201231333 六、發明說明： 【發明所屬之技術領域】 本發明是關於軌道車輛用刹車來令，使與刹車碟片的 摩擦導致的熱能有效地分散，使刹車來令與刹車碟片的耐 久性共同提升。 【先前技術】 在軌道車輛或汽車及機車等的陸上運輸機器，伴隨著 車輛的高速化或大型化，作爲其制動裝置通常使用碟刹裝 置。 以下以一個例子針對軌道車輛用的碟刹裝置來說明。 碟刹裝置，將刹車卡鉗進行作動，將刹車來令按壓於 :安裝於車軸或車輪的刹車碟片的滑動面，而得到制動力 ，將車軸或車輪的旋轉予以制動，來控制車輛的速度。 此時，藉由摩擦熱讓刹車來令與刹車碟片的接觸面的 溫度上升，而該接觸面的溫度，藉由伴隨車輛的高速化所 造成的刹車負荷的增加而變高。 在習知類型的碟剎裝置，如第6圖所示’刹車來令1 ，將與刹車碟片2的滑動面2a接觸的摩擦構件la’藉由 鉚釘（省略圖示）或黏接劑等’安裝於背板1 b。 從刹車卡鉗對該剎車來令施加負荷的按壓力’在安裝 部的構造上’並不作用於刹車來令的全體’而是集中作用 於某特定的部分。例如油壓式卡鉗的情況’如第6圖所示 ，按壓荷重的中心位置3存在於按壓活塞的位置。槓桿式 -5- 201231333 卡鉗的情況也與油壓式卡鉗的情況同樣地，按壓荷重是對 於卡鉗的臂部與來令座連接的位置造成負荷。 如上述，習知的碟刹裝置，在構造上，來自刹車卡鉗 的按壓力僅作用於刹車來令的一部分。所以，在按壓力作 用的正下方，刹車來令與刹車碟片的接觸面壓力變高，而 產生局部性的溫度上升。 因此，爲了緩和上述局部性的溫度上升情形，而需要 等面壓來令。 例如在專利文獻1，如第7圖所示，揭示有一種刹車 來令，將爲了避開緊固孔2 1所配置的摩擦構件1 1，隔介 著彈性構件1 3而安裝於背板1 2。藉由作成這種構造，使 刹車來令與刹車碟片的接觸面壓力均等，能防止產生局部 性溫度上升的情形。 可是，在專利文獻1所揭示的技術，朝向摩擦構件的 背板的安裝是隔介著彈性構件，所以當按壓力作用而摩擦 構件變得高溫時，彈性構件降伏（yield )，則之後，就無 法有效發揮原本的等面壓功能。 在專利文獻2、3所揭示的技術，是藉由將分割爲複 數個的摩擦構件，隔介著球面座來安裝，均等地負荷來自 刹車卡鉗的按壓力，防止產生局部性的溫度上升。 可是，在該專利文獻2、3所揭示的技術的情況，當 藉由按壓力讓球面座的構成部分塑性變形時，會喪失等面 壓功能。 201231333 [先前技術文獻] [專利文獻] 專利文獻1:日本特表2008-151188號公報 專利文獻2:日本特表平ίο-50 72 50號公報 專利文獻3 :日本特開2008-223852號公報 【發明內容】 [發明欲解決的課題] 本發明要解決的問題點，是在使刹車來令與刹車碟片 的接觸面壓力均等化’防止局部性的溫度上升的先前技術 的情況，沒有考慮到將發揮等面壓功能的構成部分進行保 護。 [用以解決課題的手段] 本發明的軌道車輛用刹車來令， 爲了保護用來發揮等面壓功能的彈性構件， 在刹車碟片的滑動面’藉由刹車卡鉗所按壓的軌道車 輛用刹車來令，其主要特徵爲： ’ 具備有： 按壓於刹車碟片的上述滑動面的摩擦構件、 以及安裝於上述剎車卡鉗’用來支承上述摩擦構 件的背板； 上述摩擦構件，在上述刹車碟片的半徑方向及周 方向’分割配置有2個以上’並且在各個摩擦構件與上述 201231333 背板之間中介有彈性構件，且將各個摩擦構件之與上述背 板相對向的面的較彈性構件更外緣側，形成爲凸彎曲狀， 當輕按壓時，藉由從背板經由彈性構件將按壓力 傳達到摩擦構件，來達成等面壓，當重按壓時，背板與凸 彎曲狀部接觸，而以凸彎曲狀部儘可能維持等面壓，且直 接將按壓力傳達到摩擦構件。 本發明的軌道車輛用剎車來令，藉由將摩擦構件之與 背板相對向的面形成爲凸彎曲狀，當重按壓時，背板與凸 彎曲狀部接觸，而以凸彎曲狀部儘可能維持等面壓，且直 接將按壓力傳達到摩擦構件。 於是，發揮等面壓的彈性構件，能夠防止重按壓力與 高溫共同導致的降伏，而能保護彈性構件。 [發明效果] 在本發明，藉由將摩擦構件之與背板相對向的面形成 爲凸彎曲狀，當重按壓時，背板與凸彎曲狀部接觸，而直 接將按壓力傳達到摩擦構件，所以能夠防止：中介在摩擦 構件與背板之間發揮等面壓的彈性構件的變形、惡化。 由於將摩擦構件之與背板相對向的面的較彈性構件更 外緣側，形成爲凸彎曲狀，所以當重按壓時，也能以該凸 彎曲狀部廣闊地分散荷重，而儘可能地維持等面壓。 【實施方式】 在本發明，是藉由將摩擦構件之與背板相對向的面形 201231333 成爲凸彎曲狀，當重按壓時’位於彈性構件外側的凸彎曲 狀部與背板接觸，將按壓力直接傳達到摩擦構件’來達成 對於中介在摩擦構件與背板之間的彈性構件的保護與等面 壓維持。 [實施例] 以下針對從本發明的發想到解決課題的過程、及實施 本發明的最佳型態來說明。 發明者等考慮到：當重按壓時，摩擦構件變得高溫， 而中介在摩擦構件與背板之間的彈性構件降伏，所以爲了 讓彈性構件長時間維持等面壓功能，當重按壓時，限制彈 性構件的使用來防止其極度變形的方式是有效的。 並且了解到當重按壓時，即使不使用彈性構件的功能 ，藉由摩擦構件本身的彈性及來令裝置全體的彈性，也能 達成足夠的等面壓。 本發明的軌道車輛用刹車來令，是根據以上的想法而 硏究的結果所成立的。 也就是說，本發明的軌道車輛用刹車來令，例如，藉 由刹車卡鉗被按壓在··安裝於車軸的碟片體、或以螺栓緊 固於車輪的刹車碟片的滑動面，所以採用以下的構造。 在第1圖，1 1是被按壓在刹車碟片的上述滑動面的摩 擦構件，藉由安裝於上述剎車卡鉗的背板1 2，例如隔介著 盤簧13被彈性支承。該盤簧13的彈簧係數，是當常用最 大制動力時，撓曲成摩擦構件11的後述的球面部11a與 -9- 201231333 背板1 2的間隙程度。 該摩擦構件1 1，例如如第2圖所示，在上述刹車碟片 的半徑方向分割爲兩個。在其周方向外周側有6個，在周 方向內周側有4個，總共分割爲1 0個，配置成與背板i 2 的周方向中央線1 2b呈線對稱。 在本發明’將上述各個摩擦構件11之與上述背板12 相對向的面形成爲例如球面狀，並且使其中心部朝向背板 12突出’且在其中心部周圍設置有：用來收容上述盤簧 13的凹部11c。第1圖中的11a是表示形成於上述球面狀 的球面部，lib是表示朝向背板12突出的突起。 另一方面，在與摩擦構件11的上述突起llb相對向 的背板12’以在上述突起lib的外周側及突出高度方向具 有預定的間隙di的狀態，設置有：將上述突起llb嵌入 的凹部12a。 上述預定的間隙dl’只要大於上述摩擦構件η的球 面部1 1 a與背板1 2的間隙d2即可。 藉由作成上述構造1當摩擦構件11朝平行於背板12 的水平方向移動時，藉由讓突起lib抵接於凹部丨2a，抑 制上述移動，朝背板12傳達力量。另—方面，當摩擦構 件11朝接近於背板12的方向移動時，在上述摩擦構件η 的球面部11 a抵接於背板1 2之前，盤簧1 3收縮，抵接後 則沒有進一步的荷重作用在盤簧1 3。 在第1圖的例子，按壓板14與設置在摩擦構件】】的 凸緣部1 1 d卡合’藉由將按壓板1 4與背板1 2貫穿的鉚釘 -10- 201231333 1 5，將按壓板1 4朝背板1 2側拉近，成爲稍微按壓盤簧i 3 的狀態，將上述摩擦構件1 1安裝於背板1 2。 在上述構造的本發明的軌道車輛用刹車來令，當頻繁 使用的輕按壓時，藉由從背板12經由盤簧13將按壓力傳 達到摩擦構件11，來達成等面壓。 另一方面，當較少使用的重按壓時，在將盤簧13按 壓預定尺寸之後，背板12與球面部Ua接觸，以球面部 11a儘可能維持等面壓，且直接將按壓力傳達到摩擦構件 11。於是，即使藉由重按壓而成爲高溫而高按壓力的環境 ，盤簧1 3也不會永久變形，能永遠保持其功能。由於球 面部1 1 a設置在較盤簧1 3更外緣側（外周側），所以與 將球面部11a設置在較盤簧13更內側（中央側）的情況 相比，荷重廣闊地分散到外緣側，更能成爲等面壓。 第3圖是顯示：在第1圖所示的本發明的刹車來令， 以讓摩擦構件（燒結合金製，外徑60mm，厚度15mm)未 與背板（鋼製，厚度4.5mm )接觸的程度的按壓力（ 5〜10kN )，進行刹車實驗時的各摩擦構件的溫度。 