.14 χ〇=0.16 x^2.\6 χ =2.36 χ ^2.55 χ =2.72 Α = 3° 〇二〇.16 ^~0.18 -^0=0.21 χ〇= 0.24 χ ^2.16 x=237 ^=2.55 χ =2.73 -—---__. Φ〇=^° ^0^0.24 ^0=0.28 χ〇-031 ^:=2.16 x=2.37 ^=2.56 χ =2.73 Table 3, where the rod length/moving stroke > 3 (cm) > 4.5 (cm) and the initial angle, and the electric raft of the present invention 1 4 < » «s 24°, the method is matched, the solenoid valve Shown. When the wire-controlled brake system is normal, according to the actual vehicle verification, it is found that the financial section 13 200920632 early 7G 8 may still generate a spring 84 between the driver 5b and the dry oscillating weight 82 in the braking situation (as shown in FIG. );; !=Is early 7G 8 'and _ 5b (solenoid valve) driving force is large ^ : the tension, · According to this, when the line control type is lost, : : push the toggle unit 8, promote Qing 2 moves down to the vertical slide j; 5b - occupies to increase the lever ratio of the brake pedal 3. The death below can be derived from Equation 6 through Fig. 12 and Fig. 13. F = 2 (mg(4). -ma_Rx+〇J equation 6 Among them, \?-〇々?-〇.5w(iZ + gtan") Indignation (style: F = solenoid valve thrust mechanism weight; • teach car 0 ± ^ sexual force) know B point fixed bearing The reaction force) ..., the rut is added to the toggle unit 8 of Figure 13 - the magazine + the equation 7. 泮 、, 84 elastic, can be derived X: 〇々 "·5 (TM (four) + structure. ) square (style, spring pull). Column 7 and then return (7) to (6), which can be derived from the formula 8. V out of the bow! Pulling force, such as the equation ° Equation 8 Assume that (F) is the maximum value of the two values in the formula (8), such as the ":, ♦, paying for the spring tension ΊΧ 四种 under four angles. 14 200920632 ^ initial angle of the vehicle ^ \ ]~ TOYOTA Premio CHRYSLER Spirit GM Saturn Φο = 1〇Λ 2 246.2 Λ = 175.2 Λ, 3 Φ〇=2° ------- Λ =129.4 Λ =58.4 --- Λ 7 =76.2 Φ〇= 3° fs ^90.6 Λ =19.4 Λ =37.3 ^0=4° fs '70.9 '~~---- 1 Λ ~〇_ Λ =17.8 Table 4 Pull force is zero' means that it is not necessary to install the bullet in the 箬^ The Jingla 84 pulls back to the (8) type and reverses the thrust between the electromagnetics, as shown in Table 5. ^Automated initial angle ^ Φο =1° 一· — j-------- TOYOTA Premio ~~——__ CHRYSLER Spirit GM Saturn F=4.7 F=3.8 F=5 5 Φ〇=2° F=ll.l F=7.7 F=11 1 Φο =3° F=14.〇F=11.6 丄i. I . 1 F— λ f\ Φ〇=^° F=18.7 JF=15.5 丄JL 0.0 F=22.2 Table 5 Shangxinxin==::= can push _, marketability; a viable temple for recognizing the practical application of the invention The effect modification or replacement should be included in the following description and completed 15 200920632 [Simple diagram of the diagram Figure 1: This is the hair Figure 2 is a state diagram of the implementation of Figure 1. Figure 3 is a diagram showing another embodiment of Figure 1. Figure 4 is a geometrical diagram of the configuration of Figure 1. Figure 5 Fig. 6 is a schematic view showing the state of the embodiment of Fig. 5. Fig. 7 is a schematic view showing the configuration of the third embodiment of the present invention. Fig. 8 is a view showing the state of implementation of Fig. 7. = is the position diagram of the toggle unit when the drive is not in Figure 7. Figure 11 is the position diagram of the toggle unit when the drive of Figure 7 is operated. 2. The third embodiment of the present invention is the financial statement of the present invention: configuration ~ Figure 13: This is a diagram containing the elastic crystals of the present invention. The main component symbol description] Free body Figure 1 2 21 3 4 5, 5a, 5b 5la 52a ....... Lever pivot ----- - Rod ------- pedal...Pushing rod...Driver...Linking rod pivoting 16 200920632 6 - ------- Output End 7, 71 - ------- bone rail 8 - ------- elbow $ one day 81 - ------- upper swing rod 82 - ------- hem stick 83 - ------- pivot joint 84 - ------- spring 9 - ------- body ί 17