另一方面，第4圖是顯示以讓摩擦構件與背板接觸的 按壓力（12〜22kN )，進行刹車實驗時的各摩擦構件的溫 度。 在第2圖顯示了第3圖、第4圖的No.1~5是哪個摩 擦構件。 在任何情況各摩擦構件的溫度的變動都很少，而可以 了解呈現出本發明的等面壓的效果。 -11 - 201231333 在第3圖及第4圖使用的刹車碟片，是锻造鋼製，內 徑爲425mm，外徑爲715mm’與刹車來令接觸的滑動面的 內徑爲428mm，外徑爲702mm。 本發明並不限於上述例子，只要在各請求項記載的技 術思想的範圍，變更適當實施方式也可以。 例如，摩擦構件1 1的朝背板1 2的安裝，並不限於第 1圖所示的構造，如第5圖所示，在摩擦構件1 1的中心部 、以及在與該中心部相對的背板1 2處設置的貫穿孔，使 鉚釘15通過所構成也可以。 中介於摩擦構件1 1與背板1 2之間的彈性構件，將盤 簧13置換而使用線圈彈簧也可以。 在摩擦構件11的與背板12相對向的面形成的形狀， 只要儘可能地維持等面壓，且將按壓力直接傳達到摩擦構 件11的話，只要是凸彎曲狀，並不限於球面狀。 [產業上的可利用性] 上述構造的本發明，並不限於軌道車輛用的刹車碟片 ，也能適用於汽車或機車等的刹車碟片。 【圖式簡單說明】 第1圖（a)是顯示本發明的刹車來令的第1例子的 主要部分的剖面圖，（b)是（a)圖的A部放大圖。 第2圖是顯示本發明的刹車來令的第1例子的俯視圖 -12- 201231333 第3圖是輕按壓時的本發明的各摩擦構件的溫度的顯 示圖。 第4圖是重按壓時的本發明的各摩擦構件的溫度的顯 示圖。 第5圖是顯示本發明的刹車來令的第2例子的主要部 分的剖面圖。 第6圖是構成習知型的軌道車輛用碟刹裝置的刹車來 令及刹車碟片的顯不圖，（a )是從摩擦構件側觀察刹車 來令的俯視圖，（b)是（a)圖的A-B剖面圖。 第7圖是構成習知型的軌道車輛用碟刹裝置的刹車來 令的顯示圖，（a )是從摩擦構件側觀察刹車來令的俯視 圖，（b)是（a)圖的A-B剖面圖。 【主要元件符號說明】 1 1 :摩擦構件 1 1 a :球面部 1 1 b :突起 1 1 d :凸緣部 1 2 :背板 12a =凹部 13 :盤簧 1 4 :按壓板 1 5 :鉚釘 2 1 :緊固孔 -13-201231333 VI. Description of the Invention: [Technical Field] The present invention relates to a brake for a rail vehicle, which effectively disperses heat energy caused by friction with a brake disc, and causes the brake to be compatible with the durability of the brake disc Upgrade. [Prior Art] In a land transportation machine such as a rail vehicle or an automobile or a locomotive, a disc brake device is generally used as a brake device in accordance with an increase in speed or an increase in size of the vehicle. Hereinafter, an example will be described with respect to a disc brake device for a rail vehicle. The disc brake device operates the brake caliper to press the brake to the sliding surface of the brake disc attached to the axle or the wheel to obtain a braking force, and brake the rotation of the axle or the wheel to control the speed of the vehicle. At this time, the temperature of the contact surface with the brake disc is increased by the friction heat, and the temperature of the contact surface is increased by an increase in the braking load due to the increase in speed of the vehicle. In the conventional disc brake device, as shown in Fig. 6, the brake device 1 is a friction member la' that is in contact with the sliding surface 2a of the brake disc 2 by a rivet (not shown) or an adhesive. 'Installed on the back panel 1 b. From the brake caliper, the pressing force of the brake applied to the brakes does not act on the entire structure of the brakes, but concentrates on a specific portion. For example, in the case of a hydraulic caliper, as shown in Fig. 6, the center position 3 of the pressing load exists at the position where the piston is pressed. Lever type -5- 201231333 In the case of a caliper, as in the case of a hydraulic caliper, the pressing load is a load on the position where the arm of the caliper is connected to the seat. As described above, the conventional disc brake device is constructed such that the pressing force from the brake caliper acts only on a part of the brake. Therefore, immediately below the pressing force, the brakes cause the pressure on the contact surface with the brake disc to become high, resulting in a local temperature rise. Therefore, in order to alleviate the above-mentioned local temperature rise, it is necessary to make an equal surface pressure. For example, in Patent Document 1, as shown in Fig. 7, there is disclosed a brake for attaching the friction member 1 1 disposed to avoid the fastening hole 21 to the back plate 1 via the elastic member 13 2. By constructing such a structure, the brakes are equalized in pressure on the contact surface with the brake disc, and local temperature rise can be prevented. However, in the technique disclosed in Patent Document 1, the attachment to the backing plate of the friction member is interposed between the elastic members, so that when the friction member becomes high temperature by the pressing force, the elastic member is yielded, and then, The original equal face pressure function cannot be effectively utilized. The techniques disclosed in Patent Documents 2 and 3 are carried out by interposing a plurality of friction members, which are interposed between the spherical seats, and uniformly load the pressing force from the brake calipers to prevent local temperature rise. However, in the case of the technique disclosed in Patent Documents 2 and 3, when the constituent portion of the spherical seat is plastically deformed by the pressing force, the iso-pressure function is lost. [Patent Document 1] Japanese Patent Application Publication No. 2008-151188 (Patent Document 1) Japanese Patent Publication No. 2008-151188 (Patent Document 2) Japanese Patent Application No. JP-A No. 2008-223852 Disclosure of the Invention [Problems to be Solved by the Invention] The problem to be solved by the present invention is that the brake is used to equalize the pressure on the contact surface of the brake disc to prevent the local temperature from rising, and the case is not considered. The components that perform the isosurface pressing function are protected. [Means for Solving the Problem] The brake for a rail vehicle according to the present invention is a brake for a rail vehicle that is pressed by a brake caliper on a sliding surface of the brake disc in order to protect an elastic member that functions as a surface pressure function. The main features are: 'provided with: a friction member pressed against the sliding surface of the brake disc, and a back plate attached to the brake caliper for supporting the friction member; the friction member in the brake disc In the radial direction and the circumferential direction of the sheet, two or more are arranged in a divided manner, and an elastic member is interposed between each of the friction members and the back sheet of the 201231333, and a relatively elastic member of a surface of each of the friction members facing the backing plate is provided. The outer edge side is formed in a convex curved shape, and when lightly pressed, the pressing force is transmitted from the back plate to the friction member via the elastic member to achieve equal surface pressure, and when pressed, the back plate and the convex curved portion Contact, while maintaining the iso-face pressure as much as possible in the convex curved portion, and directly transmitting the pressing force to the friction member. In the rail vehicle brake of the present invention, the surface of the friction member facing the back plate is formed into a convex curved shape, and when the heavy pressing is performed, the back plate is in contact with the convex curved portion, and the convex curved portion is exhausted. It is possible to maintain an equal face pressure and directly transmit the pressing force to the friction member. Therefore, the elastic member which exerts the surface pressure can prevent the fall of the heavy pressing pressure and the high temperature, and can protect the elastic member. [Effect of the Invention] In the present invention, the surface of the friction member facing the backing plate is formed into a convex curved shape, and when the heavy pressing is performed, the backing plate is in contact with the convex curved portion, and the pressing force is directly transmitted to the friction member. Therefore, it is possible to prevent deformation and deterioration of the elastic member that exerts a constant surface pressure between the friction member and the back plate. Since the elastic member of the surface of the friction member facing the back plate is formed on the outer edge side and is formed in a convex curved shape, when the heavy pressing is performed, the load can be widely distributed by the convex curved portion, and as much as possible. Maintain equal surface pressure. [Embodiment] In the present invention, the surface shape 201231333 of the friction member facing the back plate is convexly curved, and when the heavy pressing is performed, the convex curved portion located outside the elastic member is in contact with the back plate, and will be pressed. The pressure is directly transmitted to the friction member' to achieve protection and isosurface pressure maintenance for the elastic member interposed between the friction member and the backing plate. [Embodiment] Hereinafter, a process for solving the problems from the present invention and an optimum mode for carrying out the invention will be described. The inventors have considered that when the heavy pressing, the friction member becomes high temperature, and the elastic member interposed between the friction member and the back plate is lowered, so in order to maintain the elastic pressing member for a long time, when heavy pressing, The manner in which the use of the elastic member is restricted to prevent it from being extremely deformed is effective. Further, it is understood that when the weight is pressed, even if the function of the elastic member is not used, sufficient isosurface pressure can be achieved by the elasticity of the friction member itself and the elasticity of the entire device. The brake for a rail vehicle of the present invention is established based on the above findings. In other words, the rail vehicle brake of the present invention is used, for example, by a brake caliper that is pressed against a disc body attached to the axle or a sliding surface of a brake disc that is fastened to the wheel by a bolt. The following structure. In Fig. 1, reference numeral 1 is a friction member that is pressed against the sliding surface of the brake disc, and is elastically supported by, for example, a coil spring 13 by being attached to the back plate 12 of the brake caliper. The spring constant of the coil spring 13 is the degree of clearance of the spherical portion 11a and the -9-201231333 back plate 12 which will be described later of the friction member 11 when the maximum braking force is commonly used. The friction member 1 1 is divided into two in the radial direction of the brake disc, as shown in Fig. 2, for example. There are six on the outer peripheral side in the circumferential direction and four on the inner peripheral side in the circumferential direction, and the total is divided into ten, and is arranged in line symmetry with the circumferential center line 1 2b of the backing plate i 2 . In the present invention, the surface of each of the friction members 11 facing the backing plate 12 is formed in, for example, a spherical shape, and its center portion is protruded toward the backing plate 12, and is disposed around the center portion thereof for housing the above. The recess 11c of the coil spring 13. 11a in Fig. 1 denotes a spherical surface formed on the spherical surface, and lib denotes a projection that protrudes toward the backing plate 12. On the other hand, in the backing plate 12' facing the above-mentioned projections 11b of the friction member 11, a predetermined gap d is provided in the outer peripheral side and the protruding height direction of the projection lib, and a recess in which the projection 11b is fitted is provided. 12a. The predetermined gap d1' may be larger than the gap d2 between the spherical portion 1 1 a of the friction member η and the back plate 1 2 . By the above configuration 1, when the friction member 11 is moved in the horizontal direction parallel to the backing plate 12, the movement is suppressed by the projection lib abutting against the concave portion 2a, and the force is transmitted to the backing plate 12. On the other hand, when the friction member 11 moves in the direction close to the backing plate 12, the coil spring 13 contracts before the spherical portion 11a of the friction member η abuts against the backing plate 12, and there is no further after the abutment. The load is applied to the coil spring 1 3 . In the example of Fig. 1, the pressing plate 14 is engaged with the flange portion 1 1 d provided on the friction member, and the rivet -10- 201231333 1 5 that penetrates the pressing plate 14 and the back plate 1 2 will The pressing plate 14 is pulled toward the side of the backing plate 12 to be slightly pressed against the coil spring i 3 , and the friction member 11 is attached to the backing plate 1 2 . In the rail vehicle brake of the present invention constructed as described above, when the light press is frequently used, the pressing force is transmitted from the backing plate 12 to the friction member 11 via the coil spring 13, thereby achieving the equal surface pressure. On the other hand, when the heavy press is used less, after the coil spring 13 is pressed by a predetermined size, the back plate 12 is in contact with the spherical portion Ua, the equal pressure is maintained as much as possible by the spherical portion 11a, and the pressing force is directly transmitted to Friction member 11. Therefore, even in a high-pressure and high-pressure environment by heavy pressing, the coil spring 13 is not permanently deformed, and its function can be maintained forever. Since the spherical portion 11 1 a is provided on the outer edge side (outer peripheral side) of the coil spring 13 , the load is widely dispersed as compared with the case where the spherical portion 11 a is provided on the inner side (center side) of the coil spring 13 . On the outer edge side, it can become equal surface pressure. Fig. 3 is a view showing the brake of the present invention shown in Fig. 1 so that the friction member (made of sintered alloy, outer diameter 60 mm, thickness 15 mm) is not in contact with the back plate (steel, thickness 4.5 mm). The degree of pressing force (5 to 10 kN), the temperature of each friction member during the braking test. On the other hand, Fig. 4 is a view showing the temperature of each of the friction members when the braking test is performed at a pressing force (12 to 22 kN) in which the friction member is brought into contact with the backing plate. Fig. 2 shows which of the friction members No. 1 to 5 in Fig. 3 and Fig. 4 are. In any case, the variation of the temperature of each of the friction members is small, and the effect of exhibiting the isosurface pressure of the present invention can be understood. -11 - 201231333 The brake disc used in Figures 3 and 4 is made of forged steel with an inner diameter of 425 mm and an outer diameter of 715 mm. The inner surface of the sliding surface that comes into contact with the brake is 428 mm and the outer diameter is OD. 702mm. The present invention is not limited to the above examples, and any appropriate embodiment may be modified as long as it is within the scope of the technical idea described in each of the claims. For example, the attachment of the friction member 11 to the backing plate 12 is not limited to the configuration shown in Fig. 1, as shown in Fig. 5, at the center portion of the friction member 11 and at the center portion The through hole provided in the back plate 12 may be configured such that the rivet 15 passes therethrough. The elastic member interposed between the friction member 11 and the backing plate 1 may be replaced by a coil spring 13 and a coil spring may be used. The shape formed on the surface of the friction member 11 facing the backing plate 12 is not limited to a spherical shape as long as it is a convex curved shape as long as the surface pressure is maintained as much as possible and the pressing force is directly transmitted to the friction member 11. [Industrial Applicability] The present invention having the above-described structure is not limited to the brake disc for a rail vehicle, and can be applied to a brake disc such as an automobile or a motorcycle. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1(a) is a cross-sectional view showing a main portion of a first example of a brake according to the present invention, and Fig. 1(b) is an enlarged view of a portion A of the figure (a). Fig. 2 is a plan view showing a first example of the brake of the present invention. -12 - 201231333 Fig. 3 is a view showing the temperature of each of the friction members of the present invention at the time of light pressing. Fig. 4 is a view showing the temperature of each of the friction members of the present invention at the time of heavy pressing. Fig. 5 is a cross-sectional view showing a main part of a second example of the brake of the present invention. Fig. 6 is a view showing the brakes of the conventional disc brake device for a rail vehicle and the brake disc, and (a) is a plan view of the brake from the side of the friction member, and (b) is (a) A cross-sectional view of the AB. Fig. 7 is a view showing a brake of a brake device for a rail vehicle of a conventional type, wherein (a) is a plan view of the brake from the side of the friction member, and (b) is a sectional view taken along line AB of (a). . [Description of main component symbols] 1 1 : Friction member 1 1 a : spherical portion 1 1 b : projection 1 1 d : flange portion 1 2 : back plate 12a = recess 13 : coil spring 1 4 : pressing plate 1 5 : rivet 2 1 : fastening hole-13-